JPS6234922B2 - - Google Patents
Info
- Publication number
- JPS6234922B2 JPS6234922B2 JP18385080A JP18385080A JPS6234922B2 JP S6234922 B2 JPS6234922 B2 JP S6234922B2 JP 18385080 A JP18385080 A JP 18385080A JP 18385080 A JP18385080 A JP 18385080A JP S6234922 B2 JPS6234922 B2 JP S6234922B2
- Authority
- JP
- Japan
- Prior art keywords
- cooling
- pipe
- oil
- piston
- passage
- 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
- Lubrication Of Internal Combustion Engines (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は内燃機関等のピストン冷却用オイルジ
エツトノズルに関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an oil jet nozzle for cooling a piston of an internal combustion engine or the like.
本発明の目的は、特定形状のノズル穴により、
冷却用のオイル噴射の流量、流速を適切に得ると
共に、気泡を混在することなく、また拡散するこ
となく所定位置に対して噴射させることである。 The purpose of the present invention is to
The objective is to obtain an appropriate flow rate and flow velocity of cooling oil injection, and to inject it to a predetermined position without mixing air bubbles or diffusing.
内燃機関のピストンをオイルジエツトにより冷
却する方法は従来より知られている。その手段の
一例としては第１図に示すように、シリンダ内下
部に上向きの噴出口を有するノズル１を設け、こ
れより噴射される冷却用のオイルジエツトをピス
トン２の下面に開口する通路２ａを介してピスト
ン２の上部断面内に穿設されたドーナツ型のギヤ
ラリー２ｂに供給する構造となつている。このノ
ズル１より噴射されるオイルジエツトは、流量と
流速とが適切であること、オイルジエツト中に気
泡を混在しないこと、さらにオイルジエツトは拡
散されず、適確にピストン２の通路２ａに噴射さ
れるブレイクアツプ圧を有することが有効な冷却
作用を得るための条件である。ここでブレイクア
ツプ圧とはオイルジエツト中に気泡が混在し、ジ
エツトに拡散が生じる圧力を云う。 Methods of cooling the pistons of internal combustion engines using oil jets are known in the art. As an example of this means, as shown in FIG. 1, a nozzle 1 having an upward spout is provided in the lower part of the cylinder, and the cooling oil jet injected from the nozzle is sent through a passage 2a opening on the lower surface of the piston 2. The structure is such that the piston 2 is supplied to a donut-shaped gear rally 2b bored in the upper cross section of the piston 2. The oil jet injected from this nozzle 1 must have an appropriate flow rate and flow velocity, and must not contain air bubbles in the oil jet.Furthermore, the oil jet must not be dispersed and can be properly injected into the passage 2a of the piston 2. Having a certain pressure is a condition for obtaining an effective cooling effect. The breakup pressure here refers to the pressure at which air bubbles are mixed in the oil jet and diffuse into the jet.
ところが、従来一般に用いられているノズル
は、その噴口を単にパイプの先端部を絞り加工し
て細孔としたものや、細孔を穿設したピースをパ
イプの開口端にロー付けしたものであるために、
流量を適切に得ようとすれば流速が不足し、又流
速を適切に得ようとすると流量が不足する相反す
る結果となり、さらに、オイルジエツトの拡散並
びに気泡混在の白濁状となつてブレイクアツプ圧
を適切に得ることが甚だ困難な問題があつて理想
的な冷却作用が得られていないのが現状であつ
た。 However, in the conventional nozzles commonly used, the nozzle is simply formed by drawing the tip of a pipe to create a pore, or a piece with a pore drilled is brazed to the open end of the pipe. for,
If you try to get an appropriate flow rate, the flow rate will be insufficient, and if you try to get an appropriate flow rate, the flow rate will be insufficient, contradictory results.Furthermore, the oil jet will diffuse and become cloudy with air bubbles, which will increase the breakup pressure. At present, it is extremely difficult to obtain an appropriate cooling effect, and an ideal cooling effect cannot be obtained.
本発明はこのような従来の問題を解決すべく研
究の結果、パイプの絞り成形により特定な形状の
ノズル穴とし、前記諸条件の全てを満足したオイ
ルジエツトを得たものである。 The present invention has been made as a result of research to solve these conventional problems, and has resulted in an oil jet that satisfies all of the above conditions by forming a nozzle hole in a specific shape by drawing a pipe.
以下本発明の実施例を図面に基いて説明する。
第２図においては１はノズルパイプであり、矢
視部、すなわち、ノズル穴部を第３図に示す形状
としたものである。 Embodiments of the present invention will be described below based on the drawings.
In FIG. 2, numeral 1 is a nozzle pipe, and the portion seen by the arrow, that is, the nozzle hole portion, has the shape shown in FIG.
ノズルパイプ１の先端部内径を細径のストレー
ト通路部３と、これに連るテーパ状に拡がる開口
端部４とを絞り形成したものである。そして、こ
れらの形状寸法は次の数値に限定される。 The inner diameter of the tip of the nozzle pipe 1 is formed by constricting a small diameter straight passage part 3 and an open end part 4 which is connected to the straight passage part 3 and widens in a tapered shape. These shapes and dimensions are limited to the following numerical values.
ノズルパイプ１の内径をd1とし、ストレート通
路３の内径をd2とし、ストレート通路部３の長さ
をl1とし、さらにストレート通路部３と開口端部
４との全長をl2とした場合、
d2＝（0.35〜0.6）d1
l2＝（２〜４）d2
l1＝0.5l2以上
である。また従来のパイプを切断したノズルや、
細孔を穿設したピースを用いる場合には開口部に
バリが生じ、これがブレイクアツプ圧を低下させ
る一要因になつていることが判明した。これを防
止するために開口部を１〜５゜のテーパ状にする
ことにより、ブレイクアツプ圧の低下を防止する
ことが出来ることが明らかになつた。斯る数値の
関係により流量、流速及びブレイクアツプ圧が適
切に得られ、前記従来の問題点の全てを解決した
オイルジエツトが得られるのである。 The inner diameter of the nozzle pipe 1 is d 1 , the inner diameter of the straight passage 3 is d 2 , the length of the straight passage 3 is l 1 , and the total length of the straight passage 3 and the open end 4 is l 2 . In this case, d2 =(0.35-0.6) d1l2 = (2-4) d2l1 = 0.5l2 or more . There are also nozzles made by cutting conventional pipes,
It has been found that when a piece with pores is used, burrs are formed at the openings, and this is one of the factors that lowers the breakup pressure. In order to prevent this, it has been found that by making the opening tapered by 1 to 5 degrees, it is possible to prevent the breakup pressure from decreasing. Through this numerical relationship, flow rate, flow velocity, and break-up pressure can be appropriately obtained, and an oil jet that solves all of the above-mentioned conventional problems can be obtained.
そこで、上記数値限定による有効性について実
験結果で得た根拠を第４図〜第６図によつて説明
する。 Therefore, the basis obtained from experimental results regarding the effectiveness of the above-mentioned numerical limitation will be explained with reference to FIGS. 4 to 6.
先ず第４図はノズルパイプ１の内径d1に対する
ストレート通路部３の内径d2の寸法比によるオイ
ルジエツトの流量ｑと流速ｖのデータである。こ
のグラフで明らかなようにd2／d1が0.35〜0.6の数
値の範囲内で流量ｑと流速ｖとは大きな偏差がな
く両者は略調和して適切に得られている。 First, FIG. 4 shows data on the oil jet flow rate q and flow velocity v depending on the dimensional ratio of the inner diameter d 2 of the straight passage section 3 to the inner diameter d 1 of the nozzle pipe 1. As is clear from this graph, within the range of d 2 /d 1 from 0.35 to 0.6, there is no large deviation between the flow rate q and the flow velocity v, and the two are appropriately obtained in approximately harmony.
また、第５図に示すグラフのようにl2／d2は２
〜４の数値範囲で良好なブレークアツプ圧が得ら
れ、第６図に示すグラフのようにl1／l2が0.5以上
の数値でブレイクアツプ圧が良好に得られてい
る。 Also, as shown in the graph shown in Figure 5, l 2 /d 2 is 2
A good break-up pressure is obtained in the numerical value range of -4, and a good break-up pressure is obtained when l 1 /l 2 is a value of 0.5 or more, as shown in the graph shown in FIG.
従つて、上記ノズル穴の形状並びに寸法関係の
限定された数値により流量と流速が適切に得ら
れ、また良好なブレイクアツプ圧によりオイルジ
エツトを拡散並びに気泡を混在した白濁状とする
ことなく理想的な噴射が得られ、ピストンの冷却
作用を向上する利点を有しているものである。 Therefore, the flow rate and flow velocity can be appropriately obtained by the shape of the nozzle hole and the limited numerical values related to the dimensions, and the good breakup pressure allows the oil jet to be ideally diffused without becoming cloudy with air bubbles. This has the advantage of providing injection and improving the cooling effect of the piston.
第１図はピストン冷却機構の一般例を示す断面
図、第２図は本発明によるジエツトノズルの一部
断面側面図、第３図は第２図矢視部分の拡大断
面図、第４図、第５図及び第６図は本発明ジエツ
トノズルの形状寸法限定数値の根拠を説明するグ
ラフである。
１……ノズルパイプ、３……ストレート通路
部、４……テーパ状の開口端部。
Fig. 1 is a sectional view showing a general example of a piston cooling mechanism, Fig. 2 is a partially sectional side view of a jet nozzle according to the present invention, Fig. 3 is an enlarged sectional view of the part shown by the arrow in Fig. 2, Figs. FIGS. 5 and 6 are graphs explaining the basis for limiting the shape and dimensions of the jet nozzle of the present invention. 1...Nozzle pipe, 3...Straight passage section, 4...Tapered opening end.
Claims (1)
ツトを噴射するノズルであつて、パイプの先端部
内径を細径のストレート通路部、このストレート
通路部と連るテーパ状に拡がる開口端部とを絞り
形成し、前記パイプの内径をd1、ストレート通路
の内径をd2、ストレート通路の長さl1及びストレ
ート通路と開口端部との全長をl2とした場合、d2
＝（0.35〜0.6）d1、l2＝（２〜４）d2及びl1≧0.5l2
としたことを特徴とするピストン冷却用ジエツト
ノズル。1 A nozzle that injects a cooling oil jet to the lower surface of the piston, which is formed by narrowing the inner diameter of the tip of the pipe into a narrow straight passage and an open end that expands into a tapered shape connected to the straight passage. If the inner diameter of the pipe is d 1 , the inner diameter of the straight passage is d 2 , the length of the straight passage is l 1 , and the total length of the straight passage and the open end is l 2 , then d 2
= (0.35-0.6) d 1 , l 2 = (2-4) d 2 and l 1 ≧0.5 l 2
A jet nozzle for piston cooling characterized by the following.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18385080A JPS57108408A (en) | 1980-12-26 | 1980-12-26 | Jet nozzle for cooling piston |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18385080A JPS57108408A (en) | 1980-12-26 | 1980-12-26 | Jet nozzle for cooling piston |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS57108408A JPS57108408A (en) | 1982-07-06 |
| JPS6234922B2 true JPS6234922B2 (en) | 1987-07-29 |
Family
ID=16142918
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP18385080A Granted JPS57108408A (en) | 1980-12-26 | 1980-12-26 | Jet nozzle for cooling piston |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS57108408A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19943516B4 (en) * | 1999-09-11 | 2017-01-19 | Schaeffler Technologies AG & Co. KG | nozzle valve |
| US7406941B2 (en) | 2004-07-21 | 2008-08-05 | Federal - Mogul World Wide, Inc. | One piece cast steel monobloc piston |
-
1980
- 1980-12-26 JP JP18385080A patent/JPS57108408A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS57108408A (en) | 1982-07-06 |
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