JPH0814312B2 - Lubrication mechanism of transmission - Google Patents

Lubrication mechanism of transmission

Info

Publication number
JPH0814312B2
JPH0814312B2 JP63329433A JP32943388A JPH0814312B2 JP H0814312 B2 JPH0814312 B2 JP H0814312B2 JP 63329433 A JP63329433 A JP 63329433A JP 32943388 A JP32943388 A JP 32943388A JP H0814312 B2 JPH0814312 B2 JP H0814312B2
Authority
JP
Japan
Prior art keywords
gear
main shaft
lubricating oil
oil
shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
JP63329433A
Other languages
Japanese (ja)
Other versions
JPH02176247A (en
Inventor
薫 木越
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Isuzu Motors Ltd
Original Assignee
Isuzu Motors Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Isuzu Motors Ltd filed Critical Isuzu Motors Ltd
Priority to JP63329433A priority Critical patent/JPH0814312B2/en
Publication of JPH02176247A publication Critical patent/JPH02176247A/en
Publication of JPH0814312B2 publication Critical patent/JPH0814312B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Classifications

    • 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
    • F16H57/0478—Synchromesh devices
    • 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
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0493—Gearings with spur or bevel gears
    • F16H57/0494—Gearings with spur or bevel gears with variable gear ratio or for reversing rotary motion

Landscapes

  • General Details Of Gearings (AREA)

Description

【発明の詳細な説明】 〔産業上の利用分野〕 この発明は、変速機の潤滑機構、特に、車両に用いら
れる同期装置を設けた主軸に対して副軸を配設した歯車
変速機に用いられる変速機の潤滑機構に関する。DETAILED DESCRIPTION OF THE INVENTION [Industrial field of application] The present invention is used for a lubrication mechanism of a transmission, and particularly for a gear transmission in which an auxiliary shaft is provided for a main shaft provided with a synchronizing device used in a vehicle. The present invention relates to a lubrication mechanism of a transmission.

〔従来の技術〕[Conventional technology]

一般に、車両等に用いられる歯車変速機は、第３図に
示すように構成されている。該歯車変速機は、主軸１及
び副軸11が軸方向に平行に配置されている。主軸１に
は、クラッチハブ４がスプライン嵌合７しており、該ク
ラッチハブ４の両側面に一対のギヤ2,3がニードルベア
リングである軸受5,6を介して主軸１に回転自在に支持
されている。Generally, a gear transmission used in a vehicle or the like is configured as shown in FIG. In the gear transmission, a main shaft 1 and a sub shaft 11 are arranged parallel to the axial direction. A clutch hub 4 is spline-fitted to the main shaft 1, and a pair of gears 2 and 3 are rotatably supported on the main shaft 1 via bearings 5 and 6 which are needle bearings on both side surfaces of the clutch hub 4. Has been done.

また、主軸１と各ギヤ2,3間には、同期装置10が組み
込まれている。同期装置10は、クラッチハブ４の外周部
にスプライン嵌合したスリーブ17、各ギヤ2,3に設けた
ドグ歯12,13及びクラッチハブ４とドグ歯12,13間に配設
された同期リング8,9を備えている。それ故に、スリー
ブ17をクラッチハブ４に対していずれかの軸方向に摺動
移動させることによって、スリーブ17は同期リング８又
は９を介してギヤ２又は３のドグ歯12又は13に噛合する
こととなる。従って、主軸１は、同期装置10を介してギ
ヤ２又は３に動力伝達を行うようになる。A synchronizing device 10 is incorporated between the main shaft 1 and the gears 2 and 3. The synchronizer 10 includes a sleeve 17 spline-fitted to the outer peripheral portion of the clutch hub 4, dog teeth 12 and 13 provided on the gears 2 and 3, and a synchronizing ring arranged between the clutch hub 4 and the dog teeth 12 and 13. Equipped with 8,9. Therefore, by sliding the sleeve 17 in either axial direction with respect to the clutch hub 4, the sleeve 17 engages with the dog tooth 12 or 13 of the gear 2 or 3 via the synchronizing ring 8 or 9. Becomes Therefore, the main shaft 1 transmits power to the gear 2 or 3 via the synchronizer 10.

一方、副軸11にはギヤ14,15が設けられており、各ギ
ヤ14,15は主軸１に回転自在に支持された各ギヤ2,3にそ
れぞれ常時噛合状態に配設されている。更に、変速機ケ
ース22側に位置するギヤ３の側面には、主軸１を回転自
在に支持する軸受19、該軸受19とギヤ３との間に配設さ
れたスラスト軸受18等が配設されている。On the other hand, the auxiliary shaft 11 is provided with gears 14 and 15, and the gears 14 and 15 are always arranged in mesh with the gears 2 and 3 rotatably supported by the main shaft 1, respectively. Further, a bearing 19 for rotatably supporting the main shaft 1, a thrust bearing 18 arranged between the bearing 19 and the gear 3, and the like are arranged on the side surface of the gear 3 located on the transmission case 22 side. ing.

このような歯車変速機は、例えば、１速段と２速段と
の変速装置、３速段と４速段との変速装置、或いは入力
軸の主軸への直結した高速段と入力軸から副軸を介した
結合して主軸に連結する低速段の二段階変速を行う変速
装置に適用されるものである。歯車変速機の潤滑機構
は、後述するが、ギヤ14,15による潤滑油16のかき上
げ、及び主軸１にスプライン嵌合７したクラッチハブ４
の両側のボス部スラスト面に形成された油溝23を通じて
潤滑油16を被潤滑部位に供給し、該被潤滑部位の潤滑を
補助している。Such a gear transmission may be, for example, a speed change device having a first speed and a second speed, a speed change device having a third speed and a fourth speed, or a high speed directly connected to a main shaft of an input shaft and an auxiliary shaft from the input shaft. The present invention is applied to a speed change device that performs a two-stage speed change at a low speed stage, which is connected via a shaft and connected to a main shaft. The lubrication mechanism of the gear transmission will be described later, but the lubricating oil 16 is lifted up by the gears 14 and 15, and the clutch hub 4 is spline-fitted to the main shaft 1.
Lubricating oil 16 is supplied to the lubricated portion through the oil grooves 23 formed on the thrust surfaces of the boss portions on both sides of the boss portion to assist lubrication of the lubricated portion.

ところで、従来、上記のような歯車変速機において、
主軸１即ちシャフトと該シャフトに相対回転可能に支持
されたギヤ2,3を支持する軸受5,6,18等の可動部の潤滑
は、例えば、第４図、第５図又は第６図に示すような対
策が取られている。By the way, conventionally, in the gear transmission as described above,
Lubrication of the movable part such as the bearings 5, 6, 18 supporting the main shaft 1, that is, the shaft and the gears 2, 3 rotatably supported by the shaft is described in, for example, FIG. 4, FIG. 5 or FIG. The following measures have been taken.

まず、第４図には、歯車変速機の潤滑機構が示されて
いる。変速機ケース内の潤滑油45の油面下に位置する副
軸41に設けたギヤ43の回転によって、潤滑油45をかき上
げて潤滑油45を飛散させ、それによって、主軸40にギヤ
42を回転可能に支持する軸受等の被潤滑部位へ潤滑油45
を供給し、潤滑する方法がある。或いは、変速機ケース
に潤滑油供給樋44を設け、副軸41のギヤ43等のギヤの回
転でかき上げられた潤滑油45を潤滑油供給樋44で受け、
該潤滑油供給樋44で潤滑油45を軸受等の被潤滑部位にガ
イドして潤滑する方法がある。First, FIG. 4 shows the lubrication mechanism of the gear transmission. The rotation of the gear 43 provided on the sub shaft 41 located below the oil level of the lubrication oil 45 in the transmission case causes the lubrication oil 45 to be lifted up and scattered so that the main shaft 40 is geared.
Lubricating oil 45 to lubricated parts such as bearings that rotatably support 42
There is a method of supplying and lubricating. Alternatively, a lubricating oil supply trough 44 is provided in the transmission case, and the lubricating oil 45 is picked up by the rotation of gears such as the gear 43 of the auxiliary shaft 41, and the lubricating oil supply trough 44 receives the lubricating oil 45.
There is a method in which the lubricating oil supply gutter 44 guides the lubricating oil 45 to a lubricated portion such as a bearing to lubricate it.

また、第５図には、シャフト50に軸受54を介してギヤ
51を支持した軸受の潤滑機構が示されている。シャフト
50には潤滑油を通す油路として機能する軸方向の中空穴
52及び該中空穴52と連通する半径方向の小穴53が形成さ
れている。潤滑油供給ポンプによって供給された潤滑油
は、シャフト50に形成した軸方向の中空穴52、次いで半
径方向の小穴53から軸受54に潤滑油を吐出させて潤滑す
る方法がある。Further, in FIG. 5, a gear is attached to the shaft 50 through a bearing 54.
The lubrication mechanism of the bearing supporting 51 is shown. shaft
50 is a hollow hole in the axial direction that functions as an oil passage for lubricating oil.
52 and a radial small hole 53 communicating with the hollow hole 52 are formed. The lubricating oil supplied by the lubricating oil supply pump may be lubricated by discharging the lubricating oil from the axial hollow hole 52 formed in the shaft 50 and then the small radial hole 53 to the bearing 54.

更に、第６図には、主軸にスプライン嵌合したクラッ
チハブ60及び該クラッチハブ60の両側に配設される一対
のギヤ61,62が示されている。クラッチハブ60のボス部
スラスト面に油溝63が形成されている。油溝63を通じて
潤滑油を供給し、被潤滑部位の潤滑を補助する方法であ
る。この場合には、ギヤ61,62のボス部スラスト面に油
溝を形成したものもある。Further, FIG. 6 shows a clutch hub 60 spline-fitted to the main shaft and a pair of gears 61 and 62 arranged on both sides of the clutch hub 60. An oil groove 63 is formed on the thrust surface of the boss portion of the clutch hub 60. This is a method of supplying lubricating oil through the oil groove 63 to assist the lubrication of the lubricated portion. In this case, some gears 61, 62 have an oil groove formed on the thrust surface of the boss portion.

或いは、上記各潤滑方法を組み合わせた潤滑方法も行
うことができるものである。Alternatively, a lubrication method combining the above-mentioned respective lubrication methods can be performed.

また、実開昭59−157161号公報には、変速機の回転軸
に対する潤滑機構が開示されている。該公報で開示され
た潤滑機構は、第１回転軸の一端面に開口する軸方向の
軸孔に、同一軸心線上の第２回転軸の一端面に突出する
端部をベアリングを介して回転自在に支持し、前記第１
回転軸と前記第２回転軸との相対する端面の間に両軸外
周側から軸部側へ潤滑油を通す間隙部を設け、前記軸孔
の内径面に、開口部の方向に流出する潤滑油を阻止する
ための堰を設けたものである。Further, Japanese Utility Model Laid-Open No. 59-157161 discloses a lubrication mechanism for a rotary shaft of a transmission. In the lubrication mechanism disclosed in this publication, an end portion projecting to one end surface of a second rotary shaft on the same axis is rotated through a bearing in an axial axial hole that opens at one end surface of the first rotary shaft. Freely supported, the first
A gap is provided between the opposite end surfaces of the rotating shaft and the second rotating shaft to allow lubricating oil to pass from the outer peripheral side of both shafts to the shaft side, and the lubricating oil that flows toward the opening is provided on the inner diameter surface of the shaft hole. It has a weir to prevent oil.

〔発明が解決しようとする課題〕[Problems to be Solved by the Invention]

しかしながら、上記歯車変速機では、油量の低減、小
型コンパクト化、ギヤレシオワイド化等によって上記潤
滑機構のみでは、対応できない部位がでてきた。例え
ば、油量の低減、ギヤレシオワイド化等によって、変速
機ケース内の潤滑油にギヤが当たらなくなり、ギヤによ
る潤滑油のかき上げが不可能になってきた。However, in the above-mentioned gear transmission, there are some parts that cannot be dealt with only by the above-mentioned lubrication mechanism due to reduction of the amount of oil, downsizing, compactness, widening of gear ratio and the like. For example, due to a reduction in the amount of oil, a wider gear ratio, etc., the gear oil does not hit the lubricating oil in the transmission case, making it impossible to lift up the lubricating oil by the gear.

また、上記歯車変速機では、第３図に示すように、構
造上、ギヤ２と該ギヤ２に隣接するギヤ21との間の隙間
L1は比較的に大きく形成されているのに対して、ギヤ３
と該ギヤ３に隣接する変速機ケース22との間の隙間L2は
小さく構成されている。Further, in the above gear transmission, as shown in FIG. 3, due to the structure, a gap between the gear 2 and the gear 21 adjacent to the gear 2 is provided.
L 1 is relatively large, while gear 3
The gap L 2 between the gearbox 3 and the transmission case 22 adjacent to the gear 3 is made small.

従って、第４図に示すような潤滑方法では、副軸11の
ギヤ14によってかき上げられる潤滑油は、ギヤ２、軸受
５等の被潤滑部位に十分に供給されるが、これに反し
て、副軸11のギヤ15によってかき上げられる潤滑油は、
ギヤ３、軸受６、スラスト軸受18等の被潤滑部位に供給
されるのが困難となる。Therefore, in the lubrication method as shown in FIG. 4, the lubricating oil scraped up by the gear 14 of the counter shaft 11 is sufficiently supplied to the lubricated parts such as the gear 2 and the bearing 5, but on the contrary, The lubricating oil lifted by the gear 15 of the counter shaft 11 is
It becomes difficult to supply it to the lubricated parts such as the gear 3, the bearing 6, and the thrust bearing 18.

また、第４図に示すように、変速機ケースに潤滑油供
給樋44を設けて潤滑油45を軸受等の被潤滑部位にガイド
して潤滑方法は、コンパクト化によって変速機のケース
内におけるスペースが減少し、潤滑油供給樋44を設置す
るスペースがなく、成立できなくなっている。Further, as shown in FIG. 4, a lubricating oil supply gutter 44 is provided in the transmission case to guide the lubricating oil 45 to a lubricated portion such as a bearing, and the lubrication method is a compact space in the transmission case. Has been reduced, and there is no space to install the lubricating oil supply gutter 44, so it cannot be established.

更に、第５図に示すように、シャフト50の軸方向の中
空穴52及び該中空穴52と連通する半径方向の小穴53が形
成して被潤滑部位へ潤滑油供給ポンプによって潤滑油を
供給する潤滑方法は、FR車での変速機の搭載位置がエン
ジンの後方に位置し、運転席に近くクランク軸と同一軸
上に配置され、レイアウト上機構が複雑化する。Further, as shown in FIG. 5, a hollow hole 52 in the axial direction of the shaft 50 and a small hole 53 in the radial direction which communicates with the hollow hole 52 are formed to supply lubricating oil to a lubricated portion by a lubricating oil supply pump. As for the lubrication method, the mounting position of the transmission in the FR vehicle is located behind the engine, and it is located near the driver's seat and on the same axis as the crankshaft, which complicates the layout mechanism.

或いは、第６図に示すように、クラッチハブ60、ギヤ
61、62のボス部スラスト面に油溝63を形成する潤滑方法
は、第４図に示した潤滑油かき上げ潤滑方法が良好でな
ければ、効果が低減されるものである。Alternatively, as shown in FIG. 6, the clutch hub 60, the gear
The effect of the lubricating method of forming the oil groove 63 on the thrust surface of the boss portion of 61, 62 is reduced unless the lubricating oil lift-up lubricating method shown in FIG. 4 is good.

また、前掲実開昭59−157161号公報に開示された潤滑
機構は、同期リングを備えた同期装置の部位を通じて潤
滑油を供給するものでなく、油溝は主軸に形成されたも
のである。しかしながら、主軸に対して大きなトルクが
かかるような部位には、主軸の強度上、主軸に対して油
溝等を形成することはできない。従って、主軸に対して
大きなトルクが掛かり、しかも潤滑油を供給するのに厳
しい被潤滑部位への潤滑には、該潤滑機構は適用できな
い。Further, the lubricating mechanism disclosed in Japanese Utility Model Laid-Open No. 59-157161, supra, does not supply the lubricating oil through the portion of the synchronizing device having the synchronizing ring, but the oil groove is formed in the main shaft. However, due to the strength of the main shaft, it is not possible to form an oil groove or the like at the portion where a large torque is applied to the main shaft. Therefore, the lubrication mechanism cannot be applied to lubrication of a lubricated portion where a large torque is applied to the main shaft and the lubrication oil is difficult to supply.

この発明の目的は、上記の諸課題を解決することであ
り、エンジンの高出力、高回転化、シンクロ容量のアッ
プ、潤滑油量の低減、シペース低減によるコンパクト
化、ギヤレシオワイド化等に対応するため、例えば、同
期装置が配設されたギヤと該ギヤに隣接する変速機ケー
スとの間の隙間が小さく構成されている潤滑油の供給が
厳しい部位にも、比較的に潤滑油量が多い被潤滑部位か
ら潤滑油を供給して、積極的に且つスムースに潤滑油を
供給して潤滑効率を向上させ、しかも変速機についての
強度上の問題を克服できる変速機の潤滑機構を提供する
ことである。An object of the present invention is to solve the above problems, and to cope with high engine output, high rotation, increased synchro capacity, reduced lubricating oil amount, compactness by reducing pacing, widened gear ratio, etc. Therefore, for example, even in a region where the supply of lubricating oil is difficult, in which the gap between the gear in which the synchronizing device is arranged and the transmission case adjacent to the gear is small, the amount of lubricating oil is relatively large. To provide a lubrication mechanism of a transmission, which can supply lubrication oil from a portion to be lubricated to positively and smoothly supply lubrication oil to improve lubrication efficiency and overcome strength problems of the transmission. Is.

〔課題を解決するための手段〕[Means for solving the problem]

この発明は、上記の目的を達成するため、次のように
構成されている。即ち、この発明は、主軸にスプライン
嵌合したクラッチハブ、前記主軸に各軸受を介して前記
クラッチハブの両側面に回転可能に配置した各ギヤ、及
び前記主軸と前記各ギヤとをトルク伝達状態に作動する
各同期装置を有し、前記軸受の側面に対向する前記クラ
ッチハブ内周のスプライン部に軸方向に貫通する油溝を
形成し、一方の前記軸受に供給された潤滑油を前記油溝
を通して他方の前記軸受に供給するように構成したこと
を特徴とする変速機の潤滑機構に関する。The present invention is configured as follows to achieve the above object. That is, the present invention provides a clutch hub spline-fitted to a main shaft, gears rotatably arranged on both sides of the clutch hub via bearings on the main shaft, and a torque transmission state between the main shaft and each gear. An oil groove penetrating in the axial direction in the spline portion of the inner circumference of the clutch hub facing the side surface of the bearing, and the lubricating oil supplied to one of the bearings is used as the oil. A lubricating mechanism for a transmission, characterized in that it is configured to supply the other bearing through a groove.

また、この変速機の潤滑機構は、前記主軸に径が異な
る径の小さいギヤと径の大きいギヤの径の異なるギヤが
配設され、該各ギヤは前記主軸に平行に配設された副軸
に支持されたギヤと各々噛合し、前記径の小さいギヤと
噛合する前記副軸の前記ギヤによって少なくとも潤滑油
がかき上げられ、前記油溝は前記主軸に配設された前記
径の小さいギヤに対向する潤滑油入口側から前記径の大
きいギヤに対向する潤滑油出口側に半径方向に傾斜状に
形成されているものである。Further, in the lubrication mechanism of this transmission, a gear having a small diameter and a gear having a large diameter having different diameters are arranged on the main shaft, and each of the gears is a sub shaft arranged in parallel with the main shaft. At least lubricating oil is raked up by the gear of the auxiliary shaft that meshes with the gear supported by the gear of the small diameter, and the oil groove is formed in the small gear of the main shaft. It is formed so as to be inclined in the radial direction from the opposing lubricating oil inlet side to the lubricating oil outlet side facing the gear having the larger diameter.

〔作用〕[Action]

この発明による変速機の潤滑機構は、以上のように構
成されており、次の作用を有する。即ち、この変速機の
潤滑機構は、主軸に各ギヤを回転可能に配置した軸受の
側面に対向するクラッチハブ内周のスプライン部に軸方
向に貫通する油溝を形成し、前記軸受の一方に供給され
た潤滑油を前記油溝を通して前記軸受の他方に供給する
ように構成したので、一方のギヤによる潤滑油のかき上
げが不可能になったとしても、或いは構造上、前記ギヤ
に隣接して形成される隙間が小さく、潤滑油の供給が厳
しい被潤滑部位であったとしても、他の一方のギヤの軸
受に供給された潤滑油を前記油溝を通して潤滑油の供給
が厳しいギヤ側の軸受に供給することができる。The lubrication mechanism of the transmission according to the present invention is configured as described above and has the following actions. That is, the lubrication mechanism of this transmission forms an oil groove axially penetrating in the spline portion of the inner circumference of the clutch hub facing the side surface of the bearing in which each gear is rotatably arranged on the main shaft, and one of the bearings is formed. Since the supplied lubricating oil is configured to be supplied to the other of the bearings through the oil groove, even if it is impossible to lift the lubricating oil by one gear, or because of the structure, it is adjacent to the gear. Even if there is a small gap formed by lubrication and the lubrication oil is supplied in a severely lubricated area, the lubrication oil supplied to the bearing of the other gear is passed through the oil groove to prevent the supply of lubrication oil from the gear side. Can be supplied to bearings.

また、前記主軸に配設された各ギヤは径が異なり、該
各ギヤは前記主軸に平行に配設された副軸に支持された
各ギヤと各々噛合しており、前記油溝は前記主軸に配設
された各ギヤの径の小さい一方のギヤに対向する潤滑油
入口側から径の大きい他方のギヤに対向する潤滑油出口
側に半径方向に傾斜状に形成したので、潤滑油量が少な
く前記主軸に配設された径の大きい他方のギヤと噛合う
副軸に支持されたギヤによる潤滑油のかき上げが不可能
になったとしても、主軸に配設された径の小さい一方の
ギヤと噛合う副軸に支持されたギヤによってかき上げら
れた潤滑油が該一方のギヤの軸受けに供給され、この潤
滑油が更に前記油溝を通して他方のギヤの軸受に供給さ
れる。The gears arranged on the main shaft have different diameters, and the gears mesh with the gears supported by a counter shaft arranged in parallel with the main shaft, and the oil groove forms the main shaft. Each of the gears is arranged in the radial direction from the lubricating oil inlet side facing one gear with the smaller diameter to the lubricating oil outlet side facing the other gear with the larger diameter. Even if it becomes impossible to lift up the lubricating oil by the gear supported by the auxiliary shaft that meshes with the other large-diameter gear arranged on the main shaft, Lubricating oil picked up by a gear supported by a counter shaft meshing with the gear is supplied to the bearing of the one gear, and this lubricating oil is further supplied to the bearing of the other gear through the oil groove.

この時、前記油溝が前記主軸に配設された径の小さい
一方のギヤに対向する潤滑油入口側から径の大きい他方
のギヤに対向する潤滑油出口側に半径方向に傾斜状に形
成されているので、前記主軸及び前記ギヤの回転時に
は、潤滑油は遠心力によって他方のギヤの軸受への供給
が促進される。At this time, the oil groove is formed in a radial inclination from the lubricating oil inlet side facing one gear having a smaller diameter disposed on the main shaft to the lubricating oil outlet side facing the other gear having a larger diameter. Therefore, when the main shaft and the gear rotate, the supply of the lubricating oil to the bearing of the other gear is promoted by the centrifugal force.

〔実施例〕〔Example〕

以下、第１図及び第２図を参照して、この発明による
変速機の潤滑機構の一実施例を説明する。この変速機の
潤滑機構を組み込んだ歯車変速機は、第３図に示す歯車
変速機と比較して、クラッチハブに油溝を形成した以外
の構成については、両者は全く同一の構成及び機能を有
しているので、同一の部品には同一の符号を付して重複
する説明は省略する。An embodiment of a lubricating mechanism for a transmission according to the present invention will be described below with reference to FIGS. 1 and 2. Compared with the gear transmission shown in FIG. 3, the gear transmission incorporating the lubrication mechanism of this transmission has exactly the same configuration and functions except for the oil groove formed in the clutch hub. Therefore, the same parts are designated by the same reference numerals, and duplicate description will be omitted.

第１図には、この発明による変速機の潤滑機構を組み
込んだ歯車変速機が示されている。この歯車変速機につ
いては、主軸１に形成されたスプライン25とクラッチハ
ブ４に形成されたスプライン24とはスプライン嵌合７
し、主軸１とクラッチハブ４とはトルク伝達状態に構成
されている。クラッチハブ４の内周面に形成されたスプ
ライン24の部位には、クラッチハブ４のボス部スラスト
面の一側面側から他側面側へ軸方向に油溝20が複数個形
成されている。FIG. 1 shows a gear transmission incorporating a lubrication mechanism for a transmission according to the present invention. In this gear transmission, the spline 25 formed on the main shaft 1 and the spline 24 formed on the clutch hub 4 are spline-fitted to each other.
However, the main shaft 1 and the clutch hub 4 are configured to transmit torque. A plurality of oil grooves 20 are axially formed in a portion of the spline 24 formed on the inner peripheral surface of the clutch hub 4 from one side surface of the boss thrust surface of the clutch hub 4 to the other side surface thereof.

これらの油溝20は、径の小さい一方のギヤ２側から径
の大きい他方のギヤ３側に向かって溝の深さが深くなる
ように傾斜状に形成されている。即ち、ギヤ２側の油溝
20の深さH1は、ギヤ３側の油溝20の深さH2より浅く形成
されている（即ち、H2＞H1）。しかも、ギヤ２側の油溝
20の幅W1は、ギヤ３側の油溝20の幅W2より狭く形成され
（即ち、W2＞W1）、油溝20の幅はギヤ２側からギヤ３側
へ段々に広く形成されている）。These oil grooves 20 are formed in an inclined shape so that the depth of the grooves increases from the one gear 2 side having the smaller diameter to the other gear 3 side having the larger diameter. That is, the oil groove on the gear 2 side
The depth H 1 of 20 is formed shallower than the depth H 2 of the oil groove 20 on the gear 3 side (that is, H 2 > H 1 ). Moreover, the oil groove on the gear 2 side
The width W 1 of 20 is narrower than the width W 2 of the oil groove 20 on the gear 3 side (that is, W 2 > W 1 ), and the width of the oil groove 20 is gradually widened from the gear 2 side to the gear 3 side. Has been).

従って、径の小さい一方のギヤ２と噛合っている径の
大きいギヤ14によってかき上げられた潤滑油16は、ギヤ
２とギヤ21の間の比較的に大きい隙間L1を通ってギヤ２
を回転自在に支持する軸受５を通過し、次いで油溝20の
径の小さい一方のギヤ２と対向する入口側へ供給され
る。Therefore, the lubricating oil 16 scraped up by the large diameter gear 14 meshing with the small diameter gear 2 passes through the relatively large gap L 1 between the gear 2 and the gear 21 and the gear 2
Is passed through a bearing 5 that rotatably supports the oil, and is then supplied to the inlet side facing one gear 2 having a smaller diameter of the oil groove 20.

これらの油溝20に供給された潤滑油は、油溝20が徐々
に大きくなる油路として形成されているので、遠心力に
よって供給状態を促進され、油溝20を通過してギヤ３を
回転自在に支持する軸受６を潤滑し、次いでギヤ３と隣
接する軸受19、及び該軸受19とギヤ３との間に配設され
たスラスト軸受18を潤滑する。The lubricating oil supplied to these oil grooves 20 is formed as an oil passage in which the oil groove 20 gradually increases, so that the supply state is promoted by centrifugal force, and the gear 3 passes through the oil groove 20 to rotate the gear 3. The bearing 6 which is freely supported is lubricated, and then the bearing 19 adjacent to the gear 3 and the thrust bearing 18 arranged between the bearing 19 and the gear 3 are lubricated.

それ故に、ギヤ３と該ギヤ３に隣接する変速機ケース
22との間の隙間L2が形成され、潤滑油の供給が厳しい被
潤滑部位が構成されていたとしても、また、ギヤ３に常
時噛合する副軸11のギヤ15が変速機ケース内の潤滑油16
に接触しないため、潤滑油16がかき上げられない状態が
生じても、潤滑油16はクラッチハブ４に形成された油溝
20を通じて上記の被潤滑部位に十分な潤滑油16を供給す
ることができる。Therefore, the gear 3 and the transmission case adjacent to the gear 3
Even if a gap L 2 with respect to 22 is formed and a lubricated portion where the supply of lubricating oil is severe is formed, the gear 15 of the auxiliary shaft 11 that constantly meshes with the gear 3 is lubricated in the transmission case. Oil 16
Since the lubricant oil 16 does not come into contact with the oil groove 16 even if the lubricant oil 16 cannot be lifted up,
Sufficient lubricating oil 16 can be supplied to the above-mentioned lubricated portion through 20.

〔発明の効果〕〔The invention's effect〕

この発明による変速機の潤滑機構は、上記のように構
成され、次のような効果を有する。The lubrication mechanism of the transmission according to the present invention is configured as described above and has the following effects.

この変速機の潤滑機構は、主軸にスプライン嵌合した
クラッチハブ、前記主軸に各軸受を介して前記クラッチ
ハブの両側面に回転可能に配置した各ギヤ、及び前記主
軸と前記各ギヤとをトルク伝達状態に作動する各同期装
置を有し、前記軸受の側面に対向する前記クラッチハブ
内周のスプライン部に軸方向に貫通する油溝を形成し、
前記軸受の一方に供給された潤滑油を前記油溝を通して
前記軸受の他方に供給するように構成したので、例え
ば、ギヤレシオワイド化等によって変速機ケース内の潤
滑油に一方のギヤが当たらなくなり、該ギヤによる潤滑
油のかき上げが不可能になったとしても、或いは構造
上、ギヤに隣接する変速機ケースとの間の隙間が小さ
く、潤滑油の供給が厳しい被潤滑部位であったとして
も、他の一方のギヤの軸受に供給された潤滑油を前記油
溝を通して潤滑油の供給が厳しいギヤ側の軸受にスムー
スに且つ確実に供給することができる。The lubrication mechanism of the transmission includes a clutch hub spline-fitted to a main shaft, gears rotatably arranged on both sides of the clutch hub through bearings on the main shaft, and a torque between the main shaft and each gear. An oil groove that penetrates in the axial direction is formed in a spline portion of the inner circumference of the clutch hub facing each side surface of the bearing.
Since the lubricating oil supplied to one of the bearings is configured to be supplied to the other of the bearings through the oil groove, for example, one gear does not hit the lubricating oil in the transmission case due to the gear ratio widening, Even if it is impossible to lift up the lubricating oil by the gear, or even if there is a small gap between the gear and the transmission case adjacent to the gear due to the structure, and the lubricating oil is severely supplied to the lubricated portion. The lubricating oil supplied to the bearing of the other gear can be smoothly and surely supplied to the bearing on the gear side where the supply of lubricating oil is severe through the oil groove.

しかも、前記油溝は、前記クラッチハブの内周面のス
プライン部に形成しているので、例えば、トルクが最も
大きくなるような１速段歯車の部位の同期装置に適用し
たとしても、前記主軸に対する強度上の問題は生じな
く、何ら支障がない。Moreover, since the oil groove is formed in the spline portion of the inner peripheral surface of the clutch hub, even if the oil groove is applied to the synchronizer of the portion of the first speed gear that maximizes the torque, the main shaft is not affected. There is no problem in strength with respect to, and there is no problem.

従って、この変速機の潤滑機構は、エンジンの高出
力、高回転化、シンクロ容量のアップ、潤滑油量の低
減、シペース低減によるコンパクト化、ギヤレシオワイ
ド化等に対して十分に対応することができる。Therefore, the lubrication mechanism of this transmission can sufficiently cope with high output of the engine, high rotation, increase of synchro capacity, reduction of lubricating oil amount, compactness due to reduction of space, widening of gear ratio, etc. .

また、前記主軸に配設された各ギヤは径が異なり、該
各ギヤは前記主軸に平行に配設された副軸に支持された
各ギヤと各々噛合しており、前記油溝は前記主軸に配設
された各ギヤの径の小さい一方のギヤに対向する潤滑油
入口側から径の大きい他方のギヤに対向する潤滑油出口
側に半径方向に傾斜状に形成したので、潤滑油量が少な
く前記主軸に配設された径の大きい他方のギヤと噛合う
副軸に支持されたギヤによる潤滑油のかき上げが不可能
になったとしても、主軸に配設された径の小さい一方の
ギヤと噛合う副軸に支持されたギヤによってかき上げら
れた潤滑油が該一方のギヤの軸受けに供給され、この潤
滑油が更に前記油溝を通して他方のギヤの軸受に供給さ
れる。The gears arranged on the main shaft have different diameters, and the gears mesh with the gears supported by a counter shaft arranged in parallel with the main shaft, and the oil groove forms the main shaft. Each of the gears is arranged in the radial direction from the lubricating oil inlet side facing one gear with the smaller diameter to the lubricating oil outlet side facing the other gear with the larger diameter. Even if it becomes impossible to lift up the lubricating oil by the gear supported by the auxiliary shaft that meshes with the other large-diameter gear arranged on the main shaft, Lubricating oil picked up by a gear supported by a counter shaft meshing with the gear is supplied to the bearing of the one gear, and this lubricating oil is further supplied to the bearing of the other gear through the oil groove.

このとき、前記油溝が前記主軸に配設された径の小さ
い一方のギヤに対向する潤滑油入口側から径の大きい他
方のギヤに対向する潤滑油出口側に半径方向に傾斜状に
形成されているので、前記主軸及び前記ギヤの回転時に
は、潤滑油は遠心力によって他方のギヤの軸受への供給
が促進される。At this time, the oil groove is formed in a radial inclination from the lubricating oil inlet side facing one gear having a smaller diameter arranged on the main shaft to the lubricating oil outlet side facing the other gear having a larger diameter. Therefore, when the main shaft and the gear rotate, the supply of the lubricating oil to the bearing of the other gear is promoted by the centrifugal force.

【図面の簡単な説明】[Brief description of drawings]

第１図はこの発明による変速機の潤滑機構の一実施例を
示す断面図、第２図は第１図の変速機の潤滑機構におけ
るクラッチハブの一部を示す側面図、第３図は従来の歯
車変速機の一例を示す断面図、第４図は従来の潤滑機構
の一例を示す斜視図、第５図は従来の潤滑機構の別の例
を示す斜視図、及び第６図は従来の潤滑機構の更に別の
例を示す斜視図である。 １……主軸、2,3……ギヤ、４……クラッチハブ、5,6…
…軸受、７……スプライン嵌合、10……同期装置、11…
…副軸、14,15……副軸のギヤ、16……潤滑油、17……
スリーブ、18……スラスト軸受、19……軸受、20……油
溝、21……隣接のギヤ、22……変速機ケース、H1、H2…
…油溝の深さ、L1、L2……隙間。FIG. 1 is a sectional view showing an embodiment of a lubricating mechanism for a transmission according to the present invention, FIG. 2 is a side view showing a part of a clutch hub in the lubricating mechanism for a transmission of FIG. 1, and FIG. FIG. 4 is a sectional view showing an example of a gear transmission of FIG. 4, FIG. 4 is a perspective view showing an example of a conventional lubrication mechanism, FIG. 5 is a perspective view showing another example of a conventional lubrication mechanism, and FIG. It is a perspective view which shows another example of a lubrication mechanism. 1 ... spindle, 2,3 ... gear, 4 ... clutch hub, 5,6 ...
… Bearings, 7… Spline fitting, 10… Synchronizer, 11…
… Sub shaft, 14,15 …… Gear of sub shaft, 16 …… Lubricant, 17 ……
Sleeve 18 ...... thrust bearing, 19 ...... bearing, 20 ...... oil groove, 21 ...... adjacent gears, 22 ...... transmission case, H 1, H 2 ...
… Oil groove depth, L 1 , L 2 … Gap.

Claims (2)

【特許請求の範囲】[Claims] 【請求項１】主軸にスプライン嵌合したクラッチハブ、
前記主軸に各軸受を介して前記クラッチハブの両側面に
回転可能に配置した各ギヤ、及び前記主軸と前記各ギヤ
とをトルク伝達状態に作動する各同期装置を有し、前記
軸受の側面に対向する前記クラッチハブ内周のスプライ
ン部に軸方向に貫通する油溝を形成し、一方の前記軸受
に供給された潤滑油を前記油溝を通して他方の前記軸受
に供給するように構成したことを特徴とする変速機の潤
滑機構。1. A clutch hub having a main shaft spline-fitted,
The main shaft has respective gears rotatably arranged on both side surfaces of the clutch hub via respective bearings, and respective synchronizers for operating the main shaft and the respective gears in a torque transmitting state, and on the side surface of the bearing. An oil groove that penetrates in the axial direction is formed in a spline portion on the inner circumference of the opposing clutch hub, and the lubricating oil supplied to one of the bearings is supplied to the other bearing through the oil groove. Characteristic transmission lubrication mechanism. 【請求項２】前記主軸に径が異なる径の小さいギヤと径
の大きいギヤの径の異なるギヤが配設され、該各ギヤは
前記主軸に平行に配設された副軸に支持されたギヤと各
々噛合し、前記径の小さいギヤと噛合する前記副軸の前
記ギヤによって少なくとも潤滑油がかき上げられ、前記
油溝は前記主軸に配設された前記径の小さいギヤに対向
する潤滑油入口側から前記径の大きいギヤに対向する潤
滑油出口側に半径方向に傾斜状に形成されていることを
特徴とする請求項１に記載の変速機の潤滑機構。2. A main shaft is provided with a small diameter gear having a different diameter and a large diameter gear having a different diameter, and each gear is supported by an auxiliary shaft arranged in parallel with the main shaft. At least lubricating oil is scooped up by the gear of the auxiliary shaft which meshes with the gear having the smaller diameter, and the oil groove is opposed to the gear having the smaller diameter disposed on the main shaft. 2. The lubrication mechanism for a transmission according to claim 1, wherein the lubrication mechanism is formed in an inclined shape in the radial direction from the side to the lubricating oil outlet side facing the gear having the larger diameter.
JP63329433A 1988-12-28 1988-12-28 Lubrication mechanism of transmission Expired - Fee Related JPH0814312B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP63329433A JPH0814312B2 (en) 1988-12-28 1988-12-28 Lubrication mechanism of transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP63329433A JPH0814312B2 (en) 1988-12-28 1988-12-28 Lubrication mechanism of transmission

Publications (2)

Publication Number Publication Date
JPH02176247A JPH02176247A (en) 1990-07-09
JPH0814312B2 true JPH0814312B2 (en) 1996-02-14

Family

ID=18221325

Family Applications (1)

Application Number Title Priority Date Filing Date
JP63329433A Expired - Fee Related JPH0814312B2 (en) 1988-12-28 1988-12-28 Lubrication mechanism of transmission

Country Status (1)

Country Link
JP (1) JPH0814312B2 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2763986B2 (en) * 1992-04-27 1998-06-11 株式会社クボタ Synchromesh clutch lubrication system
DE102004031470A1 (en) * 2004-06-30 2006-01-26 Zf Friedrichshafen Ag Oil supply
DE102004031471A1 (en) * 2004-06-30 2006-01-26 Zf Friedrichshafen Ag Oil supply
DE102007045368A1 (en) 2007-09-22 2009-04-02 Zf Friedrichshafen Ag Method and device for lubricating the axial starts of idler gears arranged on a shaft
CN116717583B (en) * 2023-08-04 2023-10-27 德力佳传动科技(江苏)股份有限公司 Spline lubricating structure of wind power gear box

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62184257U (en) * 1986-05-16 1987-11-24
JPS6318671U (en) * 1986-07-22 1988-02-06

Also Published As

Publication number Publication date
JPH02176247A (en) 1990-07-09

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