JPH0115842Y2 - - Google Patents
Info
- Publication number
- JPH0115842Y2 JPH0115842Y2 JP1983164627U JP16462783U JPH0115842Y2 JP H0115842 Y2 JPH0115842 Y2 JP H0115842Y2 JP 1983164627 U JP1983164627 U JP 1983164627U JP 16462783 U JP16462783 U JP 16462783U JP H0115842 Y2 JPH0115842 Y2 JP H0115842Y2
- Authority
- JP
- Japan
- Prior art keywords
- main
- oil
- oil pressure
- valve
- outlet 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
- 238000002485 combustion reaction Methods 0.000 claims description 5
- 239000003921 oil Substances 0.000 description 41
- 239000012208 gear oil Substances 0.000 description 7
- 238000010586 diagram Methods 0.000 description 6
- 244000145845 chattering Species 0.000 description 4
- 230000000694 effects Effects 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
Landscapes
- Safety Valves (AREA)
Description
【考案の詳細な説明】
〔産業上の利用分野〕
本考案は、内燃機関の潤滑油回路における油圧
制御弁装置に関するものである。[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a hydraulic control valve device in a lubricating oil circuit of an internal combustion engine.
内燃機関において、低回転時、高油温時軸受の
摩耗時等を考慮してオイルポンプｂの吐出量は大
きめに決められており、定格回転時はメインギヤ
ラ油圧が高くなりすぎるため、メインギヤラ油圧
で作動する制御弁ａを設けて潤滑油をリリーフ
し、油圧を一定レベルに押えている。
In internal combustion engines, the discharge amount of oil pump b is determined to be large considering the wear of bearings at low speeds, high oil temperatures, etc. At rated speeds, the main gearer oil pressure becomes too high. An operating control valve a is provided to relieve lubricating oil and keep the oil pressure at a constant level.
一方、エンジンが定格回転以上に過回転した場
合には軸受の油温が上昇し、粘度が低下するた
め、多くの油量を軸受へ流し、油温を低下させる
必要がある。 On the other hand, when the engine overspeeds beyond the rated rotation, the oil temperature in the bearing increases and the viscosity decreases, so it is necessary to flow a large amount of oil to the bearing to lower the oil temperature.
なお第１図中ｄはクーラ、ｅはフイルタ、ｆは
軸受部分である。 In FIG. 1, d is a cooler, e is a filter, and f is a bearing part.
そして、従来の制御弁ａは第４図に示すように
リリー穴ｃが一つであつた。 The conventional control valve a had one relief hole c, as shown in FIG.
これに対し、現状は上記した油圧制御弁ａがあ
るため、過回転時にても油圧が上昇せず、焼付き
易い状態となつている。
On the other hand, at present, since there is the above-mentioned hydraulic control valve a, the hydraulic pressure does not increase even when the engine is over-rotated, making it easy to seize.
制御弁ａを廃止すれば第２図に示すように過回
転時に必要な油圧が得られるが、定格点での油圧
が高く、オイルポンプｂの駆動力が増大し燃費が
悪化していた。 If the control valve a is eliminated, the oil pressure necessary for over-speeding can be obtained as shown in FIG. 2, but the oil pressure at the rated point is high, the driving force of the oil pump b increases, and fuel efficiency deteriorates.
第２図中イは必要な油圧、ロは制御弁なしの油
圧、ホは実際の油圧であり、第３図中ハは理想的
な温度、ニは実際の温度を示す。 In Fig. 2, A shows the required oil pressure, B shows the oil pressure without a control valve, E shows the actual oil pressure, C shows the ideal temperature, and D shows the actual temperature in Fig. 3.
本考案は上記の事情に鑑みなされたものであつ
て、その目的とするところはメインギヤラ油圧の
上昇によつてリリーフが二段階になされて定格点
での油圧を一定にコントロールしながら過回転時
の油圧を上げることができ、過回転時の焼付等軸
受関係の不具合を防止することができしかもリリ
ーフ特性が急激に変化せず弁のチヤタリングが防
止できる内燃機関用油圧制御弁装置を提供するこ
とにある。 The present invention was developed in view of the above circumstances, and its purpose is to provide relief in two stages by increasing the main gear oil pressure, and to control the oil pressure at the rated point to a constant level, while at the same time controlling the oil pressure at the rated point. To provide a hydraulic control valve device for an internal combustion engine that can increase oil pressure, prevent bearing-related problems such as seizure during over-speed, and prevent valve chattering without sudden changes in relief characteristics. be.
上記の目的を達成するために本考案は、弁本体
１にオイルパンに通じる第１・第２出口ポート
３，４を設け、弁本体１に、オイルギヤラに通じ
る第１入口ポート２から第１出口ポート３に至る
主通路Ａと第１入口ポート２から第２出口ポート
４に至る主通路Ｂとを設け、弁本体１にメインギ
ヤラ油圧によつてばね７に抗して移動して主通路
Ａ，Ｂを順次開ける弁６を設け、両主通路Ａ，Ｂ
を狭い通路Ｄで連通した構成にしてある。
In order to achieve the above object, the present invention provides the valve body 1 with first and second outlet ports 3 and 4 leading to the oil pan, and the valve body 1 has a first inlet port 2 leading to the oil gearer and a first outlet port 2 leading to the oil gear. A main passage A leading to the port 3 and a main passage B leading from the first inlet port 2 to the second outlet port 4 are provided, and the main passage A, Both main passages A and B are provided with valves 6 that sequentially open passages A and B.
The two are connected through a narrow passage D.
定格時等メインギヤラ圧がP1に達すると弁６
がばね７に抗して移動し、第１０図Ａに示すよう
に第１出口ポート３からのオイルのリリーフを開
始する。したがつてあるメインギヤラ油圧まで一
定油圧となる。
When the main gearer pressure reaches P1 at rated time, valve 6
moves against the spring 7 and begins to relieve oil from the first outlet port 3 as shown in FIG. 10A. Therefore, the oil pressure becomes constant up to a certain main gear oil pressure.
メインギヤラ圧がP2に達すると第１０図Ｂの
ようにリリーフ油圧は一定となる。したがつて、
エンジン回転が上昇すれば油圧は上昇する。 When the main gearer pressure reaches P2 , the relief oil pressure becomes constant as shown in FIG. 10B. Therefore,
As the engine speed increases, the oil pressure increases.
メインギヤラ圧がP3に達すると第２出口ポー
ト４が開き、第１０図Ｃのように再びリリーフを
はじめる。 When the main gearer pressure reaches P3 , the second outlet port 4 opens and relief begins again as shown in Fig. 10C.
また、第１入口ポート２から第１出口ポート３
に至る主通路Ａと第１入口ポート２から第２出口
ポート４に至る主通路Ｂとを狭い通路Ｄで連通す
ることによつてリリーフ特性の急激な変化をなく
し弁６のチヤタリングを防止する。 Also, from the first inlet port 2 to the first outlet port 3
By communicating the main passage A leading from the first inlet port 2 to the second outlet port 4 through a narrow passage D, a sudden change in the relief characteristic is eliminated and chattering of the valve 6 is prevented.
以下、本考案を第５図以下を参照して説明す
る。
Hereinafter, the present invention will be explained with reference to FIG. 5 and subsequent figures.
図面中１は弁本体であり、この弁本体１には第
１・第２入口ポート２，５と第１・第２出口ポー
ト３，４とが設けてある。第１入口ポート２には
オイルギヤラからの油圧が導入され第２入口ポー
ト５にはメインギヤラからの油圧が導入されるも
のである。 Reference numeral 1 in the drawings indicates a valve body, and the valve body 1 is provided with first and second inlet ports 2 and 5 and first and second outlet ports 3 and 4. Hydraulic pressure from an oil gearer is introduced into the first inlet port 2, and oil pressure from a main gearer is introduced into the second inlet port 5.
また、第１入口ポート２から第１出口ポート３
に至る主通路Ａと第１入口ポート２から第２出口
ポート４に至る主通路Ｂとがスリツトより成る狭
い通路Ｄで連通されている。 Also, from the first inlet port 2 to the first outlet port 3
A main passage A extending from the first inlet port 2 to the second outlet port 4 communicates with each other through a narrow passage D formed by a slit.
弁本体１内には弁６が設けてあり、弁６はばね
７により第２入口ポート５側に付勢されていて第
２入口ポート５及び第１、第２出口ポート３，４
を閉塞している。 A valve 6 is provided in the valve body 1, and the valve 6 is biased toward the second inlet port 5 by a spring 7, and is connected to the second inlet port 5 and the first and second outlet ports 3, 4.
is blocked.
しかして、定格時等メインギヤラ圧がP1に達
すると弁６がばね７に抗して移動し、第１０図Ａ
に示すように第１出口ポート３からオイルのリリ
ーフを開始する（第６図参照）。したがつてある
メインギヤラ油圧まで一定油圧となる。 However, when the main gearer pressure reaches P 1 at rated time, the valve 6 moves against the spring 7, and as shown in FIG.
As shown in Fig. 6, oil relief is started from the first outlet port 3 (see Fig. 6). Therefore, the oil pressure becomes constant up to a certain main gear oil pressure.
メインギヤラ圧がP2に達すると第１０図Ｂの
ようにリリーフ油圧は一定となる。したがつて、
エンジン回転が上昇すれば油圧は上昇する（第７
図参照）。 When the main gearer pressure reaches P2 , the relief oil pressure becomes constant as shown in FIG. 10B. Therefore,
As the engine speed increases, the oil pressure increases (7th
(see figure).
メインギヤラ圧がP3に達すると第２出口ポー
ト４が開き、第１０図Ｃのように再びリリーフを
はじめる（第８図参照）。第２出口ポート４は主
に低温始動の時の油圧上昇を防止している。 When the main gearer pressure reaches P3 , the second outlet port 4 opens and relief starts again as shown in Fig. 10C (see Fig. 8). The second outlet port 4 mainly prevents oil pressure from increasing during cold start.
主通路Ａと主通路Ｂとを分離したままだとリリ
ーフ特性が急激に変化するため弁６のチヤタリン
グ（細く動くこと）が発生することがあるが、本
考案の場合、主通路Ａと主通路Ｂとが狭い通路Ｄ
で連通されているのでリリーフ特性が急激に変化
せず弁６のチヤタリングが防止される。 If the main passage A and the main passage B remain separated, the relief characteristics will change rapidly, which may cause the valve 6 to chatter (slow movement), but in the case of the present invention, the main passage A and the main passage B and narrow passage D
Since the relief characteristics do not change suddenly, chattering of the valve 6 is prevented.
本考案は以上詳述したように、弁本体１にオイ
ルパンに通じる第１・第２出口ポート３，４を設
け、弁本体１に、オイルギヤラに通じる第１入口
ポート２から第１出口ポート３に至る主通路Ａと
第１入口ポート２から第２出口ポート４に至る主
通路Ｂととを設け、弁本体１にメインギヤラ油圧
によつてばね７に抗して移動して主通路Ａ，Ｂを
順次開ける弁６を設け、両主通路Ａ，Ｂを狭い通
路Ｄで連通したことを特徴とする内燃機関用油圧
制御弁装置である。
As described in detail above, in the present invention, the valve body 1 is provided with the first and second outlet ports 3 and 4 communicating with the oil pan, and the valve body 1 is provided with the first inlet port 2 and the first outlet port 3 communicating with the oil gear. A main passage A leading from the first inlet port 2 to the second outlet port 4 is provided, and the main passage A, B is moved in the valve body 1 against the spring 7 by the main gear oil pressure This hydraulic control valve device for an internal combustion engine is characterized in that a valve 6 is provided to sequentially open the main passages A and B, and both main passages A and B are communicated through a narrow passage D.
したがつて、定格時等メインギヤラ圧がP1に
達すると弁６がばね７に抗して移動し、第１０図
Ａに示すように第１出口ポート３からオイルのリ
リーフを開始する。したがつてあるメインギヤラ
油圧まで一定油圧となる。 Therefore, when the main gearer pressure reaches P1 , such as at the rated time, the valve 6 moves against the spring 7 and begins to relieve oil from the first outlet port 3, as shown in FIG. 10A. Therefore, the oil pressure becomes constant up to a certain main gear oil pressure.
メインギヤラ圧がP2に達すると第１０図Ｂの
ようにリリーフ油圧は一定となる。したがつて、
エンジン回転が上昇すれば油圧は上昇する。 When the main gearer pressure reaches P2 , the relief oil pressure becomes constant as shown in FIG. 10B. Therefore,
As the engine speed increases, the oil pressure increases.
メインギヤラ圧がP3に達すると第２出口ポー
ト４が開き、第１０図Ｃのように再びリリーフを
はじめる。第２出口ポート４は主に低温始動の時
の油圧上昇を防止している。 When the main gearer pressure reaches P3 , the second outlet port 4 opens and relief begins again as shown in Fig. 10C. The second outlet port 4 mainly prevents oil pressure from increasing during cold start.
このように、メインギヤラ油圧の上昇によつて
リリーフが二段階になされ、このために定格点で
の油圧を一定にコントロールしながら過回転時の
油圧を上げることができ、過回転時の焼付等軸受
関係の不具合を防止するこができる。 In this way, relief is achieved in two stages by increasing the main gear oil pressure, and this makes it possible to increase the oil pressure during over-speed while controlling the oil pressure at the rated point to a constant level. Relationship problems can be prevented.
また、主通路Ａと主通路Ｂとを分離したままだ
とリリーフ特性が急激に変化するため弁６のチヤ
タリング（細く動くこと）が発生することがある
が、本考案の場合、主通路Ａと主通路Ｂとが狭い
通路Ｄで連通されているのでリリーフ特性が急激
に変化せず弁６のチヤタリングが防止できる。 In addition, if the main passage A and the main passage B are kept separated, the relief characteristics will change rapidly, which may cause the valve 6 to chatter (slow movement); however, in the case of the present invention, the main passage A and the main passage B Since the main passage B is communicated with the narrow passage D, the relief characteristic does not change suddenly and chattering of the valve 6 can be prevented.
第１図はエンジン潤滑回路の構成説明図、第２
図はエンジン各部軸受の油圧の線図、第３図は軸
受温度の線図、第４図は従来の制御弁の縦断面
図、第５図は本考案一実施例の縦断面図、第６図
乃至第８図は同作用説明図、第９図はメインギヤ
ラ油圧の線図、第１０図はリリーフ油量の線図、
第１１図は第５図XI方向からの矢視図である。
１は弁本体、３，４は第１・第２出口ポート、
Ａ，Ｂは主通路。
Figure 1 is an explanatory diagram of the configuration of the engine lubrication circuit, Figure 2
Figure 3 is a diagram of oil pressure of bearings in various parts of the engine, Figure 3 is a diagram of bearing temperature, Figure 4 is a vertical cross-sectional view of a conventional control valve, Figure 5 is a vertical cross-sectional view of an embodiment of the present invention, and Figure 6 is a vertical cross-sectional view of an embodiment of the present invention. Figures 8 to 8 are explanatory diagrams of the same operation, Figure 9 is a diagram of main gear oil pressure, Figure 10 is a diagram of relief oil amount,
FIG. 11 is a view taken from the direction of arrow XI in FIG. 1 is the valve body, 3 and 4 are the first and second outlet ports,
A and B are the main passages.
Claims (1)
ポート３，４に設け、弁本体１に、オイルギヤラ
に通じる第１入口ポート２から第１出口ポート３
に至る主通路Ａと第１入口ポート２から第２出口
ポート４に至る主通路Ｂとを設け、弁本体１にメ
インギヤラ油圧によつてばね７に抗して移動して
主通路Ａ，Ｂを順次開ける弁６を設け、両主通路
Ａ，Ｂを狭い通路Ｄで連通したことを特徴とする
内燃機関用油圧制御弁装置。 The valve body 1 is provided with first and second outlet ports 3 and 4 that communicate with the oil pan, and the valve body 1 is provided with a first inlet port 2 and a first outlet port 3 that communicate with the oil gear.
A main passage A leading from the first inlet port 2 to the second outlet port 4 is provided. A hydraulic control valve device for an internal combustion engine, characterized in that a valve 6 that opens sequentially is provided, and both main passages A and B are communicated through a narrow passage D.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16462783U JPS6072909U (en) | 1983-10-26 | 1983-10-26 | Hydraulic control valve device for internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16462783U JPS6072909U (en) | 1983-10-26 | 1983-10-26 | Hydraulic control valve device for internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6072909U JPS6072909U (en) | 1985-05-22 |
| JPH0115842Y2 true JPH0115842Y2 (en) | 1989-05-11 |
Family
ID=30360880
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP16462783U Granted JPS6072909U (en) | 1983-10-26 | 1983-10-26 | Hydraulic control valve device for internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6072909U (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0442552Y2 (en) * | 1986-07-21 | 1992-10-07 | ||
| JP2015017687A (en) * | 2013-07-12 | 2015-01-29 | 豊興工業株式会社 | Pressure control valve |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5759908B2 (en) * | 1976-05-20 | 1982-12-16 | Kenesu Ibotsuto Jatsuku |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6036728Y2 (en) * | 1980-09-27 | 1985-10-31 | いすゞ自動車株式会社 | Internal combustion engine refueling system |
| JPS59169470U (en) * | 1983-04-28 | 1984-11-13 | トヨタ自動車株式会社 | Oil relief valve for internal combustion engines |
-
1983
- 1983-10-26 JP JP16462783U patent/JPS6072909U/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5759908B2 (en) * | 1976-05-20 | 1982-12-16 | Kenesu Ibotsuto Jatsuku |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6072909U (en) | 1985-05-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4058981A (en) | Lubricating system and method for turbocharged engines | |
| US5339776A (en) | Lubrication system with an oil bypass valve | |
| US4622817A (en) | Hydraulic assist turbocharger system and method of operation | |
| JPH04287815A (en) | Variable valve system of engine | |
| JPH01257712A (en) | Controller for hydraulic driving type cooling fan | |
| JP2971593B2 (en) | Valve timing control device | |
| JPS6116232A (en) | Supercharged internal-combustion engine provided with roots pump | |
| JPH0115842Y2 (en) | ||
| JPH06159029A (en) | Hydraulic pressure control device of engine | |
| US5685266A (en) | Ring gear pumps | |
| JP2003193819A (en) | Oil pump device of internal combustion engine | |
| JPH0721953Y2 (en) | Lubrication structure of automatic transmission | |
| US20020050435A1 (en) | Fluid clutch | |
| JPS6310290B2 (en) | ||
| JPH0742401U (en) | Lubrication device for valve train | |
| JPH077648Y2 (en) | Lubrication structure of automatic transmission | |
| JP2512279Y2 (en) | Lubricator for engine with supercharger | |
| JPS61222857A (en) | Power steering pump provided with vacuum pump | |
| JPH0426660Y2 (en) | ||
| JPS6385223A (en) | Rotor cooling device for rotary piston engine | |
| JPS5822975Y2 (en) | Lubrication system for supercharger in internal combustion engine with supercharger | |
| JP2571065B2 (en) | Engine lubrication device | |
| JPH0221523Y2 (en) | ||
| JPH0619875Y2 (en) | Hydraulic controller for reduction / reversing machine | |
| JPS647245B2 (en) |