JP2008202488A - Pressure control device for oil pump - Google Patents

Pressure control device for oil pump Download PDF

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JP2008202488A
JP2008202488A JP2007039135A JP2007039135A JP2008202488A JP 2008202488 A JP2008202488 A JP 2008202488A JP 2007039135 A JP2007039135 A JP 2007039135A JP 2007039135 A JP2007039135 A JP 2007039135A JP 2008202488 A JP2008202488 A JP 2008202488A
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Prior art keywords
rotor
discharge
path
discharge path
passage
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JP2007039135A
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JP4521005B2 (en
Inventor
Keiichi Kai
圭一 甲斐
Kenichi Fujiki
謙一 藤木
Yasunori Ono
靖典 小野
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Yamada Manufacturing Co Ltd
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Yamada Seisakusho KK
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Priority to JP2007039135A priority Critical patent/JP4521005B2/en
Priority to DE602007012206T priority patent/DE602007012206D1/en
Priority to EP07122748A priority patent/EP1961961B1/en
Priority to ES07122748T priority patent/ES2358286T3/en
Priority to US12/000,735 priority patent/US20080253904A1/en
Priority to CN2008100092597A priority patent/CN101251108B/en
Publication of JP2008202488A publication Critical patent/JP2008202488A/en
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    • 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
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • 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
    • F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
    • F04C14/065—Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable
    • 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

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To reduce friction with keeping equivalent characteristics to pressure characteristics of ordinary oil pumps in a variable flow rate type oil pump having two delivery ports and using three rotors. <P>SOLUTION: This device comprises a first delivery passage 11 to an engine, a return passage E returning to a suction side of an outer circumference side rotor A, a second delivery passage 13 to the engine, a return passage E returning a suction side of an inner circumference side rotor B, and a pressure control valve C having a valve body 20 thereof provided between a delivery port 130 from the inner circumference side rotor B and the first delivery passage. The first delivery passage 11 and the second delivery passage 13 are connected and flow passage control is done under a condition where only the first delivery passage 11 and the second delivery passage 13 are opened in a low speed zone, under a condition where the first delivery passage 11 and the second delivery passage 13 are opened, a first inlet side of the return passage E is blocked and a second inlet side of the return passage E is opened in a middle speed zone, and under a condition where the second delivery passage 13 is blocked, the first delivery passage is opened, and the return passage E is opened in a high speed zone. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本発明は、吐出ポートが２つ存在し、該２つの吐出源を提供する手段として３つのロータを使用した可変流量タイプのオイルポンプであって、油路切り替え方法を工夫することで、圧力（油圧）特性を多段特性でなく、一般的なオイルポンプの圧力特性と同様の特性のままでありながら、フリクションを低減することができるオイルポンプにおける圧力制御装置に関する。   The present invention is a variable flow type oil pump that has two discharge ports and uses three rotors as means for providing the two discharge sources. By devising an oil passage switching method, the pressure ( The present invention relates to a pressure control device in an oil pump that can reduce friction while maintaining the same hydraulic pressure characteristic as a pressure characteristic of a general oil pump.

従来より、２か所にオイルを輸送する手段としての３つのロータ自体は特許文献１により公知である。該特許文献１では、2箇所にオイルを輸送する手段として示されているだけで、それ以上の効果は示されていない。
特開平１１−２８０６６６号 特開２００５−１４００２２ 特開２００２−７０７５６ Conventionally, the three rotors themselves as means for transporting oil to two places are known from Japanese Patent Application Laid-Open No. H10-228707. In Patent Document 1, it is only shown as a means for transporting oil to two locations, and no further effect is shown.
JP 11-280666 A JP2005-140022 JP 2002-70756 A

引用文献１では、内側ロータと外側ロータでの流量は一度製作してしまえば歯形が決まっているため、流量比率はどんな回転数でも略一定である。特に、内側歯形と外側歯形の諸元によっては内側歯間空間と外側歯間空間との間に圧力差が発生し、中間ロータが片側に押し付けられ歯面の摩耗が促進される恐れがある。つまり、圧力差によって、中間ロータの片減りが発生する重大な欠点がある。   In Cited Document 1, since the flow rate at the inner rotor and the outer rotor is determined once the tooth profile is determined, the flow rate ratio is substantially constant at any rotational speed. In particular, depending on the specifications of the inner tooth profile and the outer tooth profile, a pressure difference may be generated between the inner interdental space and the outer interdental space, and the intermediate rotor may be pressed to one side to promote tooth surface wear. That is, there is a serious drawback that the intermediate rotor is partially reduced due to the pressure difference.

特許文献２は、望んだ回転数域でオイルをリリーフさせることで、無駄仕事を減らし、その回転数域での効率アップを狙ったものである。第１３頁図８を見ると、望んだ回転数域での吐出量を下げることで、無駄仕事を減らし、効率をアップさせている。このように可変流量オイルポンプにすることにより、効率をアップさせることができるが、以下のような問題が存在する。   Patent Document 2 aims at reducing unnecessary work and improving efficiency in the rotational speed range by relieving oil in a desired rotational speed range. As shown in FIG. 8 on page 13, unnecessary work is reduced and efficiency is increased by lowering the discharge amount in the desired rotational speed range. Although the efficiency can be increased by using the variable flow rate oil pump as described above, there are the following problems.

一組のロータの吐出ポートを２分割することから吐出流路一つ一つの開口面積が少なくなり、それをカバーするためにはロータ径を大きくせざるを得ず、ロータ径を大きくするとフリクション（トルク）が大きくなり、効率が低下する欠点がある。また、無駄仕事を排除するため可変容量仕様にして効率アップを狙ったのに、効率ダウンしてしまう不都合がある。さらに、−組のロータの吐出ポートを２つに分割しただけなので、２つの吐出ポートのロータ諸元は当然同一であり、２つの吐出量の分配比の自由度には限界がある。つまり、ポート位置、開口面積には一定の設計的制約があるためである。また、２つの吐出源が同一ロータからの吐出であるため、吐出脈動のタイミングが重なり合い、騒音・振動が重なり合って大きくなってしまう欠点もある。また、ロータが1組のため、無駄仕事が発生しても、削減する手段がロータに無いという欠点もある。   Since the discharge port of a pair of rotors is divided into two, the opening area of each discharge flow path is reduced, and in order to cover it, the rotor diameter must be increased, and if the rotor diameter is increased, the friction ( (Torque) increases and the efficiency decreases. In addition, in order to eliminate useless work, there is a disadvantage that the efficiency is reduced although the variable capacity specification is aimed at increasing the efficiency. Furthermore, since the discharge ports of the pair of rotors are only divided into two, the rotor specifications of the two discharge ports are naturally the same, and the degree of freedom in the distribution ratio of the two discharge amounts is limited. That is, there are certain design restrictions on the port position and the opening area. Further, since the two discharge sources are discharges from the same rotor, there are also disadvantages that the timing of discharge pulsation overlaps and noise and vibration overlap and increase. In addition, since there is one set of rotors, there is a disadvantage that even if useless work occurs, there is no means for reducing the rotor.

そこで、本発明が解決しようとする課題（技術的課題又は目的等）としては、吐出ポートが２つ存在し、該２つの吐出源を提供する手段として３つのロータを使用した可変流量タイプのオイルポンプであって、油路切り替え方法を工夫することで、圧力（油圧）特性を多段特性でなく、一般的なオイルポンプの圧力特性（引用文献３において、その第７頁の図１０の点線を通過する非階段状の特性があり、バルブはリリーフＯＮ、OFFのみの機能を持つものである。また、特性の変極点は略1つである。）と略同様の特性のままでありながら、フリクションを低減することができる３つのロータを使用したオイルポンプを実現することである。   Therefore, as a problem (technical problem or purpose) to be solved by the present invention, there are two discharge ports, and a variable flow type oil using three rotors as means for providing the two discharge sources. By devising the oil path switching method, the pressure (hydraulic) characteristic is not a multistage characteristic, and the pressure characteristic of a general oil pump (in the cited reference 3, the dotted line in FIG. There is a non-step-like characteristic to pass through, and the valve has only the function of relief ON and OFF.In addition, the characteristic inflection point is about one.) An oil pump using three rotors that can reduce friction is realized.

そこで、発明者は上記課題を解決すべく鋭意，研究を重ねた結果、請求項１の発明を、外周側ロータと内周側ロータとを備えた３つのロータを有するオイルポンプと、前記外周側ロータからエンジンに送油する第１吐出路と、前記外周側ロータの吸入側に帰還する帰還路と、前記内周側ロータからエンジンに送油する第２吐出路と、前記内周側ロータの吸入側に帰還する前記帰還路と、弁本体が前記内周側ロータからの吐出口と前記第１吐出路との間に設けられた圧力制御弁とからなり、前記第１吐出路と前記第２吐出路とが連結され、低回転域には、第１吐出路及び第２吐出路のみが開口された状態で、中回転域には、第１吐出路と第２吐出路とが開口されると共に、前記帰還路の第１の入口側は閉鎖されて前記帰還路の第２の入口側が開口された状態で、高回転域には、第２吐出路は閉鎖されて第１吐出路が開口され、前記帰還路は開口された状態でそれぞれ流路制御されてなることを特徴とするオイルポンプにおける圧力制御装置としたことにより、前記課題を解決した。   In view of the above, the inventor has intensively and researched to solve the above-described problems. As a result, the invention of claim 1 is changed to an oil pump having three rotors including an outer rotor and an inner rotor, and the outer peripheral side. A first discharge path for feeding oil from the rotor to the engine, a return path for returning to the suction side of the outer circumferential rotor, a second discharge path for feeding oil from the inner circumferential rotor to the engine, and the inner circumferential rotor The return path returning to the suction side, and a pressure control valve having a valve body provided between the discharge port from the inner rotor and the first discharge path, the first discharge path and the first discharge path The two discharge paths are connected, only the first discharge path and the second discharge path are opened in the low rotation area, and the first discharge path and the second discharge path are opened in the middle rotation area. In addition, the first entrance side of the return path is closed and the second entrance side of the return path is opened. The oil pump is characterized in that the second discharge path is closed and the first discharge path is opened in the high rotation range, and the return path is opened and the flow path is controlled respectively. The above-mentioned problem was solved by using the pressure control device in the above.

請求項２の発明を、外周側ロータと内周側ロータとを備えた３つのロータを有するオイルポンプと、前記外周側ロータからエンジンに送油する第１吐出路と、前記外周側ロータの吸入側に帰還する第１帰還路と、前記内周側ロータからエンジンに送油する第２吐出路と、前記内周側ロータの吸入側に帰還する第２帰還路と、弁本体が前記内周側ロータからの吐出口と前記第１吐出路との間に設けられた圧力制御弁とからなり、前記第１吐出路と前記第２吐出路の端部側とが連結され、低回転域には、第１吐出路及び第２吐出路のみが開口された状態で、中回転域には、第１吐出路と第２吐出路とが開口されると共に、前記第１帰還路は閉鎖されて第２帰還路が開口された状態で、高回転域には、第２吐出路は閉鎖されて第１吐出路が開口され、第１帰還路及び第２帰還路は開口された状態でそれぞれ流路制御されてなることを特徴とするオイルポンプにおける圧力制御装置としたことにより、前記課題を解決した。   According to a second aspect of the present invention, there is provided an oil pump having three rotors including an outer peripheral rotor and an inner peripheral rotor, a first discharge passage for supplying oil from the outer peripheral rotor to the engine, and suction of the outer peripheral rotor. A first return path that returns to the side, a second discharge path that feeds oil from the inner peripheral rotor to the engine, a second return path that returns to the suction side of the inner peripheral rotor, and a valve body that is connected to the inner periphery A pressure control valve provided between the discharge port from the side rotor and the first discharge path, and the first discharge path and the end side of the second discharge path are connected to each other in a low rotation range. In the state where only the first discharge path and the second discharge path are opened, the first discharge path and the second discharge path are opened in the middle rotation region, and the first return path is closed. With the second return path opened, the second discharge path is closed and the first discharge path is opened in the high rotation range. First feedback path and said second feedback path by which the pressure control system in the oil pump, characterized in that formed by each controlled flow path opening state, has solved the problems.

請求項２の発明を、前述の構成において、前記圧力制御弁は、第１弁部と第２弁部を有するタイプとしてなることを特徴とするオイルポンプにおける圧力制御装置としたことにより、前記課題を解決した。また、請求項３の発明では、前述の構成において、前記圧力制御弁は、第１弁部と第２弁部と第３弁部を有するタイプとしてなることを特徴とするオイルポンプにおける圧力制御装置としたことにより、前記課題を解決したものである。     According to a second aspect of the present invention, in the above-described configuration, the pressure control valve is a type having a first valve portion and a second valve portion. Solved. According to a third aspect of the present invention, in the above-described configuration, the pressure control valve is of a type having a first valve portion, a second valve portion, and a third valve portion. Thus, the above-mentioned problem is solved.

請求項１の発明においては、特に、３つのロータを使用した可変流量タイプのオイルポンプであっても、設計段階で決定する圧力比を他の吐出路及び帰還路の存在によって圧力差をなくすことができるし、内周側ロータを構成する中間ロータが片側に押し付けられなくなり、その歯面の摩耗を防止でき、耐久性を向上させることができるという最大の利点がある。さらに、外周側ロータと内周側ロータとの高速回転時は内周側ロータの第２吐出路が完全に閉塞されて内周側ロータは独立回路になり、内周側ロータは無駄な仕事圧力を発生させなくてもポンプ全体圧が低下することはないという効果を得られる。また、仕事＝圧力×流量のため、圧力を下げられれば無駄仕事は削減出来、外周側ロータのポンプ（メーンポンプ）と内周側ロータのポンプ（サブポンプ）が連通していないのでサブポンプの圧力を大きく下げられる。   In the first aspect of the invention, in particular, even in a variable flow type oil pump using three rotors, the pressure ratio determined in the design stage is eliminated by the presence of other discharge passages and return passages. In addition, the intermediate rotor constituting the inner circumferential side rotor is not pressed against one side, the wear of the tooth surface can be prevented, and the durability can be improved. Furthermore, when the outer peripheral rotor and the inner peripheral rotor rotate at high speed, the second discharge path of the inner peripheral rotor is completely closed, the inner peripheral rotor becomes an independent circuit, and the inner peripheral rotor is useless work pressure. Even if it does not generate | occur | produce, the effect that the pump whole pressure does not fall can be acquired. Also, since work = pressure x flow rate, if the pressure can be reduced, wasteful work can be reduced, and the pump on the outer rotor (main pump) and the pump on the inner rotor (sub pump) are not in communication. It is greatly lowered.

また、内周側ロータのポンプ（サブポンプ）は高回転時は独立回路のため、同ポンプの帰還路開口面積を大きくすれば、より−層油が吐き出され、同ポンプの圧力はより低下する。その２つの吐出源を1つの吐出ポートを分割することなく、それぞれ1つの吐出ポートとして成り立たせることができるため、流量が分割されない。よって通常の1組のロータと比較して、３つのロータはロータ径を小さく出来て、ロータの摺動面積を減少できるため、フリクション（トルク）が小さくなり、ポンプ効率をアップさせることができる。さらに、３つのロータはロータとしてみれば２組のロータでできているため、片方のロータの無駄仕事を削減させることができる利点もある。請求項２の発明では、請求項１の発明と同等な効果を奏する。   Further, since the pump (sub pump) of the inner circumferential side rotor is an independent circuit at high speed, if the return path opening area of the pump is increased, more -layer oil is discharged and the pressure of the pump is further reduced. Since the two discharge sources can be realized as one discharge port without dividing one discharge port, the flow rate is not divided. Therefore, compared with a normal set of rotors, the three rotors can reduce the rotor diameter and reduce the sliding area of the rotor, so that the friction (torque) is reduced and the pump efficiency can be increased. Furthermore, since the three rotors are made up of two sets of rotors when viewed as rotors, there is an advantage that unnecessary work of one rotor can be reduced. The invention of claim 2 has the same effect as that of the invention of claim 1.

また、請求項３の発明では、請求項１の発明と同等な効果を奏するのみならず、簡易なる圧力制御弁の存在により、部品点数の削減が達成できる。また、請求項４の発明では、３弁タイプとした圧力制御弁の存在により、より要望に近い値の圧力制御ができるものである。   Further, in the invention of claim 3, not only the same effect as that of the invention of claim 1 is exhibited, but also the reduction of the number of parts can be achieved by the presence of a simple pressure control valve. In the invention of claim 4, pressure control with a value closer to the desired value can be performed by the presence of the pressure control valve of the three-valve type.

以下、本発明の実施形態について図面に基づいて説明すると、各図に示したものは、３つのロータ型のオイルポンプであって、主に、アウターロータ１と中間ロータ２とインナーロータ３とで構成されている。前記アウターロータ１と前記中間ロータ２とに、外周側吸入ポート４及び外周側吐出ポート５が、前記中間ロータ２と前記インナーロータ３とに、内周側吸入ポート６及び内周側吐出ポート７がそれぞれ設けられている。前記アウターロータ１と前記中間ロータ２と外周側吸入ポート４及び外周側吐出ポート５とを総称して外周側ロータと、前記中間ロータ２と前記インナーロータ３と内周側吸入ポート６及び内周側吐出ポート７とを総称して内周側ロータとそれぞれいう。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. Each figure shows three rotor-type oil pumps, which are mainly composed of an outer rotor 1, an intermediate rotor 2, and an inner rotor 3. It is configured. The outer rotor 1 and the intermediate rotor 2 have an outer peripheral suction port 4 and an outer peripheral discharge port 5, and the intermediate rotor 2 and the inner rotor 3 have an inner peripheral suction port 6 and an inner peripheral discharge port 7. Are provided. The outer rotor 1, the intermediate rotor 2, the outer peripheral suction port 4 and the outer peripheral discharge port 5 are collectively referred to as an outer peripheral rotor, the intermediate rotor 2, the inner rotor 3, an inner peripheral suction port 6, and an inner peripheral. The side discharge port 7 is collectively referred to as an inner peripheral rotor.

３つのロータ型のオイルポンプには、前記外周側吐出ポート５からエンジンＥに送油する第１吐出路１１と、前記外周側吸入ポート４の吸入路８に帰還する第１帰還路１２と、前記内周側吐出ポート７からエンジンＥに送油する第２吐出路１３と、前記内周側吸入ポート６の吸入路９に帰還する第２帰還路１４とからなり、前記第１吐出路１１の中間の適宜な位置と前記第２吐出路１３の端部側とが連結されている。また、前記吸入路８と前記吸入路９とを総称して吸入体Ｄとすることもある（図４参照）。また、前記第１帰還路１２と前記第２帰還路１４とを総称して帰還路Ｅとすることもある（図４参照）。   The three rotor-type oil pumps include a first discharge passage 11 that feeds oil from the outer peripheral discharge port 5 to the engine E, a first return passage 12 that returns to the suction passage 8 of the outer peripheral suction port 4, The first discharge path 11 includes a second discharge path 13 that feeds oil from the inner peripheral discharge port 7 to the engine E and a second return path 14 that returns to the suction path 9 of the inner peripheral suction port 6. The intermediate appropriate position is connected to the end portion side of the second discharge path 13. Further, the suction path 8 and the suction path 9 may be collectively referred to as an inhaler D (see FIG. 4). Further, the first return path 12 and the second return path 14 may be collectively referred to as a return path E (see FIG. 4).

Ｃは圧力制御弁であって、弁本体２０と弁ハウジング３０とで構成され、前記第１吐出路１１、第１帰還路１２、第２吐出路１３、第２帰還路１４間に設けられている。前記弁本体２０は、第１弁部２１と細径連結部２３と第２弁部２２とから構成されている。前記第１弁部２１と第２弁部２２を有する弁を２弁型の圧力制御弁Ｃという。また、前記圧力制御弁Ｃには、前記弁本体２０に対して適宜摺動可能な長穴部３１が形成され、該長穴部３１内において前記弁本体２０の第２弁部２２の後部側に固定された蓋体３３より圧縮コイルバネ４０による弾発力にて前記第１弁部２１側に常時押圧されている。３２は停止段部で、前記第１吐出路１１の適所に位置すると共に、前記長穴部３１の端に形成されている。   C is a pressure control valve, which is composed of a valve body 20 and a valve housing 30, and is provided between the first discharge path 11, the first return path 12, the second discharge path 13 and the second return path 14. Yes. The valve body 20 includes a first valve portion 21, a small diameter connecting portion 23, and a second valve portion 22. The valve having the first valve portion 21 and the second valve portion 22 is referred to as a two-valve pressure control valve C. Further, the pressure control valve C is formed with a long hole portion 31 that can slide appropriately with respect to the valve main body 20, and the rear side of the second valve portion 22 of the valve main body 20 in the long hole portion 31. The cover 33 is fixed to the first valve portion 21 side by the elastic force of the compression coil spring 40. Reference numeral 32 denotes a stop step portion, which is located at an appropriate position of the first discharge path 11 and is formed at the end of the elongated hole portion 31.

前記圧力制御弁Ｃの制御には、圧力状況、前記弁本体２０の直径、圧縮コイルバネ４０のバネ定数などを種々決定する事項が存在するが、前記第１吐出路１１の吐出圧の変化などによっても、種々の条件を満たす必要がある。具体的には、低回転域には、図１に示すように、第１吐出路１１及び第２吐出路１３のみが開口された状態で、中回転域には、図２に示すように、第１吐出路１１と第２吐出路１３とが開口されると共に、前記第１帰還路１２は閉鎖されて第２帰還路１４が開口された状態で、高回転域には、図３に示すように、第２吐出路１３は閉鎖されて第１吐出路１１が開口され、第１帰還路１２及び第２帰還路１４は開口された状態でそれぞれ流路制御されることが必要である。   The control of the pressure control valve C includes various items that determine the pressure state, the diameter of the valve body 20, the spring constant of the compression coil spring 40, etc., depending on the change in the discharge pressure of the first discharge passage 11 and the like. However, it is necessary to satisfy various conditions. Specifically, as shown in FIG. 1, only the first discharge path 11 and the second discharge path 13 are opened in the low rotation range, and in the middle rotation range, as shown in FIG. The first discharge path 11 and the second discharge path 13 are opened, and the first return path 12 is closed and the second return path 14 is opened. As described above, the second discharge path 13 is closed, the first discharge path 11 is opened, and the first return path 12 and the second return path 14 need to be controlled in the opened state.

次に、圧力制御弁Ｃの動作について説明する。まず、外周側ロータＡ及び内周側ロータＢが低回転域の場合、つまりエンジン回転数が低回転域の場合は、図１の状態であり、外周側ロータＡも内周側ロータＢも帰還路は圧力制御弁Ｃの第１弁部２１及び第２弁部２２にて塞がれ、第１吐出路１１及び第２吐出路１３から吐出されたオイルは全てエンジンに吐出される。外周側ロータＡの第１吐出路１１と内周側ロータＢの第２吐出路１３は連通しているので、圧力は等しくなる。また帰還路は塞がれているので、オイルポンプ全体の吐出流量は外周側ロータＡ及び内周側ロータＢの流量を足したものとなる。回転数と吐出圧力との特性表［図８（Ａ）参照］又は回転数と吐出流量との特性表［図８（Ｂ）参照］における低回転域となる。   Next, the operation of the pressure control valve C will be described. First, when the outer circumferential side rotor A and the inner circumferential side rotor B are in the low rotation range, that is, when the engine speed is in the low rotation range, the state shown in FIG. The passage is closed by the first valve portion 21 and the second valve portion 22 of the pressure control valve C, and all the oil discharged from the first discharge passage 11 and the second discharge passage 13 is discharged to the engine. Since the first discharge passage 11 of the outer rotor A and the second discharge passage 13 of the inner rotor B are in communication, the pressures are equal. In addition, since the return path is blocked, the discharge flow rate of the entire oil pump is the sum of the flow rates of the outer peripheral side rotor A and the inner peripheral side rotor B. This is a low rotation range in the characteristic table of the rotational speed and the discharge pressure [see FIG. 8A] or the characteristic table of the rotational speed and the discharge flow rate [see FIG. 8B].

さらに、エンジンの回転数が上昇した状態を、中回転域とする。この状態は、図２の状態であり、第２帰還路１４の開口部１４１が開口開始となると共に、第２吐出路１３の開口部１３１が閉鎖開始となる。具体的に説明する。外周側ロータＡの第１吐出路１１と内周側ロータＢの第２吐出路１３は連通したままである。内周側ロータＢの第２帰還路１４の開口部１４１の開口が開始となるので、まず内周側ロータＢの圧力上昇が停止する。同時に、第１吐出路１１と第２吐出路１３は連通しているので外周側ロータＡの吐出から内周側ロータＢの吐出側にオイルが逆流しそのまま内周側ロータＢの第２帰還路１４から排出され、内周側ロータＢの吸入路９に帰還する。この一連の作用状態によって外周側ロータＡ吐出と内周側ロータＢ吐出の圧力が略等しくなる。   Furthermore, let the state which the rotation speed of the engine rose be a middle rotation area. This state is the state of FIG. 2, and the opening 141 of the second return path 14 starts to open, and the opening 131 of the second discharge path 13 starts to close. This will be specifically described. The first discharge path 11 of the outer peripheral side rotor A and the second discharge path 13 of the inner peripheral side rotor B remain in communication. Since the opening of the opening 141 of the second return path 14 of the inner rotor B is started, the pressure increase of the inner rotor B first stops. At the same time, since the first discharge path 11 and the second discharge path 13 are in communication, the oil flows backward from the discharge of the outer rotor A to the discharge side of the inner rotor B, and the second return path of the inner rotor B is left as it is. 14 and is returned to the suction path 9 of the inner rotor B. By this series of action states, the pressures of the outer rotor A discharge and the inner rotor B discharge become substantially equal.

中回転域では回転数が上昇するにしたがって、内周側ロータＢの第２吐出路１３の開口部１３１がだんだん閉じていき、内周側ロータＢの第２帰還路１４の開口部１４１がだんだん開いてくるため、回転数が上昇しても全体の流量はほとんど増加しない。内周側ロータＢの吐出の真の表面にあらわれない圧力は実際には内周側ロータＢの第２帰還路１４の開口部１４１がだんだん開いてくるために、徐々に下がる。しかし、第１吐出路１１と第２吐出路１３は連通しているため、外周側ロータＡと内周側ロータＢの圧力は等しくなり、内周側ロータＢの圧力につき表面上は下がらない。   As the rotational speed increases in the middle rotation range, the opening 131 of the second discharge path 13 of the inner rotor B gradually closes, and the opening 141 of the second return path 14 of the inner rotor B gradually increases. Since it opens, the overall flow rate hardly increases even if the rotational speed increases. The pressure that does not appear on the true surface of the discharge from the inner rotor B gradually decreases because the opening 141 of the second return path 14 of the inner rotor B gradually opens. However, since the first discharge path 11 and the second discharge path 13 communicate with each other, the pressures of the outer peripheral side rotor A and the inner peripheral side rotor B become equal, and the surface does not drop with respect to the pressure of the inner peripheral side rotor B.

また、中回転域では第１帰還路１２の開口部１２１はまだ開いていないため、外周側ロータＡの吐出流量は回転数と共に増えていく。内周側ロータＢの吐出流量は回転数と共に内周側ロータＢの第２帰還路１４の開口部１４１が開いてくるため、流量は減っていく。ある一定以上の回転数になると外周側ロータＡの吐出からの逆流量の方が内周側ロータＢの吐出流量を上回るため、内周側ロータＢの吐出流量は差し引きマイナスとなる。このようにマイナスにもできるのでオイルポンプ合計流量は２つのポンプを合計した流量にもできるし、１つのポンプ以下の流量にもでき、幅広く可変できる。この中回転域は、回転数と吐出圧力又は吐出流量との圧力特性表（図８参照）に表れ、外周側ロータＡは単調増加するが、内周側ロータＢ側は、逆流してマイナスとなり、外周側ロータＡと内周側ロータＢとの合計した圧力連結線が従来のオイルポンプの圧力特性とほぼ同じにできる。   Moreover, since the opening part 121 of the 1st return path 12 has not yet opened in the middle rotation area, the discharge flow rate of the outer peripheral side rotor A increases with the rotation speed. The discharge flow rate of the inner circumferential rotor B decreases with the rotational speed because the opening 141 of the second return path 14 of the inner circumferential rotor B opens. When the rotation speed exceeds a certain level, the reverse flow rate from the discharge of the outer rotor A exceeds the discharge flow of the inner rotor B, and the discharge flow of the inner rotor B is subtracted minus. Since it can be negative in this way, the total flow rate of the oil pump can be the total flow rate of the two pumps, can be a flow rate less than one pump, and can be varied widely. This middle rotation region appears in the pressure characteristics table (see FIG. 8) of the rotational speed and the discharge pressure or discharge flow rate, and the outer rotor A increases monotonously, but the inner rotor B side reverses and becomes negative. The total pressure connecting line of the outer rotor A and the inner rotor B can be made substantially the same as the pressure characteristics of the conventional oil pump.

さらに、エンジンの回転数が増加した状態を、高回転域とする。この状態は、図３の状態であり、第１帰還路１２の開口部１２１の開口開始となると共に、第２吐出路１３の開口部１３１の閉鎖終了となる。具体的に説明する。内周側ロータＢの吐出が完全に閉鎖されるため、外周側ロータＡの吐出と内周側ロータＢの吐出の連通が無くなる。すなわち内周側ロータＢは外周側ロータＡから独立した油回路となる。内周側ロータＢには外周側ロータＡの吐出からの圧力が到達できず、内周側ロータＢの第２帰還路１４から帰還されるだけとなり、内周側ロータＢの圧力は一気に低下する。内周側ロータＢへの逆流も停止し、内周側ロータＢから吐出されたオイルは全て第２帰還路１４を介して帰還されるため、内周側ロータＢからエンジンＥヘの流量はゼロとなる。   Furthermore, the state in which the engine speed has increased is defined as a high engine speed range. This state is the state of FIG. 3, and the opening of the opening 121 of the first return path 12 starts and the closing of the opening 131 of the second discharge path 13 ends. This will be specifically described. Since the discharge of the inner peripheral rotor B is completely closed, communication between the discharge of the outer peripheral rotor A and the discharge of the inner peripheral rotor B is lost. In other words, the inner rotor B is an oil circuit independent of the outer rotor A. The pressure from the discharge of the outer peripheral side rotor A cannot reach the inner peripheral side rotor B, but is only returned from the second return path 14 of the inner peripheral side rotor B, and the pressure of the inner peripheral side rotor B decreases at a stretch. . The reverse flow to the inner circumferential side rotor B is also stopped, and all the oil discharged from the inner circumferential side rotor B is returned through the second return path 14, so that the flow rate from the inner circumferential side rotor B to the engine E is zero. It becomes.

つまり、内周側ロータＢの流量はゼロとなり、内周側ロータＢの吐出は全く仕事をしないため、フリクション（トルク）が一気に低下し、無駄仕事が削減できるためポンプ全体の効率が上昇する。この高回転域は、回転数と吐出圧力又は吐出流量との圧力特性表（図８参照）に表れ、外周側ロータＡは緩やかに上昇するが、内周側ロータＢは閉鎖状態であり、外周側ロータＡと内周側ロータＢとの合計した圧力連結線が外周側ロータＡのみとなる。このように、内周側ロータＢの圧力が下がり、フリクション（トルク）が低減するため効率が上昇する。   That is, the flow rate of the inner circumferential side rotor B becomes zero, and the discharge of the inner circumferential side rotor B does not work at all. Therefore, the friction (torque) is reduced at a stroke, and unnecessary work can be reduced, so that the efficiency of the entire pump increases. This high rotation region appears in the pressure characteristic table (see FIG. 8) of the rotation speed and the discharge pressure or the discharge flow rate, and the outer rotor A gradually rises, but the inner rotor B is in a closed state. The total pressure connecting line of the side rotor A and the inner circumferential rotor B is the outer circumferential rotor A only. In this way, the pressure on the inner circumferential rotor B decreases and the friction (torque) decreases, so that the efficiency increases.

外周側ロータＡの圧力については、中回転域では、第１吐出路１１と第２吐出路１３が連通しているために、オイルが第２帰還路１４を通って帰還されていたが、高回転域では、第１帰還路１２から引き続き帰還されるため、外周側ロータの圧力は、中回転域でも高回転域でも、ほとんど変わらない。また、外周側ロータＡの流量は第１帰還路１２の開口部１２１が開口し、開口した瞬間に第１帰還路１２に流れ出すため、流量が一旦低下した後はあまり変化しない。厳密に説明すると、回転数の上昇にしたがって極僅かに上昇する。   Regarding the pressure of the outer circumferential side rotor A, the oil is returned through the second return path 14 because the first discharge path 11 and the second discharge path 13 are in communication in the middle rotation range. In the rotation region, since the feedback is continued from the first return path 12, the pressure of the outer peripheral rotor hardly changes in the middle rotation region or the high rotation region. Further, the flow rate of the outer rotor A does not change so much after the flow rate once decreases because the opening 121 of the first return path 12 opens and flows into the first return path 12 at the moment of opening. Strictly speaking, it increases slightly as the rotational speed increases.

ポンプ全体（外周側ロータＡと内周側ロータＢの総和）としての「圧力」は、内周側ロータＢの第２吐出路１３の開口部１３１が完全閉鎖されているため、外周側ロータＡのみの圧力となる。外周側ロータＡの圧力は第１帰還路１２の開口部１２１が開口しているため、あまり変化しないが、厳密に言えば回転数増加にしたがって、極僅かずつ増加する。また、ポンプ全体としての「流量」は、内周側ロータＢの第２吐出路１３の開口部１３１が完全閉鎖されているため、外周側ロータＡの「流量」がポンプ全体流量となる。外周側ロータＡの流量は第１帰還路１２の開口部１２１が開口しているため、あまり変化しないが、厳密に言えば回転数増加にしたがって、極僅かずつ増加する。   The "pressure" as the entire pump (the sum of the outer peripheral rotor A and the inner peripheral rotor B) is the outer peripheral rotor A because the opening 131 of the second discharge passage 13 of the inner peripheral rotor B is completely closed. Only pressure. The pressure of the outer rotor A does not change much because the opening 121 of the first return path 12 is open, but strictly speaking, it increases little by little as the rotational speed increases. Moreover, since the opening 131 of the second discharge passage 13 of the inner circumferential rotor B is completely closed, the “flow rate” of the outer circumferential rotor A becomes the entire pump flow rate. The flow rate of the outer rotor A does not change so much because the opening 121 of the first return path 12 is open. Strictly speaking, the flow rate increases slightly as the rotational speed increases.

さらに、圧力制御弁Ｃの別の実施形態について説明する。該圧力制御弁Ｃは、弁本体２０と弁ハウジング３０とで構成され、前記第１吐出路１１、第１帰還路１２、第２吐出路１３、第２帰還路１４間に設けられている。前記弁本体２０は、第１弁部２１と細径連結部２３と第２弁部２２と第３弁部２４と細径連結部２５とから構成されている。他の構成は、図１乃至図３と同等である。前記第１弁部２１と第２弁部２２と第３弁部２４とを有する弁を３弁型の圧力制御弁Ｃという。   Furthermore, another embodiment of the pressure control valve C will be described. The pressure control valve C includes a valve body 20 and a valve housing 30 and is provided between the first discharge path 11, the first return path 12, the second discharge path 13, and the second return path 14. The valve body 20 includes a first valve portion 21, a small diameter connecting portion 23, a second valve portion 22, a third valve portion 24, and a small diameter connecting portion 25. Other configurations are the same as those in FIGS. 1 to 3. A valve having the first valve portion 21, the second valve portion 22, and the third valve portion 24 is referred to as a three-valve pressure control valve C.

この作用について説明する。まず、外周側ロータＡ及び内周側ロータＢが低回転域の場合、つまりエンジン回転数が低回転域の場合は、図４の状態であり、外周側ロータＡも内周側ロータＢも帰還路は圧力制御弁Ｃの第１弁部２１及び第３弁部２４にて塞がれ、第１吐出路１１及び第２吐出路１３から吐出されたオイルは全てエンジンに吐出される。外周側ロータＡの第１吐出路１１と内周側ロータＢの第２吐出路１３は連通しているので、圧力は等しくなる。また帰還路は塞がれているので、オイルポンプ全体の吐出流量は外周側ロータＡ及び内周側ロータＢの流量を足したものとなる。   This operation will be described. First, when the outer peripheral rotor A and the inner peripheral rotor B are in the low rotation range, that is, when the engine speed is in the low rotation range, the state shown in FIG. The passage is closed by the first valve portion 21 and the third valve portion 24 of the pressure control valve C, and all the oil discharged from the first discharge passage 11 and the second discharge passage 13 is discharged to the engine. Since the first discharge passage 11 of the outer rotor A and the second discharge passage 13 of the inner rotor B are in communication, the pressures are equal. In addition, since the return path is blocked, the discharge flow rate of the entire oil pump is the sum of the flow rates of the outer peripheral side rotor A and the inner peripheral side rotor B.

さらに、エンジンの回転数が上昇した状態を、中回転域とする。この状態では、図５の状態であり、第２帰還路１４の開口部１４１が開口開始となると共に、第２吐出路１３の開口部１３１が閉鎖になるように開始される。その説明は省略する。エンジンの回転数が増加した状態を、高回転域とする。この状態では、図６の状態であり、第１帰還路１２の開口部１２１の開口開始となると共に、第２吐出路１３の開口部１３１の閉鎖の終了となる。内周側ロータＢの吐出が完全に閉鎖されるため、外周側ロータＡの吐出と内周側ロータＢの吐出の連通が無くなる。すなわち内周側ロータＢは外周側ロータＡから独立した油回路となる。内周側ロータＢには外周側ロータＡの吐出からの圧力が到達できず、内周側ロータＢの第２帰還路１４から帰還されるだけとなり、内周側ロータＢの圧力は一気に低下する。内周側ロータＢへの逆流も停止し、内周側ロータＢから吐出されたオイルは全て第２帰還路１４を介して帰還されるため、内周側ロータＢからエンジンＥヘの流量はゼロとなる。   Furthermore, let the state which the rotation speed of the engine rose be a middle rotation area. In this state, the state shown in FIG. 5 is started, and the opening 141 of the second return path 14 starts to be opened, and the opening 131 of the second discharge path 13 is started to be closed. The description is omitted. A state in which the engine speed has increased is defined as a high engine speed range. This state is the state of FIG. 6, and the opening of the opening 121 of the first return path 12 is started and the closing of the opening 131 of the second discharge path 13 is ended. Since the discharge of the inner peripheral rotor B is completely closed, communication between the discharge of the outer peripheral rotor A and the discharge of the inner peripheral rotor B is lost. In other words, the inner rotor B is an oil circuit independent of the outer rotor A. The pressure from the discharge of the outer peripheral side rotor A cannot reach the inner peripheral side rotor B, but is only returned from the second return path 14 of the inner peripheral side rotor B, and the pressure of the inner peripheral side rotor B decreases at a stretch. . The reverse flow to the inner circumferential side rotor B is also stopped, and all the oil discharged from the inner circumferential side rotor B is returned through the second return path 14, so that the flow rate from the inner circumferential side rotor B to the engine E is zero. It becomes.

つまり、内周側ロータＢの流量はゼロとなり、内周側ロータＢの吐出は全く仕事をしないため、フリクション（トルク）が一気に低下し、無駄仕事が削減できるためポンプ全体の効率が上昇する。この高回転域は、回転数と吐出圧力又は吐出流量との圧力特性表（図８参照）に表れ、外周側ロータＡは緩やかに上昇するが、内周側ロータＢは閉鎖状態であり、外周側ロータＡと内周側ロータＢとの合計した圧力連結線が外周側ロータＡのみとなる。このように、内周側ロータＢの圧力が下がるため、フリクション（トルク）が低減するため効率が上昇する。   That is, the flow rate of the inner circumferential side rotor B becomes zero, and the discharge of the inner circumferential side rotor B does not work at all. Therefore, the friction (torque) is reduced at a stroke, and unnecessary work can be reduced, so that the efficiency of the entire pump increases. This high rotation region appears in the pressure characteristic table (see FIG. 8) of the rotation speed and the discharge pressure or the discharge flow rate, and the outer rotor A gradually rises, but the inner rotor B is in a closed state. The total pressure connecting line of the side rotor A and the inner circumferential rotor B is the outer circumferential rotor A only. Thus, since the pressure of the inner circumferential rotor B is lowered, the friction (torque) is reduced, and the efficiency is increased.

外周側ロータＡの圧力については、中回転域では、第１吐出路１１と第２吐出路１３が連通しているために、オイルが第２帰還路１４を通って帰還されていたが、高回転域では、第１帰還路１２から引き続き帰還されるため、外周側ロータの圧力は、中回転域でも高回転域でも、ほとんど変わらない。また、外周側ロータＡの流量は第１帰還路１２の開口部１２１が開口し、開口した瞬間に第１帰還路１２に流れ出すため、流量が一旦低下した後はあまり変化しない。厳密に説明すると、回転数の上昇にしたがって極僅かに上昇する。   Regarding the pressure of the outer circumferential side rotor A, the oil is returned through the second return path 14 because the first discharge path 11 and the second discharge path 13 are in communication in the middle rotation range. In the rotation region, since the feedback is continued from the first return path 12, the pressure of the outer peripheral rotor hardly changes in the middle rotation region or the high rotation region. Further, the flow rate of the outer rotor A does not change so much after the flow rate once decreases because the opening 121 of the first return path 12 opens and flows into the first return path 12 at the moment of opening. Strictly speaking, it increases slightly as the rotational speed increases.

ポンプ全体（外周側ロータＡと内周側ロータＢの総和）としての「圧力」は、内周側ロータＢの第２吐出路１３の開口部１３１が完全閉鎖されているため、外周側ロータＡのみの圧力となる。外周側ロータＡの圧力は第１帰還路１２の開口部１２１が開口しているため、あまり変化しないが、厳密に言えば回転数増加にしたがって、極僅かずつ増加する。また、ポンプ全体としての「流量」は、内周側ロータＢの第２吐出路１３の開口部１３１が完全閉鎖されているため、外周側ロータＡの「流量」がポンプ全体流量となる。外周側ロータＡの流量は第１帰還路１２の開口部１２１が開口しているため、あまり変化しないが、厳密に言えば回転数増加にしたがって、極僅かずつ増加する。   The "pressure" as the entire pump (the sum of the outer peripheral rotor A and the inner peripheral rotor B) is the outer peripheral rotor A because the opening 131 of the second discharge passage 13 of the inner peripheral rotor B is completely closed. Only pressure. The pressure of the outer rotor A does not change much because the opening 121 of the first return path 12 is open, but strictly speaking, it increases little by little as the rotational speed increases. Moreover, since the opening 131 of the second discharge passage 13 of the inner circumferential rotor B is completely closed, the “flow rate” of the outer circumferential rotor A becomes the entire pump flow rate. The flow rate of the outer rotor A does not change so much because the opening 121 of the first return path 12 is open. Strictly speaking, the flow rate increases slightly as the rotational speed increases.

以上のように、本願発明は、オイルポンプにおける圧力制御装置であるが、可変流量オイルポンプでもある。また、吐出ポートが２つ存在し、該２つの吐出源を提供する手段として３つのロータを使用したオイルポンプである。また、ポンプの消費動力の大きい高回転時に内周側ロータＢの吐出口１３０又は第２吐出路１３が塞がれるため、外周側ロータＡと内周側ロータＢとは切り離される。内周側ロータＢの流量や圧力はポンプ全体の流量や圧力に何ら影響を与えなくなるため、効率アップなどを狙って内周側ロータＢの流量や圧力を調節しても、ポンプ特性には何の影響も与えないため設計自由度がアップできる。   As described above, the present invention is a pressure control device in an oil pump, but is also a variable flow rate oil pump. In addition, the oil pump includes two discharge ports and uses three rotors as means for providing the two discharge sources. Further, since the discharge port 130 or the second discharge passage 13 of the inner peripheral rotor B is closed during high rotation with high power consumption of the pump, the outer peripheral rotor A and the inner peripheral rotor B are separated. The flow rate and pressure of the inner rotor B do not affect the flow rate and pressure of the entire pump. Therefore, even if the flow rate and pressure of the inner rotor B are adjusted to improve efficiency, the pump characteristics The degree of freedom in design can be improved.

本発明の第１実施形態のシステム図であって、エンジンの低回転域での状態図である。It is a system diagram of a 1st embodiment of the present invention, and is a state figure in a low engine speed range. 本発明の第１実施形態のシステム図であって、エンジンの中回転域での状態図である。It is a system diagram of a 1st embodiment of the present invention, and is a state figure in an engine middle speed range. 本発明の第１実施形態のシステム図であって、エンジンの高回転域での状態図である。It is a system diagram of a 1st embodiment of the present invention, and is a state figure in a high engine speed range. 本発明の第２実施形態のシステム図であって、エンジンの低回転域での状態図である。It is a system diagram of a second embodiment of the present invention, and is a state diagram in a low rotation range of the engine. 本発明の第２実施形態の一部のシステム図であって、エンジンの中回転域での状態図である。It is a system diagram of a part of the second embodiment of the present invention, and is a state diagram in an intermediate rotation region of an engine. 本発明の第２実施形態の一部のシステム図であって、エンジンの高回転域での状態図である。It is a system diagram of a part of the second embodiment of the present invention, and is a state diagram in a high engine speed range. 本発明の簡略のシステム図である。1 is a simplified system diagram of the present invention. （Ａ）は本発明におけるエンジン回転数と吐出圧力との特性表、（Ｂ）は本発明におけるエンジン回転数と吐出流量との特性表である。(A) is a characteristic table of engine speed and discharge pressure in the present invention, and (B) is a characteristic table of engine speed and discharge flow rate in the present invention.

符号の説明Explanation of symbols

Ａ…外周側ロータ、Ｂ…内周側ロータ、Ｅ…エンジン、１１…第１吐出路、
８，９…吸入路、１２…第１帰還路、１３…第２吐出路、１４…第２帰還路、
Ｃ…圧力制御弁、２１…第１弁部、２２…第２弁部、２４…第３弁部。 A: Outer rotor, B: Inner rotor, E: Engine, 11: First discharge path,
8, 9 ... suction path, 12 ... first return path, 13 ... second discharge path, 14 ... second return path,
C ... Pressure control valve, 21 ... First valve portion, 22 ... Second valve portion, 24 ... Third valve portion.

Claims (4)

外周側ロータと内周側ロータとを備えた３つのロータを有するオイルポンプと、前記外周側ロータからエンジンに送油する第１吐出路と、前記外周側ロータの吸入側に帰還する帰還路と、前記内周側ロータからエンジンに送油する第２吐出路と、前記内周側ロータの吸入側に帰還する前記帰還路と、弁本体が前記内周側ロータからの吐出口と前記第１吐出路との間に設けられた圧力制御弁とからなり、前記第１吐出路と前記第２吐出路とが連結され、低回転域には、第１吐出路及び第２吐出路のみが開口された状態で、中回転域には、第１吐出路と第２吐出路とが開口されると共に、前記帰還路の第１の入口側は閉鎖されて前記帰還路の第２の入口側が開口された状態で、高回転域には、第２吐出路は閉鎖されて第１吐出路が開口され、前記帰還路は開口された状態でそれぞれ流路制御されてなることを特徴とするオイルポンプにおける圧力制御装置。   An oil pump having three rotors including an outer rotor and an inner rotor, a first discharge passage for sending oil from the outer rotor to the engine, and a return passage for returning to the suction side of the outer rotor A second discharge path for feeding oil from the inner circumferential rotor to the engine, the return path for returning to the suction side of the inner circumferential rotor, a valve body having a discharge port from the inner circumferential rotor and the first A pressure control valve provided between the discharge path, the first discharge path and the second discharge path are connected, and only the first discharge path and the second discharge path are open in the low rotation range. In this state, the first discharge path and the second discharge path are opened in the middle rotation region, the first inlet side of the return path is closed, and the second inlet side of the return path is opened. In this state, the second discharge path is closed and the first discharge path is opened in the high rotation range, Kaero the pressure control system in the oil pump, characterized in that formed by each controlled channel at the opening state. 外周側ロータと内周側ロータとを備えた３つのロータを有するオイルポンプと、前記外周側ロータからエンジンに送油する第１吐出路と、前記外周側ロータの吸入側に帰還する第１帰還路と、前記内周側ロータからエンジンに送油する第２吐出路と、前記内周側ロータの吸入側に帰還する第２帰還路と、弁本体が前記内周側ロータからの吐出口と前記第１吐出路との間に設けられた圧力制御弁とからなり、前記第１吐出路と前記第２吐出路の端部側とが連結され、低回転域には、第１吐出路及び第２吐出路のみが開口された状態で、中回転域には、第１吐出路と第２吐出路とが開口されると共に、前記第１帰還路は閉鎖されて第２帰還路が開口された状態で、高回転域には、第２吐出路は閉鎖されて第１吐出路が開口され、第１帰還路及び第２帰還路は開口された状態でそれぞれ流路制御されてなることを特徴とするオイルポンプにおける圧力制御装置。   An oil pump having three rotors including an outer circumferential rotor and an inner circumferential rotor, a first discharge passage for sending oil from the outer circumferential rotor to the engine, and a first feedback returning to the suction side of the outer circumferential rotor A second discharge path that feeds oil from the inner rotor to the engine, a second return path that returns to the suction side of the inner rotor, and a valve body that discharges from the inner rotor. A pressure control valve provided between the first discharge path, the first discharge path and the end of the second discharge path are connected to each other, and the low rotation range includes the first discharge path and In the state where only the second discharge path is opened, the first discharge path and the second discharge path are opened in the middle rotation region, and the first return path is closed and the second return path is opened. In the high rotation region, the second discharge path is closed and the first discharge path is opened, and the first return path and the first Feedback path pressure control system in the oil pump, characterized in that formed by each controlled channel at the opening state. 請求項１又は２の発明において、前記圧力制御弁は、第１弁部と第２弁部を有するタイプとしてなることを特徴とするオイルポンプにおける圧力制御装置。   The pressure control device for an oil pump according to claim 1 or 2, wherein the pressure control valve is of a type having a first valve portion and a second valve portion. 請求項１又は２の発明において、前記圧力制御弁は、第１弁部と第２弁部と第３弁部を有するタイプとしてなることを特徴とするオイルポンプにおける圧力制御装置。   3. The pressure control device for an oil pump according to claim 1, wherein the pressure control valve is of a type having a first valve portion, a second valve portion, and a third valve portion.
JP2007039135A 2007-02-20 2007-02-20 Pressure control device in oil pump Expired - Fee Related JP4521005B2 (en)

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JP2007039135A JP4521005B2 (en) 2007-02-20 2007-02-20 Pressure control device in oil pump
DE602007012206T DE602007012206D1 (en) 2007-02-20 2007-12-10 Device for controlling the oil pump pressure
EP07122748A EP1961961B1 (en) 2007-02-20 2007-12-10 Oil pump pressure control device
ES07122748T ES2358286T3 (en) 2007-02-20 2007-12-10 OIL PUMP PRESSURE CONTROL DEVICE.
US12/000,735 US20080253904A1 (en) 2007-02-20 2007-12-17 Oil pump pressure control device
CN2008100092597A CN101251108B (en) 2007-02-20 2008-01-31 Oil pump pressure control device

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EP1961961B1 (en) 2011-01-26

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