JPH05164059A - Trochoid type oil pump - Google Patents
Trochoid type oil pumpInfo
- Publication number
- JPH05164059A JPH05164059A JP33080991A JP33080991A JPH05164059A JP H05164059 A JPH05164059 A JP H05164059A JP 33080991 A JP33080991 A JP 33080991A JP 33080991 A JP33080991 A JP 33080991A JP H05164059 A JPH05164059 A JP H05164059A
- Authority
- JP
- Japan
- Prior art keywords
- tooth
- rotor
- chamber
- discharge
- suction
- 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
- 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)
- Rotary Pumps (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、エンジン潤滑用のトロ
コイド型オイルポンプに関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a trochoidal oil pump for lubricating an engine.
【０００２】[0002]
【従来の技術】本発明に関する従来技術としては、図４
に示されるものが知られている。図４は、この公知の従
来例のポンプカバーを取り除いた平面図を示している。2. Description of the Related Art As a prior art relating to the present invention, FIG.
The one shown in is known. FIG. 4 shows a plan view in which the well-known conventional pump cover is removed.
【０００３】同図に示すように、ポンプボデー１と図示
しないポンプカバーとによって区画された円筒状密閉室
３内に、トコロイド噛み合いする一組の内歯アウターロ
ータ４と外歯インナーロータ５とが納められている。イ
ンナーロータ５はエンジン動力に応じて回転される駆動
軸８に固着されており、その回転によってアウターロー
タ４を回転させる。これらのロータ４，５が回転する
と、トロコイド噛み合いする両ロータ４，５の歯により
区画される歯間室９容積の変化によって、吸入ポート６
０よりオイルを吸入し、吐出ポート７０より吐出して、
オイルを所定の潤滑箇所へ圧送する。As shown in the figure, a pair of inner-tooth outer rotor 4 and outer-tooth inner rotor 5 meshing with a colloid are formed in a cylindrical closed chamber 3 defined by a pump body 1 and a pump cover (not shown). Has been paid. The inner rotor 5 is fixed to a drive shaft 8 that is rotated according to engine power, and the rotation thereof causes the outer rotor 4 to rotate. When these rotors 4 and 5 rotate, the suction port 6 changes due to a change in the volume of the interdental chamber 9 defined by the teeth of the rotors 4 and 5 that mesh with each other.
Intake oil from 0 and discharge from the discharge port 70,
Pump oil to designated lubrication points.
【０００４】歯間室９が最大容積時において吸入ポート
６０から遮断されるようになっており、吸入ポート６０
及び吐出ポート７０内のアウターロータ４の偏心方向側
に位置する端部６０ａ，７０ａは偏心方向に対して平行
になっている。The interdental chamber 9 is designed to be blocked from the suction port 60 at the maximum volume.
The end portions 60a, 70a located on the eccentric direction side of the outer rotor 4 in the discharge port 70 are parallel to the eccentric direction.
【０００５】[0005]
【発明が解決しようとする課題】ところが、この種のポ
ンプは、エンジン動力によって駆動されるものであるか
ら、広範囲の回転数域で使用されるものであるが、性質
上、歯間室９が最大容積に近づくに連れて吸入ポート６
０の開口面積が減少し、歯間室９が最大容積時において
吸入ポート６０から遮断されるために、歯間室へのオイ
ルの吸入効率が低下し、高回転時においてキャビテーシ
ョン現象を生じることになる。However, since this type of pump is driven by the engine power, it is used in a wide range of rotational speeds. Suction port 6 as it approaches the maximum volume
The opening area of 0 decreases and the interdental chamber 9 is blocked from the suction port 60 at the time of maximum volume, so that the efficiency of sucking oil into the interdental chamber decreases, and a cavitation phenomenon occurs at high rotation. Become.
【０００６】更に、この種のポンプは、吸入ポート６０
内のアウターロータ４の偏心方向側に位置する端部６０
ａが偏心方向に対して平行になっている為に、歯間室９
が最大容積になる直前において、急激に通路が狭くなる
ので、高回転時のキャビテーション現象を生じる恐れが
ある。また、吐出ポート７０内のアウターロータ４の偏
心方向側に位置する端部７０ａが偏心方向に対して平行
になっている為に、歯間室９が最大容積になった直後に
おいて、急激に通路が狭くなるので、高回転時のキャビ
テーション現象を生じる恐れがある。Further, this type of pump has a suction port 60.
End 60 located on the eccentric direction side of the outer rotor 4 inside
Since a is parallel to the eccentric direction, the interdental space 9
Immediately before the maximum volume is reached, the passage narrows sharply, which may cause a cavitation phenomenon during high rotation. Further, since the end portion 70a located on the eccentric direction side of the outer rotor 4 in the discharge port 70 is parallel to the eccentric direction, immediately after the interdental chamber 9 reaches the maximum volume, the passage is rapidly changed. Is narrowed, there is a possibility that a cavitation phenomenon may occur at high rotation.
【０００７】高回転時のキャビテーション現象により、
吐出油圧の脈動が増加することになる。このために、吐
出量が低下したり、異常摩耗や騒音を発する恐れがあ
る。Due to the cavitation phenomenon during high rotation,
The pulsation of the discharge hydraulic pressure will increase. For this reason, the discharge amount may be reduced, and abnormal wear or noise may occur.
【０００８】故に、本発明は、上記の問題点を解決する
ことをその技術的課題とするものである。Therefore, the present invention has as its technical problem the solution of the above problems.
【０００９】[0009]
【課題を解決するための手段】上記の技術的課題を解決
するための第１の技術的手段は、歯間室と吸入及び吐出
ポートとの連通が、歯間室の容積が最大となる位置から
インナーロータの回転方向に偏角された位置で遮断され
るようにしたことである。A first technical means for solving the above technical problem is a position in which communication between the interdental chamber and the suction and discharge ports is such that the volume of the interdental chamber is maximized. Is to block at a position deviated in the rotation direction of the inner rotor.
【００１０】また、第２の技術的手段は、アウターロー
タの偏心方向側に位置する吸入ポート及び吐出ポートの
端部が内側に窪まれた外周形状にされたことである。The second technical means is that the end portions of the intake port and the discharge port located on the eccentric direction side of the outer rotor are formed in an outer peripheral shape in which they are recessed inward.
【００１１】[0011]
【作用】高回転時におけるオイルの慣性力を考慮に入れ
て、歯間室の容積が最大となる位置からインナーロータ
の回転方向に偏角された位置で、歯間室と吸入，吐出ポ
ートとの連通を遮断したことにより、歯間室へのオイル
の吸入効率を向上させ、高回転時におけるキャビテーシ
ョン現象を減少させている。[Function] Taking into consideration the inertial force of the oil at high rotation speed, the interdental chamber and the suction and discharge ports are arranged at a position deviated in the rotation direction of the inner rotor from the position where the volume of the interdental chamber is maximum. By cutting off the communication between the two, the efficiency of oil intake into the interdental space is improved and the cavitation phenomenon at high rotation is reduced.
【００１２】また、アウターロータの偏心方向側に位置
する吸入ポートの端部が内側に窪まれた外周形状にされ
たことにより、歯間室が最大容積になる直前まで、広範
囲のオイルの供給路を形成している為に、歯間室へのオ
イルの吸入効率を向上させ、高回転時のキャビテーショ
ン現象を減少させている。更に、アウターロータの偏心
方向側に位置する吐出ポートの端部が内側に窪まれた外
周形状にされたことにより、歯間室が最大容積になった
直後にも、広範囲のオイルの吐出路が形成される為に、
高回転時のキャビテーション現象を減少させている。Further, since the end portion of the suction port located on the eccentric direction side of the outer rotor has an outer peripheral shape that is recessed inward, a wide range of oil supply passage is provided until just before the interdental chamber reaches the maximum volume. Because of this, the efficiency of oil intake into the interdental space is improved and the cavitation phenomenon at high rotation is reduced. Furthermore, the end portion of the discharge port located on the eccentric direction side of the outer rotor has an outer peripheral shape that is recessed inward, so that a wide range of oil discharge passages is provided even immediately after the interdental chamber reaches the maximum volume. To be formed,
It reduces the cavitation phenomenon at high speeds.
【００１３】以上のことのより、吐出油圧の脈動が低減
できるので、吐出量が向上し、異常摩耗や騒音の発生を
減少することができる。As described above, since the pulsation of the discharge hydraulic pressure can be reduced, the discharge amount can be improved and abnormal wear and noise can be reduced.
【００１４】[0014]
【実施例】以下、本発明における実施例を図面を用いて
説明する。Embodiments of the present invention will be described below with reference to the drawings.
【００１５】図１は、本発明によるトロコイド型オイル
ポンプのオイルカバーを取り除いた平面図を示し、図２
は、図１のＡ−Ａ要部断面図を示し、図３は、図１のＢ
−Ｂ要部断面図を示している。FIG. 1 is a plan view of the trochoid type oil pump according to the present invention with the oil cover removed, and FIG.
Shows a cross-sectional view of the main part of AA in FIG. 1, and FIG.
-B shows a sectional view of a main part.
【００１６】これらの図面に示すように、ポンプボデー
１とポンプカバー２とによって区画された円筒状密閉室
３内に、トロコイド噛み合いする一組の内歯アウターロ
ータ４と外歯インナーロータ５とが納められている。こ
れらのロータ４，５の端面に臨んで弓形の吸入ポート６
と吐出ポート７とを開口させている。インナーロータ５
はエンジン動力に応じて回転される駆動軸８に固着され
ており、その回転によってアウターロータ４を回転させ
る。これらのロータ４，５が回転すると、トロコイド噛
み合いする両ロータ４，５の歯により区画される歯間室
９容積の変化によって、吸入ポート６よりオイルを吸入
し、吐出ポート７より吐出して、オイルを所定の潤滑箇
所へ圧送する。As shown in these drawings, a set of an inner tooth outer rotor 4 and an outer tooth inner rotor 5 meshing with a trochoid are provided in a cylindrical closed chamber 3 defined by a pump body 1 and a pump cover 2. Has been paid. An arc-shaped intake port 6 facing the end faces of the rotors 4 and 5
And the discharge port 7 are opened. Inner rotor 5
Is fixed to a drive shaft 8 which is rotated according to the engine power, and the rotation thereof causes the outer rotor 4 to rotate. When these rotors 4 and 5 rotate, oil is sucked from the suction port 6 and discharged from the discharge port 7 due to the change in the volume of the interdental chamber 9 defined by the teeth of the rotors 4 and 5 meshing with each other in the trochoid. Pump oil to designated lubrication points.
【００１７】本発明においては、高回転時におけるオイ
ルの慣性力を考慮に入れて、図２に示す如く歯間室９と
吸入ポート６との連通及び歯間室９と吐出ポート７との
連通が、歯間室９の容積が最大となる位置からインナー
ロータ５の回転方向に所定の角度θ偏角された位置で遮
断されている。尚、θの範囲は５°〜２０°が望まし
い。何故ならば、θが５°以下では、歯間室９へのオイ
ルの吸入効率が小さく、２０°以上では、歯間室９内の
圧力が上昇しすぎて逆に吸入効率が低下してしまう為で
ある。本発明は、高回転域においては、オイルの慣性力
により、歯間室９の容積が最大となった直後でも歯間室
９にオイルが供給される為に、従来例よりも多量のオイ
ルが歯間室９に供給されることになり、高回転時におけ
るキャビテーション現象を減少させている。In the present invention, taking into consideration the inertial force of the oil at the time of high speed rotation, as shown in FIG. 2, the interdental chamber 9 and the suction port 6 communicate with each other and the interdental chamber 9 and the discharge port 7 communicate with each other. Is blocked at a position deviated by a predetermined angle θ in the rotation direction of the inner rotor 5 from the position where the volume of the interdental chamber 9 is maximum. The range of θ is preferably 5 ° to 20 °. The reason is that if θ is 5 ° or less, the oil suction efficiency into the interdental chamber 9 is small, and if 20 ° or more, the pressure in the interdental chamber 9 rises too much, and conversely the suction efficiency decreases. Because of that. According to the present invention, in a high rotation range, oil is supplied to the interdental chamber 9 immediately after the volume of the interdental chamber 9 is maximized due to the inertial force of the oil. Since it is supplied to the interdental space 9, the cavitation phenomenon at the time of high rotation is reduced.
【００１８】また、本発明においては、アウターロータ
４の偏心方向側に位置する吸入ポート６の端部６ａ及び
吐出ポート７の端部７ａが内側に窪まれた外周形状すな
わち、鳥の嘴のような形状になっている。吸入ポート６
の端部６ａが内側に窪まれた外周形状にされたことによ
り、歯間室９が最大容積となる直前にまで広範囲のオイ
ルの供給路が形成される為に、歯間室９へのオイルの吸
入効率を向上させ、高回転時のキャビテーション現象を
減少させている。また、吐出ポート７の端部７ａが内側
に窪まれた外周形状にされたことにより、歯間室９が最
大容積になった直後においても、広範囲のオイルの吐出
路が形成される為に、高回転時のキャビテーション現象
を減少させている。Further, according to the present invention, the end portion 6a of the intake port 6 and the end portion 7a of the discharge port 7 located on the eccentric direction side of the outer rotor 4 are recessed inward, that is, like a bird's beak. It has a simple shape. Suction port 6
Since the end portion 6a of the tooth is formed into an outer peripheral shape that is recessed inward, a wide-range oil supply path is formed just before the interdental chamber 9 reaches the maximum volume, and therefore the oil to the interdental chamber 9 is formed. It improves the suction efficiency and reduces the cavitation phenomenon at high speed. Further, since the end portion 7a of the discharge port 7 is formed into the outer peripheral shape that is recessed inward, a wide range of oil discharge passage is formed even immediately after the interdental chamber 9 reaches the maximum volume. The cavitation phenomenon at high rotation is reduced.
【００１９】図５及び図６は、本実施例と従来例とにお
いて、高回転域での吐出油圧の脈動を比較したものであ
る。FIGS. 5 and 6 compare the pulsation of the discharge hydraulic pressure in the high rotation range between the present embodiment and the conventional example.
【００２０】図５において、ポンプの回転数が高くなる
につれて、吐出油圧の脈動全振幅が、従来例においては
急激に増加しているのに対して、本実施例においては少
しずつ増加しているにすぎない。従って、本発明は、従
来例に比べて高回転時における油圧脈動を低減させたこ
とになる。つまり、本発明においては、高回転域におけ
るキャビテーション現象が減少することが実証されたこ
とになる。In FIG. 5, the total pulsation amplitude of the discharge hydraulic pressure increases sharply in the conventional example as the rotational speed of the pump increases, whereas it gradually increases in the present example. Nothing more. Therefore, the present invention reduces the hydraulic pulsation at the time of high rotation as compared with the conventional example. That is, in the present invention, it was proved that the cavitation phenomenon in the high rotation range is reduced.
【００２１】図６において、吐出圧が高くなるにつれ
て、油圧の脈動全振幅が、従来例においては５０kgf/cm
2 まで増加しているのに対して、本実施例においては、
２０kgf/cm2 までしか増加していないことが分かる。従
って、本発明は、吐出圧を高くしても、あまり油圧脈動
を増加させないことが分かる。つまり、本発明において
は、高回転域におけるキャビテーション現象が吐出圧に
関係なく減少することが実証されたことになる。In FIG. 6, as the discharge pressure increases, the total pulsation amplitude of the hydraulic pressure becomes 50 kgf / cm in the conventional example.
In contrast to the increase to 2 , in this example,
It can be seen that the increase is only up to 20 kgf / cm 2 . Therefore, it can be seen that the present invention does not increase the hydraulic pressure pulsation even if the discharge pressure is increased. That is, in the present invention, it has been proved that the cavitation phenomenon in the high rotation range is reduced regardless of the discharge pressure.
【００２２】[0022]
【発明の効果】本発明は、歯間室と吸入，吐出ポートと
の連通が、歯間室の容積が最大となる位置からインナー
ロータの回転方向に偏角された位置で遮断され、アウタ
ーロータの偏心方向側に位置する吸入ポート及び吐出ポ
ートの端部が内側に窪まれた外周形状にさせることによ
り、以下の如く効果を有する。As described above, according to the present invention, the communication between the interdental chamber and the suction and discharge ports is blocked at the position deviated in the rotation direction of the inner rotor from the position where the volume of the interdental chamber is maximum, and the outer rotor is blocked. The following effects can be obtained by making the ends of the suction port and the discharge port located on the eccentric direction side have a peripheral shape that is recessed inward.
【００２３】歯間室に供給されるオイルの吸入効率が向
上し、高回転域でのキャビテーション現象が減少する
為、吐出油圧の脈動を低減することが可能になる。この
ことにより、吐出量が向上し、騒音や異常摩耗の発生を
減少することができる。Since the suction efficiency of the oil supplied to the interdental chamber is improved and the cavitation phenomenon in the high rotation range is reduced, the pulsation of the discharge hydraulic pressure can be reduced. As a result, the discharge amount can be improved and the occurrence of noise and abnormal wear can be reduced.
【図１】本発明によるトロコイド型ポンプのポンプカバ
ーを取り除いた平面図である。FIG. 1 is a plan view of a trochoidal pump according to the present invention with a pump cover removed.
【図２】図１のＡ−Ａ要部断面図である。FIG. 2 is a sectional view taken along the line AA of FIG.
【図３】図１のＢ−Ｂ要部断面図である。3 is a cross-sectional view of the main part of BB of FIG.
【図４】従来例のポンプカバーを取り除いた平面図であ
る。FIG. 4 is a plan view with a pump cover of a conventional example removed.
【図５】本実施例と従来例において、油温８０℃，油種
ＳＡＥ＃３０，吐出圧３kgf/cm2 の条件下でのポンプの
回転数と油圧の脈動全振幅との関係を示す説明図であ
る。FIG. 5 is an explanation showing the relationship between the rotational speed of the pump and the total pulsation amplitude of the hydraulic pressure under the conditions of the oil temperature of 80 ° C., the oil type SAE # 30, and the discharge pressure of 3 kgf / cm 2 in this example and the conventional example. It is a figure.
【図６】本実施例と従来例において、油温８０℃，油種
ＳＡＥ＃３０，ポンプ回転数５０００rpm の条件下での
吐出圧と油圧の脈動全振幅との関係を示す説明図であ
る。FIG. 6 is an explanatory diagram showing the relationship between the discharge pressure and the total pulsation amplitude of hydraulic pressure under the conditions of an oil temperature of 80 ° C., an oil type SAE # 30, and a pump rotation speed of 5000 rpm in the present example and the conventional example.
１ ポンプボデー ２ ポンプカバー ３ 円筒状密閉室 ４ 内歯アウターロータ ５ 外歯インナーロータ ６，６０ 吸入ポート ６ａ，６０ａ 吸入ポートの端部（端部） ７，７０ 吐出ポート ７ａ，７０ａ 吐出ポートの端部（端部） ８ 駆動軸 ９ 歯間室 1 Pump Body 2 Pump Cover 3 Cylindrical Sealed Chamber 4 Inner Tooth Outer Rotor 5 Outer Tooth Inner Rotor 6,60 Suction Port 6a, 60a Suction Port End (End) 7,70 Discharge Port 7a, 70a Discharge Port End Part (end) 8 Drive shaft 9 Interdental space
Claims (2)
れる円筒状密閉室にトロコイド歯型の外歯インナーロー
タと内歯アウターロータとが噛み合い状態で収納され、
前記ロータ端面の吸入側及び吐出側に位置する前記ポン
プボデーにそれぞれ吸入ポート及び吐出ポートが形成さ
れ、前記円筒状密閉室内に前記外歯インナーロータと前
記内歯アウターロータとで区画された歯間室を備えたト
ロコイド型オイルポンプにおいて、前記歯間室と前記吸
入，吐出ポートとの連通が、前記歯間室の容積が最大と
なる位置から前記インナーロータの回転方向に偏角され
た位置で遮断されることを特徴とするトロコイド型オイ
ルポンプ。1. An outer tooth inner rotor and an inner tooth outer rotor of a trochoidal tooth type are accommodated in a cylindrical closed chamber defined by a pump body and a pump cover in an engaged state,
A suction port and a discharge port are formed in the pump body located on the suction side and the discharge side of the rotor end surface, respectively, and an inter-tooth space defined by the outer tooth inner rotor and the inner tooth outer rotor in the cylindrical closed chamber. In a trochoidal type oil pump having a chamber, communication between the interdental chamber and the suction and discharge ports is performed at a position deviated in a rotation direction of the inner rotor from a position where the volume of the interdental chamber is maximum. Trochoidal type oil pump characterized by being cut off.
れる円筒状密閉室にトロコイド歯型の外歯インナーロー
タと内歯アウターロータとが噛み合い状態で収納され、
前記ロータ端面の吸入側及び吐出側に位置する前記ポン
プボデーにそれぞれ吸入ポート及び吐出ポートが形成さ
れ、前記円筒状密閉室内に前記外歯インナーロータと前
記内歯アウターロータとで区画された歯間室を備えたト
ロコイド型オイルポンプにおいて、前記アウターロータ
の偏心方向側に位置する前記吸入ポート及び前記吐出ポ
ートの端部が内側に窪まれた外周形状であることを特徴
とするトロコイド型オイルポンプ。2. A trochoidal tooth-shaped outer tooth inner rotor and inner tooth outer rotor are meshedly housed in a cylindrical closed chamber defined by a pump body and a pump cover,
A suction port and a discharge port are formed in the pump body located on the suction side and the discharge side of the rotor end surface, respectively, and an inter-tooth space defined by the outer tooth inner rotor and the inner tooth outer rotor in the cylindrical closed chamber. A trochoidal oil pump provided with a chamber, wherein the suction port and the discharge port located on the eccentric direction side of the outer rotor have an outer peripheral shape that is recessed inward.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP33080991A JPH05164059A (en) | 1991-12-13 | 1991-12-13 | Trochoid type oil pump |
| DE19924241873 DE4241873A1 (en) | 1991-12-13 | 1992-12-11 | Oil pump for engine lubrication - has inner gear and outer gear which form pump chambers with increased suction efficiency |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP33080991A JPH05164059A (en) | 1991-12-13 | 1991-12-13 | Trochoid type oil pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH05164059A true JPH05164059A (en) | 1993-06-29 |
Family
ID=18236797
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP33080991A Pending JPH05164059A (en) | 1991-12-13 | 1991-12-13 | Trochoid type oil pump |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JPH05164059A (en) |
| DE (1) | DE4241873A1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002147367A (en) * | 2000-11-09 | 2002-05-22 | Unisia Jecs Corp | Oil pump |
| KR20020043727A (en) * | 2000-12-04 | 2002-06-12 | 이계안 | Oil pump |
| US6929967B2 (en) * | 2001-12-27 | 2005-08-16 | Lg. Philips Lcd Co., Ltd. | Method of forming pattern |
| JP2008127991A (en) * | 2006-11-16 | 2008-06-05 | Miura Co Ltd | Internal gear pump |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3893959B2 (en) | 2001-11-29 | 2007-03-14 | アイシン精機株式会社 | Oil pump pressure regulating valve mechanism mounting structure |
| DE10245814B3 (en) * | 2002-10-01 | 2004-02-12 | SCHWäBISCHE HüTTENWERKE GMBH | Internal-gear pump e.g. for pumping engine oil has at least one recess in feet of external teeth extending to one endface of external teeth |
| CN102966536A (en) * | 2012-11-22 | 2013-03-13 | 无锡市东方液压件制造有限公司 | Cycloid internal gear oil pump |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS618485A (en) * | 1984-06-22 | 1986-01-16 | Aisin Seiki Co Ltd | Oil pump |
| JPS6441686A (en) * | 1987-08-06 | 1989-02-13 | Giyuuji Negishi | Trochoid pump |
| DE3933978A1 (en) * | 1989-10-11 | 1991-05-02 | Eisenmann Siegfried A | SUCTION-CONTROLLED GEAR RING PUMP |
-
1991
- 1991-12-13 JP JP33080991A patent/JPH05164059A/en active Pending
-
1992
- 1992-12-11 DE DE19924241873 patent/DE4241873A1/en not_active Withdrawn
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002147367A (en) * | 2000-11-09 | 2002-05-22 | Unisia Jecs Corp | Oil pump |
| KR20020043727A (en) * | 2000-12-04 | 2002-06-12 | 이계안 | Oil pump |
| US6929967B2 (en) * | 2001-12-27 | 2005-08-16 | Lg. Philips Lcd Co., Ltd. | Method of forming pattern |
| JP2008127991A (en) * | 2006-11-16 | 2008-06-05 | Miura Co Ltd | Internal gear pump |
Also Published As
| Publication number | Publication date |
|---|---|
| DE4241873A1 (en) | 1993-07-01 |
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