JPH0444929Y2 - - Google Patents
Info
- Publication number
- JPH0444929Y2 JPH0444929Y2 JP1987015088U JP1508887U JPH0444929Y2 JP H0444929 Y2 JPH0444929 Y2 JP H0444929Y2 JP 1987015088 U JP1987015088 U JP 1987015088U JP 1508887 U JP1508887 U JP 1508887U JP H0444929 Y2 JPH0444929 Y2 JP H0444929Y2
- Authority
- JP
- Japan
- Prior art keywords
- helical gear
- gear
- shaft
- pivot
- receiving
- 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
Landscapes
- Sliding-Contact Bearings (AREA)
- General Details Of Gearings (AREA)
Description
【考案の詳細な説明】
〈産業上の利用分野〉
本考案は、固定軸に遊転自在に枢支したはすば
歯車の遊転枢支部へ潤滑油を圧送する潤滑装置に
関し、はすば歯車の傾きによる遊転枢支部の片当
り箇所へ潤滑油を十分に供給できるようにする技
術である。[Detailed description of the invention] <Industrial application field> The present invention relates to a lubricating device that pumps lubricating oil to the free-rotating pivot of a helical gear that is freely rotatably supported on a fixed shaft. This technology enables a sufficient supply of lubricating oil to the uneven contact points of the free rotation pivot due to the inclination of the gear.
〈従来の技術〉
はすば歯車は、例えばアイドルギヤなどとして
固定軸に遊転自在に枢支されて用いられる場合が
ある。この場合、その遊転枢支部を潤滑するため
の基本的な構造が次のようになつているものがあ
る。<Prior Art> A helical gear is sometimes used as, for example, an idle gear, which is rotatably supported on a fixed shaft. In this case, the basic structure for lubricating the free rotation pivot is as follows.
例えば第１図と第３図、又は第８図で示すよう
に、固定軸１６の枢支軸部１８にはすば歯車１５
のボス孔２７を遊嵌し、はすば歯車１５の斜歯で
伝動力を受けることにより生じた軸方向分力で傾
斜するはすば歯車１５のボス孔２７の内周面２８
両端部２８ａ，２８ｂを、枢支軸部１８両端の各
片当り受止軸部３５，３６で片当り状に受止め、
枢支軸部１８とボス孔２７との軸受隙間２１ａに
潤滑油を案内する給油孔２９を固定軸１６内に形
成して構成したものである。 For example, as shown in FIGS. 1 and 3 or 8, a helical gear 15 is attached to the pivot shaft 18 of the fixed shaft 16.
The inner circumferential surface 28 of the boss hole 27 of the helical gear 15 is loosely fitted into the boss hole 27 of the helical gear 15 and tilted by the axial component force generated by receiving the transmission force with the diagonal teeth of the helical gear 15.
Both end portions 28a and 28b are received in a one-sided manner by respective one-sided receiving shaft portions 35 and 36 at both ends of the pivot shaft portion 18,
An oil supply hole 29 is formed in the fixed shaft 16 to guide lubricating oil into the bearing gap 21a between the pivot shaft 18 and the boss hole 27.
上記基本構造において、従来では第８図に示す
ように、はすば歯車１５の両端面は、基端側受面
である端面受座２０と、先端側受面であるはすば
歯車位置決め用ワツシヤ２２の歯車受止用端面２
２ａとにより、それぞれ受け止められているが、
いずれの受面もはすば歯車１５の一端面を受止め
るだけのために、単に偏平面に形成されているだ
けであつた。 In the above basic structure, conventionally, as shown in FIG. 8, both end faces of the helical gear 15 have an end face seat 20 which is a base end receiving face and a helical gear positioning face which is a distal end receiving face. Gear receiving end face 2 of washer 22
Although it is accepted by 2a and 2a, respectively,
Each receiving surface was simply formed into a flat surface in order to receive one end surface of the helical gear 15.
〈考案が解決しようとする問題点〉
前記基本構造において、例えば第２図に示すエ
ンジン１の調時歯車組８のアイドルギヤとして前
記はすば歯車１５を用いる場合、このはすば歯車
１５は伝動力により第３図又は第８図において右
倒れに傾けられる。<Problems to be solved by the invention> In the above basic structure, for example, when the helical gear 15 is used as the idle gear of the timing gear set 8 of the engine 1 shown in FIG. Due to the transmission force, it is tilted to the right in FIG. 3 or 8.
即ち、はすば歯車１５は、斜歯を右ねじれに形
成したときには、歯車下部がクランクギヤ１０か
らの伝動力のスラスト方向の分力F1で左方へ押
されるのに対し、歯車上部が動弁カムギヤ１２及
び燃料噴射カムギヤ１４からの各伝動反力のスラ
スト方向の分力F2，F3で右方へ押圧される。そ
の結果、はすば歯車１５は、モーメントを受けて
右倒れ（第３図又は第８図中矢印Ａ）に傾くので
ある。 That is, when the helical gear 15 has helical teeth with a right-handed helix, the lower part of the gear is pushed to the left by the component force F 1 in the thrust direction of the transmission force from the crank gear 10, whereas the upper part of the gear is pushed to the left. It is pushed to the right by thrust direction component forces F 2 and F 3 of each transmission reaction force from the valve train cam gear 12 and the fuel injection cam gear 14 . As a result, the helical gear 15 receives the moment and tilts to the right (arrow A in FIG. 3 or FIG. 8).
これにより、枢支軸部１８の基端部１８ａの外
周面において、その下周部が、ボス孔２７の内周
面２８の基端部２８の下周部を片当り状に受止め
る。このため、軸受隙間２１ａは、基端側の片当
り受止軸部３５に近い下周部では狭くなり、上周
部では広くなる。また、端面受座２０とはすば歯
車１５の基端側端面との間の端面隙間２１ｂも、
この基端側の片当り受止軸部３５に近い下側部で
は狭くなり、上側部では広くなる。 As a result, the lower circumferential portion of the outer circumferential surface of the base end 18a of the pivot shaft portion 18 receives the lower circumferential portion of the proximal end 28 of the inner circumferential surface 28 of the boss hole 27 in a one-sided manner. Therefore, the bearing gap 21a becomes narrower at the lower circumferential portion near the one-sided contact receiving shaft portion 35 on the base end side, and widened at the upper circumferential portion. In addition, the end face gap 21b between the end face seat 20 and the proximal end face of the helical gear 15 is also
It becomes narrower in the lower part near the one-sided contact receiving shaft part 35 on the base end side, and becomes wider in the upper part.
一方、枢支軸部１８の先端部１８ｂの外周面に
おいては、その上周部がボス孔２７の内周面２８
の先端部２８Ｂの上周部を片当り状に受止める。
このため、軸受隙間２１ａは、この先端側の片当
り受止軸部３６に近い上周部では狭くなり、下周
部では広くなる。また、歯車受止用端面２２ａと
はすば歯車１５の先端側端面との間の端面隙間２
１ｃもこの先端側の片当り受止軸部３６に近い上
側では狭くなり、下側部では広くなる。 On the other hand, in the outer circumferential surface of the distal end portion 18b of the pivot shaft portion 18, the upper circumferential portion corresponds to the inner circumferential surface 27 of the boss hole 27.
The upper peripheral part of the tip part 28B is received in a one-sided manner.
Therefore, the bearing gap 21a becomes narrower at the upper circumferential portion near the one-sided contact receiving shaft portion 36 on the distal end side, and becomes wider at the lower circumferential portion. Also, the end face gap 2 between the gear receiving end face 22a and the end face of the helical gear 15 is
1c also becomes narrower at the upper side near the one-sided contact receiving shaft portion 36 on the tip side, and becomes wider at the lower side.
また、従来技術においては、偏平な端面受座２
０とはすば歯車１５の一端面との間の端面隙間２
１ｂも片当り受止軸部３５に近い下側部では狭く
なり、上側部では広くなる。 In addition, in the conventional technology, the flat end face seat 2
End face clearance 2 between 0 and one end face of the helical gear 15
1b also becomes narrower at the lower side near the one-sided contact receiving shaft portion 35, and becomes wider at the upper side.
ところで、給油孔２９を介して軸受隙間２１ａ
の中央部に圧入された潤滑油は、左右両側部へ圧
送されたのち、左右の各端面隙間２１ｂ，２１ｃ
から遠心方向へ押出される。このとき、枢支軸部
１８の基端部１８ａ側においては、潤滑油は、軸
受隙間２１ａの広い上周部、及び端面隙間２１ｂ
の広い上側部を通つて多量に流れるのに対し、各
隙間２１ａ，２１ｂの狭い下周部及び下側部を流
れにくくなる。このため、基端側の片当り受止軸
部３５が潤滑不足となつて偏摩耗し、早期に傷
む。 By the way, through the oil supply hole 29, the bearing gap 21a
The lubricating oil press-fitted into the center of the
is pushed out in the centrifugal direction. At this time, on the base end 18a side of the pivot shaft 18, the lubricating oil is applied to the wide upper circumference of the bearing gap 21a and the end face gap 21b.
While a large amount of water flows through the wide upper side of the gap, it becomes difficult to flow through the narrow lower circumference and lower side of each gap 21a, 21b. For this reason, the uneven contact receiving shaft portion 35 on the proximal end side lacks lubrication and wears unevenly, causing early damage.
一方、枢支軸部１８の先端部１８ｂにおいて
は、潤滑油は、軸受隙間２１ａの広い下周部、及
び先端側の端面隙間２１ｃの広い下側部を通つて
多量に流れるのに対し、各隙間２１ａ，２１ｃの
狭い上周部及び上側部を流れにくくなる。このた
め、先端側の片当り受止軸部３６が潤滑不足とな
つて偏摩耗し、早期に傷む。 On the other hand, in the distal end portion 18b of the pivot shaft portion 18, a large amount of lubricating oil flows through the wide lower peripheral portion of the bearing gap 21a and the wide lower side portion of the end face gap 21c on the distal end side. It becomes difficult to flow through the narrow upper periphery and upper side of the gaps 21a and 21c. For this reason, the uneven contact receiving shaft portion 36 on the tip side lacks lubrication and wears unevenly, causing early damage.
本考案は、軸受隙間が狭められた片当り受止軸
部に潤滑油を十分に供給できるようにすることを
目的とする。 The object of the present invention is to enable a sufficient supply of lubricating oil to a one-sided bearing shaft portion with a narrowed bearing gap.
〈問題点を解決するための手段〉
本考案は、上記目的を達成するために、前述の
基本構造に次の改良を加えたものである。<Means for Solving the Problems> In order to achieve the above object, the present invention adds the following improvements to the above-mentioned basic structure.
例えば第１図から第５図に示すように、はすば
歯車１５の両端面をそれぞれ受止める基端側受面
２０と先端側受面２２ａとを枢支軸部１８に回転
不能に設け、この両受面２０，２２ａのうちの少
なくともいずれか一方に通油溝３７，３８を横断
状に形成し、この通油溝３７，３８を形成した受
面２０，２２ａの、前記片当り受止軸部３５，３
６よりもはすば歯車１５の回転方向Ｒの少し上手
側部分の位相部分に、上記通油溝３７，３８を位
置させたことを特徴とするものである。 For example, as shown in FIGS. 1 to 5, a proximal side receiving surface 20 and a distal side receiving surface 22a that respectively receive both end surfaces of the helical gear 15 are provided on the pivot shaft 18 in a non-rotatable manner, Oil passage grooves 37, 38 are formed in a transverse shape on at least one of the two receiving surfaces 20, 22a, and the one-sided contact receiving surface of the receiving surfaces 20, 22a on which the oil passage grooves 37, 38 are formed is formed. Shaft portion 35, 3
The oil passage grooves 37 and 38 are located at a phase portion slightly above the rotation direction R of the helical gear 15 than the helical gear 6.
〈作用〉 本考案は次のように作用する。<Effect> The invention works as follows.
枢支軸部１８の各端部１８ａ，１８ｂにおいて
は、潤滑油が軸受隙間２１ａから各受面２０，２
２ａとはすば歯車１５の各端面との間の端面隙間
２１ｂ，２１ｃへ流れ込もうとするときに、この
端面隙間２１ｂ，２１ｃのうちで通油溝３７，３
８を設けた部所が大きな通路断面積に形成されて
いるので、潤滑油は、軸受隙間２１ａから通油溝
３７，３８へ向かつて多量に流れる。 At each end 18a, 18b of the pivot shaft 18, lubricating oil flows from the bearing gap 21a to each bearing surface 20, 2.
2a and each end face of the helical gear 15, when the oil flows into the end face gaps 21b, 21c between the end face of the helical gear 15, the oil passage grooves 37, 3
8 is formed with a large passage cross-sectional area, a large amount of lubricating oil flows from the bearing gap 21a toward the oil passage grooves 37 and 38.
このため、軸受隙間２１ａのうちの片当り受止
軸部３５，３６よりも回転方向Ｒの少し上手側の
部分に潤滑油が多量に供給され、ここからさら
に、ボス孔２７の内周面２８の回転に伴つて片当
り受止軸部３５へ多量に持込まれ、この片当り受
止軸部３５を十分に潤滑する。 Therefore, a large amount of lubricating oil is supplied to a portion of the bearing gap 21a that is slightly above the one-sided contact receiving shaft portions 35 and 36 in the rotational direction R, and from there, the lubricating oil is further supplied to the inner circumferential surface 28 of the boss hole 27. As the shaft rotates, a large amount of the oil is brought into the one-sided contact receiving shaft portion 35, and the one-sided contact receiving shaft portion 35 is sufficiently lubricated.
〈実施例〉 以下、本考案の実施例を図面により説明する。<Example> Embodiments of the present invention will be described below with reference to the drawings.
第１図から第５図はその一実施例で、第１図は
展開斜視図、第２図は立形デイーゼルエンジンの
斜視図、第３図は第２図の−線矢視断面図、
第４図は第３図の−線矢視断面図、第５図は
同第３図の−線矢視断面図である。 FIGS. 1 to 5 show one embodiment of the invention, in which FIG. 1 is an exploded perspective view, FIG. 2 is a perspective view of a vertical diesel engine, and FIG. 3 is a sectional view taken along the - line in FIG.
4 is a sectional view taken along the - line in FIG. 3, and FIG. 5 is a sectional view taken along the - line in FIG. 3.
第２図において、１は立形デイーゼルエンジ
ン、２はシリンダブロツク、３はシリンダヘツド
である。シリンダブロツク２の上部側面に燃料噴
射ポンプ４が固定されるとともに、シリンダヘツ
ド３に複数の燃料噴射器５が固定されている。ま
た、シリンダブロツク前壁２ａからギヤケース７
が突設され、このギヤケース７に、複数のはすば
歯車で構成した調時歯車組８が収容される。 In FIG. 2, 1 is a vertical diesel engine, 2 is a cylinder block, and 3 is a cylinder head. A fuel injection pump 4 is fixed to the upper side surface of the cylinder block 2, and a plurality of fuel injectors 5 are fixed to the cylinder head 3. Also, from the cylinder block front wall 2a to the gear case 7
A timing gear set 8 composed of a plurality of helical gears is housed in the gear case 7.
この調時歯車組８について説明すると、シリン
ダブロツク前壁２ａの下部を貫通してギヤケース
７内にクランク軸９が突出され、その突出端にク
ランクギヤ１０が固定される。また、シリンダブ
ロツク前壁２ａの上部右側を貫通した動弁カム軸
１１に動弁カムギヤ１２が固定されるとともに、
燃料噴射ポンプ４から突出した燃料噴射カム軸１
３に燃料噴射カムギヤ１４が固定される。上記ク
ランクギヤ１０と動弁カムギヤ１２・燃料噴射カ
ム軸１３との間にアイドルギヤ１５が介在され
る。このアイドルギヤ１５はシリンダブロツク前
壁２ａに取付けた固定軸１６で遊転自在に枢支さ
れており、クランクギヤ１０からの動力がアイド
ルギヤ１５を介して動弁カムギヤ１２及び燃料噴
射カムギヤ１４へ伝達される。 To explain the timing gear set 8, a crankshaft 9 protrudes into the gear case 7 through the lower part of the front wall 2a of the cylinder block, and a crank gear 10 is fixed to the protruding end of the crankshaft 9. Further, a valve cam gear 12 is fixed to a valve camshaft 11 passing through the upper right side of the cylinder block front wall 2a, and
Fuel injection camshaft 1 protruding from fuel injection pump 4
A fuel injection cam gear 14 is fixed to 3. An idle gear 15 is interposed between the crank gear 10 and the valve train cam gear 12/fuel injection camshaft 13. This idle gear 15 is rotatably supported by a fixed shaft 16 attached to the front wall 2a of the cylinder block, and power from the crank gear 10 is transmitted through the idle gear 15 to the valve train cam gear 12 and the fuel injection cam gear 14. communicated.
以下、上記アイドルギヤ１５を遊転自在に枢支
するとともに、この遊転枢支部を潤滑するための
構造について、第１図及び第３図から第５図に基
づいて説明する。 Hereinafter, a structure for freely rotating the idle gear 15 and for lubricating this freely rotating support will be explained based on FIGS. 1 and 3 to 5.
固定軸１６は、フランジ部１７とこのフランジ
部１７から突設した枢支軸部１８とからなり、フ
ランジ部１７が複数のボルト１９でシリンダブロ
ツク前壁２ａに固定される。上記枢支軸部１８に
アイドルギヤ１５が遊転自在に支持される。即
ち、枢支軸部１８の基端部１８ａに端面受座２０
が形成されるとともに、先端部１８ｂに位置決め
用ワツシヤ２２が回り止め手段２３を介して固定
される。この回り止め手段２３は、枢支軸部１８
の先端部１８ｂとワツシヤ２２との嵌合面に形成
した回転拘束部２４と、ワツシヤ２２を軸方向に
拘束する止め輪２５とからなる。一方、アイドル
ギヤ１５は、ボス部１５ａ内にブツシユメタル２
６を嵌合固定してなり、このブツシユメタル２６
の内周面に形成したボス孔２７が枢支軸部１８に
遊嵌される。そして、アイドルギヤ１５は、その
一端面を端面受座２０に接当させるとともに、そ
の他端面をワツシヤ２２の歯車受止用端面２２ａ
に接当させることによつて、軸方向の移動を規制
している。 The fixed shaft 16 includes a flange portion 17 and a pivot shaft portion 18 projecting from the flange portion 17, and the flange portion 17 is fixed to the cylinder block front wall 2a with a plurality of bolts 19. An idle gear 15 is freely rotatably supported by the pivot shaft portion 18 . That is, the end face seat 20 is attached to the base end 18a of the pivot shaft 18.
is formed, and a positioning washer 22 is fixed to the distal end portion 18b via a detent means 23. This anti-rotation means 23
It consists of a rotation restraint part 24 formed on the fitting surface between the distal end part 18b and the washer 22, and a retaining ring 25 that restrains the washer 22 in the axial direction. On the other hand, the idle gear 15 has a bushing metal 2 in the boss portion 15a.
6 is fitted and fixed, and this button metal 26
A boss hole 27 formed on the inner circumferential surface of the pivot shaft 18 is loosely fitted into the pivot shaft 18 . The idle gear 15 has one end surface in contact with the end face seat 20, and the other end face in contact with the gear receiving end face 22a of the washer 22.
The movement in the axial direction is regulated by contacting with.
次に、上記アイドルギヤ１５の遊転枢支部を潤
滑するための構造について説明すると、固定軸１
６には、枢支軸部１８とボス孔２７との嵌合面間
に潤滑油を案内する給油孔２９が形成される。即
ち、給油孔２９は、給油孔入口２９ａをシリンダ
ブロツク前壁２ａの送油孔３０に連通させるとと
もに、給油孔出口２９ｂを枢支軸部１８の軸方向
中央部の外周面に開口させている。一方、ブツシ
ユメタル２６において、その内周面２８の中央部
に環状油溝３２が形成される。この環状油溝３２
が給油孔出口２９ｂに連通されている。 Next, the structure for lubricating the free rotating pivot portion of the idle gear 15 will be explained.
6 is formed with an oil supply hole 29 for guiding lubricating oil between the fitting surfaces of the pivot shaft 18 and the boss hole 27. That is, the oil supply hole 29 communicates the oil supply hole inlet 29a with the oil supply hole 30 of the cylinder block front wall 2a, and has the oil supply hole outlet 29b open on the outer circumferential surface of the axially central portion of the pivot shaft portion 18. . On the other hand, in the bush metal 26, an annular oil groove 32 is formed in the center of the inner peripheral surface 28 thereof. This annular oil groove 32
is communicated with the oil supply hole outlet 29b.
上記構成のアイドルギヤ１５は、第２図で示す
ように、クラツチギヤ１０とのかみ合部から後向
きのスラスト力F1が加わるとともに、動弁カム
ギヤ１２及び燃料噴射カムギヤ１４との各かみ合
部から前向きのスラスト反力F2，F3が加わる。
このため、アイドルギヤ１５は、第３図中矢印Ａ
で示すように軸心が下向きに傾く。このように、
アイドルギヤ１５が斜歯で受ける伝動力から生じ
る軸方向分力によつて傾けられた状態において
は、枢支軸部１８の両端部１８ａ，１８ｂがボス
孔２７の内周面２８の両端部２８ａ，２８ｂを片
当り状に受止める。 As shown in FIG. 2, the idle gear 15 having the above configuration is subjected to a rearward thrust force F 1 from the meshing portion with the clutch gear 10 and from each meshing portion with the valve train cam gear 12 and the fuel injection cam gear 14. Forward thrust reaction forces F 2 and F 3 are applied.
For this reason, the idle gear 15 is located at the arrow A in FIG.
The axis is tilted downward as shown in . in this way,
When the idle gear 15 is tilted by the axial component generated from the transmission force received by the diagonal teeth, both ends 18a and 18b of the pivot shaft 18 are aligned with the ends 28a of the inner circumferential surface 28 of the boss hole 27. , 28b in a one-sided manner.
これら両片当り受止軸部３５，３６のうち、枢
支軸部１８の基端部１８ａがボス孔２７の内周面
２８の基端部２８ａを片当り状に受止める箇所に
おいて、その片当り受止軸部３５よりもアイドル
ギヤ１５の回転方向Ｒの少し上手側の位相部分で
端面受座２０に通油溝３７が横断状に形成され
る。また、枢支軸部１８の先端部１８ｂがボス孔
２７の内周面２８の先端部２８ｂを片当り状に受
止める箇所において、その片当り受止軸部３６よ
りもアイドルギヤ１５の回転方向Ｒの少し上手側
の位相部分でワツシヤ２２の歯車受止用端面２２
ａに通油溝３８が横断状に形成される。 Of these two-sided contact receiving shaft portions 35 and 36, the base end portion 18a of the pivot shaft portion 18 receives the base end portion 28a of the inner circumferential surface 28 of the boss hole 27 in a one-sided manner. An oil passage groove 37 is formed in a transverse shape in the end face seat 20 at a phase portion slightly above the contact receiving shaft portion 35 in the rotation direction R of the idle gear 15. Further, at a location where the tip end 18b of the pivot shaft 18 receives the tip 28b of the inner circumferential surface 28 of the boss hole 27 in a one-sided manner, the direction of rotation of the idle gear 15 is lower than that of the one-sided receiving shaft 36. The gear receiving end face 22 of the washer 22 is located at the phase part on the slightly upper side of R.
An oil passage groove 38 is formed in a transverse shape in a.
なお、上記実施例では、アイドルギヤ１５のボ
ス孔２７をブツシユメタル２６の内周面で構成す
るとしたが、このブツシユメタル２６を省略し
て、ボス部１５ａにボス孔２７を直接形成するよ
うにしてもよい。 In the above embodiment, the boss hole 27 of the idle gear 15 is formed from the inner circumferential surface of the bush metal 26, but the bush metal 26 may be omitted and the boss hole 27 may be formed directly in the boss portion 15a. good.
また、第６図と第７図は、上記考案に先立つて
提案した先考案例を示し、第６図は第３図相当図
で、第７図は第６図の−線矢視断面図であ
る。 6 and 7 show an example of an earlier invention proposed prior to the above invention, and FIG. 6 is a view corresponding to FIG. 3, and FIG. 7 is a cross-sectional view taken along the - line in FIG. be.
この先考案例によれば、アイドルギヤ１５の一
端面と端面受座２０との間で枢支軸部１８にワツ
シヤ４０を回転自在に介装するとともに、このワ
ツシヤ４０の端面受座２０側の接当面に複数の通
油溝４１を横断状に形成したので、軸受隙間２１
ａからこれら通油溝４１へ向けて潤滑油を多量に
流すことができる。これに対し、本考案は、軸受
隙間２１ａの狭められた箇所へ潤滑油を集中的に
供給できる点で優れる。 According to the previous example, the washer 40 is rotatably interposed on the pivot shaft portion 18 between one end face of the idle gear 15 and the end face seat 20, and the washer 40 is connected to the end face seat 20 side. Since a plurality of oil passage grooves 41 are formed in a transverse shape for the time being, the bearing gap 21
A large amount of lubricating oil can flow toward these oil passage grooves 41 from a. In contrast, the present invention is superior in that lubricating oil can be supplied intensively to the narrowed portion of the bearing gap 21a.
〈考案の効果〉
本考案は、上記のように構成され作用すること
から次の効果を奏する。<Effects of the invention> Since the present invention is constructed and operates as described above, it has the following effects.
枢支軸部の各端部においては、潤滑油が軸受隙
間から端面隙間へ流れ込もうとするときに、この
端面隙間のうちで通油溝を設けた部所が大きな通
路断面積に形成されているので、潤滑油は、軸受
隙間から通油溝へ向かつて多量に流れる。 At each end of the pivot shaft, when lubricating oil attempts to flow from the bearing gap to the end gap, the portion of the end gap where the oil passage groove is provided is formed with a large passage cross-sectional area. Therefore, a large amount of lubricating oil flows from the bearing gap toward the oil passage groove.
このため、軸受隙間のうちの片当り受止軸部よ
りも回転方向の少し上手側の部分に潤滑油が多量
に供給され、ここからさらに、ボス孔の内周面の
回転に伴つて片当り受止軸部へ多量に持込まれ、
この片当り受止軸部を十分に潤滑する。 For this reason, a large amount of lubricating oil is supplied to a portion of the bearing gap that is slightly upstream in the rotational direction from the partial contact receiving shaft part, and from there, as the inner peripheral surface of the boss hole rotates, the partial contact occurs. A large amount is brought into the receiving shaft,
Sufficiently lubricate this one-sided support shaft.
しかも、上記効果は、はすば歯車の両端面をそ
れぞれ受止める基端側受面と先端側受面とを枢支
軸部に回転不能に設け、この受面の少なくともい
ずれか一方に通油溝を形成するだけで達成され、
別途の部品を付加する必要がないので、潤滑装置
を簡素な構造にして安価につくることができる。 Moreover, the above effect is obtained by providing a base end bearing surface and a distal end bearing surface that respectively receive both end surfaces of the helical gear in a non-rotatable manner on the pivot shaft, and allowing oil to flow through at least one of these bearing surfaces. Achieved by simply forming a groove,
Since there is no need to add additional parts, the lubricating device can be manufactured with a simple structure and at low cost.
第１図から第５図は本考案の一実施例を示し、
第１図は展開斜視図、第２図は立形デイーゼルエ
ンジンの斜視図、第３図は第２図の−線矢視
断面図、第４図は第３図の−線矢視断面図、
第５図は同第３図の−線矢視断面図で、第６
図と第７図は先考案例を示し、第６図は第３図相
当図、第７図は第６図の−線矢視断面図で、
第８図は従来例を示す第３図相当図である。
１５……はすば歯車（アイドルギヤ）、１６…
…固定軸、１８……枢支軸部、１８ａ……基端
部、２０……基端側受面（端面受座）、２１ａ…
…軸受隙間、２２ａ……先端側受面（ワツシヤの
歯車受止用端面）、２７……ボス孔、２８……内
周面、２８ａ……内周面の基端部、２８ｂ……内
周面の先端部、２９……給油孔、３５……基端側
の片当り受止軸部、３６……先端側の片当り受止
軸部、３７……基端側の通油溝、３８……先端側
の通油溝、Ｒ……はすば歯車の回転方向。
1 to 5 show an embodiment of the present invention,
FIG. 1 is an exploded perspective view, FIG. 2 is a perspective view of a vertical diesel engine, FIG. 3 is a sectional view taken along the - line in FIG. 2, and FIG. 4 is a sectional view taken in the direction shown in FIG.
Figure 5 is a sectional view taken along the - line in Figure 3;
7 and 7 show an example of the previous design, FIG. 6 is a view corresponding to FIG. 3, and FIG. 7 is a cross-sectional view taken along the - line in FIG.
FIG. 8 is a diagram corresponding to FIG. 3 showing a conventional example. 15...Helical gear (idle gear), 16...
...Fixed shaft, 18...Pivot shaft portion, 18a...Proximal end portion, 20...Proximal side receiving surface (end surface receiving seat), 21a...
...Bearing gap, 22a...Tip side receiving surface (gear receiving end surface of washer), 27...Boss hole, 28...Inner circumferential surface, 28a...Base end of inner circumferential surface, 28b...Inner circumference Tip of surface, 29...Oil supply hole, 35...One-stop receiving shaft portion on the proximal end side, 36...One-stop receiving shaft portion on the distal end side, 37...Oil passage groove on the proximal end side, 38 ...Oil groove on the tip side, R...Rotation direction of helical gear.
Claims (1)
ボス孔２７を遊嵌し、 はすば歯車１５の斜歯で伝動力を受けることに
より生じた軸方向分力で傾斜するはすば歯車１５
のボス孔２７の内周面２８両端部２８ａ，２８ｂ
を、枢支軸部１８両端の各片当り受止軸部３５，
３６で片当り状に受止め、 枢支軸部１８とボス孔２７との軸受隙間２１ａ
に潤滑油を案内する給油孔２９を固定軸１６内に
形成して構成したはすば歯車の遊転枢支部への圧
送式潤滑装置において、 はすば歯車１５の両端面をそれぞれ受止める基
端側受面２０と先端側受面２２ａとを上記枢支軸
部１８に回転不能に設け、 上記両受面２０，２２ａのうちの少なくともい
ずれか一方に通油溝３７，３８を横断状に形成
し、 この通油溝３７，３８を形成した受面２０，２
２ａの、前記片当り受止軸部３５，３６よりもは
すば歯車１５の回転方向Ｒの少し上手側部分の位
相部分に、上記通油溝３７，３８を位置させたこ
とを特徴とするはすば歯車の遊転枢支部への圧送
式潤滑装置。[Claims for Utility Model Registration] The boss hole 27 of the helical gear 15 is loosely fitted into the pivot shaft 18 of the fixed shaft 16, and the shaft is generated by receiving the transmission force with the helical teeth of the helical gear 15. Helical gear 15 that tilts due to directional force
Both ends 28a, 28b of the inner peripheral surface 28 of the boss hole 27
, each one-piece receiving shaft portion 35 at both ends of the pivot shaft portion 18,
36 in a one-sided manner, and the bearing gap 21a between the pivot shaft portion 18 and the boss hole 27
In a pressure-feeding type lubrication device for an idling pivot portion of a helical gear, which is constructed by forming an oil supply hole 29 in the fixed shaft 16 to guide lubricating oil, bases that respectively receive both end faces of the helical gear 15 are used. An end side bearing surface 20 and a tip side bearing surface 22a are non-rotatably provided on the pivot shaft 18, and oil passage grooves 37, 38 are provided in a transverse shape in at least one of the two bearing surfaces 20, 22a. The receiving surfaces 20, 2 with the oil passage grooves 37, 38 formed thereon.
2a, the oil passage grooves 37 and 38 are located at a phase portion of the helical gear 15 slightly above the rotational direction R of the helical gear 15 than the one-sided contact receiving shaft portions 35 and 36. A pressure-feeding lubrication device for the idling pivot of helical gears.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1987015088U JPH0444929Y2 (en) | 1987-02-03 | 1987-02-03 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1987015088U JPH0444929Y2 (en) | 1987-02-03 | 1987-02-03 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS63123861U JPS63123861U (en) | 1988-08-11 |
| JPH0444929Y2 true JPH0444929Y2 (en) | 1992-10-22 |
Family
ID=30805695
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1987015088U Expired JPH0444929Y2 (en) | 1987-02-03 | 1987-02-03 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0444929Y2 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003090201A (en) * | 2001-09-18 | 2003-03-28 | Yanmar Co Ltd | Lubricating oil supply device for engine |
| JP5040856B2 (en) * | 2008-08-21 | 2012-10-03 | 日産自動車株式会社 | Lubricating oil supply device for fuel pump |
| CN102312988A (en) * | 2011-08-25 | 2012-01-11 | 奇瑞汽车股份有限公司 | Chain wheel with double driving ends and engine oil pump assembled with chain wheel |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58138815U (en) * | 1982-03-16 | 1983-09-19 | 川崎重工業株式会社 | crankshaft |
| JPS5922356U (en) * | 1982-07-31 | 1984-02-10 | 日野自動車株式会社 | Air compressor drive gear device |
| JPS6215089A (en) * | 1985-07-15 | 1987-01-23 | 株式会社日立製作所 | Robot wrist motion detection device |
-
1987
- 1987-02-03 JP JP1987015088U patent/JPH0444929Y2/ja not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS63123861U (en) | 1988-08-11 |
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