JPH0786322B2 - Engine oil supply device - Google Patents
Engine oil supply deviceInfo
- Publication number
- JPH0786322B2 JPH0786322B2 JP23770787A JP23770787A JPH0786322B2 JP H0786322 B2 JPH0786322 B2 JP H0786322B2 JP 23770787 A JP23770787 A JP 23770787A JP 23770787 A JP23770787 A JP 23770787A JP H0786322 B2 JPH0786322 B2 JP H0786322B2
- Authority
- JP
- Japan
- Prior art keywords
- oil
- engine
- pump
- discharge
- sub
- 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 - Lifetime
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/16—Controlling lubricant pressure or quantity
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/12—Closed-circuit lubricating systems not provided for in groups F01M1/02 - F01M1/10
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M5/00—Heating, cooling, or controlling temperature of lubricant; Lubrication means facilitating engine starting
- F01M5/002—Cooling
Description
【発明の詳細な説明】 A.発明の目的 （１） 産業上の利用分野 本発明は、オイルパン内のエンジンオイルをオイルギャ
ラリに供給すべくエンジンに連動連結されたメインポン
プと、オイルパン内のエンジンオイルをオイルクーラに
圧送すべくエンジンに連動連結されたサブポンプとを備
えるエンジンオイル供給装置に関する。DETAILED DESCRIPTION OF THE INVENTION A. Object of the Invention (1) Field of Industrial Application The present invention relates to a main pump that is interlocked with an engine for supplying engine oil in an oil pan to an oil gallery, and an inside of the oil pan. And a sub-pump interlockingly connected to the engine to pump the engine oil to the oil cooler.
（２） 従来の技術 従来、かかる装置はたとえば実公昭56−42403号公報に
より公知である。(2) Conventional Technology Conventionally, such an apparatus is known from, for example, Japanese Utility Model Publication No. 56-42403.
（３） 発明が解決しようとする問題点 ところで、かかるエンジンオイル供給装置において、オ
イルギャラリを介してエンジンオイルが供給される動弁
系におけるカム・スリッパの摩耗を抑えるためには、エ
ンジンのアイドル運動時のエンジンオイル供給量増大、
ならびにエンジン始動時の無潤滑時間短縮を図ることが
重要であり、このため従来では、メインポンプの吐出容
量増大、あるいはエンジン内オイル通路等の容積を低減
してオイル供給系路内充満時間の短縮を図ることが考え
られている。(3) Problems to be Solved by the Invention In such an engine oil supply apparatus, in order to suppress wear of cams and slippers in a valve train in which engine oil is supplied through an oil gallery, engine idle motion is required. Increase in engine oil supply during
In addition, it is important to shorten the no-lubrication time when starting the engine. Therefore, in the past, the discharge capacity of the main pump was increased or the volume of the oil passage in the engine was reduced to shorten the filling time in the oil supply system passage. It is considered that
ところが、メインポンプの吐出量を増大すると、メイン
ポンプの消費動力が増加し、燃費および性能に悪影響を
及ぼす。すなわちメインポンプの吐出容量は、エンジン
低回転時の動弁系オイル量確保ならびにコンロッド・メ
イン軸受への供給油圧確保の２点から決定されており、
メインポンプがエンジンに連動連結されていて吐出量と
エンジン回転数との関係がほぼリニアとなっていること
から、エンジン高回転時には必要オイル量以上のオイル
が吐出されることになり、吐出オイルの一部がリリーフ
弁を介してオイルパンに戻されるからである。However, when the discharge amount of the main pump is increased, the power consumption of the main pump is increased, which adversely affects fuel economy and performance. That is, the discharge capacity of the main pump is determined from two points: securing the amount of oil in the valve train when the engine is running at low speed and securing the hydraulic pressure supplied to the connecting rod and the main bearing.
Since the main pump is linked to the engine and the relationship between the discharge amount and the engine speed is almost linear, more than the required amount of oil is discharged at high engine speed, and This is because a part is returned to the oil pan via the relief valve.
またオイル通路等の容積を減少すると、オイル通路での
流通抵抗が大きくなり、キャビテーションが発生した
り、供給油圧の低下等の問題が生じる。Further, when the volume of the oil passage or the like is reduced, the flow resistance in the oil passage becomes large, causing problems such as cavitation or a decrease in the supplied hydraulic pressure.
本発明は、かかる事情に鑑みてなされたものであり、上
記問題を解決してエンジンアイドル運転時のエンジンオ
イル供給量増大および始動時の無潤滑時間短縮を図るよ
うにしたエンジンオイル供給装置を提供することを目的
とする。The present invention has been made in view of the above circumstances, and provides an engine oil supply device that solves the above problems and increases the engine oil supply amount during engine idle operation and shortens the no-lubrication time during start-up. The purpose is to do.
B.発明の構成 （１） 問題点を解決するための手段 本発明によれば、サブポンプおよびオイルクーラ間と、
メインポンプおよびオイルギャラリ間とは、エンジン低
回転時にはサブポンプの吐出オイルをオイルギャラリに
供給するとともにエンジン高回転時にはサブポンプの吐
出オイルをオイルクーラのみに供給すべくエンジン回転
に応じて接続状態を切換える切換機構を介して接続され
る。B. Configuration of the Invention (1) Means for Solving Problems According to the present invention, between the sub pump and the oil cooler,
Between the main pump and the oil gallery is a switch that switches the connection state according to the engine rotation so that the sub pump discharge oil is supplied to the oil gallery when the engine is running at low speed and the sub pump discharge oil is supplied only to the oil cooler when the engine is running at high speed. Connected via the mechanism.
（２） 作用 上記構成によれば、エンジン低回転時にはサブポンプか
らの吐出オイルがメインポンプの吐出オイルに加わるの
で、メインポンプの設定吐出量を増大することなしに、
エンジン低回転時のオイルポンプ供給量を増大すること
ができる。(2) Operation According to the above configuration, the discharge oil from the sub-pump is added to the discharge oil of the main pump when the engine is running at a low speed, so that the set discharge amount of the main pump is not increased.
It is possible to increase the oil pump supply amount when the engine speed is low.
（３） 実施例 以下、図面により本発明の一実施例について説明する
と、先ず第１図において、このエンジンオイル供給装置
は、オイルパン１内のエンジンオイルを図示しないオイ
ルギャラリに供給するための比較的大容量のメインポン
プ２と、主としてオイルパン１内のエンジンオイルをオ
イルクーラ３に圧送、冷却してオイルパン１に戻すため
の比較的小容量のサブポンプ４とを有し、メインポンプ
２およびサブポンプ４は、クランク軸（図示せず）に連
動する共通の駆動軸５により駆動される。したがってメ
インポンプ２およびサブポンプ４の吐出量はエンジン回
転数が増大するにつれて増大する。(3) Embodiment Hereinafter, one embodiment of the present invention will be described with reference to the drawings. First, in FIG. 1, this engine oil supply device is a comparison for supplying engine oil in an oil pan 1 to an oil gallery (not shown). Has a relatively large capacity main pump 2 and a relatively small capacity sub-pump 4 mainly for pumping engine oil in the oil pan 1 to the oil cooler 3 to cool and return it to the oil pan 1. The sub-pump 4 is driven by a common drive shaft 5 that interlocks with a crank shaft (not shown). Therefore, the discharge amounts of the main pump 2 and the sub pump 4 increase as the engine speed increases.
メインポンプ２の吸入口は、ストレーナ６を介してオイ
ルパン１内に通じる吸入油路７に接続され、吐出口はオ
イルギャラリに通じる吐出油路８に接続される。しかも
メインポンプ２の吐出口および吸入口間は、たとえば6.
2kg/cm2の圧力で開弁するリリーフ弁９を介して接続さ
れる。またサブポンプ４の吸入口は前記吸入油路７に共
通に接続されており、このサブポンプ４の吐出口および
吸入口間は、たとえば3kg/cm2の圧力で開弁するリリー
フ弁10を介して接続される。オイルクーラ３の入口には
オリフィス11を備える油路12が接続されており、オイル
クーラ３の出口は戻し油路13を介して吸入油路７に接続
される。さらにサブポンプ４の吐出口は油路14に接続さ
れる。The suction port of the main pump 2 is connected to a suction oil passage 7 that communicates with the oil pan 1 through a strainer 6, and the discharge port is connected to a discharge oil passage 8 that communicates with an oil gallery. Moreover, the distance between the discharge port and the suction port of the main pump 2 is, for example, 6.
It is connected via a relief valve 9 which opens at a pressure of 2 kg / cm 2 . Further, the suction port of the sub-pump 4 is commonly connected to the suction oil passage 7, and the discharge port and the suction port of the sub-pump 4 are connected via a relief valve 10 which opens at a pressure of, for example, 3 kg / cm 2. To be done. An oil passage 12 having an orifice 11 is connected to an inlet of the oil cooler 3, and an outlet of the oil cooler 3 is connected to a suction oil passage 7 via a return oil passage 13. Further, the discharge port of the sub pump 4 is connected to the oil passage 14.
メインポンプ２の吐出口およびオイルギャラリ間すなわ
ち吐出油路８と、サブポンプ４の吐出口およびオイルク
ーラ３間すなわち油路14,12間とは、エンジン低回転時
にはサブポンプ４の吐出オイルを吐出油路８に供給する
とともにエンジン高回転時にはサブポンプ４の吐出オイ
ルをオイルクーラ３のみに供給すべくエンジン回転に応
じて接続状態を切換える切換機構としての切換制御弁15
を介して接続される。Between the discharge port of the main pump 2 and the oil gallery, that is, the discharge oil passage 8, and between the discharge port of the sub pump 4 and the oil cooler 3, that is, between the oil passages 14 and 12, the discharge oil of the sub pump 4 is discharged when the engine is running at low speed. 8 and a switching control valve as a switching mechanism that switches the connection state according to the engine rotation so that the oil discharged from the sub-pump 4 is supplied only to the oil cooler 3 when the engine is rotating at high speed.
Connected via.
この切換制御弁15は、シリンダ体16と、該シリンダ体16
内に軸方向移動自在に嵌合されるプランジャ17と、該プ
ランジャ17の軸方向一端およびシリンダ体16間に画成さ
れるパイロット油圧室18と、パイロット油圧室18の油圧
力に抗してプランジャ17を軸方向一方側に付勢すべくプ
ランジャ17の軸方向他端およびシリンダ体16間に縮設さ
れる戻しばね19とを備える。シリンダ体16には、油路14
に通じる第１および第２入口ポート20,21と、油路12に
通じる第１出口ポート22と、吐出油路８に通じる第２出
口ポート23とが設けられ、パイロット油圧室18はパイロ
ット油路24を介して吐出油路８に接続される。The switching control valve 15 includes a cylinder body 16 and the cylinder body 16
A plunger 17 that is axially movably fitted therein, a pilot hydraulic chamber 18 defined between one axial end of the plunger 17 and the cylinder body 16, and a plunger against the hydraulic pressure in the pilot hydraulic chamber 18. A return spring 19 is provided between the other end of the plunger 17 in the axial direction and the cylinder body 16 so as to urge the one side in the axial direction. The cylinder body 16 has an oil passage 14
Are provided with first and second inlet ports 20 and 21, which communicate with the oil passage 12, a first outlet port 22 which communicates with the oil passage 12, and a second outlet port 23 which communicates with the discharge oil passage 8, and the pilot hydraulic chamber 18 has a pilot oil passage. It is connected to the discharge oil passage 8 via 24.
プランジャ17には環状溝25が設けられており、プランジ
ャ17は、該環状溝25を介して第２入口ポート21および第
２出口ポート23間を連通する右動位置（第１図示の位
置）と、環状溝25を介して第１入口ポート20および第１
出口ポート22間を連通する左動位置との間で、第１およ
び第２入口ポート20,21ならびに第１および第２出口ポ
ート22,23間を環状溝25を介して連通しながら移動可能
である。しかも戻しばね19のセット荷重は、パイロット
油圧室18の油圧すなわち吐出油路８の油圧P0が第１設定
圧P1たとえば1kg/cm2未満のとき（P0＜P1＝1kg/cm2）に
はプランジャ17を右動位置とし、前記油圧P0が第２設定
圧P2たとえば2.1kg/cm2以上のとき（P0≧P2＝2.1kg/c
m2）にはプランジャ17を左動位置とし、それ以外のとき
（P1≦P0＜P2）にはプランジャ17をその環状溝25が第１
および第２入口ポート20,21ならびに第１および第２出
口ポート22,23間を連通させた状態にあるように設定さ
れる。またP1≦P0＜P2のときには、油圧P0が大となるの
に応じてプランジャ17が左動し、第２出口ポート23の開
口面積が減少するのに対し第１出口ポート22の開口面積
が増大していく。The plunger 17 is provided with an annular groove 25, and the plunger 17 is connected to the right moving position (the position shown in the first illustration) where the second inlet port 21 and the second outlet port 23 communicate with each other via the annular groove 25. Through the annular groove 25, the first inlet port 20 and the first
The first and second inlet ports 20 and 21 and the first and second outlet ports 22 and 23 can be moved while communicating with each other via the annular groove 25 between the left and right moving positions communicating between the outlet ports 22. is there. Moreover, the set load of the return spring 19 is set when the hydraulic pressure of the pilot hydraulic chamber 18, that is, the hydraulic pressure P 0 of the discharge oil passage 8 is less than the first set pressure P 1, for example, 1 kg / cm 2 (P 0 <P 1 = 1 kg / cm 2 ), The plunger 17 is set to the right position and the hydraulic pressure P 0 is equal to or higher than the second set pressure P 2 of 2.1 kg / cm 2 (P 0 ≧ P 2 = 2.1 kg / c).
m 2 ), the plunger 17 is moved to the left position, and at other times (P 1 ≦ P 0 <P 2 ), the plunger 17 is moved to the first position where the annular groove 25
The second inlet port 20 and 21, and the first and second outlet port 22 and 23 are set to communicate with each other. When P 1 ≤P 0 <P 2 , the plunger 17 moves left in response to the increase in the hydraulic pressure P 0 , and the opening area of the second outlet port 23 decreases while the first outlet port 22 The opening area increases.
かかる切換制御弁15では、プランジャ17はパイロット油
圧室18の油圧すなわち吐出油路８の油圧P0に応じて作動
するものであり、前記油圧P0はリリーフ弁９が開弁する
までは、エンジン回転数に応じて増大するものである。
したがって切換制御弁15もエンジン回転数に応じて作動
することになる。In such a switching control valve 15, the plunger 17 operates in accordance with the oil pressure in the pilot hydraulic chamber 18, that is, the oil pressure P 0 in the discharge oil passage 8, and the oil pressure P 0 remains unchanged until the relief valve 9 opens. It increases according to the rotation speed.
Therefore, the switching control valve 15 also operates according to the engine speed.
次にこの実施例の作用について第２図を参照しながら説
明すると、メインポンプ２の吐出量は曲線Ｍで示すよう
に設定されており、このメインポンプ２の吐出量とサブ
ポンプ４の吐出量との和は曲線MSで示すように設定され
ている。すなわちサブポンプ４の吐出量は左下りの斜線
で示す範囲となる。これに対しエンジン側で必要なエン
ジンオイル量は曲線Ｅで示すようになり、実際に吐出油
路８を介してオイルギャラリに供給されるオイル量は曲
線Ａで示され、吐出油路８の油圧は曲線P0で示される。Next, the operation of this embodiment will be described with reference to FIG. 2. The discharge amount of the main pump 2 is set as shown by the curve M, and the discharge amount of the main pump 2 and the discharge amount of the sub pump 4 are The sum of is set as shown by the curve MS. That is, the discharge amount of the sub-pump 4 is in the range indicated by the diagonal line to the left. On the other hand, the amount of engine oil required on the engine side is shown by the curve E, and the amount of oil actually supplied to the oil gallery through the discharge oil passage 8 is shown by the curve A. Is shown by the curve P 0 .
先ずエンジン始動時やアイドル運転時等のエンジン回転
数が低いとき、すなわち吐出油圧P0が第１設定圧P1とな
るエンジン回転数N1に達するまでは、第１図で示したよ
うに切換制御弁15のプランジャ17は右動位置にある。こ
の状態では、第２入口ポート21が第２出口ポート23に連
通した状態にあり、サブポンプ４からの吐出オイルは切
換制御弁15を介して吐出油路８に全量供給されている。
したがってエンジン始動時やアイドル運転時等の低エン
ジン回転数のときには、エンジンで必要とされるオイル
量がメインポンプ２およびサブポンプ４からオイルギャ
ラリに供給されることになり、動弁系への潤滑油量を増
大するとともに無潤滑時間の短縮を図ることができ、カ
ム・スリッパの摩耗防止に寄与することができる。First, when the engine speed is low at the time of starting the engine or during idle operation, that is, until the discharge hydraulic pressure P 0 reaches the engine speed N 1 at which the first set pressure P 1 is reached, switching is performed as shown in FIG. The plunger 17 of the control valve 15 is in the right movement position. In this state, the second inlet port 21 is in communication with the second outlet port 23, and the discharge oil from the sub-pump 4 is completely supplied to the discharge oil passage 8 via the switching control valve 15.
Therefore, at a low engine speed such as when the engine is started or when the engine is idling, the amount of oil required for the engine is supplied from the main pump 2 and the sub pump 4 to the oil gallery, and the lubricating oil for the valve train is supplied. The amount can be increased and the non-lubrication time can be shortened, which contributes to prevention of wear of the cams and slippers.
エンジン回転数が増大して前記回転数N1を超えると、第
３図で示すように、パイロット油圧室18の油圧P0が第１
設定圧P1を超えるのに応じて切換制御弁15のプランジャ
17は、その右動位置から左動位置側へと移動し、第１お
よび第２入口ポート20,21が第１および第２出口ポート2
2,23に連通する。このようにP1≦P0＜P2の状態でプラン
ジャ17がストローク途中にあるときには、サブポンプ４
からの吐出オイルの一部が吐出油路８に供給されること
になるので、吐出油路８からオイルギャラリに流れるオ
イル量は一時的に低下し、それに応じて油圧Ｐも低下す
る。この際オリフィス11は、吐出油路８側への流量とオ
イルクーラ３側への流量とのバランスをとるものであ
り、このオリフィス11の開度によりオイル量および油圧
P0の低下度合が調整される。When the engine rotational speed increases and exceeds the rotational speed N 1 , as shown in FIG. 3, the hydraulic pressure P 0 of the pilot hydraulic chamber 18 becomes the first hydraulic pressure P 0 .
The plunger of the switching control valve 15 in response to exceeding the set pressure P 1
17 moves from the right movement position to the left movement position side, and the first and second inlet ports 20 and 21 are connected to the first and second outlet ports 2.
Connect to 2,23. As described above, when the plunger 17 is in the middle of the stroke with P 1 ≤P 0 <P 2 , the sub pump 4
Since a part of the oil discharged from the discharge oil passage 8 is supplied to the discharge oil passage 8, the amount of oil flowing from the discharge oil passage 8 to the oil gallery temporarily decreases, and the hydraulic pressure P also decreases accordingly. At this time, the orifice 11 balances the flow rate to the discharge oil passage 8 side and the flow rate to the oil cooler 3 side.
The degree of decrease in P 0 is adjusted.
エンジン回転数がさらに増大してP0≧2.1kg/cm2となる
回転数N3に達すると、第４図に示すように切換制御弁15
のプランジャ17は左動位置となり、第１および第２入口
ポート20,21は第１出口ホート22に連通する。したがっ
てサブポンプ４からの吐出オイルはオイルクーラ３に全
量供給されることになり、吐出油路８の油圧およびオイ
ル量はメインポンプ２の回転数がエンジン回転数に応じ
て増大するのに伴って増大する。而して吐出油路８の油
圧がリリーフ弁９の設定圧たとえば6kg/cm2以上となる
と、リリーフ弁９が開弁するので吐出油路８の油圧はエ
ンジン回転数の増大にも拘らず一定となる。When the engine speed further increases and reaches the engine speed N 3 at which P 0 ≧ 2.1 kg / cm 2 , the switching control valve 15 as shown in FIG.
The plunger 17 is in the leftward movement position, and the first and second inlet ports 20 and 21 communicate with the first outlet hoat 22. Therefore, the total amount of oil discharged from the sub-pump 4 is supplied to the oil cooler 3, and the oil pressure and the oil amount of the discharge oil passage 8 increase as the rotational speed of the main pump 2 increases in accordance with the engine rotational speed. To do. When the oil pressure in the discharge oil passage 8 becomes equal to or higher than the set pressure of the relief valve 9, for example, 6 kg / cm 2 , the relief valve 9 opens, so that the oil pressure in the discharge oil passage 8 is constant despite the increase in the engine speed. Becomes
このようにしてエンジンのアイドル運転時や始動時の低
回転時に、サブポンプ４からの吐出オイルがメインポン
プ２の吐出オイルに加わって吐出油路８に供給されるの
で、アイドル運転時のエンジンオイル供給量増大ならび
に無潤滑時間の短縮を図り、動弁系でのカム・スリッパ
の摩耗を抑えることができる。しかも切換制御弁15は、
油路14を吐出油路８に連通させた右動位置と、油路14を
油路12に連通させた左位置との間でプランジャ17が移動
する際に、油路14を吐出油路８および油路12にともに連
通させながら油路14から吐出油路８への流量を絞ってい
くので、切換時に吐出油路８のオイル量に極端な落ち込
みがなく、吐出油路８のオイル供給量を滑らかに変化さ
せることができる。In this way, the oil discharged from the sub-pump 4 is added to the oil discharged from the main pump 2 and supplied to the oil discharge passage 8 when the engine is idling or at low speed during starting. It is possible to increase the amount and shorten the non-lubrication time, and to suppress the wear of the cam slippers in the valve train. Moreover, the switching control valve 15 is
When the plunger 17 moves between the right position where the oil passage 14 is communicated with the discharge oil passage 8 and the left position where the oil passage 14 is communicated with the oil passage 12, the oil passage 14 is discharged through the discharge oil passage 8 Since the flow rate from the oil passage 14 to the discharge oil passage 8 is reduced while communicating with both the oil passage 12 and the oil passage 12, the oil amount in the discharge oil passage 8 does not drop extremely at the time of switching, and the oil supply amount in the discharge oil passage 8 is reduced. Can be changed smoothly.
本発明の他の実施例として、切換機構をソレノイドの励
磁および消磁による電磁切換式制御弁としてもよい。As another embodiment of the present invention, the switching mechanism may be an electromagnetic switching control valve by exciting and deactivating a solenoid.
C.発明の効果 以上のように本発明によれば、サブポンプおよびオイル
クーラ間と、メインポンプおよびオイルギャラリ間と
は、エンジン低回転時にはサブポンプの吐出オイルをオ
イルギャラリに供給するとともにエンジン高回転時には
サブポンプの吐出オイルをオイルクーラのみに供給すべ
くエンジン回転に応じて接続状態を切換える切換機構を
介して接続されるので、エンジンのアイドル運転時や始
動時にメインポンプおよびサブポンプから吐出されるオ
イルをエンジンに供給して、動弁系での摩耗低減に寄与
することができる。しかもオイル供給量の増大がメイン
ポンプの設定容量増大を伴わず、したがってエンジン高
回転時にオイルパンに戻されるリリーフ油を極力少なく
して消費動力を低減することができる。C. Effect of the Invention As described above, according to the present invention, between the sub-pump and the oil cooler and between the main pump and the oil gallery, the discharge oil of the sub-pump is supplied to the oil gallery at the time of low engine speed, and at the time of high engine speed. Since the sub pump is connected via a switching mechanism that switches the connection state according to the engine rotation so that the oil discharged from the sub pump is supplied only to the oil cooler, the oil discharged from the main pump and the sub pump during engine idle operation and start Can contribute to the reduction of wear in the valve train. Moreover, the increase in the oil supply amount does not accompany the increase in the set capacity of the main pump, and therefore the relief oil returned to the oil pan at the time of high engine speed can be reduced as much as possible to reduce the power consumption.
図面は本発明の一実施例を示すものであり、第１図はエ
ンジン低回転時を示す回路図、第２図はエンジンオイル
吐出量および油圧の特性図、第３図は切換途中を示す第
１図に対応する回路図、第４図はエンジン高回転時を示
す第１図に対応した回路図である。 １……オイルパン、２……メインポンプ、３……オイル
クーラ、４……サブポンプ、15……切換機構としての切
換制御弁The drawings show an embodiment of the present invention. FIG. 1 is a circuit diagram showing a low engine speed, FIG. 2 is a characteristic diagram of engine oil discharge amount and oil pressure, and FIG. FIG. 4 is a circuit diagram corresponding to FIG. 1, and FIG. 4 is a circuit diagram corresponding to FIG. 1 ... Oil pan, 2 ... Main pump, 3 ... Oil cooler, 4 ... Sub pump, 15 ... Switching control valve as switching mechanism
Claims (1)
ャラリに供給すべくエンジンに連動連結されたメインポ
ンプと、オイルパン内のエンジンオイルをオイルクーラ
に圧送すべくエンジンに連動連結されたサブポンプとを
備えるエンジンオイル供給装置において、サブポンプお
よびオイルクーラ間と、メインポンプおよびオイルギャ
ラリ間とは、エンジン低回転時にはサブポンプの吐出オ
イルをオイルギャラリに供給するとともにエンジン高回
転時にはサブポンプの吐出オイルをオイルクーラのみに
供給すべくエンジン回転に応じて接続状態を切換える切
換機構を介して接続されることを特徴とするエンジンオ
イル供給装置。1. A main pump interlocked with the engine to supply the engine oil in the oil pan to an oil gallery, and a sub-pump interlocked with the engine to pump the engine oil in the oil pan to an oil cooler. In the equipped engine oil supply device, between the sub pump and the oil cooler and between the main pump and the oil gallery, the discharge oil of the sub pump is supplied to the oil gallery when the engine is running at low speed, and the discharge oil of the sub pump is sent only to the oil cooler when the engine is running at high speed. The engine oil supply device is characterized in that it is connected via a switching mechanism that switches the connection state according to the engine rotation so as to be supplied to the engine oil.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23770787A JPH0786322B2 (en) | 1987-09-22 | 1987-09-22 | Engine oil supply device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23770787A JPH0786322B2 (en) | 1987-09-22 | 1987-09-22 | Engine oil supply device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6480717A JPS6480717A (en) | 1989-03-27 |
| JPH0786322B2 true JPH0786322B2 (en) | 1995-09-20 |
Family
ID=17019312
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP23770787A Expired - Lifetime JPH0786322B2 (en) | 1987-09-22 | 1987-09-22 | Engine oil supply device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0786322B2 (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2286017A (en) * | 1994-01-21 | 1995-08-02 | Concentric Pumps Ltd | Improvements relating to pumps |
| BRPI0419216A (en) * | 2004-11-30 | 2007-12-18 | Ap Moeller Maersk As | method and system for reducing fuel consumption in a diesel engine |
| KR101680648B1 (en) * | 2015-09-10 | 2016-11-30 | 명화공업주식회사 | Dual pump system |
| DE102017101090A1 (en) * | 2017-01-20 | 2018-07-26 | Man Diesel & Turbo Se | Oil supply system and method of operating the same |
| CA3060655C (en) * | 2017-04-21 | 2021-10-19 | Atlas Copco Airpower, Naamloze Vennootschap | Oil circuit, oil-free compressor provided with such oil circuit and a method to control lubrication and/or cooling of such oil-free compressor via such oil circuit |
| US11085448B2 (en) | 2017-04-21 | 2021-08-10 | Atlas Copco Airpower, Naamloze Vennootschap | Oil circuit, oil-free compressor provided with such oil circuit and a method to control lubrication and/or cooling of such oil-free compressor via such oil circuit |
| BE1024746B1 (en) * | 2017-04-21 | 2018-06-18 | Atlas Copco Airpower Nv | Oil circuit and machine equipped with such an oil circuit. |
| WO2018193325A1 (en) * | 2017-04-21 | 2018-10-25 | Atlas Copco Airpower, Naamloze Vennootschap | Oil circuit, oil-free compressor provided with such oil circuit and a method to control lubrication and/or cooling of such oil-free compressor via such oil circuit |
| IT201700121440A1 (en) * | 2017-10-25 | 2019-04-25 | Vhit S P A Soc Unipersonale | Recirculating hydraulic circuit |
-
1987
- 1987-09-22 JP JP23770787A patent/JPH0786322B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6480717A (en) | 1989-03-27 |
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