JPH0474522B2 - - Google Patents
Info
- Publication number
- JPH0474522B2 JPH0474522B2 JP21946388A JP21946388A JPH0474522B2 JP H0474522 B2 JPH0474522 B2 JP H0474522B2 JP 21946388 A JP21946388 A JP 21946388A JP 21946388 A JP21946388 A JP 21946388A JP H0474522 B2 JPH0474522 B2 JP H0474522B2
- Authority
- JP
- Japan
- Prior art keywords
- idle gear
- bearing
- gear
- oil supply
- supply port
- 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
Links
- 239000003921 oil Substances 0.000 claims abstract description 44
- 230000005540 biological transmission Effects 0.000 claims abstract description 18
- 230000002093 peripheral effect Effects 0.000 claims abstract description 15
- 238000005461 lubrication Methods 0.000 claims abstract description 11
- 230000001050 lubricating effect Effects 0.000 claims abstract description 6
- 239000010687 lubricating oil Substances 0.000 claims abstract description 4
- 239000000446 fuel Substances 0.000 description 8
- 238000002347 injection Methods 0.000 description 8
- 239000007924 injection Substances 0.000 description 8
- 238000010586 diagram Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- 238000005086 pumping Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
Landscapes
- Valve-Gear Or Valve Arrangements (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、エンジンの調時ハスバ歯車伝動装置
のアイドルギヤ軸受部圧送式潤滑装置に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a pressure-feed lubricating device for an idle gear bearing of a timing helical gear transmission for an engine.
エンジンの調時ハスバ歯車伝動装置は、周知の
ように、動弁装置の吸排気カム軸や、燃料噴射装
置の燃料噴射カム軸をクランク軸に調時伝動する
ものである。その基本的な構造は、例えばデイー
ゼルエンジンの場合、第5図に示すようになつて
いる。
As is well known, a timing helical gear transmission for an engine transmits the timing of an intake/exhaust camshaft of a valve train or a fuel injection camshaft of a fuel injection device to a crankshaft. The basic structure of a diesel engine, for example, is as shown in FIG.
即ち、エンジン1の調時ハスバ歯車伝動装置2
のクランクギヤ3にアイドルギヤ4を介して調時
伝動ギヤ5,6を噛み合わせ、これらの各ギヤ3
〜6にはハスバ歯車を用い、アイドルギヤ4のボ
ス孔7をアイドルギヤ軸8の軸受周面9に回転自
在に枢支し、アイドルギヤ軸8をエンジン1の固
定壁10に固定したものである。 That is, the timing helical gear transmission 2 of the engine 1
The timing transmission gears 5 and 6 are meshed with the crank gear 3 of the engine via the idle gear 4, and each of these gears 3
- 6 are helical gears, the boss hole 7 of the idle gear 4 is rotatably supported on the bearing peripheral surface 9 of the idle gear shaft 8, and the idle gear shaft 8 is fixed to the fixed wall 10 of the engine 1. be.
調時伝動ギヤ5,6は2枚あり、1枚は動弁ギ
ヤ5、もう1枚は燃料噴射ギヤ6である。ガソリ
ンエンジンの場合、燃料噴射ギヤ5は無い。 There are two timing transmission gears 5 and 6, one of which is the valve gear 5 and the other is the fuel injection gear 6. In the case of a gasoline engine, there is no fuel injection gear 5.
上記伝動装置2において、アイドルギヤ4の軸
受部にオイルを圧送して潤滑する装置は、基本的
には次のようになつている。 In the transmission device 2 described above, the device for lubricating the bearing portion of the idle gear 4 by force feeding it is basically as follows.
例えば第2図、第7図又は第9図に示すよう
に、アイドルギヤ軸8の軸受周面9に圧送式潤滑
装置のオイル供給口11を開口し、潤滑オイルを
圧送式潤滑装置によりオイル給口部11からアイ
ドルギヤ軸8の軸受周面9とアイドルギヤ4のボ
ス孔7との回転嵌合面間12に圧送するように構
成したものである。 For example, as shown in FIG. 2, FIG. 7, or FIG. 9, an oil supply port 11 of a pressure-feeding type lubrication device is opened on the bearing peripheral surface 9 of the idle gear shaft 8, and lubricating oil is supplied by the pressure-feeding type lubrication device. It is configured such that it is fed under pressure from the opening 11 to the space 12 between the rotational fitting surfaces between the bearing circumferential surface 9 of the idle gear shaft 8 and the boss hole 7 of the idle gear 4.
上記アイドルギヤ軸受部の圧送式潤滑装置は、
従来では一般に、第9図に示すように構成されて
いる。
The pressure feed type lubrication device for the idle gear bearing section is as follows:
Conventionally, the configuration is generally as shown in FIG. 9.
すなわち、アイドルギヤ軸8の軸受周面9の軸
方向の中央部にオイル給口部11を開口する。ア
イドルギヤ4のボス孔7の内周面の軸方向の中央
部に円周形の油溝14を形成したものである。 That is, the oil supply port 11 is opened at the center of the bearing peripheral surface 9 of the idle gear shaft 8 in the axial direction. A circumferential oil groove 14 is formed in the axial center of the inner peripheral surface of the boss hole 7 of the idle gear 4.
上記第9図の従来技術では、オイルを充分に圧
送供給しているにも拘わず、アイドルギヤ軸8の
軸受周面9のうち、その周方向の一部でその軸方
向に沿う螺旋状片当り面部分13が現実に偏摩耗
を起こしている。
In the prior art shown in FIG. 9, although the oil is sufficiently pumped and supplied, a part of the bearing peripheral surface 9 of the idle gear shaft 8 in the circumferential direction has a spiral shape along the axial direction. The uneven contact surface portion 13 actually suffers uneven wear.
本発明は、上記偏摩耗の発生原因を解明して、
その偏摩耗を解消する事を課題とする。 The present invention aims to clarify the cause of uneven wear described above, and
The challenge is to eliminate this uneven wear.
まず、偏摩耗の発生原因を解明する。 First, we will clarify the cause of uneven wear.
第6図に示すように、アイドルギヤ4は、クラ
ンクギヤ3とのハスバ噛合いの入力部15で駆動
力による周方向分力f1を右向きに受け、動弁ギヤ
5・燃料噴射ギヤ6との各ハスバ噛合いの出力部
16,17で駆動抵抗による周方向分力f2,f3を
右向きに受ける。これらの周方向分力f1,f2,f3
の合力Fで、アイドルギヤ4が右側へ押しつけら
れる。 As shown in FIG. 6, the idle gear 4 receives a circumferential component force f 1 in the right direction due to the driving force at the input portion 15 in helical mesh with the crank gear 3, and the The output portions 16 and 17 of each helical mesh receive circumferential component forces f 2 and f 3 due to the drive resistance in a rightward direction. These circumferential component forces f 1 , f 2 , f 3
The resultant force F forces the idle gear 4 to the right.
また、第5図に示すように、アイドルギヤ4
は、ハスバ噛合いの入力部15で駆動力による軸
方向分力f11を後ろ向きに受け、ハスバ噛合いの
入力部16,17で駆動抵抗による軸方向分力
f12,f13を前向きに受ける。 Also, as shown in Fig. 5, the idle gear 4
The helical mesh input section 15 receives the axial component force f 11 due to the driving force backwards, and the helical mesh input sections 16 and 17 receive the axial component force due to the driving resistance.
Receive f 12 and f 13 forward.
これらの軸方向分力f11,f12,f13から生ずる偶
力Mで、アイドルギヤ4が前下りに傾けられる。 The idle gear 4 is tilted forward and downward by the force couple M generated from these axial component forces f 11 , f 12 , and f 13 .
アイドルギヤ4が上記のように合力Fで右側へ
押付けられながら、偶力Mで前だおれに傾けられ
ることにより、アイドルギヤ軸8の軸受周面9の
うち、その左側面部分でその軸方向に沿う前下り
螺旋状片当り部分13に、アイドルギヤ4のボス
孔7の内周面が押しつけられる。 As the idle gear 4 is pushed to the right side by the resultant force F as described above and tilted forward by the force couple M, the left side surface portion of the bearing circumferential surface 9 of the idle gear shaft 8 is pushed in the axial direction. The inner circumferential surface of the boss hole 7 of the idle gear 4 is pressed against the front downward spiral piece contact portion 13 along the front downward spiral piece.
アイドルギヤ4のボス孔7とアイドルギヤ軸8
の軸受周面9との回転嵌合面間12の隙間は、螺
旋状片当り面部分13で塞さがれ、ここから周方
向に遠ざかるにつれて大きくなる。 Boss hole 7 of idle gear 4 and idle gear shaft 8
A gap 12 between the rotational fitting surface 9 and the bearing circumferential surface 9 is closed by the spiral piece abutting surface portion 13, and increases as the distance from this portion in the circumferential direction increases.
オイルはオイル供給口11から円周形油溝14
を通つて、前記回転嵌合面間12へ圧送される。
そのオイルは、回転嵌合面間12のうち、螺旋状
片当り部分13とは反対側の隙間の大きい部分を
通つて外部へ簡単に漏れ出す。このため、隙間が
塞がれた螺旋状片当り面部分13は、オイルが殆
ど供給されず、偏摩耗を起すことになるのであ
る。 Oil flows from the oil supply port 11 to the circumferential oil groove 14
through the rotary mating surfaces 12.
The oil easily leaks to the outside through a large gap between the rotating fitting surfaces 12 on the side opposite to the spiral piece abutting portion 13. For this reason, the spiral piece abutting surface portion 13 whose gap is closed is hardly supplied with oil, resulting in uneven wear.
本発明は、以上の偏摩耗の発生原因において、
オイルが回転嵌合面間12のうちの隙間の大きい
部分を通つて外部へ簡単に漏れ出すことを無くす
ことにより、螺旋状片当り面部分13にオイルを
充分に供給できるようにするものである。 The present invention solves the above causes of uneven wear.
By preventing oil from easily leaking to the outside through the part with a large gap between the rotating fitting surfaces 12, a sufficient amount of oil can be supplied to the helical piece abutting surface part 13. .
そのために、例えば第1図乃至第4図、又は第
7図及び第8図に示すように、アイドルギヤ軸8
の軸受周面9のうち、その周方向の一部でその軸
方向に沿う螺旋状片当り面部分13に、回転伝動
中のアイドルギヤ4のボス孔7の内周面が押し付
けられ、アイドルギヤ軸8の軸受周面9のうち、
螺旋状片当り面部分13よりもアイドルギヤ4の
回転方向の少し上手側の周面部分において、螺旋
状片当り面部分13の長さ方向に沿わせてオイル
供給口11を開口した事を特徴とするものであ
る。 For this purpose, as shown in FIGS. 1 to 4 or 7 and 8, for example, the idle gear shaft 8
The inner circumferential surface of the boss hole 7 of the idle gear 4 during rotation transmission is pressed against the spiral piece abutting surface portion 13 of the bearing circumferential surface 9 along the axial direction in a part of the circumferential direction of the bearing circumferential surface 9, and the idle gear Of the bearing peripheral surface 9 of the shaft 8,
It is characterized in that the oil supply port 11 is opened along the length direction of the spiral piece contact surface portion 13 in a peripheral surface portion slightly above the spiral piece contact surface portion 13 in the rotational direction of the idle gear 4. That is.
オイル供給口11を螺旋状片当り面部分13の
長さ方向に沿わせて開口する部分の具体的な構造
として、第1図乃至第4図に示すように複数個の
オイル供給口11…を並列状に開口する事、又は
第3図に示すようにオイル供給口11を長溝状に
形成する事が考えられる。 As a specific structure of the portion where the oil supply port 11 is opened along the length direction of the spiral piece contact surface portion 13, as shown in FIGS. 1 to 4, a plurality of oil supply ports 11 are formed. It is conceivable to open the oil supply ports 11 in parallel, or to form the oil supply ports 11 in the form of long grooves as shown in FIG.
本発明の作用を、第3図及び第4図、又は第8
図に基づき説明する。
The effects of the present invention are illustrated in FIGS. 3 and 4 or 8.
This will be explained based on the diagram.
オイルは、回転嵌合面間12のうち、螺旋状片
当り面部分13よりも少し回転上手側部分の隙間
の狭い箇所に、オイル供給口11から圧送され
る。 The oil is fed under pressure from the oil supply port 11 to a part of the rotary fitting surface 12 where the gap is slightly narrower on the upper side of the rotation than the helical piece abutting surface portion 13.
オイルはまず、オイル供給口11から出た所
で、仮想線図18で示すように放射状に圧し出さ
れようとする。 First, at the point where the oil comes out from the oil supply port 11, the oil tends to be forced out radially as shown in the imaginary diagram 18.
次に、放射状に押し出されてきたオイルのう
ち、前端領域部分19のものは前方へ、後端領域
部分20のものは後方へと、破線図で示すように
漏れ出そうとするが、隙間が狭くて漏れ出しにく
い。このため、中間領域部分21のものが前後両
方から圧されてそこにおし止どめられようとす
る。 Next, among the oil that has been pushed out radially, the oil in the front end region 19 tries to leak forward, and the oil in the rear end region 20 tries to leak backward, as shown in the broken line diagram, but there is a gap. It's narrow and doesn't leak easily. For this reason, the intermediate region portion 21 is pressed from both the front and back and tends to be held there.
そして、中間領域部分21のオイルは、回転中
のアイドルギヤ8のボス孔9の内周面に付着し
て、実線図22に示すように螺旋状片当り面部分
13に強力に塗込まれていく。 The oil in the intermediate region 21 adheres to the inner circumferential surface of the boss hole 9 of the rotating idle gear 8 and is strongly applied to the helical piece contact surface 13 as shown in the solid line diagram 22. go.
本発明は、次の効果を奏する。 The present invention has the following effects.
イ 上述のようにして、第4図又は第8図に例示
する中間領域部分21のオイルが、実線図22
で示すように螺旋状片当り面部分13に強力に
塗込まれていくので、螺旋状片当り面部分13
の偏摩耗を強力に防止することができる。B. As described above, the oil in the intermediate region portion 21 illustrated in FIG. 4 or FIG.
As shown in FIG.
It can strongly prevent uneven wear.
ロ しかも、そのために必要な新たな構造は、オ
イル供給口を複数個にするか長溝状にするかだ
けですむので、簡単であり、安価に実施でき
る。Moreover, the new structure required for this purpose is simple and can be implemented at low cost since it only requires a plurality of oil supply ports or a long groove shape.
以下、本発明の実施例を図面に基づき説明す
る。
Embodiments of the present invention will be described below based on the drawings.
◎実施例 1(第1図乃至第5図参照)
第5図は縦形多気筒デイーゼルエンジン1の調
時ハスバ歯車装置2を示す。◎Embodiment 1 (See Figs. 1 to 5) Fig. 5 shows a timing helical gear device 2 of a vertical multi-cylinder diesel engine 1.
クランクギヤ3にアイドルギヤ4を介して動弁
ギヤ5及び燃料噴射ギヤ6が噛み合わされる。こ
れらの各ギヤ3〜6にはバスバ歯車が用いられ
る。 A valve gear 5 and a fuel injection gear 6 are meshed with the crank gear 3 via an idle gear 4. Busbar gears are used for each of these gears 3-6.
第1図及び第2図に示すように、アイドルギヤ
4のボス孔7がアイドルギヤ軸8の軸受周面9に
回転自在に枢支される。アイドルギヤ4はアイド
ルギヤ軸8に座金31及びC形止め輪32で抜止
めされる。アイドルギヤ軸8はボルト33でエン
ジン1のクランクケース10の前壁に固定され
る。 As shown in FIGS. 1 and 2, the boss hole 7 of the idle gear 4 is rotatably supported on the bearing peripheral surface 9 of the idle gear shaft 8. As shown in FIGS. The idle gear 4 is secured to the idle gear shaft 8 by a washer 31 and a C-shaped retaining ring 32. The idle gear shaft 8 is fixed to the front wall of the crankcase 10 of the engine 1 with bolts 33.
第1図乃至第4図は、上記伝動装置2のアイド
ルギヤ4の軸受部の圧送式潤滑装置を示す。 1 to 4 show a pressure feed type lubrication device for the bearing portion of the idle gear 4 of the transmission device 2. As shown in FIG.
アイドルギヤ軸8の軸受周面9に、圧送式潤滑
装置(図示省略)のオイル圧送路の末端のオイル
供給口11が開口される。これにより、潤滑オイ
ルが圧送式潤滑装置の潤滑ポンプ(図示省略)に
より、オイル供給口11からアイドルギヤ軸8の
軸受周面9とアイドルギヤ4のボス孔7との回転
嵌合面間12に圧送されるように構成されてい
る。 An oil supply port 11 at the end of an oil pumping path of a pumping type lubrication device (not shown) is opened in the bearing circumferential surface 9 of the idle gear shaft 8 . As a result, lubricating oil is supplied from the oil supply port 11 to the rotating fitting surface 12 between the bearing circumferential surface 9 of the idle gear shaft 8 and the boss hole 7 of the idle gear 4 by the lubricating pump (not shown) of the pressure-feeding lubrication device. It is configured to be pumped.
クランクギヤ3は右回転、アイドルギヤ4は左
回転動弁ギヤ5及び燃料噴射ギヤ6は右回転す
る。アイドルギヤ軸8の軸受周面9のうち、その
左側面部分でその軸方向に沿う螺旋状片当り面部
分13に、回転伝動中のアイドルギヤ4のボス孔
7の内周面が押し付けられる。 The crank gear 3 rotates to the right, and the idle gear 4 rotates to the left. The valve train gear 5 and the fuel injection gear 6 rotate to the right. The inner circumferential surface of the boss hole 7 of the idle gear 4 during rotational transmission is pressed against the spiral piece abutting surface portion 13 of the bearing circumferential surface 9 of the idle gear shaft 8, which extends along the axial direction on the left side surface portion thereof.
アイドルギヤ軸8の軸受周面9のうち、螺旋状
片当り面部分13よりもアイドルギヤ4の回転方
向の少し上手側の周面部分において、螺旋状片当
り面部分13の長さ方向に沿つて、3個のオイル
供給口11が並列して開口する。 Of the bearing circumferential surface 9 of the idle gear shaft 8, a portion of the circumferential surface slightly above the helical piece abutting surface portion 13 in the rotational direction of the idle gear 4, along the length direction of the helical piece abutting surface portion 13. Thus, three oil supply ports 11 are opened in parallel.
オイル供給口11は、2個・4個又は5個以上
を並設してもよい。 Two, four, or five or more oil supply ports 11 may be arranged in parallel.
なお、第5図において、仮想線図で示すよう
に、油圧作業用の油圧ポンプなどの作業機器34
をエンジン1に付設し、作業機器34の入力用作
業ギヤ35を燃料噴射ギヤ6に噛み合わせて使用
する場合がある。 In addition, in FIG. 5, as shown in a virtual diagram, work equipment 34 such as a hydraulic pump for hydraulic work is
may be attached to the engine 1 and used by meshing the input work gear 35 of the work equipment 34 with the fuel injection gear 6.
この場合には、作業機器34の駆動反力が、ア
イドルギヤ4の燃料噴射ギヤ6側のハスバ噛合い
の出力部17にかかる。このため、このハスバ噛
合いの出力部17及び入力部15が受ける周方向
分力f3,f1及び軸方向分力f13,f11が非常に大きく
なり、螺旋状片当り面部分13は、面圧が極度に
高くなり、オイルぎれで偏摩耗が発生し易くな
る。 In this case, the driving reaction force of the working equipment 34 is applied to the helical mesh output portion 17 of the idle gear 4 on the fuel injection gear 6 side. For this reason, the circumferential component forces f 3 , f 1 and the axial components f 13 , f 11 that the output portion 17 and input portion 15 of the helical mesh receive become extremely large, and the helical piece contact surface portion 13 , surface pressure becomes extremely high, and uneven wear is likely to occur due to oil leakage.
このような場合でも、本発明によれば、前記
〔作用〕及び〔発明の効果〕の項で説明したよう
に、第4図又は第8図に例示する中間領域部分2
1のオイルが、実線図22で示すように螺旋状片
当り面部分13に強力に塗込まれていくので、螺
旋状片当り面部分13の偏摩耗を強力に防止する
ことができる。 Even in such a case, according to the present invention, as explained in the above [Operation] and [Advantageous Effects] sections, the intermediate region portion 2 illustrated in FIG. 4 or FIG.
Since the oil of No. 1 is strongly applied to the helical piece abutment surface portion 13 as shown in the solid line diagram 22, uneven wear of the helical piece abutment surface portion 13 can be strongly prevented.
◎実施例 2(第7図及び第8図参照)
この実施例2では、上記実施例1(第1図〜第
6図)の構造の一部を、次のように変更したもの
である。◎Embodiment 2 (see FIGS. 7 and 8) In this embodiment 2, a part of the structure of the above embodiment 1 (FIGS. 1 to 6) is changed as follows.
第7図及び第8図に示すように、前記オイル供
給口部11を1本の長溝状に形成する。この長溝
状のオイル供給口11は、実施例1の場合と同様
に、アイドルギヤ軸8の軸受周面9のうち、螺旋
状片当り面部分13よりもアイドルギヤ4の回転
方向の少し上手側の周面部分において、螺旋状片
当り面部分13の長さ方向に沿つて走らせたもの
である。 As shown in FIGS. 7 and 8, the oil supply port 11 is formed in the shape of one long groove. As in the case of the first embodiment, this long groove-shaped oil supply port 11 is located on the side of the bearing peripheral surface 9 of the idle gear shaft 8 that is slightly above the spiral piece contact surface portion 13 in the rotational direction of the idle gear 4. The spiral piece runs along the length of the contact surface portion 13 on the circumferential surface portion of the spiral piece.
第1図乃至第6図は本発明の実施例1を示す。
第1図はアイドルギヤ部分の分解斜視図、第2図
は第1図の組立て縦断側面図、第3図は作用説明
のために要部を誇張した第1図の組立縦断正面
図、第4図は作用説明用第2図部の展開図、第
5図は縦形多気筒デイーゼルエンジンの調時ハス
バ歯車伝動装置の斜視図、第6図は第5図の要部
取出し正面図である。第7図及び第8図は本発明
の実施例2を示し、第7図はアイドルギヤ部分の
縦断側面図、第8図は第7図部の展開図であ
る。第9図は従来例のアイドルギヤ部分の縦断側
面図である。
1……エンジン、2……調時ハスバ歯車伝動装
置、3……クランクギヤ、4……アイドルギヤ、
5,6……調時伝動ギヤ、7……ボス孔、8……
アイドルギヤ軸、9……軸受周面、10……固定
壁、11……オイル供給口、12……回転嵌合面
間、13……螺旋状片当り面部分。
1 to 6 show a first embodiment of the present invention.
Fig. 1 is an exploded perspective view of the idle gear portion, Fig. 2 is an assembled longitudinal sectional side view of Fig. 1, Fig. 3 is an assembled longitudinal sectional front view of Fig. 1 with important parts exaggerated for explanation of operation, and Fig. 4 5 is a perspective view of a timing helical gear transmission for a vertical multi-cylinder diesel engine, and FIG. 6 is an exploded front view of the main parts of FIG. 5. Embodiment 2 of the present invention is shown in FIGS. 7 and 8, in which FIG. 7 is a longitudinal cross-sectional side view of the idle gear portion, and FIG. 8 is a developed view of the portion shown in FIG. FIG. 9 is a vertical sectional side view of a conventional idle gear portion. 1... Engine, 2... Timing helical gear transmission, 3... Crank gear, 4... Idle gear,
5, 6... Timing transmission gear, 7... Boss hole, 8...
Idle gear shaft, 9... Bearing peripheral surface, 10... Fixed wall, 11... Oil supply port, 12... Between rotating fitting surfaces, 13... Spiral piece contact surface portion.
Claims (1)
ランクギヤ3にアイドルギヤ4を介して調時伝動
ギヤ5,6を噛み合わせ、これらの各ギヤ3〜6
にはハスバ歯車を用い、アイドルギヤ4のボス孔
7をアイドルギヤ軸8の軸受周面9に回転自在に
枢支し、アイドルギヤ軸8をエンジン1の固定壁
10に固定し、アイドルギヤ軸8の軸受周面9に
圧送式潤滑装置のオイル供給口11を開口し、潤
滑オイルを圧送式潤滑装置によりオイル給口部1
1からアイドルギヤ軸8の軸受周面9とアイドル
ギヤ4のボス孔7との回転嵌合面間12に圧送す
るように構成したエンジンの調時ハスバ歯車伝動
装置のアイドルギヤ軸受部圧送式潤滑装置におい
て、 アイドルギヤ軸8の軸受周面9のうち、その周
方向の一部でその軸方向に沿う螺旋状片当り面部
分13に、回転伝動中のアイドルギヤ4のボス孔
7の内周面が押し付けられ、 アイドルギヤ軸8の軸受周面9のうち、螺旋状
片当り面部分13よりもアイドルギヤ4の回転方
向の少し上手側の周面部分において、螺旋状片当
り面部分13の長さ方向に沿わせてオイル供給口
11を開口した事を特徴とするエンジンの調時ハ
スバ歯車伝動装置のアイドルギヤ軸受部圧送式潤
滑装置。[Scope of Claims] 1 Timing transmission gears 5 and 6 are meshed with the crank gear 3 of the timing helical gear transmission 2 of the engine 1 via the idle gear 4, and each of these gears 3 to 6
Using a helical gear, the boss hole 7 of the idle gear 4 is rotatably supported on the bearing circumferential surface 9 of the idle gear shaft 8, the idle gear shaft 8 is fixed to the fixed wall 10 of the engine 1, and the idle gear shaft An oil supply port 11 of a pressure-feeding type lubrication device is opened on the bearing circumferential surface 9 of 8, and lubricating oil is supplied to the oil supply port 1 by the pressure-feeding type lubrication device.
Pressure-feed lubrication of an idle gear bearing part of an engine timing helical gear transmission device configured to pump lubrication from 1 to a rotating fitting surface 12 between a bearing peripheral surface 9 of an idle gear shaft 8 and a boss hole 7 of an idle gear 4 In the device, the inner periphery of the boss hole 7 of the idle gear 4 during rotation transmission is attached to the spiral piece contact surface portion 13 along the axial direction in a part of the circumferential direction of the bearing peripheral surface 9 of the idle gear shaft 8. The surfaces are pressed against each other, and the spiral piece contact surface portion 13 is pressed against the surface of the bearing peripheral surface 9 of the idle gear shaft 8 at a portion of the peripheral surface slightly above the spiral piece contact surface portion 13 in the rotational direction of the idle gear 4. A pressure-feed lubricating device for an idle gear bearing part of an engine timing helical gear transmission device, characterized in that an oil supply port 11 is opened along the length direction.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP21946388A JPH0267411A (en) | 1988-08-31 | 1988-08-31 | Idle gear bearing force feed type lubricator of timing helical gear transmission in engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP21946388A JPH0267411A (en) | 1988-08-31 | 1988-08-31 | Idle gear bearing force feed type lubricator of timing helical gear transmission in engine |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH0267411A JPH0267411A (en) | 1990-03-07 |
JPH0474522B2 true JPH0474522B2 (en) | 1992-11-26 |
Family
ID=16735826
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP21946388A Granted JPH0267411A (en) | 1988-08-31 | 1988-08-31 | Idle gear bearing force feed type lubricator of timing helical gear transmission in engine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0267411A (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5990122B2 (en) * | 2013-03-21 | 2016-09-07 | 株式会社クボタ | Engine gear transmission |
-
1988
- 1988-08-31 JP JP21946388A patent/JPH0267411A/en active Granted
Also Published As
Publication number | Publication date |
---|---|
JPH0267411A (en) | 1990-03-07 |
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