JP6452281B2 - Shaft member support structure - Google Patents

Shaft member support structure Download PDF

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Publication number
JP6452281B2
JP6452281B2 JP2013209641A JP2013209641A JP6452281B2 JP 6452281 B2 JP6452281 B2 JP 6452281B2 JP 2013209641 A JP2013209641 A JP 2013209641A JP 2013209641 A JP2013209641 A JP 2013209641A JP 6452281 B2 JP6452281 B2 JP 6452281B2
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retaining ring
bearing
collar
peripheral portion
axial
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JP2015075125A (en
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芳賀　卓
卓 芳賀
為永　淳
淳 為永
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Sumitomo Heavy Industries Ltd
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Sumitomo Heavy Industries Ltd
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Priority to JP2013209641A priority Critical patent/JP6452281B2/en
Priority to KR1020140087569A priority patent/KR101582935B1/en
Priority to CN201410330962.3A priority patent/CN104514797B/en
Publication of JP2015075125A publication Critical patent/JP2015075125A/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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/22—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or type of main drive shafting, e.g. cardan shaft
    • B60K17/24—Arrangements of mountings for shafting
    • 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
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/029—Gearboxes; Mounting gearing therein characterised by means for sealing the gearboxes, e.g. to improve airtightness
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0469—Bearings or seals
    • F16H57/0472—Seals
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • General Details Of Gearings (AREA)
  • Sealing Of Bearings (AREA)
  • Rolling Contact Bearings (AREA)
  • Sealing With Elastic Sealing Lips (AREA)

Description

本発明は、軸部材の支持構造に関する。   The present invention relates to a shaft member support structure.

特許文献１に、減速機の出力軸の支持に当たって、該出力軸に外嵌された軸受と、出力軸に設けられた止め輪溝に配置された止め輪と、を備えた支持構造が開示されている。止め輪は、軸受の内輪の軸方向移動を規制している。   Patent Document 1 discloses a support structure including a bearing that is externally fitted to the output shaft and a retaining ring that is disposed in a retaining ring groove provided on the output shaft when supporting the output shaft of the reduction gear. ing. The retaining ring restricts the axial movement of the inner ring of the bearing.

このような止め輪を用いて軸受の軸方向移動を規制する構造は、特に、出力軸にアキシャル荷重が掛かるような用途において、該出力軸をより確実に支持することができるというメリットがある。   The structure that restricts the axial movement of the bearing using such a retaining ring has an advantage that the output shaft can be more reliably supported particularly in an application in which an axial load is applied to the output shaft.

この支持構造では、出力軸上における止め輪の反軸受側に、オイルシールが配置され、軸受および止め輪の存在する空間を、減速機の外部に対して封止している。   In this support structure, an oil seal is disposed on the output shaft on the side opposite to the retaining ring, and the space where the bearing and retaining ring are present is sealed from the outside of the speed reducer.

中国実用新案ＣＮ２０２０４８１４３Ｕ号公報（図１）Chinese utility model CN202041433U (FIG. 1)

しかしながら、上記止め輪は、単に出力軸に設けられた止め輪溝に係止されたものであったため、軸部材に強いアキシャル荷重が掛かった場合には、まれに、止め輪が抜け落ちることがあるという問題があった。   However, since the retaining ring is simply locked in a retaining ring groove provided on the output shaft, the retaining ring may come off in rare cases when a strong axial load is applied to the shaft member. There was a problem.

本発明は、このような従来の問題を解消するためになされたものであって、軸部材をより確実に支持することのできる軸部材の支持構造を提供することをその課題としている。   The present invention has been made to solve such a conventional problem, and an object thereof is to provide a support structure for a shaft member that can support the shaft member more reliably.

本発明は、軸部材と、該軸部材に外嵌された軸受と、前記軸部材に設けられた止め輪溝に配置され、前記軸受の内輪の軸方向移動を規制する止め輪と、前記軸部材に外嵌され、前記止め輪が前記止め輪溝から外れるのを防止する抜け止め部材と、を有し、該抜け止め部材の外周にオイルシールが配置され、前記軸部材は、大径部と小径部とを有し、前記止め輪は、前記大径部に配置され、前記抜け止め部材は、前記小径部に嵌合される内周部と、内周部より径方向外側に位置する外周部と、径方向から見て前記内周部と前記外周部の間に設けられるセンター部と、を有し、前記外周部は、前記大径部と径方向に対向するように延在された延在部を有し、前記外周部の外周に前記オイルシールが配置され、前記延在部は、前記止め輪と径方向に対向し、前記オイルシールは、前記大径部と径方向から見て重なり、前記センター部の軸方向幅は、前記内周部の軸方向幅よりも大きく、かつ前記外周部の軸方向幅よりも小さく、前記センター部は、前記止め輪と軸方向に対向する構成とすることにより、上記課題を解決したものである。 The present invention includes a shaft member, a bearing externally fitted to the shaft member, a retaining ring that is disposed in a retaining ring groove provided in the shaft member and restricts axial movement of an inner ring of the bearing, and the shaft A retaining member that is externally fitted to the member and prevents the retaining ring from being removed from the retaining ring groove, and an oil seal is disposed on an outer periphery of the retaining member, and the shaft member has a large-diameter portion. The retaining ring is disposed in the large diameter portion, and the retaining member is positioned on the radially outer side of the inner peripheral portion and the inner peripheral portion that are fitted in the small diameter portion. An outer peripheral portion, and a center portion provided between the inner peripheral portion and the outer peripheral portion as viewed from the radial direction, and the outer peripheral portion extends so as to face the large diameter portion in the radial direction. The oil seal is disposed on an outer periphery of the outer peripheral portion, and the extended portion is in a radial direction with the retaining ring. The oil seal overlaps with the large diameter portion when viewed from the radial direction, and the axial width of the center portion is larger than the axial width of the inner peripheral portion and is larger than the axial width of the outer peripheral portion. The center portion is configured to face the retaining ring in the axial direction, thereby solving the above-described problem.

本発明では、止め輪が止め輪溝から外れるのを防止する抜け止め部材を軸部材に外嵌している。この構成により、止め輪が外れるのを防止し、軸部材をより確実に支持することができるようになる。   In the present invention, a retaining member for preventing the retaining ring from coming off the retaining ring groove is externally fitted to the shaft member. With this configuration, the retaining ring can be prevented from coming off, and the shaft member can be supported more reliably.

本発明によれば、軸部材をより確実に支持することのできる軸部材の支持構造を得ることができる。   ADVANTAGE OF THE INVENTION According to this invention, the support structure of the shaft member which can support a shaft member more reliably can be obtained.

本発明の実施形態の一例に係る軸部材の支持構造を示す断面図Sectional drawing which shows the support structure of the shaft member which concerns on an example of embodiment of this invention 図１の要部拡大断面図1 is an enlarged cross-sectional view of the main part of FIG.

以下、図面に基づいて本発明の実施形態の一例を詳細に説明する。   Hereinafter, an example of an embodiment of the present invention will be described in detail based on the drawings.

図１は、本発明の実施形態の一例に係る軸部材の支持構造を示す断面図、図２は、図１の要部拡大断面図である。   FIG. 1 is a cross-sectional view showing a shaft member support structure according to an example of an embodiment of the present invention, and FIG. 2 is an enlarged cross-sectional view of a main part of FIG.

この実施形態では、減速機（全体は図示略）１２の出力軸（軸部材）１４の支持に、本発明が適用されている。   In this embodiment, the present invention is applied to support of an output shaft (shaft member) 14 of a speed reducer (not shown) 12.

すなわち、この出力軸１４の支持構造は、支持されるべき軸部材である出力軸１４と、該出力軸１４に外嵌された第１、第２軸受１６、１８と、第１軸受１６の内輪１６Ｂの軸方向移動を規制する止め輪２０と、出力軸１４に外嵌され、止め輪２０が止め輪溝２２から外れるのを防止するカラー（抜け止め部材）２４と、を有している。止め輪２０は、出力軸１４に設けられた止め輪溝２２に配置されており、カラー２４の外周８０にオイルシール２６が配置されている。   That is, the output shaft 14 is supported by an output shaft 14 that is a shaft member to be supported, first and second bearings 16 and 18 that are externally fitted to the output shaft 14, and an inner ring of the first bearing 16. A retaining ring 20 that restricts the axial movement of 16B and a collar (a retaining member) 24 that is externally fitted to the output shaft 14 and prevents the retaining ring 20 from being removed from the retaining ring groove 22 are provided. The retaining ring 20 is disposed in a retaining ring groove 22 provided on the output shaft 14, and an oil seal 26 is disposed on the outer periphery 80 of the collar 24.

以下、より具体的な構造について、詳細に説明する。   Hereinafter, a more specific structure will be described in detail.

出力軸１４は、減速機１２の減速機構１２Ａによって減速された回転を取り出すキャリヤフランジ部３０、第２軸受１８が配置される第２軸受配置部３２、第１軸受１６が配置される第１軸受配置部３４、前記止め輪溝２２、前記カラー２４が配置されるカラー配置部３６、および相手機械（被駆動部材）３８が配置される連結部４０を、軸方向にこの順で備えている。   The output shaft 14 includes a carrier flange portion 30 for extracting rotation decelerated by the speed reduction mechanism 12A of the speed reducer 12, a second bearing arrangement portion 32 where the second bearing 18 is arranged, and a first bearing where the first bearing 16 is arranged. An arrangement portion 34, the retaining ring groove 22, a collar arrangement portion 36 in which the collar 24 is arranged, and a connecting portion 40 in which a counterpart machine (driven member) 38 is arranged in this order in the axial direction.

キャリヤフランジ部３０の外径は、ｄ３０、第２軸受配置部３２の外径は、ｄ３２、第１軸受配置部３４の外径は、ｄ３４、止め輪溝２２は、第１軸受配置部３４に配置されているため、その周辺の外径ｄ２２は、第１軸受配置部３４と同一（ｄ３４＝ｄ２２）、カラー配置部３６の外径は、ｄ３６、連結部４０の外径は、ｄ４０であり、この順に小さくなっている（ｄ３０＞ｄ３２＞ｄ３４＝ｄ２２＞ｄ３６＞ｄ４０）。   The outer diameter of the carrier flange portion 30 is d30, the outer diameter of the second bearing arrangement portion 32 is d32, the outer diameter of the first bearing arrangement portion 34 is d34, and the retaining ring groove 22 is in the first bearing arrangement portion 34. Since the outer diameter d22 of the periphery is the same as that of the first bearing arrangement portion 34 (d34 = d22), the outer diameter of the collar arrangement portion 36 is d36, and the outer diameter of the connecting portion 40 is d40. , Decreasing in this order (d30> d32> d34 = d22> d36> d40).

出力軸１４の外側には、空間Ｐ１を挟んで減速機１２のケーシング４４が対向している。前記第１、第２軸受１６、１８は、この空間Ｐ１に配置され、出力軸１４を該ケーシング４４によって支持している。   The casing 44 of the speed reducer 12 faces the outside of the output shaft 14 with the space P1 interposed therebetween. The first and second bearings 16 and 18 are disposed in the space P <b> 1, and the output shaft 14 is supported by the casing 44.

なお、出力軸１４上の符号５０は、第１軸受配置部３４を加工するときの工具の逃げ溝、符号５２は、第２軸受配置部３２を加工するときの工具の逃げ溝である。また、出力軸１４の連結部４０には、キー溝４０Ａおよびタップ孔４０Ｂ（図１）が形成されており、出力軸１４は、該キー溝４０Ａまたはタップ孔４０Ｂを介して相手機械３８と連結される構成とされている。   Reference numeral 50 on the output shaft 14 is a tool relief groove when machining the first bearing arrangement portion 34, and reference numeral 52 is a tool relief groove when machining the second bearing arrangement portion 32. Further, a key groove 40A and a tap hole 40B (FIG. 1) are formed in the connecting portion 40 of the output shaft 14, and the output shaft 14 is connected to the counterpart machine 38 through the key groove 40A or the tap hole 40B. It is supposed to be configured.

第１軸受１６は、テーパローラ軸受であり、転動体１６Ａとして、円錐ローラが組み込まれている。第２軸受１８は、テーパローラ軸受であり、転動体１８Ａとして円錐ローラが組み込まれている。   The first bearing 16 is a tapered roller bearing, and a conical roller is incorporated as the rolling element 16A. The second bearing 18 is a tapered roller bearing, and a conical roller is incorporated as the rolling element 18A.

具体的には、第１軸受１６は、その内輪１６Ｂが出力軸１４の第１軸受配置部３４に圧入されている。第１軸受１６の内輪１６Ｂは、スペーサ１７を介して止め輪２０によって、軸方向反減速機構側に移動するのが規制されている。第１軸受１６の外輪１６Ｃは、ケーシング４４のケース段差部５４に当接することによって、軸方向減速機構側に移動するのが規制されている。   Specifically, the inner ring 16 </ b> B of the first bearing 16 is press-fitted into the first bearing arrangement portion 34 of the output shaft 14. The inner ring 16 </ b> B of the first bearing 16 is restricted from moving toward the axial anti-deceleration mechanism by the retaining ring 20 via the spacer 17. The outer ring 16 </ b> C of the first bearing 16 is restricted from moving to the axial speed reduction mechanism side by contacting the case step 54 of the casing 44.

なお、スペーサ１７は、軸方向幅の広いメインスペーサ１７Ａと、軸方向幅の狭いサブスペーサ１７Ｂとで構成されている。サブスペーサ１７Ｂは、軸方向幅が僅かに異なる複数の部材が用意されており、第１、第２軸受１６、１８の与圧を調整するためのシムとして機能している。軸方向幅の広いメインスペーサ１７Ａと軸方向幅の狭いサブスペーサ１７Ｂを組み合わせて用い、かつメインスペーサ１７Ａを止め輪２０側に配置することにより、複数用意する部材コストを低減すると共に、組付け時にサブスペーサ１７Ｂが止め輪溝２２内に落ち込んでしまう不具合が発生するのを防止できる。   The spacer 17 includes a main spacer 17A having a wide axial width and a sub-spacer 17B having a narrow axial width. The sub-spacer 17B is provided with a plurality of members having slightly different axial widths, and functions as a shim for adjusting the pressurization of the first and second bearings 16 and 18. By using a combination of the main spacer 17A having a wide axial width and the sub-spacer 17B having a narrow axial width, and arranging the main spacer 17A on the retaining ring 20 side, the cost of a plurality of members can be reduced, and at the time of assembly. It is possible to prevent a problem that the sub-spacer 17B falls into the retaining ring groove 22.

一方、第２軸受１８は、その内輪１８Ｂが出力軸１４の第２軸受配置部３２に圧入されると共に、キャリヤフランジ部３０と第２軸受配置部３２との径差によって形成されている出力軸段差部５６によって、軸方向減速機構側に移動するのが規制されている。第２軸受１８の外輪１８Ｃは、ケーシング４４のケース段差部５８に当接することによって、軸方向反減速機構側に移動するのが規制されている。   On the other hand, the second bearing 18 has an inner ring 18B that is press-fitted into the second bearing arrangement portion 32 of the output shaft 14, and an output shaft that is formed by a diameter difference between the carrier flange portion 30 and the second bearing arrangement portion 32. The step portion 56 restricts the movement to the axial speed reduction mechanism side. The outer ring 18 </ b> C of the second bearing 18 is restricted from moving toward the axial anti-deceleration mechanism by contacting the case step 58 of the casing 44.

第１、第２軸受１６、１８は、このような構成を有して、背面合わせで出力軸１４に組み込まれており、該出力軸１４に掛かるラジアル荷重およびアキシャル荷重の双方を支持している。   The first and second bearings 16 and 18 have such a configuration and are incorporated in the output shaft 14 in back-to-back alignment, and support both the radial load and the axial load applied to the output shaft 14. .

第１軸受１６の軸方向移動を規制している止め輪２０は、出力軸１４に設けられた前記止め輪溝２２に配置され、第１軸受１６の内輪１６Ｂの軸方向反減速機構側への移動を規制している。この実施形態では、止め輪２０が止め輪溝２２から外れるのを防止するために、カラー（抜け止め部材）２４が、出力軸１４のカラー配置部３６に外嵌されている。カラー２４は、止め輪２０と軸方向に対向している。   A retaining ring 20 that restricts the axial movement of the first bearing 16 is disposed in the retaining ring groove 22 provided in the output shaft 14, and the inner ring 16 </ b> B of the first bearing 16 toward the axial anti-deceleration mechanism side. Restricts movement. In this embodiment, in order to prevent the retaining ring 20 from coming off from the retaining ring groove 22, a collar (a retaining member) 24 is externally fitted to the collar arrangement portion 36 of the output shaft 14. The collar 24 faces the retaining ring 20 in the axial direction.

具体的には、カラー２４は、全体がリング状に形成されている。カラー２４の出力軸１４の軸心Ｏ１を通る断面は、その最内周部６０が出力軸１４のカラー配置部３６の軸方向幅Ｌ３６と同一の軸方向幅を有している。ただし、異なる軸方向幅としてもよい。そして、当該断面の減速機構側が、面取り部６２を経て３段のステップ状に軸方向に突出している。すなわち、カラー２４の軸方向幅は、径方向内側の内周部６６では、Ｌ６６であり、径方向中央のセンター部６８では、Ｌ６６よりも大きなＬ６８であり、径方向外側の外周部７０では、Ｌ６８よりもさらに大きなＬ７０に形成されている。そして、このうちのセンター部６８の軸方向側面６８Ａが、止め輪２０の反減速機構側の側面２１と軸方向に対向している。   Specifically, the collar 24 is entirely formed in a ring shape. In the cross section passing through the axis O1 of the output shaft 14 of the collar 24, the innermost peripheral portion 60 has the same axial width as the axial width L36 of the collar arrangement portion 36 of the output shaft 14. However, different axial widths may be used. And the speed-reduction mechanism side of the said cross section protrudes in the axial direction in the shape of three steps through the chamfered portion 62. That is, the axial width of the collar 24 is L66 at the radially inner inner peripheral portion 66, L68 is larger than L66 at the radially central portion 68, and the radially outer peripheral portion 70 is It is formed in L70 which is larger than L68. Of these, the side surface 68A in the axial direction of the center portion 68 is opposed to the side surface 21 of the retaining ring 20 on the anti-deceleration mechanism side in the axial direction.

この構成により、カラー２４は、止め輪２０がスラスト力を受けたときに、そのセンター部６８が変形した止め輪２０に当接し、該止め輪２０に当該スラスト力に対する反力を付与可能である。   With this configuration, when the retaining ring 20 receives a thrust force, the collar 24 abuts the retaining ring 20 whose center portion 68 is deformed, and can apply a reaction force against the thrust force to the retaining ring 20. .

なお、この実施形態では、センター部６８の軸方向側面６８Ａと止め輪２０の反減速機構側の側面２１との間には、組付け時において極めて僅かな隙間が確保されている。つまり、カラー２４は、止め輪２０にスラスト力が掛かっていない状態では、該止め輪２０とは当接しておらず、止め輪２０にスラスト力が掛かることによって初めて当接するような軸方向位置で出力軸１４に外嵌（具体的には圧入）されている。これは、組付け時にカラー２４を（止め輪２０に圧力を与えることなく）、確実に出力軸段差部５５に当接するまで押し込めるようにすることを担保するためである。しかし、カラー２４は、初めから止め輪２０に当接するような態様で出力軸１４に外嵌されていてもよい。   In this embodiment, an extremely small gap is secured between the axial side surface 68A of the center portion 68 and the side surface 21 of the retaining ring 20 on the side opposite to the deceleration mechanism. That is, the collar 24 is not in contact with the retaining ring 20 in a state where no thrust force is applied to the retaining ring 20, and is in an axial position where the collar 24 abuts only when the thrusting force is applied to the retaining ring 20. The output shaft 14 is externally fitted (specifically press-fitted). This is to ensure that the collar 24 can be pushed in until it comes into contact with the output shaft step portion 55 (without applying pressure to the retaining ring 20) during assembly. However, the collar 24 may be externally fitted to the output shaft 14 so as to contact the retaining ring 20 from the beginning.

また、カラー２４は、止め輪２０と（軸方向だけでなく）径方向にも対向している。すなわち、カラー２４は、出力軸１４の小径部に相当するカラー配置部３６に嵌合されると共に、その外周部７０が、大径部に相当する第１軸受配置部３４と径方向に対向するように延在された「延在部」を構成している。より具体的には、このカラー２４の外周部７０は、止め輪２０の径方向外側にまで延在されており、該外周部７０の内周７１（の一部）が止め輪２０の外周２３（の一部）と対向している。   The collar 24 also faces the retaining ring 20 in the radial direction (not only in the axial direction). That is, the collar 24 is fitted to the collar arrangement portion 36 corresponding to the small diameter portion of the output shaft 14, and the outer peripheral portion 70 is opposed to the first bearing arrangement portion 34 corresponding to the large diameter portion in the radial direction. Thus, the “extending portion” is formed. More specifically, the outer peripheral portion 70 of the collar 24 extends to the outer side in the radial direction of the retaining ring 20, and an inner periphery 71 (a part thereof) of the outer peripheral portion 70 is the outer periphery 23 of the retaining ring 20. (Part of).

そして、本実施形態では、カラー２４の外周８０が、オイルシール２６の配置面とされている。既に説明したように、この実施形態におけるカラー２４は、特に外周部７０の軸方向幅が広いＬ７０に設定されている。外周部７０の軸方向幅Ｌ７０は、オイルシール２６の軸方向幅Ｌ２６よりも大きく（Ｌ７０＞Ｌ２６）、十分に余裕を持ってオイルシール２６の配置面とすることができている。   In the present embodiment, the outer periphery 80 of the collar 24 is an arrangement surface of the oil seal 26. As already described, the collar 24 in this embodiment is set to L70 where the axial width of the outer peripheral portion 70 is particularly wide. The axial width L70 of the outer peripheral portion 70 is larger than the axial width L26 of the oil seal 26 (L70> L26), and the oil seal 26 can be disposed with a sufficient margin.

なお、カラー２４の軸方向反減速機構側は、面取り部７４の径方向外側のほぼ全部が、出力軸１４と直角の側面７６とされている。この実施形態では、この側面７６に相手機械３８の一部が当接しており、カラー２４によって該相手機械３８から入力されてくるアキシャル荷重が受け止められるように構成されている。   Note that, on the side of the collar 24 on the side opposite to the speed reducing mechanism, almost all of the radially outer side of the chamfered portion 74 is a side surface 76 perpendicular to the output shaft 14. In this embodiment, a part of the counterpart machine 38 is in contact with the side surface 76, and the axial load input from the counterpart machine 38 is received by the collar 24.

本実施形態の第１軸受１６、止め輪２０、カラー２４、およびオイルシール２６近傍の構成を纏めるならば、出力軸１４は、大径部に相当する第１軸受配置部３４と小径部に相当するカラー配置部３６とを有し、止め輪２０は、（大径部に相当する）第１軸受配置部３４に配置され、カラー２４は、（小径部に相当する）カラー配置部３６に嵌合されると共に、第１軸受配置部３４と径方向に対向するように延在された（延在部としての）外周部７０を有し、かつ、オイルシール２６は、（大径部に相当する）第１軸受配置部３４と径方向から見て重なっている、という構成を有していることになる。   If the configuration in the vicinity of the first bearing 16, the retaining ring 20, the collar 24, and the oil seal 26 according to the present embodiment is summarized, the output shaft 14 corresponds to the first bearing arrangement portion 34 corresponding to the large diameter portion and the small diameter portion. The retaining ring 20 is disposed on the first bearing arrangement portion 34 (corresponding to the large diameter portion), and the collar 24 is fitted on the collar arrangement portion 36 (corresponding to the small diameter portion). And has an outer peripheral portion 70 (as an extended portion) extending so as to face the first bearing arrangement portion 34 in the radial direction, and the oil seal 26 corresponds to a large-diameter portion. Yes) the first bearing arrangement portion 34 and the first bearing arrangement portion 34 are overlapped when viewed from the radial direction.

次に、この出力軸の支持構造の作用を説明する。   Next, the operation of the output shaft support structure will be described.

本実施形態のように、第１軸受１６に対して該第１軸受１６の内輪１６Ｂの軸方向移動を規制する止め輪２０を配置すると、第１軸受１６の内輪１６Ｂに係るアキシャル荷重に対して、出力軸１４と第１軸受１６の内輪１６Ｂとの間の圧入によって発生し得る応力よりも大きな応力を確保することができる。しかしながら、［発明が解決しようとする課題］の欄で既に説明したように、例えば、止め輪２０を有しただけの構成では、該止め輪２０に大きなアキシャル荷重が掛かったような場合には、該止め輪２０が止め輪溝２２から抜け出てしまうことがあり得る。   When the retaining ring 20 that restricts the axial movement of the inner ring 16B of the first bearing 16 is arranged with respect to the first bearing 16 as in the present embodiment, the axial load related to the inner ring 16B of the first bearing 16 is reduced. A stress larger than the stress that can be generated by press-fitting between the output shaft 14 and the inner ring 16B of the first bearing 16 can be secured. However, as already described in the section [Problems to be Solved by the Invention], for example, in a configuration in which only the retaining ring 20 is provided, when a large axial load is applied to the retaining ring 20, The retaining ring 20 may come out of the retaining ring groove 22.

特に、本実施形態のように、背面合わせで配置している一対の軸受のうちの一方である第１軸受１６を止め輪２０によって、軸方向の移動を規制する場合、該止め輪２０は、（外輪１６Ｃではなく）内輪１６Ｂの軸方向の移動を規制することになる。そのため、止め輪２０は、ケーシング４４に内嵌するのではなく、軸部材である出力軸１４に外嵌する必要があるため、止め輪２０と止め輪溝２２との掛かり面積が小さく、止め輪２０の抜け落ちの問題がより生じ易いという事情がある。   In particular, when the axial movement of the first bearing 16, which is one of a pair of bearings arranged in back-to-back alignment, is restricted by the retaining ring 20 as in the present embodiment, the retaining ring 20 is The movement of the inner ring 16B (not the outer ring 16C) in the axial direction is restricted. For this reason, the retaining ring 20 does not fit inside the casing 44 but needs to be fitted around the output shaft 14 that is a shaft member. Therefore, the retaining area between the retaining ring 20 and the retaining ring groove 22 is small, and the retaining ring There is a situation that the problem of omission of 20 is more likely to occur.

本実施形態では、止め輪２０が止め輪溝２２から外れるのを防止するカラー（抜け止め部材）２４を出力軸１４に外嵌するようにしているため、止め輪２０が止め輪溝２２から抜け出てしまうのを確実に防止することができる。   In this embodiment, since the collar (prevention member) 24 that prevents the retaining ring 20 from coming off the retaining ring groove 22 is fitted on the output shaft 14, the retaining ring 20 comes out of the retaining ring groove 22. Can be surely prevented.

また、カラー２４を止め輪２０と軸方向に対向させ、止め輪２０にスラスト力が掛かったときに、カラー２４と当接するようにした場合、カラー２４の組み込みが行われることにより、仮に、止め輪２０が止め輪溝２２に完全に嵌り込んでいない場合には、カラー２４を出力軸段差部５５に当接する位置にまで押し込むことができない、という事態が発生する。したがって、実利的な効果として、これにより、止め輪２０の嵌め込みミスを見逃すことなく、必ず発見できるようになるという検証効果も得られるようになる。   In addition, when the collar 24 is opposed to the retaining ring 20 in the axial direction so that the collar 24 comes into contact with the retaining ring 20 when a thrust force is applied, the collar 24 is incorporated, so that the retaining ring 20 is temporarily stopped. When the ring 20 is not completely fitted in the retaining ring groove 22, a situation occurs in which the collar 24 cannot be pushed to a position where it contacts the output shaft stepped portion 55. Therefore, as a practical effect, a verification effect can be obtained in that it can always be discovered without missing a fitting error of the retaining ring 20.

ここで、このようにカラー２４を止め輪２０に隣接して配置するように構成すると、出力軸１４とケーシング４４との間を封止しているオイルシール２６は、もし、従来の構造を踏襲するならば、必然的にこのカラー２４のさらに軸方向反減速機構側に配置することになる。その結果、出力軸１４の連結部４０において外部荷重が掛かるポイント（荷重重心ポイント）Ｌｐから第１軸受１６の作用点までの軸方向長さＬｐ１６がそれだけ長くなり、特に、出力軸１４に相手機械３８側からラジアル荷重が掛かったときの第１軸受１６の負担が大きくなるという問題が発生する。同様に、出力軸１４の荷重重心ポイントＬｐから止め輪溝２２までの軸方向長さＬｐ２２もそれだけ長くなるため、止め輪溝２２の周辺において出力軸１４に発生する応力集中が大きくなるという問題も発生する。   Here, when the collar 24 is arranged adjacent to the retaining ring 20 in this way, the oil seal 26 that seals between the output shaft 14 and the casing 44 follows the conventional structure. If this is the case, the collar 24 is inevitably disposed further on the side of the axial anti-deceleration mechanism. As a result, the axial length Lp16 from the point (load center-of-gravity point) Lp at which the external load is applied to the connecting portion 40 of the output shaft 14 to the operating point of the first bearing 16 is increased by that much. There arises a problem that the load on the first bearing 16 becomes large when a radial load is applied from the 38th side. Similarly, since the axial length Lp22 from the load gravity center point Lp of the output shaft 14 to the retaining ring groove 22 is also increased accordingly, there is a problem that stress concentration generated on the output shaft 14 increases around the retaining ring groove 22. Occur.

しかし、本実施形態では、出力軸１４とケーシング４４との間を封止するオイルシール２６を、出力軸１４にではなく、カラー２４の外周８０に配置するようにしている。そのため、カラー２４を配置したにも拘わらず、第１軸受１６の作用点あるいは止め輪２０から荷重重心ポイントＬｐまでの軸方向長さＬｐ１６、Ｌｐ２２が増大するのを抑えた設計をすることができる（たとえ、ぎりぎりまで短く抑えない場合でも、軸方向において、スペース的により余裕のある設計が可能となる）。   However, in this embodiment, the oil seal 26 that seals between the output shaft 14 and the casing 44 is arranged not on the output shaft 14 but on the outer periphery 80 of the collar 24. Therefore, in spite of the arrangement of the collar 24, it is possible to design to suppress an increase in the axial length Lp16, Lp22 from the operating point of the first bearing 16 or the retaining ring 20 to the load gravity center point Lp. (Even if it is not kept as short as possible, it is possible to design with more space in the axial direction).

また、第１軸受１６からオイルシール２６の反減速機構側の面２７までの距離Ｌ（１６−２７）を短く抑えることができることから、ケーシング４４の外形が大きくなって、重量増大、コスト増大の要因となるのを回避する設計をすることもできる。   Further, since the distance L (16-27) from the first bearing 16 to the surface 27 of the oil seal 26 on the anti-deceleration mechanism side can be kept short, the outer shape of the casing 44 is increased, resulting in an increase in weight and cost. It can also be designed to avoid the factor.

本実施形態では、さらに、カラー２４は、止め輪２０と軸方向に対向し、該止め輪２０がスラスト力を受けたときに、（変形した）止め輪２０に当接し、該止め輪２０に当該スラスト力に対する反力を付与できるように構成してあるため、単に止め輪２０が抜け落ちるのを防止するだけでなく、止め輪２０による第１軸受１６の移動の規制効果をより高めることができる。   In the present embodiment, the collar 24 further faces the retaining ring 20 in the axial direction. When the retaining ring 20 receives a thrust force, the collar 24 contacts the (deformed) retaining ring 20 and Since the reaction force against the thrust force can be applied, it is possible not only to prevent the retaining ring 20 from falling off but also to further increase the effect of restricting the movement of the first bearing 16 by the retaining ring 20. .

また、カラー２４は、止め輪２０と（軸方向に対向しているだけでなく）径方向にも対向しているため、止め輪２０は、径方向に対しても動きが拘束されている。そのため、止め輪２０が止め輪溝２２から抜け出るのが、一層効果的に防止されている。さらには、カラー２４の軸方向反減速機構側の側面７６の軸方向位置が、反減速機構側へシフトする距離を抑えながら（場合によってはむしろ減速機構側にシフトさせながら）、オイルシール２６の配置面として、カラー２４の外周部７０の軸方向長さＬ７０（外周８０の軸方向長さ）を大きく確保することができている。   Further, since the collar 24 also faces the retaining ring 20 in the radial direction (not only facing the axial direction), the retaining ring 20 is also restrained from moving in the radial direction. Therefore, the retaining ring 20 is more effectively prevented from coming out of the retaining ring groove 22. Further, the axial position of the side surface 76 of the collar 24 on the side opposite to the speed reduction mechanism is restrained by the distance shifted to the side of the speed reduction mechanism (in some cases, rather than being shifted to the speed reduction mechanism), A large axial length L70 (the axial length of the outer periphery 80) of the outer peripheral portion 70 of the collar 24 can be secured as the arrangement surface.

要するならば、本実施形態では、出力軸１４は、（大径部に相当する）大径の第１軸受配置部３４と（小径部に相当する）小径のカラー配置部３６とを有し、止め輪２０は、大径の第１軸受配置部３４に配置され、カラー２４は、小径のカラー配置部３６に嵌合されている。そして、カラー２４は、第１軸受配置部３４と径方向に対向するように延在された（延在部としての）外周部７０を有し、かつ、（該外周部７０の外周８０上に配置された）オイルシール２６は、第１軸受配置部３４と径方向から見て重なっている。   In short, in this embodiment, the output shaft 14 includes a first bearing arrangement portion 34 having a large diameter (corresponding to a large diameter portion) and a collar arrangement portion 36 having a small diameter (corresponding to a small diameter portion), The retaining ring 20 is arranged on the first bearing arrangement portion 34 having a large diameter, and the collar 24 is fitted on a collar arrangement portion 36 having a small diameter. The collar 24 has an outer peripheral portion 70 (as an extending portion) that extends so as to face the first bearing arrangement portion 34 in the radial direction, and (on the outer periphery 80 of the outer peripheral portion 70). The arranged oil seal 26 overlaps the first bearing arrangement portion 34 as viewed from the radial direction.

そのため、カラー２４が追加で配置されているにも関わらず、オイルシール２６の配置面となるカラー２４の外周部７０（の外周８０）の軸方向幅Ｌ７０を十分大きく確保しつつ、第１軸受１６の作用点や止め輪溝２２から荷重重心ポイントＬｐまでの距離Ｌｐ１６、Ｌｐ２２を小さく維持することができ、第１軸受１６の荷重負担や、止め輪溝２２周辺の応力集中をより小さく抑制することができているものである。また、第１軸受１６からオイルシール２６の反減速機構側の面２７までの距離Ｌ（１６−２７）を短く抑えることができることから、ケーシング４４の外形が大きくなって、重量増大、コスト増大の要因となるのを回避する設計を可能としているものである。   Therefore, although the collar 24 is additionally arranged, the first bearing is provided with a sufficiently large axial width L70 of the outer peripheral portion 70 (the outer periphery 80) of the collar 24 serving as the arrangement surface of the oil seal 26. 16 and the distances Lp16 and Lp22 from the retaining ring groove 22 to the load center of gravity point Lp can be kept small, and the load on the first bearing 16 and the stress concentration around the retaining ring groove 22 can be further reduced. Is something that can be done. Further, since the distance L (16-27) from the first bearing 16 to the surface 27 of the oil seal 26 on the anti-deceleration mechanism side can be kept short, the outer shape of the casing 44 is increased, resulting in an increase in weight and cost. The design which avoids becoming a factor is enabled.

なお、上記実施形態においては、カラー２４に対し、止め輪２０の抜け防止機能のほかに、止め輪２０がスラスト力を受けたときに、該止め輪２０に当該スラスト力に対する反力を付与する機能をも持たせるようにしていた。しかし、本発明においては、カラー２４は、最低限、止め輪２０の抜け防止機能を有していれば足りる。つまり、カラー２４が止め輪２０に対し、スラスト力に対する反力を付与する機能は、必ずしも要求されない。   In the above embodiment, in addition to the function of preventing the retaining ring 20 from being pulled out, the collar 24 is applied with a reaction force against the thrust force when the retaining ring 20 receives a thrust force. I was trying to have a function. However, in the present invention, it is sufficient that the collar 24 has at least a function of preventing the retaining ring 20 from coming off. That is, the function that the collar 24 gives the reaction force against the thrust force to the retaining ring 20 is not necessarily required.

したがって、上記実施形態ベースで例示するならば、例えば、カラー（２４）が、止め輪２０と径方向に対向していることによって、止め輪２０の抜け防止を図ることができているならば、該カラー（２４）は、必ずしも止め輪２０と軸方向に対向している必要はなく、また、止め輪２０がスラスト力を受けた場合であっても、必ずしも止め輪２０と当接して該止め輪２０に当該スラスト力に対する反力を付与するような構成とされていなくてもよい。   Therefore, if illustrated on the basis of the above embodiment, for example, if the collar (24) is opposed to the retaining ring 20 in the radial direction to prevent the retaining ring 20 from coming off, The collar (24) does not necessarily have to face the retaining ring 20 in the axial direction, and even when the retaining ring 20 receives a thrust force, the collar (24) does not necessarily abut against the retaining ring 20. The wheel 20 may not be configured to apply a reaction force against the thrust force.

逆に言うならば、カラーは、要するに、何らかの構成で止め輪が止め輪溝から外れるのを防止する形状あるいは機能を有していれば足り、必ずしも止め輪と軸方向や径方向に対向している必要はない。   To put it the other way around, the collar need only have a shape or function that prevents the retaining ring from coming off the retaining ring groove in any configuration, and is not necessarily opposed to the retaining ring in the axial or radial direction. There is no need to be.

また、上記実施形態においては、減速機の出力軸に本発明の軸部材の支持構造を適用した例を説明したが、これに限定されず、本発明は、例えば、減速機の出力軸以外の軸に適用してもよいし、さらには、減速機以外の装置の軸部材に適用してもよい。   Moreover, in the said embodiment, although the example which applied the support structure of the shaft member of this invention to the output shaft of the reduction gear was demonstrated, it is not limited to this, For example, this invention is other than the output shaft of a reduction gear. The present invention may be applied to the shaft, or may be applied to a shaft member of a device other than the speed reducer.

１２…減速機
１４…出力軸（軸部材）
１６…第１軸受
１８…第２軸受
２０…止め輪
２２…止め輪溝
２４…カラー（抜け止め部材）
２６…オイルシール
３２…第２軸受配置部
３４…第１軸受配置部（大径部）
３６…カラー配置部（小径部）
３８…相手機械
４０…連結部
４４…ケーシング 12 ... Reducer 14 ... Output shaft (shaft member)
16 ... 1st bearing 18 ... 2nd bearing 20 ... Retaining ring 22 ... Retaining ring groove 24 ... Collar (Retaining member)
26 ... Oil seal 32 ... Second bearing arrangement part 34 ... First bearing arrangement part (large diameter part)
36 ... Collar arrangement part (small diameter part)
38 ... Counter machine 40 ... Connecting part 44 ... Casing

Claims (2)

軸部材と、
該軸部材に外嵌された軸受と、
前記軸部材に設けられた止め輪溝に配置され、前記軸受の内輪の軸方向移動を規制する止め輪と、
前記軸部材に外嵌され、前記止め輪が前記止め輪溝から外れるのを防止する抜け止め部材と、を有し、
前記抜け止め部材と前記軸受の内輪との間に前記止め輪が配置され、
前記抜け止め部材の外周にオイルシールが配置され、
前記軸部材は、大径部と小径部とを有し、
前記止め輪は、前記大径部に配置され、
前記抜け止め部材は、前記小径部に嵌合される内周部と、内周部より径方向外側に位置する外周部と、径方向から見て前記内周部と前記外周部の間に設けられるセンター部と、を有し、
前記外周部は、前記大径部と径方向に対向するように延在された延在部を有し、
前記外周部の外周に前記オイルシールが配置され、前記延在部は、前記止め輪と径方向に対向し、
前記オイルシールは、前記大径部と径方向から見て重なり、
前記センター部の軸方向幅は、前記内周部の軸方向幅よりも大きく、かつ前記外周部の軸方向幅よりも小さく、
前記センター部は、前記止め輪と軸方向に対向する
ことを特徴とする軸部材の支持構造。 A shaft member;
A bearing externally fitted to the shaft member;
A retaining ring that is disposed in a retaining ring groove provided in the shaft member and restricts axial movement of the inner ring of the bearing;
A retaining member that is externally fitted to the shaft member and prevents the retaining ring from coming off the retaining ring groove;
The retaining ring is disposed between the retaining member and the inner ring of the bearing;
An oil seal is disposed on the outer periphery of the retaining member ,
The shaft member has a large diameter portion and a small diameter portion,
The retaining ring is disposed on the large diameter portion,
The retaining member is provided between an inner peripheral portion fitted into the small diameter portion, an outer peripheral portion positioned radially outward from the inner peripheral portion, and between the inner peripheral portion and the outer peripheral portion as viewed from the radial direction. A center part, and
The outer peripheral portion has an extending portion that extends to face the large diameter portion in the radial direction,
The oil seal is disposed on the outer periphery of the outer peripheral portion, and the extending portion is opposed to the retaining ring in the radial direction,
The oil seal overlaps with the large diameter portion when viewed from the radial direction,
The axial width of the center portion is larger than the axial width of the inner peripheral portion and smaller than the axial width of the outer peripheral portion,
A support structure for a shaft member, wherein the center portion faces the retaining ring in the axial direction . 請求項１において、
前記止め輪と前記軸受の内輪との間にスペーサが配置され、
前記スペーサは、メインスペーサと、該メインスペーサよりも軸方向幅の狭いサブスペーサと、を有し、
前記メインスペーサが前記止め輪側に配置される
ことを特徴とする軸部材の支持構造。 In claim 1,
A spacer is disposed between the retaining ring and the inner ring of the bearing;
The spacer includes a main spacer and a sub-spacer having a narrower axial width than the main spacer,
The shaft support supporting structure, wherein the main spacer is disposed on the retaining ring side.
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