JPS5828456B2 - Balancer shaft bearing structure - Google Patents
Balancer shaft bearing structureInfo
- Publication number
- JPS5828456B2 JPS5828456B2 JP15204678A JP15204678A JPS5828456B2 JP S5828456 B2 JPS5828456 B2 JP S5828456B2 JP 15204678 A JP15204678 A JP 15204678A JP 15204678 A JP15204678 A JP 15204678A JP S5828456 B2 JPS5828456 B2 JP S5828456B2
- Authority
- JP
- Japan
- Prior art keywords
- side bearing
- oil
- bearing
- load side
- oil supply
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
Abstract
Description
【発明の詳細な説明】 本発明はバランサ軸の軸受部構造に関する。[Detailed description of the invention] The present invention relates to a bearing structure for a balancer shaft.
従来のバランサ軸の構造の1例として、4サイクル直列
4気筒機関の2次バランサ軸について示すと第4図のよ
うになる。As an example of the structure of a conventional balancer shaft, the secondary balancer shaft of a 4-cycle in-line 4-cylinder engine is shown in FIG.
01a、Olbはバランサ軸、02はクランク軸、03
a、03bはバランスウェイトであり、04a、04b
は給油側軸受、05a 、Q5bは負荷側軸受であり、
2次慣性力を平衡させるためバランサ軸01a、01b
はクランク軸02の回転速度ωの2倍の速度2ωで相互
に反対方向に回動する。01a, Olb is the balancer shaft, 02 is the crankshaft, 03
a, 03b are balance weights, 04a, 04b
is the bearing on the oil supply side, 05a and Q5b are the bearing on the load side,
Balancer shafts 01a and 01b are used to balance the secondary inertia force.
rotate in opposite directions at a speed 2ω that is twice the rotational speed ω of the crankshaft 02.
第1図は上記バランサ軸の軸受部構造を拡大して示す断
面図であり、給油側軸受04側のバランサ軸の軸受部径
は負荷側軸受05の軸受部径よりやや大きく、抽出可能
の形状とされている。FIG. 1 is an enlarged sectional view showing the bearing structure of the balancer shaft, and the diameter of the bearing part of the balancer shaft on the oil supply side bearing 04 side is slightly larger than the bearing part diameter of the load side bearing 05, and it has a shape that can be extracted. It is said that
また軸心に沿う油孔09よりそれぞれ半径方向にのびる
油孔06および010が形成されていて、矢印07にて
示す給油は上記油孔06,09,010により負荷側軸
受面に達する。Further, oil holes 06 and 010 are formed extending radially from the oil hole 09 along the axis, and oil supply indicated by arrow 07 reaches the load-side bearing surface through the oil holes 06, 09, 010.
この構成では軸受部径が給油側でやや大きく、しかも回
転はクランク軸の2倍となるので、高速時の遠心力が給
油圧力よりも大きくなり、給油困難となって焼損を起こ
す恐れがある。In this configuration, the diameter of the bearing part is slightly larger on the oil supply side, and the rotation is twice that of the crankshaft, so the centrifugal force at high speeds becomes greater than the oil supply pressure, making oil supply difficult and potentially causing burnout.
本発明の目的は上記の点に着目し、高速時においても確
実に給油可能な軸受部構造を提供することであり、その
特徴とするところは、給油側軸受部の半径方向にのびる
油孔の長さを負荷側軸受部のそれよりも短かくする手段
を備えたことである。The purpose of the present invention is to focus on the above points and to provide a bearing structure that can reliably supply oil even at high speeds.The main feature of this invention is that the oil hole extending in the radial direction of the bearing on the oil supply side is A means for making the length shorter than that of the load side bearing part is provided.
これによって、給油側の油孔に発生する遠心力が小さく
なり、確実な給油が実現される。This reduces the centrifugal force generated in the oil hole on the oil supply side, and ensures reliable oil supply.
以下図面を参照して本発明による実施例につき説明する
。Embodiments of the present invention will be described below with reference to the drawings.
第2図および第3図は本発明による1実施例を示し、第
2図はバランサ軸の給油側軸受部を示す断面図、第3図
は第2図のX−Y線に沿う断面図である。2 and 3 show one embodiment of the present invention, FIG. 2 is a sectional view showing the oil supply side bearing part of the balancer shaft, and FIG. 3 is a sectional view taken along the X-Y line in FIG. 2. be.
従来例と異なる点は給油側軸受部の構造である。The difference from the conventional example is the structure of the bearing on the oil supply side.
図において、バランサ軸の給油側軸受部の径すは第1図
のものと同様に負荷側軸受部の径より大きく、軸体はク
ランクケースより抽出可能である。In the figure, the diameter of the bearing on the oil supply side of the balancer shaft is larger than the diameter of the bearing on the load side, similar to that in Figure 1, and the shaft body can be extracted from the crankcase.
12はバランサ軸の給油側軸受部に形成された凹状溝、
即ち油溝である。12 is a concave groove formed in the oil supply side bearing part of the balancer shaft;
In other words, it is an oil groove.
6は、給油側軸受部においてバランサ軸の軸心に沿って
設けられている油孔より半径方向にのびる油孔で、上記
凹状溝12に連通している。Reference numeral 6 denotes an oil hole that extends in the radial direction from the oil hole provided along the axis of the balancer shaft in the oil supply side bearing portion, and communicates with the concave groove 12.
同油孔6の長さaは適当に調整可能であり、負荷側軸受
部の半径方向にのびる油孔(第1図の010)より短か
くしである。The length a of the oil hole 6 can be adjusted appropriately, and is shorter than the oil hole (010 in FIG. 1) extending in the radial direction of the load side bearing.
上記構成の場合には、給油は矢印07(第1図参照)の
ように流れ、油孔6.軸心に沿って設けられた油孔及び
負荷側軸受部の油孔010を経て、負荷側軸受(第1図
の05)に達する。In the case of the above configuration, oil supply flows as shown by arrow 07 (see FIG. 1), and the oil supply flows through the oil hole 6. It reaches the load-side bearing (05 in FIG. 1) through an oil hole provided along the axis and an oil hole 010 in the load-side bearing.
この場合、給油側軸受部の油孔6の長さaは負荷側軸受
部の油孔010の長さより短かいので、高速の遠心力も
小さく確実に給油することができる。In this case, since the length a of the oil hole 6 of the oil supply side bearing is shorter than the length of the oil hole 010 of the load side bearing, the centrifugal force at high speed is also small and oil can be reliably supplied.
上述のように本発明による場合は次の効果がある。As described above, the present invention has the following effects.
(1)バランサ軸の給油側軸受部の油孔の長さを負荷側
軸受部の油孔の長さより短かくすることにより、高速時
にも確実に給油することができる。(1) By making the length of the oil hole in the oil supply side bearing of the balancer shaft shorter than the length of the oil hole in the load side bearing, oil can be reliably supplied even at high speeds.
(2)負荷側軸受部には、給油圧力より、油孔長さの差
により、遠心油圧の分だけ高い油圧が得られ、特に高速
回転時に有効である。(2) Due to the difference in oil hole length, a higher oil pressure than the oil supply pressure can be obtained in the load-side bearing portion by the amount of centrifugal oil pressure, which is particularly effective during high-speed rotation.
以上の説明は2次バランサ軸について説明したが、1次
バランサ軸についても勿論適用できる。Although the above description has been made regarding the secondary balancer axis, it can of course also be applied to the primary balancer axis.
第1図は従来のバランサ軸の軸受部構造を示す断面図、
第2図は本発明による1実施例のバランサ軸の給油側軸
受部構造を示す断面図、第3図は第2図のX−X線に沿
う断面図、第4図はバランサ軸の構造を示すクランクケ
ースの断面図である。
01・・・バランサ軸、03・・・バランスウェイト、
04・・・給油側軸受、05・・・負荷側軸受、06,
6゜os、oio・・・油孔、12・・・凹状溝。Figure 1 is a sectional view showing the bearing structure of a conventional balancer shaft.
Fig. 2 is a cross-sectional view showing the structure of the bearing on the oil supply side of the balancer shaft according to one embodiment of the present invention, Fig. 3 is a cross-sectional view taken along the line X-X in Fig. 2, and Fig. 4 is a cross-sectional view showing the structure of the balancer shaft. FIG. 3 is a sectional view of the crankcase shown in FIG. 01... Balancer axis, 03... Balance weight,
04...Oil supply side bearing, 05...Load side bearing, 06,
6゜os, oio...oil hole, 12...concave groove.
Claims (1)
って設けられた油孔より半径方向にのびる油孔を有する
バランサ軸において、給油側軸受部を負荷側軸受部より
大径とすると共に負荷側軸受部より小径の凹状溝を設け
、上記給油側軸受部の半径方向にのびる油孔を上記凹状
溝に連通ずることによって該油孔の長さを上記負荷側軸
受部の半径方向にのびる油孔の長さより短かくするよう
に構成したことを特徴とするバランサ軸の軸受部構造。1. In a balancer shaft that has an oil hole extending radially from the oil hole provided along the shaft center in the oil supply side bearing part and the load side bearing part, the diameter of the oil supply side bearing part is made larger than that of the load side bearing part. At the same time, a concave groove having a smaller diameter than the load side bearing is provided, and an oil hole extending in the radial direction of the oil supply side bearing is communicated with the concave groove, so that the length of the oil hole is changed in the radial direction of the load side bearing. A bearing structure of a balancer shaft characterized by being configured to be shorter than the length of an extending oil hole.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP15204678A JPS5828456B2 (en) | 1978-12-11 | 1978-12-11 | Balancer shaft bearing structure |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP15204678A JPS5828456B2 (en) | 1978-12-11 | 1978-12-11 | Balancer shaft bearing structure |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP12903674A Division JPS5155835A (en) | 1974-11-11 | 1974-11-11 | Baransajikuno jikukebukozo |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS552859A JPS552859A (en) | 1980-01-10 |
JPS5828456B2 true JPS5828456B2 (en) | 1983-06-16 |
Family
ID=15531861
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP15204678A Expired JPS5828456B2 (en) | 1978-12-11 | 1978-12-11 | Balancer shaft bearing structure |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS5828456B2 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0625733Y2 (en) * | 1986-05-21 | 1994-07-06 | トヨタ自動車株式会社 | Balance shaft of internal combustion engine |
DE19847652B4 (en) * | 1998-10-15 | 2010-06-24 | Volkswagen Ag | Balance shaft unit for internal combustion engines |
JP6418047B2 (en) * | 2015-04-13 | 2018-11-07 | トヨタ自動車株式会社 | Balance shaft support structure |
-
1978
- 1978-12-11 JP JP15204678A patent/JPS5828456B2/en not_active Expired
Also Published As
Publication number | Publication date |
---|---|
JPS552859A (en) | 1980-01-10 |
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