JP6610051B2 - Transmission lubrication structure - Google Patents

Transmission lubrication structure Download PDF

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JP6610051B2
JP6610051B2 JP2015143714A JP2015143714A JP6610051B2 JP 6610051 B2 JP6610051 B2 JP 6610051B2 JP 2015143714 A JP2015143714 A JP 2015143714A JP 2015143714 A JP2015143714 A JP 2015143714A JP 6610051 B2 JP6610051 B2 JP 6610051B2
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transmission
thrust washer
shaft
inner ring
lubricating oil
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JP2017025985A (en
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卓弘 鶴岡
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Isuzu Motors Ltd
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Isuzu Motors Ltd
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Priority to JP2015143714A priority Critical patent/JP6610051B2/en
Priority to CN201680042475.4A priority patent/CN107850204B/en
Priority to PCT/JP2016/070315 priority patent/WO2017014077A1/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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • 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
    • F16C19/24—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 radial load mainly
    • F16C19/26—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 radial load mainly with a single row of rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)
  • Sliding-Contact Bearings (AREA)
  • Rolling Contact Bearings (AREA)

Description

本発明は、変速機の潤滑構造に関し、特に、変速ギヤとベアリングとの間に配置されるスラストワッシャに関する。   The present invention relates to a transmission lubrication structure, and more particularly to a thrust washer disposed between a transmission gear and a bearing.

従来、変速機においては、複数の変速ギヤ列や各ベアリング等に発生する摩擦を低減するために、変速機ケース内の各部位に潤滑油を供給している。この種の潤滑構造として、例えば、メインシャフトの内部に形成された潤滑油路から径方向に潤滑油を吐出させると共に、係る潤滑油をスラストワッシャの側面に形成された径方向油溝から隣接するベアリングに供給する技術が知られている（例えば、特許文献１参照）。   Conventionally, in a transmission, lubricating oil is supplied to each part in a transmission case in order to reduce friction generated in a plurality of transmission gear trains and bearings. As this type of lubricating structure, for example, the lubricating oil is discharged in a radial direction from a lubricating oil passage formed inside the main shaft, and the lubricating oil is adjacent to a radial oil groove formed on a side surface of the thrust washer. A technique for supplying a bearing is known (for example, see Patent Document 1).

実開昭６０−１１０７６０号公報Japanese Utility Model Publication No. 60-110760

ところで、スラストワッシャはメインシャフトと一体に回転するため、メインシャフトの径方向油溝からベアリングに供給される潤滑油には遠心力が作用することになる。このため、潤滑油が遠心力の影響を受けてスラストワッシャの径方向油溝から外方に飛散すると、十分な量の潤滑油をベアリングに供給できなくなり、特にベアリングの内輪鍔部とコロとの接触面に油膜切れを生じさせて、これら部位の焼き付きを引き起こす課題がある。   By the way, since the thrust washer rotates integrally with the main shaft, centrifugal force acts on the lubricating oil supplied from the radial oil groove of the main shaft to the bearing. For this reason, if the lubricating oil splashes outward from the radial oil groove of the thrust washer due to the influence of centrifugal force, a sufficient amount of lubricating oil cannot be supplied to the bearing, especially between the inner ring collar of the bearing and the roller. There is a problem of causing oil film breakage on the contact surface and causing seizure of these parts.

開示の技術は、潤滑油の飛散を効果的に抑制してベアリングの焼き付きを防止することを目的とする。   An object of the disclosed technique is to effectively prevent the seizure of the lubricating oil and prevent the bearing from seizing.

開示の技術は、径方向に潤滑油を吐出可能な潤滑油路を有するシャフトに変速ギヤが設けられた変速機の潤滑構造であって、前記シャフトの外周に回転不能に設けられた内輪、変速機ケースに回転不能に設けられた外輪及び、前記内輪と前記外輪との間に摺動可能に介設されたコロを有する軸受部と、前記シャフトに挿通されると共に、前記軸受部と前記変速ギヤとの間に介設された環状のスラストワッシャと、を備え、前記スラストワッシャの側面に前記コロに向かって軸方向に突出する環状突起部を設けたものである。   The disclosed technique is a lubricating structure for a transmission in which a transmission gear is provided on a shaft having a lubricating oil passage capable of discharging lubricating oil in a radial direction, and an inner ring and a transmission that are provided on the outer periphery of the shaft so as not to rotate. A bearing part having an outer ring that is non-rotatably provided in the machine case, and a roller that is slidably interposed between the inner ring and the outer ring, and is inserted through the shaft, and the bearing part and the speed change And an annular thrust washer interposed between the gear and an annular protrusion that protrudes in the axial direction toward the roller on the side surface of the thrust washer.

前記環状突起部が前記内輪と前記外輪との間まで延設されると共に、その突出端を前記コロの側面に隣接させてもよい。   The annular protrusion may extend between the inner ring and the outer ring, and the protruding end may be adjacent to the side surface of the roller.

前記潤滑油路の吐出口が前記変速ギヤと対向する前記シャフトの外周面に設けられると共に、前記シャフトの外周面に前記吐出口から前記軸受部に向かって軸方向に延びるシャフト油溝が凹設され、前記スラストワッシャには、その内環部を軸方向に貫通する貫通油溝と、前記軸受部に臨む側面を前記貫通油溝の下流端から前記棚部に向かって径方向に延びる径方向油溝とが凹設されてもよい。   A discharge port of the lubricating oil passage is provided on the outer peripheral surface of the shaft facing the transmission gear, and a shaft oil groove extending in the axial direction from the discharge port toward the bearing portion is recessed in the outer peripheral surface of the shaft. The thrust washer includes a through oil groove that penetrates the inner ring portion in the axial direction, and a radial direction that extends in a radial direction from the downstream end of the through oil groove toward the shelf portion on a side surface facing the bearing portion. The oil groove may be recessed.

前記スラストワッシャの前記変速ギヤに臨む側面には、当該側面を前記内環部に向かって斜めに切り欠いた環状油溝が設けられてもよい。   An annular oil groove may be provided on a side surface of the thrust washer facing the transmission gear, with the side surface notched obliquely toward the inner ring portion.

前記スラストワッシャの前記軸受部に臨む側面には、当該側面を外環部に向かって斜めに切り欠いた環状傾斜面部が設けられてもよい。   An annular inclined surface portion may be provided on a side surface of the thrust washer facing the bearing portion, with the side surface notched obliquely toward the outer ring portion.

開示の技術によれば、潤滑油の飛散を効果的に抑制してベアリングの焼き付きを防止することができる。   According to the disclosed technology, it is possible to effectively prevent scattering of the lubricating oil and prevent the bearing from being seized.

本発明の一実施形態に係る変速機の一部を示す模式的な断面図である。It is typical sectional drawing which shows a part of transmission which concerns on one Embodiment of this invention. 本発明の一実施形態に係る変速機のメインシャフトの一部を示す模式的な斜視図である。1 is a schematic perspective view showing a part of a main shaft of a transmission according to an embodiment of the present invention. 本発明の一実施形態に係るスラストワッシャを円筒コロ軸受側から視た模式的な正面図である。It is the typical front view which looked at the thrust washer concerning one embodiment of the present invention from the cylindrical roller bearing side. 図３のＡ−Ａ線断面図である。FIG. 4 is a sectional view taken along line AA in FIG. 3. 本発明の一実施形態に係る変速機の潤滑構造における潤滑油の流れを説明する図である。It is a figure explaining the flow of the lubricating oil in the lubricating structure of the transmission which concerns on one Embodiment of this invention.

以下、添付図面に基づいて、本発明の一実施形態に係る変速機の潤滑構造について説明する。同一の部品には同一の符号を付してあり、それらの名称および機能も同じである。したがって、それらについての詳細な説明は繰返さない。   Hereinafter, a lubricating structure for a transmission according to an embodiment of the present invention will be described with reference to the accompanying drawings. The same parts are denoted by the same reference numerals, and their names and functions are also the same. Therefore, detailed description thereof will not be repeated.

図１に示すように、変速機１のメインシャフト１０は、円筒コロ軸受３０を介して変速機ケース２に回転自在に軸支されている。このメインシャフト１０には、ニードルベアリング３，４を介して複数の変速ギヤ１５，１６が回転可能に軸支されている。   As shown in FIG. 1, the main shaft 10 of the transmission 1 is rotatably supported by the transmission case 2 via a cylindrical roller bearing 30. A plurality of transmission gears 15 and 16 are rotatably supported on the main shaft 10 via needle bearings 3 and 4.

メインシャフト１０の内部には、軸方向に延び、潤滑油を流すための軸方向油路１１と、軸方向油路１１からメインシャフト１０の外周面に向かって径方向に延び、潤滑油を外周面の開口部１２Ａ（図２参照）から吐出するための径方向油路１２，１３が形成されている。これら径方向油路１２，１３は、例えば、各変速ギヤ１５，１６のそれぞれの内周面（ニードルベアリング３，４）に対向する位置に設けられている。   The main shaft 10 has an axial oil passage 11 extending in the axial direction for flowing the lubricating oil, and extending radially from the axial oil passage 11 toward the outer peripheral surface of the main shaft 10 so as to surround the lubricating oil. Radial oil passages 12 and 13 for discharging from the opening 12A (see FIG. 2) of the surface are formed. These radial oil passages 12 and 13 are provided, for example, at positions facing the respective inner peripheral surfaces (needle bearings 3 and 4) of the transmission gears 15 and 16.

メインシャフト１０の外周面には、開口部１２Ａ（図２参照）から詳細を後述するスラストワッシャ４０に向かって軸方向に延びるシャフト外周油溝１４（図１，２参照）が形成されている。   A shaft outer peripheral oil groove 14 (see FIGS. 1 and 2) extending in the axial direction from the opening 12A (see FIG. 2) toward a thrust washer 40, which will be described in detail later, is formed on the outer peripheral surface of the main shaft 10.

シンクロメッシュ機構２０は、その内周歯がメインシャフト１０のスプライン歯１０Ａ（図２参照）とスプライン嵌合するシンクロハブ２１と、シンクロハブ２１の外周歯と常時噛合すると共にシフトフォーク（不図示）によってシフト移動されて変速ギヤ１５のドグギヤ１５Ａと選択的に噛合可能なシンクロスリーブ２２と、シンクロハブ２１とドグギヤ１５Ａとの間に設けられて同期荷重を作用させるシンクロナイザリング２３とを備えている。   The synchromesh mechanism 20 has a synchromesh 21 whose inner peripheral teeth are spline-fitted with the spline teeth 10A (see FIG. 2) of the main shaft 10, and is always meshed with the outer peripheral teeth of the synchromesh hub 21 and a shift fork (not shown). , And a synchronizer ring 23 provided between the sync hub 21 and the dog gear 15 </ b> A to apply a synchronous load.

円筒コロ軸受３０は、外輪部３１と、内輪部３２と、これら外輪部３１と内輪部３２との間に摺動可能に挟持された円筒コロ３３とを備えている。   The cylindrical roller bearing 30 includes an outer ring portion 31, an inner ring portion 32, and a cylindrical roller 33 that is slidably sandwiched between the outer ring portion 31 and the inner ring portion 32.

外輪部３１は、その内周面の軸方向両端に径方向内方に向けて突出する一対の鍔部３１Ａ，Ｂが設けられている。この外輪部３１は、変速機ケース２の取り付け穴に圧入固定されている。内輪部３２は、円環状の第１鍔部３２Ａと、断面略Ｌ字状の円環状の第２鍔部３２Ｂとの二部品によって構成されている。内輪部３２は、その内周をメインシャフト１０の外周部１０Ｂ（図２参照）に嵌合されている。   The outer ring portion 31 is provided with a pair of flange portions 31A and 31B that protrude radially inward at both axial ends of the inner peripheral surface thereof. The outer ring portion 31 is press-fitted and fixed in a mounting hole of the transmission case 2. The inner ring portion 32 includes two parts, an annular first collar portion 32A and an annular second collar portion 32B having a substantially L-shaped cross section. The inner ring portion 32 is fitted to the outer peripheral portion 10B (see FIG. 2) of the main shaft 10 at the inner periphery thereof.

スラストワッシャ４０は、正面視で略円環状に形成されており、メインシャフト１０に摺動可能に挿通されて変速ギヤ１５と円筒コロ軸受３０との間に介設されている。なお、変速ギヤ１６と円筒コロ軸受３０との間のスラストワッシャ５０もスラストワッシャ４０と同様に構成されるため、以下、スラストワッシャ５０の詳細な説明は省略する。   The thrust washer 40 is formed in a substantially annular shape when viewed from the front, and is slidably inserted into the main shaft 10 and interposed between the transmission gear 15 and the cylindrical roller bearing 30. In addition, since the thrust washer 50 between the transmission gear 16 and the cylindrical roller bearing 30 is configured in the same manner as the thrust washer 40, detailed description of the thrust washer 50 will be omitted below.

図３，４に示すように、スラストワッシャ４０には、その円筒コロ軸受３０側の第１側面部４０Ａから軸方向に所定の高さで突出する円環状の棚部（環状突起部）４４が凸設されている。この棚部４４は、円筒コロ軸受３０の外輪部３１と内輪部３２との間まで延びると共に、その突出端と円筒コロ３３の側面との間には干渉を避けるための微少なクリアランスが確保されている。   As shown in FIGS. 3 and 4, the thrust washer 40 has an annular shelf (annular protrusion) 44 that protrudes at a predetermined height in the axial direction from the first side surface portion 40A on the cylindrical roller bearing 30 side. Projected. The shelf portion 44 extends between the outer ring portion 31 and the inner ring portion 32 of the cylindrical roller bearing 30, and a small clearance is secured between the protruding end and the side surface of the cylindrical roller 33. ing.

スラストワッシャ４０の第１側面部４０Ａには、内環部４１から棚部４４に向かって径方向に延びる複数本（図示例では４本）の径方向油溝４５が凹設されている。また、第１側面部４０Ａには、外環部４２を第１側面部４０Ａに向けて斜めに切り欠いて形成した環状傾斜面部４８が設けられている。   In the first side surface portion 40A of the thrust washer 40, a plurality of (four in the illustrated example) radial oil grooves 45 extending in the radial direction from the inner ring portion 41 toward the shelf portion 44 are recessed. Further, the first side surface portion 40A is provided with an annular inclined surface portion 48 formed by obliquely cutting the outer ring portion 42 toward the first side surface portion 40A.

スラストワッシャ４０の内環部４１には、径方向外方に所定の深さで窪むと共に、スラストワッシャ４０を軸方向に貫通して径方向油溝４５に連通する複数本（図示例では４本）の貫通油溝４６が凹設されている。また、スラストワッシャ４０の変速ギヤ１５側の第２側面部４０Ｂには、この第２側面部４０Ｂを内環部４１に向けて斜めに切り欠いて形成した環状油溝４７（図４参照）が設けられている。   The inner ring portion 41 of the thrust washer 40 has a plurality of recesses (4 in the illustrated example) that are recessed radially outward at a predetermined depth and that penetrate the thrust washer 40 in the axial direction and communicate with the radial oil groove 45. The main through-groove 46 is recessed. The second side surface portion 40B of the thrust washer 40 on the transmission gear 15 side has an annular oil groove 47 (see FIG. 4) formed by cutting the second side surface portion 40B obliquely toward the inner ring portion 41. Is provided.

次に、図５に基づいて、本実施形態の変速機の潤滑構造の作用効果について説明する。   Next, based on FIG. 5, the effect of the lubricating structure of the transmission of this embodiment is demonstrated.

図５中に破線矢印Ｘ１で示すように、潤滑油はメインシャフト１０の軸方向油路１１、径方向油路１２を流れて開口部１２Ａ（図２参照）から吐出され、さらに、シャフト外周油溝１４内をスラストワッシャ４０に向けて流される。   As indicated by a broken line arrow X1 in FIG. 5, the lubricating oil flows through the axial oil passage 11 and the radial oil passage 12 of the main shaft 10 and is discharged from the opening 12A (see FIG. 2). It flows in the groove 14 toward the thrust washer 40.

シャフト外周溝１４の下流端に達した潤滑油は、環状油溝４７内を回流しながら、破線矢印Ｘ２で示すように、貫通油路４６内を通って径方向油溝４５に到達する。径方向油溝４５に達した潤滑油は、遠心力によって径方向外方へ流れて棚部４４に突き当たり、さらに棚部４４の内周面に沿って案内されながら、円筒コロ軸受３０の外輪部３１と内輪部３２との間に導かれるようになっている。   The lubricating oil that has reached the downstream end of the shaft outer circumferential groove 14 circulates in the annular oil groove 47 and reaches the radial oil groove 45 through the through oil passage 46 as indicated by a broken arrow X2. The lubricating oil that has reached the radial oil groove 45 flows radially outward by centrifugal force, hits the shelf 44, and is guided along the inner peripheral surface of the shelf 44, while the outer ring portion of the cylindrical roller bearing 30. 31 is guided between the inner ring portion 32 and the inner ring portion 32.

すなわち、径方向油溝４５から供給される潤滑油を径方向外方に飛散させることなく、棚部４４によって確実に受け止めて案内するとで、潤滑油が円筒コロ軸受３０に向かって効果的に導入されるように構成されている。したがって、本実施形態の潤滑構造によれば、円筒コロ軸受３０への潤滑油の供給量を効果的に確保することが可能となり、特に焼き付きが生じやすい第１鍔部３２Ａと円筒コロ３３との間の油膜切れを確実に防止することができる。 That is, the lubricating oil supplied from the radial oil groove 45 is surely received and guided by the shelf portion 44 without splashing radially outward, so that the lubricating oil is effectively introduced toward the cylindrical roller bearing 30. It is configured to be. Therefore, according to the lubrication structure of the present embodiment, effectively it is possible to secure the amount of lubricating oil supplied to the cylindrical roller bearing 30, the first flange portion 32A and the cylindrical roller 33 particularly prone to air image sticking Oil film breakage between the two can be reliably prevented.

また、図５中に破線矢印Ｘ３で示すように、変速ギヤ１５等によって変速機ケース２内に掻き上げられた潤滑油の一部は、スラストワッシャ４０に落下し、環状傾斜面部４８によって棚部４４の外周面に効果的に集められる。さらに、潤滑油は棚部４４の外周面に沿って流されて、円筒コロ軸受３０の外輪部３１と内輪部３２との間に効果的に導入されるようになっている。したがって、本実施形態の潤滑構造によれば、円筒コロ軸受３０への潤滑油の供給量を効果的に増加させることが可能となり、円筒コロ軸受３０の焼き付きを確実に防止することができる。 Further, as indicated by a broken line arrow X3 in FIG. 5, part of the lubricating oil scraped up into the transmission case 2 by the transmission gear 15 or the like falls to the thrust washer 40 and is sunk by the annular inclined surface portion 48. 44 is effectively collected on the outer peripheral surface. Further, the lubricating oil is caused to flow along the outer peripheral surface of the shelf portion 44 and is effectively introduced between the outer ring portion 31 and the inner ring portion 32 of the cylindrical roller bearing 30. Therefore, according to the lubrication structure of the present embodiment, effectively it becomes possible to increase the amount of lubricating oil supplied to the cylindrical roller bearing 30, a-out image sticking of the cylindrical roller bearing 30 can be reliably prevented .

なお、本発明は、上述の実施形態に限定されるものではなく、本発明の趣旨を逸脱しない範囲で、適宜変形して実施することが可能である。   In addition, this invention is not limited to the above-mentioned embodiment, In the range which does not deviate from the meaning of this invention, it can change suitably and can implement.

例えば、シャフトはメインシャフト１０に限定されず、カウンタシャフト等、潤滑油路が形成される他のシャフトにも広く適用することが可能である。また、ベアリングは円筒コロ軸受３０に限定されず、ボールベアリング等、他のベアリングにも広く適用することが可能である。   For example, the shaft is not limited to the main shaft 10 and can be widely applied to other shafts in which a lubricating oil passage is formed, such as a counter shaft. Further, the bearing is not limited to the cylindrical roller bearing 30 and can be widely applied to other bearings such as a ball bearing.

１ 変速機
２ 変速機ケース
３，４ ニードルベアリング
１０ メインシャフト
１１ 軸方向油路
１２，１３ 径方向油路
１４ シャフト外周溝
１５，１６ 変速ギヤ
２０ シンクロメッシュ機構
２１ シンクロハブ
２２ シンクロスリーブ
２３ シンクロナイザリング
３０ 円筒コロ軸受
３１ 外輪部
３１Ａ，Ｂ 鍔部
３２ 内輪部
３２Ａ 第１鍔部
３２Ｂ 第２鍔部
３３ 円筒コロ
４０ スラストワッシャ
４１ 内環部
４２ 外環部
４４ 棚部（環状突起部）
４５ 径方向油溝
４６ 貫通油溝
４７ 環状油溝
４８ 環状傾斜面部 DESCRIPTION OF SYMBOLS 1 Transmission 2 Transmission case 3, 4 Needle bearing 10 Main shaft 11 Axial oil path 12, 13 Radial oil path 14 Shaft outer peripheral groove 15, 16 Transmission gear 20 Synchromesh mechanism 21 Synchro hub 22 Synchro sleeve 23 Synchronizer ring 30 Cylindrical roller bearing 31 Outer ring part 31A, B collar part 32 inner ring part 32A first collar part 32B second collar part 33 cylindrical roller 40 thrust washer 41 inner ring part 42 outer ring part 44 shelf part (annular projection part)
45 radial oil groove 46 through oil groove 47 annular oil groove 48 annular inclined surface portion

Claims (4)

径方向に潤滑油を吐出可能な潤滑油路を有するシャフトに変速ギヤが設けられた変速機の潤滑構造であって、
前記シャフトの外周に回転不能に設けられた内輪、変速機ケースに回転不能に設けられた外輪及び、前記内輪と前記外輪との間に摺動可能に介設された転動体を有する軸受部と、
前記シャフトに挿通されると共に、前記軸受部と前記変速ギヤとの間に介設された環状のスラストワッシャと、を備え、
前記スラストワッシャの前記軸受部に臨む側面に、軸方向に沿って前記転動体に隣接する位置まで延設される環状突起部を設け、
前記スラストワッシャには、その内環部を軸方向に貫通する貫通油溝と、前記軸受部に臨む側面を前記貫通油溝の下流端から前記環状突起部に向かって径方向に延びる径方向油溝とが凹設される
変速機の潤滑構造。 A transmission lubrication structure in which a transmission gear is provided on a shaft having a lubricating oil passage capable of discharging lubricating oil in a radial direction,
An inner ring provided non-rotatably on the outer periphery of the shaft, an outer ring non-rotatably provided on the transmission case, and a bearing portion having a rolling element slidably interposed between the inner ring and the outer ring; ,
An annular thrust washer that is inserted between the shaft and interposed between the bearing portion and the transmission gear,
Provided on the side face of the thrust washer facing the bearing portion is an annular protrusion extending in the axial direction to a position adjacent to the rolling element,
The thrust washer includes a through oil groove that penetrates the inner ring portion in the axial direction, and a radial oil that extends in a radial direction from a downstream end of the through oil groove to a side surface facing the bearing portion. A lubrication structure for a transmission in which a groove is recessed . 前記潤滑油路の吐出口が前記変速ギヤと対向する前記シャフトの外周面に設けられると共に、前記シャフトの外周面に前記吐出口から前記軸受部に向かって軸方向に延びるシャフト油溝が凹設される
請求項１に記載の変速機の潤滑構造。 A discharge port of the lubricating oil passage is provided on the outer peripheral surface of the shaft facing the transmission gear, and a shaft oil groove extending in the axial direction from the discharge port toward the bearing portion is recessed in the outer peripheral surface of the shaft. The lubrication structure for a transmission according to claim 1. 前記スラストワッシャの前記変速ギヤに臨む側面には、当該側面を前記内環部に向かって斜めに切り欠いた環状油溝が設けられる
請求項１又は２に記載の変速機の潤滑構造。 The lubrication structure for a transmission according to claim 1 or 2, wherein an annular oil groove is provided on a side surface of the thrust washer facing the transmission gear so that the side surface is notched obliquely toward the inner ring portion . 前記スラストワッシャの前記軸受部に臨む側面には、当該側面を外環部に向かって斜めに切り欠いた環状傾斜面部が設けられる
請求項１から３の何れか一項に記載の変速機の潤滑構造。 On the side surface of the thrust washer that faces the bearing portion, an annular inclined surface portion is provided by cutting the side surface obliquely toward the outer ring portion.
The transmission lubricating structure according to any one of claims 1 to 3 .
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