JPS6347916B2 - - Google Patents

Info

Publication number
JPS6347916B2
JPS6347916B2 JP59204700A JP20470084A JPS6347916B2 JP S6347916 B2 JPS6347916 B2 JP S6347916B2 JP 59204700 A JP59204700 A JP 59204700A JP 20470084 A JP20470084 A JP 20470084A JP S6347916 B2 JPS6347916 B2 JP S6347916B2
Authority
JP
Japan
Prior art keywords
rotor
discharge chamber
inner rotor
outer rotor
angle
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
Application number
JP59204700A
Other languages
Japanese (ja)
Other versions
JPS6181588A (en
Inventor
Atsushi Satomoto
Takashi Nakagawa
Koji Morita
Junichiro Sakurai
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aisin Corp
Original Assignee
Aisin Seiki Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Aisin Seiki Co Ltd filed Critical Aisin Seiki Co Ltd
Priority to JP20470084A priority Critical patent/JPS6181588A/en
Publication of JPS6181588A publication Critical patent/JPS6181588A/en
Publication of JPS6347916B2 publication Critical patent/JPS6347916B2/ja
Granted legal-status Critical Current

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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0049—Equalization of pressure pulses
    • 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)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Rotary Pumps (AREA)

Abstract

PURPOSE:To prevent peak pressure in a sealed working chamber and pulsation in discharge pressure from occurring by providing a rotor end of at least either of an outer rotor or an inner rotor with a groove to keep a sealed working space in communication with a discharge chamber. CONSTITUTION:When a sealed working space 15 occupies the maximum volume, an angle from the tooth bottom position 16 of an inner rotor 12 to a position 17 at which the tooth tip of an outer rotor 11 comes first into contact with that of the inner rotor 12 in rotating direction is represented as l1, and an angle from the tooth bottom position 16 of the inner rotor 12 to its second tooth bottom position 18 in rotating direction is represented as l2. In this case, a discharge chamber 14 is formed in rotating direction from an angle l being l2>=l>=l1. Each rotor end 19 of the inner rotor 12 is provided with a shallow groove 20 to keep a sealed working chamber in communication with with the discharge chamber 14. Thus oil is never compressed in the working chamber to have no peak pressure.

Description

【発明の詳細な説明】 〔発明の目的〕 （産業上の利用分野） 本発明は、自動車エンジンの潤滑油用オイルポ
ンプに関するもので、より詳しくはインナーロー
タとアウターロータ間の隙間（密封空間）の容積
変化によりポンプ作用を行うトロコイド型オイル
ポンプに関するものである。[Detailed Description of the Invention] [Object of the Invention] (Industrial Field of Application) The present invention relates to an oil pump for lubricating oil of an automobile engine, and more specifically relates to a gap (sealed space) between an inner rotor and an outer rotor. This relates to a trochoid type oil pump that performs a pumping action by changing the volume of the oil pump.

（従来の技術） この種のオイルポンプの一例として、特開昭58
−35212号公報に記載されるものが知られている。
このトロコイド型オイルポンプは、エンジンブロ
ツクの側面との間に内部空間を形成する様にハウ
ジングが固定され、該ハウジングの内部空間に第
４図に示される様に環状のアウターロータ５０が
回転自在に嵌合され、該アウターロータ５０の内
歯５０ａに係合する外歯５１ａを有し４葉トロコ
イド曲線を有するインナーロータ５１がアウター
ロータ５０内に嵌合され、インナーロータ５１は
該ロータ５１に結合され前記ハウジングに軸支さ
れる回転シヤフトにより駆動される。ハウジング
の内部空間の底部より更に深く、吸入チヤンバ５
２と吐出チヤンバ５３が形成され、該両チヤンバ
は夫々ハウジング内部空間に連通している。内歯
５０ａと外歯５１ａにより囲まれる密閉空間（図
示斜線部分）５４の容積変化により、吐出室５３
側に吐出される。(Prior art) As an example of this type of oil pump,
The one described in Publication No. -35212 is known.
In this trochoid type oil pump, a housing is fixed to form an internal space between the housing and the side surface of the engine block, and an annular outer rotor 50 is rotatably mounted in the internal space of the housing as shown in FIG. An inner rotor 51 is fitted into the outer rotor 50 and has outer teeth 51a that engage with the inner teeth 50a of the outer rotor 50 and has a four-lobed trochoid curve. and is driven by a rotating shaft pivotally supported by the housing. Deeper than the bottom of the internal space of the housing, the suction chamber 5
2 and a discharge chamber 53 are formed, each of which communicates with the interior space of the housing. Due to the volume change of the sealed space (shaded area in the figure) 54 surrounded by the internal teeth 50a and the external teeth 51a, the discharge chamber 53
Discharged to the side.

一方、特開昭58−70014号公報に記載されるオ
イルポンプは、クランクシヤフト直結式のもので
ある。すなわち、ハウジングの内部空間に第５図
に示される環状アウターロータ６０が回転自在に
嵌合され、該アウターロータ６０の内歯６０ａに
係合する外歯６１ａを有するインナーロータ６１
がアウターロータ６０内に嵌合され、該インナー
ロータ６１はクランクシヤフトにより直接駆動さ
れる。ハウジングの内部空間の底部より更に深
く、吸入チヤンバ６２と吐出チヤンバ６３が形成
され、該両チヤンバは夫々前記内部空間に連通し
ている。内歯６０ａと外歯６１ａにより囲まれる
密閉空間（図中斜線部分）６４の容積変化によ
り、吐出チヤンバ６３に排出される。 On the other hand, the oil pump described in Japanese Unexamined Patent Publication No. 58-70014 is of the type that is directly connected to the crankshaft. That is, an annular outer rotor 60 shown in FIG. 5 is rotatably fitted into the internal space of the housing, and an inner rotor 61 having external teeth 61a that engages with internal teeth 60a of the outer rotor 60.
is fitted within the outer rotor 60, and the inner rotor 61 is directly driven by the crankshaft. Deeper than the bottom of the interior space of the housing, a suction chamber 62 and a discharge chamber 63 are formed, each of which communicates with said interior space. The fluid is discharged into the discharge chamber 63 due to a change in volume of the sealed space (shaded area in the figure) 64 surrounded by the internal teeth 60a and the external teeth 61a.

（発明が解決しようとする問題点） 上記した従来のオイルポンプに於いては、例え
ば第５図の従来例に基づいて説明すると、密封空
間６４の最大時に於けるインナーロータ６１の歯
底位置６５（第４図の従来例では番号符号５５で
示される）を基準として、回転方向（反時計回
り）に沿つて第１番目に両歯の接する位置６６か
ら吐出チヤンバ６３が形成されている。つまり、
吐出チヤンバ６３のハウジング内部空間への開口
部は、上記位置６６から回転方向に延在するよう
に形成される。しかしながら、この従来のオイル
ポンプに於いては、インナーロータ６１が回転す
ると、吐出チヤンバ６３と密封空間６４との連通
が即座に開始し、しかも連通面積が急激に拡大し
且つ吐出チヤンバ６３はハウジング内に深く形成
されている。その為、吐出チヤンバ６３の吐出圧
の影響を受けて油が吐出チヤンバ６３より密封空
間６４内に逆流し、その結果密封空間６４内で吐
出圧より高いピーク圧が発生すると共に圧力変動
が起きる。この圧力変動の伝播により、両ロータ
の回転が変動し、油圧回路の共振等により騒音や
歯の摩耗を引き起こすという問題があつた。(Problems to be Solved by the Invention) In the above-described conventional oil pump, for example, based on the conventional example shown in FIG. (Indicated by the number 55 in the conventional example in FIG. 4), a discharge chamber 63 is formed from a position 66 where both teeth first contact along the rotation direction (counterclockwise). In other words,
The opening of the discharge chamber 63 into the housing interior space is formed so as to extend from the position 66 in the rotational direction. However, in this conventional oil pump, when the inner rotor 61 rotates, communication between the discharge chamber 63 and the sealed space 64 immediately starts, and the communication area rapidly expands, and the discharge chamber 63 is located inside the housing. is deeply formed. Therefore, oil flows back from the discharge chamber 63 into the sealed space 64 under the influence of the discharge pressure of the discharge chamber 63, and as a result, a peak pressure higher than the discharge pressure is generated in the sealed space 64, and pressure fluctuations occur. Due to the propagation of this pressure fluctuation, the rotation of both rotors fluctuates, causing problems such as resonance of the hydraulic circuit and causing noise and tooth wear.

従つて本発明は、上述の従来技術の有する問題
点に鑑みて、吐出チヤンバから密封空間への油の
逆流を阻止することを、その技術的課題とする。 Therefore, in view of the problems of the prior art described above, the technical object of the present invention is to prevent the backflow of oil from the discharge chamber to the sealed space.

〔発明の構成〕[Structure of the invention]

（問題点を解決するための手段） 上記技術的課題を解決するために講じた技術的
手段は、アウターロータの内歯とインナーロータ
の外歯とにより形成される密封空間の最大時に於
けるインナーロータの歯底位置を基準として反回
転方向に沿つて最初にアウターロータとインナー
ロータの歯先が接する位置まで吸入チヤンバを延
在して形成させると共に、回転方向に沿つて最初
にアウターロータとインナーロータの歯先が接す
る位置までの角度をl1とし、インナーロータの歯
底位置より回転方向に沿つて第２番目の歯底位置
までの角度をl2とし、l1≦ｌ≦l2となる角度ｌを
設定し、該角度ｌから回転方向に延在するように
吐出チヤンバを形成し、密閉空間と吐出チヤンバ
とを連通可能とする溝をアウターロータとインナ
ーロータの少なくとも一方の吸入チヤンバ及び吐
出チヤンバが面する側の反対側のロータ端面に設
ける、ことである。 (Means for solving the problem) The technical means taken to solve the above technical problem is that when the sealed space formed by the inner teeth of the outer rotor and the outer teeth of the inner rotor is at its maximum, A suction chamber is formed by extending along the counter-rotation direction from the tooth bottom position of the rotor to a position where the tooth tips of the outer rotor and the inner rotor first contact each other, and also Let l 1 be the angle to the point where the rotor tooth tips touch, and let l 2 be the angle from the inner rotor tooth bottom position to the second tooth bottom position along the rotational direction, and l 1 ≦l ≦ l 2 . A discharge chamber is formed to extend in the rotational direction from the angle l, and a groove that enables communication between the closed space and the discharge chamber is formed in the suction chamber of at least one of the outer rotor and the inner rotor. It is provided on the end face of the rotor opposite to the side facing the discharge chamber.

（作用） これにより、密封空間が最大になるまで油を吸
い込ませて完全に充填された状態にて吐出チヤン
バに密封空間が開口するまでロータが回転するに
つれ、密封空間の容積が減少し逃げ道のない油が
徐々に溝を通して吐出チヤンバに吐出されるた
め、密封空間において大きな内圧上昇を的確に抑
制することができると共に、密封空間と吐出チヤ
ンバとの圧力差を小さくすることができ、それに
より吐出チヤンバから密封空間への油の逆流が防
止され、圧力変動の発生を抑制し騒音及び歯の摩
耗を防止することができる。(Function) As the rotor rotates until the oil is sucked in until the sealed space reaches its maximum level and the sealed space opens in the discharge chamber in a completely filled state, the volume of the sealed space decreases and there is no escape route. Since the remaining oil is gradually discharged into the discharge chamber through the groove, it is possible to accurately suppress a large increase in internal pressure in the sealed space, and to reduce the pressure difference between the sealed space and the discharge chamber, thereby reducing the Backflow of oil from the chamber to the sealed space is prevented, pressure fluctuations are suppressed, and noise and tooth wear can be prevented.

（実施例） 以下、本発明の技術的手段を具体化した実施例
について、添付図面に基づいて説明する。(Example) Hereinafter, an example embodying the technical means of the present invention will be described based on the accompanying drawings.

第１図は本発明の第１実施例を示すオイルポン
プ１０は、ハウジング（図示せず）の内部空間に
回転自在に嵌合される環状のアウターロータ１１
を有し、該アウターロータ１１の内歯１１ａに係
合する外歯１２ａを有するインナーロータ１２
が、アウターロータ１１内に配設される。すなわ
ち、インナーロータ１２は、アウターロータ１１
の回転中心O1から偏心した回転中心O2を備える。 FIG. 1 shows a first embodiment of the present invention. An oil pump 10 has an annular outer rotor 11 that is rotatably fitted into an internal space of a housing (not shown).
and has external teeth 12a that engage with internal teeth 11a of the outer rotor 11.
is arranged within the outer rotor 11. That is, the inner rotor 12 is the outer rotor 11
It has a rotation center O 2 that is eccentric from the rotation center O 1 of .

ハウジングの内部空間の底部より更に深く、吸
入チヤンバ１３と吐出チヤンバ１４が夫々形成さ
れる。アウターロータ１１の内歯１１ａとインナ
ーロータ１２の外歯１２ａとにより形成される密
封空間１５（図中斜線部分）の最大時に於ける、
インナーロータ１２の歯底位置１６を基準として
回転方向に沿つて最初にアウターロータ１１とイ
ンナーロータ１２の歯先が接する位置１７までの
角度をl1とし、インナーロータ１２の歯底位置１
６より回転方向に沿つて第２番目の歯底位置１８
までの角度をl2とし、l1≦ｌ≦l2となる角度ｌと
設定し、該角度ｌから回転方向に延在するように
前記吐出チヤンバ１４が形成される。更に、イン
ナーロータ１２の吸入チヤンバ１３及び吐出チヤ
ンバ１４の面した反対側の各ロータ端面１９に浅
い溝２０が形成され、該溝２０を介して密封空間
１５と吐出チヤンバ１４とのなお、吸入チヤンバ
１３はアウターロータ１１の内歯とインナーロー
タ１２の外歯とにより形成される密封空間の最大
時に於けるインナーロータ１２の歯底位置を基準
として反回転方向に沿つて最初にアウターロータ
１１とインナーロータ１２の歯先が接する位置ま
で延在して形成されており、密封空間が密閉され
た状態にてその容積が拡大されないようにしてキ
ヤビテーシヨンの発生を防止していると共に、容
積効率の向上をはかつている。 Deeper than the bottom of the interior space of the housing, a suction chamber 13 and a discharge chamber 14 are formed, respectively. When the sealed space 15 (shaded area in the figure) formed by the internal teeth 11a of the outer rotor 11 and the external teeth 12a of the inner rotor 12 is at its maximum,
The angle from the tooth bottom position 16 of the inner rotor 12 to the position 17 where the tooth tips of the outer rotor 11 and the inner rotor 12 first touch each other along the rotation direction is defined as l 1 , and the tooth bottom position 1 of the inner rotor 12 is defined as l 1.
6, the second tooth root position 18 along the rotational direction
The discharge chamber 14 is formed so as to extend from the angle l in the rotational direction. Further, a shallow groove 20 is formed in each rotor end face 19 of the inner rotor 12 on the opposite side facing the suction chamber 13 and the discharge chamber 14, and the sealing space 15 and the discharge chamber 14 are connected via the groove 20. Reference numeral 13 indicates that the outer rotor 11 and the inner rotor are first aligned in the counter-rotation direction with reference to the tooth bottom position of the inner rotor 12 when the sealed space formed by the inner teeth of the outer rotor 11 and the outer teeth of the inner rotor 12 is at its maximum. It is formed to extend to the position where the tips of the teeth of the rotor 12 come into contact, and prevents the volume of the sealed space from expanding in a sealed state, thereby preventing the occurrence of cavitation and improving volumetric efficiency. It's getting older.

インナーロータ１２が回転すると密封空間１５
の容積が減少し内部油圧が増大する。この容積減
少分の油が、ロータ端面の浅い溝２０を介して吐
出チヤンハ１４に徐々に流出する。従つて、密封
空間１５が吐出チヤンバ１４に急激に連通するこ
とがなくなり、吐出チヤンバ１４から密封空間１
５への油の逆流を阻止することができ、密封空間
１５での圧力変動を減少させることが可能とな
る。 When the inner rotor 12 rotates, the sealed space 15
volume decreases and internal oil pressure increases. The oil corresponding to this volume reduction gradually flows out into the discharge channel 14 through the shallow groove 20 on the end face of the rotor. Therefore, the sealed space 15 does not suddenly communicate with the discharge chamber 14, and the sealed space 1
This makes it possible to prevent oil from flowing back into the sealed space 15, thereby reducing pressure fluctuations in the sealed space 15.

第２図はチヤンバー室内部つまりハウジングの
内部空間における脈動振幅（Ｐ−Ｐ値）を示すも
ので、測定ポイントは密封空間１５の最大時にお
ける歯底位置１６を基準（ゼロ）とするものであ
る。従来品と比較して本発明に従うオイルポンプ
は、脈動振幅を大きく減少させていることが明ら
かである。 Figure 2 shows the pulsation amplitude (P-P value) inside the chamber chamber, that is, the internal space of the housing, and the measurement point is the tooth bottom position 16 at the maximum of the sealed space 15 as the reference (zero). . It is clear that the oil pump according to the invention has significantly reduced pulsation amplitude compared to conventional products.

第３図は本発明の第２実施例を示すもので、密
封空間１５と吐出チヤンバ１４を連通する溝２０
が、アウターロータ１１の各ロータ端面１９に形
成されている。 FIG. 3 shows a second embodiment of the present invention, in which a groove 20 communicating the sealed space 15 and the discharge chamber 14 is shown.
are formed on each rotor end surface 19 of the outer rotor 11.

この様に、密封空間１５と吐出チヤンバ１４を
連通する溝は、アウターロータ１１とインナーロ
ータ１２の少なくとも一方のロータ端面に設けら
れる。 In this way, the groove that communicates the sealed space 15 and the discharge chamber 14 is provided on the rotor end surface of at least one of the outer rotor 11 and the inner rotor 12.

〔発明の効果〕〔Effect of the invention〕

以上詳述した様に本発明は、ロータ端面に設け
た溝により、密封空間の容積減少分の油を吐出チ
ヤンバに徐々に逃がすものである。従つて、密封
空間は吐出チヤンバに急激に連通することがなく
なり、吐出チヤンバ側の高圧の影響を受けない。
つまり、吐出チヤンバから密封空間への油の逆流
が防止され、圧力変動の発生を抑制することがで
きる。その結果、従来生じていた騒音や歯の摩耗
を防止することができる。また、本発明によれば
密封空間と吐出チヤンバとを連通可能な溝をアウ
ターロータとインナーロータの少なくとも一方の
吸入チヤンバ及び吐出チヤンバが面する側の反対
側のロータ端面に設けているため、ロータのカバ
ーもしくはハウジングとの間の潤滑油として該溝
を通る油が作用し、同円周上に形成される溝によ
りその円周方向において両者間が略均一に潤滑さ
れるため、ロータの円滑な回転を期待できるとい
う実用上優れた効果を奏することができる。 As described above in detail, the present invention allows the oil corresponding to the volume reduction in the sealed space to gradually escape into the discharge chamber by means of the grooves provided on the end face of the rotor. Therefore, the sealed space does not suddenly communicate with the discharge chamber and is not affected by the high pressure on the discharge chamber side.
In other words, backflow of oil from the discharge chamber to the sealed space is prevented, and the occurrence of pressure fluctuations can be suppressed. As a result, noise and tooth wear that conventionally occur can be prevented. Further, according to the present invention, the groove that allows communication between the sealed space and the discharge chamber is provided in the end face of the rotor opposite to the side facing the suction chamber and the discharge chamber of at least one of the outer rotor and the inner rotor. The oil passing through the groove acts as a lubricant between the cover or housing of the rotor, and the grooves formed on the same circumference lubricate the space almost uniformly in the circumferential direction, so that the rotor runs smoothly. It is possible to achieve an excellent practical effect of being able to expect rotation.

【図面の簡単な説明】[Brief explanation of drawings]

第１図は本発明に従つたオイルポンプの第１実
施例を示す断面図、第２図は第１図のオイルポン
プの脈動振幅を示す線図、第３図は本発明の第２
実施例を示す断面図、第４図、第５図は従来のオ
イルポンプを示す断面図である。 １０……オイルポンプ、１１……アウターロー
タ、１１ａ……内歯、１２……インナーロータ、
１２ａ……外歯、１３……吸入チヤンバ、１４…
…吐出チヤンバ、１５……密封空間、１６……歯
底位置、１９……ロータ端面、２０……溝。 FIG. 1 is a sectional view showing a first embodiment of the oil pump according to the present invention, FIG. 2 is a diagram showing the pulsation amplitude of the oil pump of FIG. 1, and FIG.
4 and 5 are cross-sectional views showing a conventional oil pump. 10...Oil pump, 11...Outer rotor, 11a...Inner teeth, 12...Inner rotor,
12a...external tooth, 13...suction chamber, 14...
...Discharge chamber, 15...Sealed space, 16...Tooth bottom position, 19...Rotor end face, 20...Groove.

Claims (1)

【特許請求の範囲】[Claims] １ 内部空間を備えるハウジング内に内歯を備え
るアウターロータを回転自在に嵌合し、該アウタ
ーロータの内歯に係合する外歯を備えるインナー
ロータを前記アウターロータ内に嵌合し、前記ハ
ウジングの内部空間に開口する吸入チヤンバを前
記ハウジング内に形成するトロコイド型オイルポ
ンプにおいて、前記アウターロータの内歯と前記
インナーロータの外歯とにより形成される密封空
間の最大時に於ける前記インナーロータの歯底位
置を基準として反回転方向に沿つて最初に前記ア
ウターロータと前記インナーロータの歯先が接す
る位置まで前記吸入チヤンバを延在して形成させ
ると共に、回転方向に沿つて最初に前記アウター
ロータと前記インナーロータの歯先が接する位置
までの角度をl1とし、前記インナーロータの歯底
位置より回転方向に沿つて第２番目の歯底位置ま
での角度をl2とし、l1≦ｌ≦l2となる角度ｌを設
定し、該角度ｌから回転方向に延在するように前
記吐出チヤンバを形成し、前記密閉空間と前記吐
出チヤンバとを連通可能とする溝を前記アウター
ロータと前記インナーロータの少なくとも一方の
前記吸入チヤンバ及び吐出チヤンバが面する側の
反対側のロータ端面に設けた、トロコイド型オイ
ルポンプ。1. An outer rotor having internal teeth is rotatably fitted into a housing having an internal space, an inner rotor having external teeth that engages with the internal teeth of the outer rotor is fitted into the outer rotor, and the housing has an inner space. In the trochoid type oil pump, in which a suction chamber is formed in the housing and opens into an internal space of the inner rotor when the sealed space formed by the internal teeth of the outer rotor and the external teeth of the inner rotor is at its maximum. The suction chamber is formed by extending along the counter-rotation direction from the tooth bottom position to a position where the tooth tips of the outer rotor and the inner rotor first contact each other, and The angle from the tooth tip of the inner rotor to the position where they touch is l 1 , and the angle from the tooth bottom position of the inner rotor to the second tooth bottom position along the rotational direction is l 2 , and l 1 ≦l. An angle l such that ≦l 2 is set, the discharge chamber is formed so as to extend in the rotational direction from the angle l, and a groove that allows communication between the sealed space and the discharge chamber is formed between the outer rotor and the discharge chamber. A trochoidal oil pump provided on a rotor end surface opposite to the side facing at least one of the suction chamber and the discharge chamber of the inner rotor.
JP20470084A 1984-09-28 1984-09-28 Trochoid type oil pump Granted JPS6181588A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP20470084A JPS6181588A (en) 1984-09-28 1984-09-28 Trochoid type oil pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP20470084A JPS6181588A (en) 1984-09-28 1984-09-28 Trochoid type oil pump

Publications (2)

Publication Number Publication Date
JPS6181588A JPS6181588A (en) 1986-04-25
JPS6347916B2 true JPS6347916B2 (en) 1988-09-26

Family

ID=16494859

Family Applications (1)

Application Number Title Priority Date Filing Date
JP20470084A Granted JPS6181588A (en) 1984-09-28 1984-09-28 Trochoid type oil pump

Country Status (1)

Country Link
JP (1) JPS6181588A (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0914152A (en) * 1995-06-30 1997-01-14 Jatco Corp Internal gear type rotary pump
US6481991B2 (en) * 2000-03-27 2002-11-19 Denso Corporation Trochoid gear type fuel pump
JP3917026B2 (en) * 2002-07-10 2007-05-23 アイシン精機株式会社 Oil pump rotor
DE102007008265A1 (en) * 2007-02-20 2008-08-21 Siemens Ag gerotor
DE102007038524A1 (en) * 2007-08-16 2009-02-19 Robert Bosch Gmbh Internal gear pump

Also Published As

Publication number Publication date
JPS6181588A (en) 1986-04-25

Similar Documents

Publication Publication Date Title
US4767296A (en) Trochoidal toothed oil pump with thin discharge channel communicating with discharge chamber
US4629403A (en) Rotary compressor with vane slot pressure groove
JP2818723B2 (en) Gear type machine
US9581156B2 (en) Gear pump including an inner rotor having a plurality of teeth
JPS61138893A (en) Trochoidal oil pump
US5711660A (en) Internal gear type rotary pump having a relief groove
JPH07109981A (en) Scroll fluid machinery
US5007813A (en) Rotary rolling piston compressor with fixed vane having a relieved incline section
JPS6347916B2 (en)
JPH0735053A (en) Trochoidal oil pump
US4934913A (en) Internal-gear machine with fluid opening in non-bearing tooth flank
JP3801536B2 (en) Internal gear type oil pump and automatic transmission equipped with the same
JPH05164059A (en) Trochoid type oil pump
JP2002005039A (en) Trochoid type oil pump
US5104303A (en) Internal gear pump with tapered oil pockets in sliding surfaces
KR100199501B1 (en) Oil pump with low friction rotor
JP3194044B2 (en) Oil pump structure
JP2527249Y2 (en) Oil pump
JPH03194180A (en) Scroll fluid machine
JPS6119991A (en) Oil pump
JPH0295788A (en) Oil pump
US3402880A (en) Flexible rotor vacuum pump
EP0664395A1 (en) Internal gear pump
JPS61223281A (en) Oil pump device
JPH03134279A (en) Trochoid oil pump

Legal Events

Date Code Title Description
LAPS Cancellation because of no payment of annual fees