JPH05263770A - Oil pump - Google Patents
Oil pumpInfo
- Publication number
- JPH05263770A JPH05263770A JP6560892A JP6560892A JPH05263770A JP H05263770 A JPH05263770 A JP H05263770A JP 6560892 A JP6560892 A JP 6560892A JP 6560892 A JP6560892 A JP 6560892A JP H05263770 A JPH05263770 A JP H05263770A
- Authority
- JP
- Japan
- Prior art keywords
- discharge
- passage
- pump
- rotor
- oil
- 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.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/10—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
- F04C14/16—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using lift valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
Abstract
(57)【要約】
【目的】 ポンプの動力損出を軽減しつつポンプ構造の
簡素化を図り、製造作業能率の向上と製造コストの低廉
化を図る。
【構成】 駆動軸２により互いの内外歯が噛合しつつ回
転するインナロータ３とアウタロータ４の内外歯３ａ，
４ａ間のボリューム室５の容積変化を得てポンプ作用を
行う。ポンプケーシング１に有する２つの吐出ポート１
０，１１に第１，第２吐出通路１５，１６を接続し、該
第２吐出通路１６に接続されたリリーフ通路１８と第２
吐出通路１６の上下流部１６ａ，１６ｂを適宜切り換え
る３ポート２位置型の切換弁１９を設けた。
(57) [Abstract] [Purpose] To reduce the power loss of the pump and to simplify the structure of the pump to improve the manufacturing work efficiency and reduce the manufacturing cost. An inner and outer teeth 3a of an inner rotor 3 and an outer rotor 4 that rotate while their inner and outer teeth mesh with each other by a drive shaft 2.
A volume change of the volume chamber 5 between 4a is obtained to perform a pumping action. Two discharge ports 1 on the pump casing 1
The first and second discharge passages 15 and 16 are connected to 0 and 11, and the relief passage 18 and the second discharge passage 18 are connected to the second discharge passage 16.
A three-port two-position type switching valve 19 for appropriately switching the upstream and downstream portions 16a and 16b of the discharge passage 16 is provided.
Description
【０００１】[0001]
【産業上の利用分野】本発明は、例えば自動車用内燃機
関の各摺動部等へ潤滑油を供給するオイルポンプに関す
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an oil pump for supplying lubricating oil to each sliding portion of an internal combustion engine for automobiles.
【０００２】[0002]
【従来の技術】この種、従来のオイルポンプとしては、
所謂トロコイド型のものが一般に知られている。2. Description of the Related Art As this type of conventional oil pump,
The so-called trochoid type is generally known.
【０００３】概略を説明すれば、ポンプケーシングの両
側部に吸入ポートと吐出ポートが設けられていると共
に、略中央に機関のクランク軸から回転力が伝達される
駆動軸が貫通配置されている。また、ポンプケーシング
の内部には、駆動軸に連結されたインナロータと、内歯
が該インナロータの外周に有する外歯に噛合するアウタ
ロータが互いに回転自在に設けられている。In brief, an intake port and a discharge port are provided on both sides of the pump casing, and a drive shaft for transmitting the rotational force from the crankshaft of the engine is disposed at substantially the center thereof. Further, inside the pump casing, an inner rotor connected to the drive shaft and an outer rotor having inner teeth meshing with outer teeth on the outer circumference of the inner rotor are rotatably provided.
【０００４】そして、前記インナロータとアウタロータ
の回転に伴い内外歯間に形成されたボリューム室の容積
変化を得て、前記吸入ポートから吸入した潤滑油を吐出
ポートに吐出することによりポンプ作用が行われるよう
になっている。Then, the volume change of the volume chamber formed between the inner and outer teeth is obtained with the rotation of the inner rotor and the outer rotor, and the lubricating oil sucked from the suction port is discharged to the discharge port to perform a pump action. It is like this.
【０００５】ところで、斯かるオイルポンプにあって
は、駆動軸が前記のように機関のクランク軸と同期回転
し、該機関回転数に比例したポンプ吐出量になる。した
がって、機関高回転域では、要求流量以上の過剰なポン
プ吐出量になってしまう。このため、吐出ポート下流の
吐出通路にリリーフバルブを設けて、機関に供給される
潤滑油量を制御するようになっている。By the way, in such an oil pump, the drive shaft rotates in synchronization with the crankshaft of the engine as described above, and the pump discharge amount is proportional to the engine speed. Therefore, in the high engine speed region, the pump discharge amount exceeds the required flow rate. Therefore, a relief valve is provided in the discharge passage downstream of the discharge port to control the amount of lubricating oil supplied to the engine.
【０００６】[0006]
【発明が解決しようとする課題】しかし、前記リリーフ
バルブは、該リリーフバルブ上流側の吐出通路内の油圧
が一定以上に上昇した場合に、この高油圧を直接スプー
ル弁体に作用させてリリーフ通路を開作動するようにな
っている。このため、斯かるリリーフ油の圧力によって
ポンプ室の内圧が上昇してしまうので、ポンプの駆動負
荷が極めて大きくなり、動力損出が増加する。However, in the relief valve, when the oil pressure in the discharge passage upstream of the relief valve rises above a certain level, this high oil pressure is directly applied to the spool valve element to cause the relief passage. It is designed to open. Therefore, the pressure of the relief oil increases the internal pressure of the pump chamber, so that the driving load of the pump becomes extremely large and the power loss increases.
【０００７】そこで、例えば特開昭６３ー１７８１号公
報に記載されているトロコイド型のオイルポンプによう
に、アウタロータの内歯の外周面を回転自在に支持する
環状部材を、駆動軸と同心上に回転可能に設け、この環
状部材の回転角度を所定の調整機構を介して調整するこ
とによりポンプ吐出量を可変するものも提供されてい
る。Therefore, an annular member for rotatably supporting the outer peripheral surface of the inner teeth of the outer rotor is concentric with the drive shaft, as in the trochoidal type oil pump disclosed in Japanese Patent Laid-Open No. 63-1781. It is also provided that the pump discharge amount is variable by rotatably providing the annular member and adjusting the rotation angle of the annular member via a predetermined adjusting mechanism.
【０００８】然し乍ら、この可変容量型のオイルポンプ
にあっては、環状部材や調整機構等を用いるため、ポン
プ全体の構造が極めて複雑になり、製造作業能率が低下
すると共に、製造コストの大巾な高騰が余儀なくされて
いる。However, in this variable displacement type oil pump, since the annular member, the adjusting mechanism and the like are used, the structure of the entire pump becomes extremely complicated, the manufacturing work efficiency decreases, and the manufacturing cost greatly increases. A sharp rise is forced.
【０００９】[0009]
【課題を解決するための手段】本発明は、前記各従来例
の問題点に鑑みて案出されたもので、両側部に吸入ポー
トと吐出ポートとを有するポンプケーシング内に、駆動
軸により互いの内外歯が噛合しつつ回転するインナロー
タとアウタロータとを設け、該各ロータの内外歯間の容
積変化を得て前記吸入ポートから吸入したオイルを複数
に分割された前記吐出ポートに吐出するオイルポンプに
おいて、前記各吐出ポートに夫々接続された複数の吐出
通路のうち一方の吐出通路に、リリーフ通路を接続する
と共に、該接続個所にリリーフ通路と一方の吐出通路の
上下流部を切り換える切換弁を設けたことを特徴として
いる。SUMMARY OF THE INVENTION The present invention has been devised in view of the problems of the above-mentioned respective prior art examples, in which a drive shaft is provided inside a pump casing having an intake port and a discharge port on both sides thereof. An oil pump that includes an inner rotor and an outer rotor that rotate while the inner and outer teeth of the rotor mesh with each other, obtains a volume change between the inner and outer teeth of each rotor, and discharges the oil sucked from the suction port to the plurality of divided discharge ports. In one of the plurality of discharge passages respectively connected to the respective discharge ports, a relief passage is connected to the relief passage, and a switching valve for switching between the relief passage and the upstream / downstream part of the one discharge passage is provided at the connection point. The feature is that it is provided.
【００１０】[0010]
【作用】例えば機関高回転域などで、両吐出ポートから
吐出される吐出量が要求量以上になった場合は、切換弁
の切り換え作動により、一方の吐出通路の上下流部の連
通を遮断すると同時に、該一方の吐出通路の上流部とリ
リーフ通路を連通させる。このため、一方の吐出通路に
吐出されたオイルは、機関に供給されずリリーフ通路か
ら例えば吸気ポート側へ速やかに戻される。したがっ
て、各吐出ポート内の油圧の過上昇が抑制される。When the discharge amount discharged from both discharge ports exceeds the required amount in a high engine speed region, for example, the switching operation of the switching valve shuts off the communication between the upstream and downstream portions of one discharge passage. At the same time, the relief passage is connected to the upstream portion of the one discharge passage. Therefore, the oil discharged into one of the discharge passages is not supplied to the engine and is quickly returned from the relief passage to, for example, the intake port side. Therefore, the excessive increase of the hydraulic pressure in each discharge port is suppressed.
【００１１】[0011]
【実施例】以下、本発明の実施例を図面に基づいて詳述
する。尚、本実施例も自動車用内燃機関に適用したトロ
コイド型オイルポンプを示している。Embodiments of the present invention will now be described in detail with reference to the drawings. This embodiment also shows a trochoidal type oil pump applied to an internal combustion engine for automobiles.
【００１２】図１の１はシリンダブロック前端部に一体
に設けられ、かつ開口端が図外のカバーによって閉塞さ
れたポンプケーシング、２は該ポンプケーシング１の略
中心部を貫通し、機関のクランク軸から回転力が伝達さ
れる駆動軸、３，４はポンプケーシング１の円形状ポン
プ室１ａ内に回転自在に収納されたインナロータとアウ
タロータであって、前記駆動軸２に結合されたインナロ
ータ３は、外周に９個の外歯３ａが形成されている。一
方、前記アウタロータ４は、その中心がインナロータ３
の中心から所定量αだけ偏心していると共に、内周には
前記外歯３ａ…と噛合する１０個の内歯４ａが形成され
ている。したがって、各ロータ３，４の間には、外歯３
ａ１個分のボリューム室５が形成されており、このボリ
ューム室５の容積が各ロータ３，４の回転に伴い変化す
るようになっている。Reference numeral 1 in FIG. 1 is a pump casing integrally provided at a front end portion of a cylinder block, and an opening end of the pump casing is closed by a cover (not shown). Drive shafts to which a rotational force is transmitted, shafts 3 and 4 are an inner rotor and an outer rotor rotatably housed in a circular pump chamber 1a of a pump casing 1, and the inner rotor 3 connected to the drive shaft 2 is , 9 outer teeth 3a are formed on the outer circumference. On the other hand, the center of the outer rotor 4 is the inner rotor 3
While being eccentric by a predetermined amount α from the center of, the ten inner teeth 4a meshing with the outer teeth 3a are formed on the inner circumference. Therefore, the outer teeth 3 are provided between the rotors 3 and 4.
A volume chamber 5 for one a is formed, and the volume of the volume chamber 5 changes with the rotation of the rotors 3 and 4.
【００１３】また、ポンプケーシング１の図中左側側部
には、略円弧状のオイル吸入室６が設けられている一方
右側側部には、上下に２分割された一対の第１，第２オ
イル吐出室７，８が設けられている。また、左右両側端
には吸入室６と各吐出室７，８とに夫々連通する吸入ポ
ート９と第１，第２吐出ポート１０，１１が設けられて
いる。前記上側の第１吐出室７は、その開口面積が下側
の第２吐出室８よりも大きく設定されてオイルの吐出量
の分配割合が第２吐出室８よりも大きくなっている。Further, a substantially arc-shaped oil suction chamber 6 is provided on the left side portion of the pump casing 1 in the figure, while a pair of first and second upper and lower parts are divided on the right side portion. Oil discharge chambers 7 and 8 are provided. A suction port 9 and first and second discharge ports 10 and 11 which communicate with the suction chamber 6 and the discharge chambers 7 and 8 are provided at both left and right ends. The opening area of the upper first discharge chamber 7 is set to be larger than that of the lower second discharge chamber 8, and the distribution ratio of the oil discharge amount is larger than that of the second discharge chamber 8.
【００１４】更に、前記吸入ポート９は、機関本体の下
端部に設けられたオイルパン１２内部とストレーナ及び
吸入通路１３を介して連通している。一方、各吐出ポー
ト１０，１１は、隣接する内歯４ａ，４ａ間のピッチよ
りも若干広い幅をもって外方に開いた隔壁１４によって
隔成されており、該隔壁１４により互いに所定の開角度
をもって並設されている。Further, the suction port 9 communicates with the inside of the oil pan 12 provided at the lower end of the engine body through a strainer and a suction passage 13. On the other hand, the discharge ports 10 and 11 are separated from each other by a partition wall 14 that opens outward with a width slightly wider than the pitch between the adjacent inner teeth 4a and 4a, and the partition walls 14 have a predetermined opening angle with each other. They are installed side by side.
【００１５】また、この各吐出ポート１０，１１には、
夫々第１，第２吐出通路１５，１６が接続されている。
この第１吐出通路１５は、下流端が機関のオイルメイン
ギャラリー１７に接続されている一方、第２吐出通路１
６は、下流端１６ｂが第１吐出通路１５の途中に接続さ
れて、両方の吐出オイルが該接続個所で合流するように
なっている。更に、前記第２吐出通路１６の途中には、
下流端１８ｂが吸入通路１３に接続されたリリーフ通路
１８の上流端１８ａが接続されていると共に、該リリー
フ通路１８との接続個所に３ポート２位置型の切換弁１
９が設けられている。The discharge ports 10 and 11 are provided with
The first and second discharge passages 15 and 16 are connected to each other.
The first discharge passage 15 has its downstream end connected to the oil main gallery 17 of the engine, while the second discharge passage 1
6, the downstream end 16b is connected in the middle of the first discharge passage 15, so that both discharge oils join together at the connection point. Further, in the middle of the second discharge passage 16,
The downstream end 18b is connected to the suction passage 13, and the upstream end 18a of the relief passage 18 is connected to the relief passage 18. At the connection point with the relief passage 18, the 3-port 2-position switching valve 1 is provided.
9 is provided.
【００１６】この切換弁１９は、スプリングオフセット
・パイロット式であって、第１吐出通路１５下流側の吐
出圧をパイロット通路２０を介してバルブボディ内に導
入し、該パイロット圧とバルブボディ内のスプリングの
ばね力との相対圧でスプール弁を摺動させて通路の切り
換えを行うようになっている。即ち、第１吐出通路１５
下流側の吐出圧が所定圧以下の場合は、スプール弁がス
プリングのばね力で一方向に保持され、第２吐出通路１
６の上下流部１６ａ，１６ｂを連通すると共に、リリー
フ通路１８を遮断する。また、吐出圧が所定圧以上にな
った場合は、スプール弁がパイロット圧によりばね力に
抗して他方向に移動し、第２吐出通路１６の下流部１６
ｂを遮断すると共に、上流部１６ａとリリーフ通路１８
を連通させる。The switching valve 19 is of a spring offset pilot type, and introduces the discharge pressure on the downstream side of the first discharge passage 15 into the valve body through the pilot passage 20, and the pilot pressure and the inside of the valve body. The passage is switched by sliding the spool valve by the relative pressure with the spring force of the spring. That is, the first discharge passage 15
When the discharge pressure on the downstream side is equal to or lower than the predetermined pressure, the spool valve is held in one direction by the spring force of the spring, and the second discharge passage 1
The upper and downstream portions 16a and 16b of the No. 6 are communicated with each other, and the relief passage 18 is blocked. Further, when the discharge pressure becomes equal to or higher than the predetermined pressure, the spool valve moves in the other direction against the spring force by the pilot pressure, and the downstream portion 16 of the second discharge passage 16 moves.
In addition to blocking b, the upstream portion 16a and the relief passage 18
To communicate.
【００１７】尚、図中２１は第１吐出通路１５の下流側
と吸入通路１３とを連通するリターン通路２２に設けら
れた圧力調整弁であって、機関へ供給される潤滑油圧を
一定に調整するようになっている。Reference numeral 21 in the drawing denotes a pressure adjusting valve provided in a return passage 22 which connects the downstream side of the first discharge passage 15 and the suction passage 13, and regulates the lubricating oil pressure supplied to the engine to a constant value. It is supposed to do.
【００１８】以下、本実施例の作用について説明する。The operation of this embodiment will be described below.
【００１９】まず、機関の低回転域では、駆動軸２の回
転に伴いインナロータ３とアウタロータ４が互いの内外
歯３ａ，４ａを噛合しつつ回転し、ボリューム室５の容
積を変化させながらポンプ作用を行う。つまり、オイル
パン１２から吸入通路１３，吸入ポート９を経て吸入室
６に吸入された潤滑油を、各吐出室７，８の容積に応じ
て分配吐出し、ここから各吐出ポート１０，１１及び各
吐出通路１５，１６に圧送されるが、この時点では切換
弁１９により第２吐出通路１６の上下流部１６ａ，１６
ｂが連通しているため、両通路１５，１６内の潤滑油は
途中で合流しながらオイルメインギャラリー１７に供給
される。First, in the low engine speed range, the inner rotor 3 and the outer rotor 4 rotate while the inner and outer teeth 3a, 4a mesh with each other as the drive shaft 2 rotates, changing the volume of the volume chamber 5 and acting as a pump. I do. That is, the lubricating oil sucked into the suction chamber 6 from the oil pan 12 through the suction passage 13 and the suction port 9 is distributed and discharged according to the volumes of the discharge chambers 7 and 8, and from this, the discharge ports 10 and 11 and The pressure is fed to the discharge passages 15 and 16, but at this time, the switching valve 19 causes the upstream and downstream portions 16a and 16a of the second discharge passage 16 to flow.
Since b is in communication, the lubricating oil in both passages 15 and 16 is supplied to the oil main gallery 17 while converging on the way.
【００２０】一方、機関高回転域に移行した場合は、駆
動軸２の高回転に伴い各吐出通路１５，１６内に吐出さ
れる潤滑油の吐出圧が上昇し、所定以上になると、該吐
出圧力の間接的なパイロット圧を利用して切換弁１９が
切り換え作動して、第２吐出通路１６の下流部１６ｂを
遮断すると共に、上流部１６ａとリリーフ通路１８を連
通する。したがって、第１吐出通路１５を通った潤滑油
は、そのままオイルメインギャラリー１７に供給されて
要求流量を満足するものの、第２吐出通路１６に流入し
た潤滑油は、リリーフ通路１８を通って吸入通路１３に
速やかに戻される。このため、第１吐出ポート１０の油
圧が機関側に供給されて要求量を確保しつつ、第２吐出
ポート１１の油圧がリリーフ側に戻されるのでポンプ室
内の過剰な圧力上昇が抑制されてポンプ駆動負荷つまり
動力損出の増加が防止される。On the other hand, when the engine speed shifts to the high engine speed range, the discharge pressure of the lubricating oil discharged into the discharge passages 15 and 16 increases with the high rotation of the drive shaft 2, and when the discharge pressure exceeds a predetermined value, the discharge pressure is increased. The indirect pilot pressure is used to switch the switching valve 19 to shut off the downstream portion 16b of the second discharge passage 16 and connect the upstream portion 16a and the relief passage 18 to each other. Therefore, although the lubricating oil that has passed through the first discharge passage 15 is directly supplied to the oil main gallery 17 and satisfies the required flow rate, the lubricating oil that has flowed into the second discharge passage 16 passes through the relief passage 18 and is sucked into the suction passage. Promptly returned to 13. Therefore, the hydraulic pressure of the first discharge port 10 is supplied to the engine side to secure the required amount, and the hydraulic pressure of the second discharge port 11 is returned to the relief side, so that an excessive pressure rise in the pump chamber is suppressed and the pump is An increase in driving load, that is, loss of power is prevented.
【００２１】しかも、第２吐出通路１６の上下流部１６
ａ，１６ｂとリリーフ通路１８とを切換弁１９によって
切り換えするだけであるから、可変容量型の従来例に比
較して、全体の構造が極めて簡素化できる。したがっ
て、製造作業能率の向上と製造コストの低廉化が図れ
る。Moreover, the upstream and downstream portions 16 of the second discharge passage 16
Since only the switching valve 19 is used to switch between a and 16b and the relief passage 18, the entire structure can be extremely simplified as compared with the conventional variable displacement type. Therefore, the manufacturing work efficiency can be improved and the manufacturing cost can be reduced.
【００２２】図２は、本発明の第２実施例を示してお
り、前記各吐出ポート１０，１１の隔壁１４の幅を狭く
して切換弁１９の切り換え作動時に一時的に発生する第
２吐出ポート１１内の圧力上昇を抑制するものである。FIG. 2 shows a second embodiment of the present invention, in which the width of the partition wall 14 of each of the discharge ports 10 and 11 is narrowed to temporarily generate the second discharge when the switching valve 19 is switched. The pressure in the port 11 is suppressed from rising.
【００２３】具体的に説明すれば、切換弁１９は前述の
ように、機関の低回転時から高回転時に移行した場合
に、スプール弁がパイロット圧によって第２吐出通路１
６の上流部１６ａと下流部１６ｂとの連通を遮断し、上
流部１６ａとリリーフ通路１８を連通しようとする際
に、該スプール弁の摺動中に弁体が一時的に下流部１６
ｂとリリーフ通路１８の各開口端を同時に閉止する。こ
のため、該第２吐出通路１６の上流部１６ａの内圧が急
激に上昇して、第２吐出ポート１１及び第２吐出室８の
内圧の過上昇し、ポンプの駆動負荷が大きくなる惧れが
ある。More specifically, as described above, the switching valve 19 has the spool valve driven by the pilot pressure when the engine shifts from the low rotation speed to the high rotation speed by the pilot pressure.
When disconnecting the communication between the upstream portion 16a and the downstream portion 16b of the No. 6 and trying to communicate between the upstream portion 16a and the relief passage 18, the valve element is temporarily moved to the downstream portion 16 while the spool valve is sliding.
b and the open ends of the relief passage 18 are closed at the same time. Therefore, the internal pressure of the upstream portion 16a of the second discharge passage 16 may rapidly increase, and the internal pressures of the second discharge port 11 and the second discharge chamber 8 may excessively increase, which may increase the driving load of the pump. is there.
【００２４】そこで、この実施例では、隔壁１４の幅を
狭く形成し、つまり、隔壁１４の両側縁１４ａ，１４ｂ
を破線で示す位置から切欠き形成して、吐出室７，８側
において噛み合った隣接する内外歯３ａ，４ａ、３ａ，
４ａ間のボリューム室５の周方向長さＬ１よりも両側縁
１４ａ，１４ｂ間の長さＬ２を小さく設定する。これに
よって、各ロータ３，４の所定回転位置において、第１
吐出ポート１０と第２吐出ポート１１がボリューム室５
を介して連通するようになっている。したがって、前記
切換弁１９による両通路１６ｂ，１８の同時閉止にも、
第２吐出ポート１１の高圧油がボリューム室５を介して
第１吐出ポート１０に流入する。この結果、該第２吐出
ポート１１の内圧の上昇が抑制され、ポンプ駆動負荷の
増加を防止できる。Therefore, in this embodiment, the width of the partition wall 14 is narrowed, that is, both side edges 14a and 14b of the partition wall 14 are formed.
Is formed from a position indicated by a broken line, and the adjacent inner and outer teeth 3a, 4a, 3a, which mesh with each other on the discharge chambers 7 and 8 side,
The length L2 between both side edges 14a and 14b is set to be smaller than the circumferential length L1 of the volume chamber 5 between 4a. As a result, at the predetermined rotation position of each rotor 3, 4, the first
The discharge port 10 and the second discharge port 11 are the volume chamber 5
It is designed to communicate via. Therefore, even if the switching valve 19 simultaneously closes both passages 16b and 18,
The high-pressure oil in the second discharge port 11 flows into the first discharge port 10 via the volume chamber 5. As a result, an increase in the internal pressure of the second discharge port 11 is suppressed, and an increase in the pump drive load can be prevented.
【００２５】本発明は、前記実施例に限定されるもので
はなく、例えば切換弁をポンプ回転数や吐出圧等の情報
信号に基づいてコントローラにより切り換え作動する電
磁式のものに変更することも可能である。また、内燃機
関以外の油圧機器類等に適用することも可能である。The present invention is not limited to the above-mentioned embodiment, and for example, the switching valve can be changed to an electromagnetic type which is switched and operated by the controller based on the information signal such as the pump speed and the discharge pressure. Is. Further, it can be applied to hydraulic equipment other than the internal combustion engine.
【００２６】[0026]
【発明の効果】以上の説明で明らかなように、本発明に
係るオイルポンプによれば、ポンプ吐出量が所定以上に
なると、切換弁によって一方側の吐出通路とリリーフ通
路を連通させ、一方側吐出ポート内のオイルを外部へ速
やかに排出する。このため、両吐出ポートの内圧の過上
昇が抑制され、ポンプの動力損出の増加を防止すること
が可能となる。As is apparent from the above description, according to the oil pump of the present invention, when the pump discharge amount becomes a predetermined value or more, the switching valve communicates the discharge passage on one side with the relief passage to make one side. Quickly discharge the oil in the discharge port to the outside. Therefore, it is possible to prevent an excessive increase in the internal pressure of both discharge ports and prevent an increase in power loss of the pump.
【００２７】しかも、本発明は単に吐出ポート及び吐出
通路を複数設けると共に、一方側吐出通路とリリーフ通
路とを切り換える切換弁を設けるだけであるから、ポン
プ全体の構造が極めて簡素化され、製造作業能率の向上
と製造コストの低廉化が図れる。Moreover, according to the present invention, since the plurality of discharge ports and the discharge passages are simply provided and the switching valve for switching the one-side discharge passage and the relief passage is provided, the structure of the entire pump is extremely simplified, and the manufacturing work is performed. The efficiency can be improved and the manufacturing cost can be reduced.
【図１】本発明に係るオイルポンプの第１実施例を示す
全体構成図。FIG. 1 is an overall configuration diagram showing a first embodiment of an oil pump according to the present invention.
【図２】本発明の第２実施例を示す全体構成図。FIG. 2 is an overall configuration diagram showing a second embodiment of the present invention.
１…ポンプケーシング、２…駆動軸、３…インナロー
タ、４…アウタロータ、５…ボリューム室、９…吸入ポ
ート、１０，１１…第１，第２吐出ポート、１５…第１
吐出通路、１６…第２吐出通路（一方の吐出通路）、１
６ａ，１６ｂ…上下流部、１８…リリーフ通路、１９…
切換弁。DESCRIPTION OF SYMBOLS 1 ... Pump casing, 2 ... Drive shaft, 3 ... Inner rotor, 4 ... Outer rotor, 5 ... Volume chamber, 9 ... Suction port, 10, 11 ... 1st, 2nd discharge port, 15 ... 1st
Discharge passage, 16 ... Second discharge passage (one discharge passage), 1
6a, 16b ... Upstream / downstream portion, 18 ... Relief passage, 19 ...
Switching valve.
Claims (1)
するポンプケーシング内に、駆動軸により互いの内外歯
が噛合しつつ回転するインナロータとアウタロータとを
設け、該各ロータの内外歯間の容積変化を得て前記吸入
ポートから吸入したオイルを複数に分割された前記吐出
ポートに吐出するオイルポンプにおいて、前記各吐出ポ
ートに夫々接続された複数の吐出通路のうち一方の吐出
通路に、リリーフ通路を接続すると共に、該接続個所に
リリーフ通路と一方の吐出通路の上下流部を切り換える
切換弁を設けたことを特徴とするオイルポンプ。1. An inner rotor and an outer rotor, which rotate while their inner and outer teeth mesh with each other by a drive shaft, are provided in a pump casing having suction ports and discharge ports on both sides, and the volume between the inner and outer teeth of each rotor. In an oil pump that changes and discharges the oil sucked from the suction port to the plurality of discharge ports, a relief passage is provided in one of the plurality of discharge passages connected to the respective discharge ports. And a switching valve for switching between a relief passage and an upstream / downstream portion of one of the discharge passages at the connection point.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6560892A JPH05263770A (en) | 1992-03-24 | 1992-03-24 | Oil pump |
| DE19934308506 DE4308506A1 (en) | 1992-03-24 | 1993-03-17 | Oil pump for IC-engine lubrication feed - has internally and externally toothed rotors with switching valve to connect outlets |
| FR9303380A FR2689185A1 (en) | 1992-03-24 | 1993-03-24 | Engine oil pump assembly. |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6560892A JPH05263770A (en) | 1992-03-24 | 1992-03-24 | Oil pump |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2003168620A Division JP2003328959A (en) | 2003-06-13 | 2003-06-13 | Oil pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH05263770A true JPH05263770A (en) | 1993-10-12 |
Family
ID=13291900
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6560892A Pending JPH05263770A (en) | 1992-03-24 | 1992-03-24 | Oil pump |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPH05263770A (en) |
| DE (1) | DE4308506A1 (en) |
| FR (1) | FR2689185A1 (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20020052538A (en) * | 2000-12-26 | 2002-07-04 | 이계안 | Pressure control system of oil pump for vehicle |
| US6761547B2 (en) * | 2000-03-27 | 2004-07-13 | Denso Corporation | Trochoid gear type fuel pump |
| US6835054B2 (en) * | 2003-02-14 | 2004-12-28 | Hitachi Unisia Automotive, Ltd. | Oil pump |
| JP2006316672A (en) * | 2005-05-11 | 2006-11-24 | Mikuni Corp | Trochoid pump and trochoid pump device |
| JP2012154340A (en) * | 2012-04-10 | 2012-08-16 | Toyooki Kogyo Kk | Internal gear pump |
| JP2014105648A (en) * | 2012-11-28 | 2014-06-09 | Toyooki Kogyo Co Ltd | Internal gear pump |
| JP2020125731A (en) * | 2019-02-05 | 2020-08-20 | アイシン精機株式会社 | Hydraulic oil supply device |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4322614C2 (en) * | 1993-07-07 | 1997-04-24 | Iav Motor Gmbh | Internal-axis gear pump with circumferential delivery spaces, preferably with trochoid teeth |
| US5797732A (en) * | 1993-12-28 | 1998-08-25 | Unisia Jecs Corporation | Variable capacity pump having a pressure responsive relief valve arrangement |
| JP3531769B2 (en) * | 1994-08-25 | 2004-05-31 | アイシン精機株式会社 | Oil pump device |
| EP0845080B1 (en) * | 1995-08-14 | 2000-11-22 | Stackpole Limited | Outlet pressure control for internal gear pump |
| US5722815A (en) * | 1995-08-14 | 1998-03-03 | Stackpole Limited | Three stage self regulating gerotor pump |
| DE10350632A1 (en) | 2003-10-29 | 2005-06-16 | Gkn Sinter Metals Gmbh | Double or multiple pump |
| WO2008046005A2 (en) * | 2006-10-11 | 2008-04-17 | Parker-Hannifin Corporation | Pre-compression relief porting for positive displacement pumps |
| CN102878077A (en) * | 2012-10-17 | 2013-01-16 | 新乡航空工业(集团)有限公司 | Oil distribution disk and cycloid pump using same |
| DE102012223907B4 (en) * | 2012-12-20 | 2022-12-01 | Robert Bosch Gmbh | Method for manufacturing at least one rotary piston pump and a high-pressure injection system |
| CN105464974A (en) * | 2014-09-05 | 2016-04-06 | 西安航空动力控制科技有限公司 | Oil distribution disc with oil feeding cavity and oil drainage cavity |
| DE102014222396A1 (en) * | 2014-11-03 | 2016-05-04 | Continental Automotive Gmbh | displacement |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2887060A (en) * | 1953-06-22 | 1959-05-19 | American Brake Shoe Co | Variable volume pumping mechanism |
| US3067689A (en) * | 1958-10-06 | 1962-12-11 | Gen Motors Corp | Variable capacity fluid supply |
| DE3210759A1 (en) * | 1981-09-17 | 1983-10-06 | Walter Schopf | Pump combination with flow control device |
| JPS631781A (en) * | 1986-06-19 | 1988-01-06 | Daihatsu Motor Co Ltd | Torocoid type variable delivery oil pump |
| DE3824398C2 (en) * | 1987-07-23 | 1993-11-18 | Barmag Barmer Maschf | Lubricating oil pump |
-
1992
- 1992-03-24 JP JP6560892A patent/JPH05263770A/en active Pending
-
1993
- 1993-03-17 DE DE19934308506 patent/DE4308506A1/en not_active Ceased
- 1993-03-24 FR FR9303380A patent/FR2689185A1/en not_active Withdrawn
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6761547B2 (en) * | 2000-03-27 | 2004-07-13 | Denso Corporation | Trochoid gear type fuel pump |
| KR20020052538A (en) * | 2000-12-26 | 2002-07-04 | 이계안 | Pressure control system of oil pump for vehicle |
| US6835054B2 (en) * | 2003-02-14 | 2004-12-28 | Hitachi Unisia Automotive, Ltd. | Oil pump |
| CN100356063C (en) * | 2003-02-14 | 2007-12-19 | 株式会社日立制作所 | Oil pump |
| JP2006316672A (en) * | 2005-05-11 | 2006-11-24 | Mikuni Corp | Trochoid pump and trochoid pump device |
| JP2012154340A (en) * | 2012-04-10 | 2012-08-16 | Toyooki Kogyo Kk | Internal gear pump |
| JP2014105648A (en) * | 2012-11-28 | 2014-06-09 | Toyooki Kogyo Co Ltd | Internal gear pump |
| JP2020125731A (en) * | 2019-02-05 | 2020-08-20 | アイシン精機株式会社 | Hydraulic oil supply device |
Also Published As
| Publication number | Publication date |
|---|---|
| FR2689185A1 (en) | 1993-10-01 |
| DE4308506A1 (en) | 1993-09-30 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPH05263770A (en) | Oil pump | |
| US4813853A (en) | Internal gear pump | |
| EP0785361B1 (en) | Oil pump apparatus | |
| US5547349A (en) | Oil pump system | |
| US5722815A (en) | Three stage self regulating gerotor pump | |
| EP1529958B1 (en) | Oil supply system for an IC engine | |
| CA2159672C (en) | A valve train with suction-controlled ring gear/internal gear pump | |
| JP2003328959A (en) | Oil pump | |
| JPH08144965A (en) | Pump delivery control device for automatic transmission | |
| US8827659B2 (en) | Oil supply apparatus | |
| GB2340188A (en) | Hydraulic circuits for internal combustion engines | |
| JP3424409B2 (en) | Oil pump device | |
| US6387000B1 (en) | Pressure medium supply arrangement for a continuous variable transmission | |
| US6045338A (en) | Compound gear pumps and engine hydraulic circuits using same | |
| JP3371709B2 (en) | Oil pump device | |
| JP4875236B2 (en) | Oil pump device | |
| JPS63235680A (en) | Variable output oil pump | |
| EP0845080B1 (en) | Outlet pressure control for internal gear pump | |
| US6478549B1 (en) | Hydraulic pump with speed dependent recirculation valve | |
| JP3291954B2 (en) | Pump for automatic transmission | |
| US6206651B1 (en) | Oil pump for an internal combustion engine having toothed wheels | |
| JP2521973Y2 (en) | Oil pump device | |
| JPH0613869B2 (en) | Dual vane pump | |
| JPS60222579A (en) | Vane type variable capacity pump | |
| JPH0714186U (en) | Vane pump |