JPH0295787A - Oil pump - Google Patents
Oil pumpInfo
- Publication number
- JPH0295787A JPH0295787A JP24765088A JP24765088A JPH0295787A JP H0295787 A JPH0295787 A JP H0295787A JP 24765088 A JP24765088 A JP 24765088A JP 24765088 A JP24765088 A JP 24765088A JP H0295787 A JPH0295787 A JP H0295787A
- Authority
- JP
- Japan
- Prior art keywords
- tooth
- rotor
- teeth
- pump
- inner rotor
- 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
- 239000012530 fluid Substances 0.000 claims abstract description 5
- 238000005498 polishing Methods 0.000 abstract description 6
- 238000007789 sealing Methods 0.000 abstract description 3
- 239000003921 oil Substances 0.000 description 28
- 238000002485 combustion reaction Methods 0.000 description 6
- 239000010687 lubricating oil Substances 0.000 description 6
- 238000005096 rolling process Methods 0.000 description 5
- 230000005540 biological transmission Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- RTAQQCXQSZGOHL-UHFFFAOYSA-N Titanium Chemical compound [Ti] RTAQQCXQSZGOHL-UHFFFAOYSA-N 0.000 description 1
- 239000010718 automatic transmission oil Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 239000010705 motor oil Substances 0.000 description 1
- 238000012805 post-processing Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 239000010936 titanium Substances 0.000 description 1
- 229910052719 titanium Inorganic materials 0.000 description 1
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
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明はオイルポンプに係り、特に内燃機関や変速機
等にオイルを供給するオイルポンプに関する。DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention relates to an oil pump, and more particularly to an oil pump that supplies oil to internal combustion engines, transmissions, and the like.
オイルポンプにおいては、２個の歯車の噛合によってオ
イルを圧送する歯車ポンプや、内ロータと外ロータとを
有するトロコイド曲線を利用したオイルポンプ等がある
。Oil pumps include gear pumps that pump oil by meshing two gears, and oil pumps that utilize a trochoidal curve having an inner rotor and an outer rotor.
このトロコイド曲線を利用したオイルポンプは、第８図
に示す如く、トロコイド曲線によって形成された内ロー
タ１０２の内１１０２ａと外ロータ１０４の外歯１０４
ａとを噛合し、夫々軸心０５．０６を異ならしめてポン
プハウジングのポケット１０６内に組込み、また、内ロ
ータ１０２の内歯１０２ａの数が外ロータ１０４の外歯
１０４ａの数よりも１何歩なく構成され、内ロータ１０
２を回転することにより外ロータ１０４が内ロータ１０
２と同一方向に回転し、内ロータ１０２の内歯１０２ａ
と外ロータ１０４の外歯１０４ａとによって形成される
空間１０８が容積変化をしてポンプ作用を行い、流体を
吸入ボートから吸入して吐出ボート側に吐出するもので
あり、同容量の他種オイルポンプに比し、小形で構造も
簡単であり、また噛合音も小さいので、車両の潤滑油用
ポンプや自動変速機用オイルポンプ等のオイルポンプと
して広範囲に利用されている。As shown in FIG. 8, an oil pump using this trochoid curve has an inner rotor 102 formed by an inner rotor 1102a and an outer tooth 104 of an outer rotor 104 formed by a trochoid curve.
a, and are assembled into the pocket 106 of the pump housing with their respective axis centers 05.06 different, and the number of internal teeth 102a of the inner rotor 102 is one step larger than the number of external teeth 104a of the outer rotor 104. The inner rotor 10
2, the outer rotor 104 becomes the inner rotor 10.
The inner teeth 102a of the inner rotor 102 rotate in the same direction as the inner rotor 102.
The space 108 formed by the outer teeth 104a of the outer rotor 104 changes its volume and performs a pumping action, sucking fluid from the suction boat and discharging it to the discharge boat. Compared to pumps, they are smaller, have a simpler structure, and produce less meshing noise, so they are widely used as oil pumps such as vehicle lubricating oil pumps and automatic transmission oil pumps.
この第８図に示すオイルポンプにおいては、上述の諸元
から得られた外ロータ１０４と内ロータ１０２との組合
せ間隙（チップクリアランス）ｇは、零であると回転不
能となるので、回転可能とするために所定の組合せ間隙
ｇを所定に形成する必要がある。In the oil pump shown in FIG. 8, if the combined gap (tip clearance) g between the outer rotor 104 and the inner rotor 102 obtained from the above-mentioned specifications is zero, the pump will not be able to rotate. In order to do this, it is necessary to form a predetermined combination gap g.
また、このようなオイルポンプとしては、例えば実公昭
５７−５９６７２号公報、実公昭５６２４２５０号公報
、実開昭５９−８４２８８号公報、および特開昭５９−
９６４１０号公を旧こ開示されている。これら公輻に記
載のオイルポンプは、ポンプハウジングに設けたロータ
室に内ロータと外ロータとの各歯を噛合して偏心回転可
能に内装するとともに、ロータ室の開口するポンプハウ
ジングのロータ回転軸心方向−側面にケーシングの当接
面を当接させ固定具により固定して設け、内ロータと外
ロータとの偏心回転により前記各歯間にロータ回転方向
に拡縮しつつ移動する空間を形成し、吸入ボートから流
体を吸入して圧縮し吐出ポートに吐出するものである。In addition, examples of such oil pumps include, for example, Japanese Utility Model Publication No. 57-59672, Japanese Utility Model Publication No. 5624250, Japanese Utility Model Application Publication No. 59-84288, and Japanese Unexamined Utility Model Publication No. 59-84288.
No. 96410 was previously disclosed. The oil pumps described in these publications are equipped with an inner rotor and an outer rotor whose teeth are meshed with each other in a rotor chamber provided in the pump housing so that they can rotate eccentrically. The abutment surface of the casing is brought into contact with the side surface of the casing in the center direction and is fixed by a fixture, and a space is formed between each of the teeth that moves while expanding and contracting in the rotor rotational direction due to eccentric rotation of the inner rotor and outer rotor. , which sucks fluid from the suction boat, compresses it, and discharges it to the discharge port.
ところで、従来のオイルポンプにおいて、その姿勢は、
ボディクリアランス（外ロータの外周面とポケットの内
周面との間隙）と内ロータの回転中心とポケットの中心
との関係によって決定されるチップクリアランスｇによ
り定められている。By the way, the posture of a conventional oil pump is as follows.
It is determined by the body clearance (the gap between the outer circumferential surface of the outer rotor and the inner circumferential surface of the pocket) and the tip clearance g determined by the relationship between the rotation center of the inner rotor and the center of the pocket.
しかし、各ロータは、焼結金属によって形成され、そし
て、型精度及び後工程によって製品精度が一義的に決定
されるので、インボリュート歯形等からなる他の歯車ポ
ンプに比し高精度が要求され、例えば０．１以上の製造
公差が必要とし、高い精度を期待し得す、精度が低下し
た際には、ポンプ性能が不安定になるとともに、ポンプ
音の発生が大きくなるという不都合を招いた。However, each rotor is made of sintered metal, and the product accuracy is uniquely determined by mold accuracy and post-processing, so higher accuracy is required compared to other gear pumps that have involute tooth profiles. For example, a manufacturing tolerance of 0.1 or more is required and high accuracy can be expected, but when the accuracy decreases, the pump performance becomes unstable and pump noise becomes louder.
そこでこの発明の目的は、上述の不都合を除去すべくロ
ータの歯先面をロータの回転中心として描かれる円筒の
一部周面に倣って形成することにより、チップクリアラ
ンスを所定に確保しつつロータの歯先面を修正し、ポン
プ性能を向上させるとともに、ポンプ音の発生を低減し
て静粛性を向上させ、しかも歯形の修正を容易に果し得
るオイルポンプを実現するにある。SUMMARY OF THE INVENTION In order to eliminate the above-mentioned disadvantages, an object of the present invention is to form the tooth tips of the rotor to follow a partial circumferential surface of a cylinder drawn as the rotation center of the rotor. To provide an oil pump in which the tooth tip surfaces of the teeth are modified to improve pump performance, the generation of pump noise is reduced to improve quietness, and the tooth profile can be easily modified.
Ｃ問題点を解決するための手段〕
この目的を達成するためにこの発明は、外ロータの外歯
に内ロータの内歯を噛合して偏心回転させることにより
前記ロータの回転方向に拡縮しつつ移動する空間を前記
内ロータの内歯と前記外ロータの外歯とによって形成し
、流体を吸入し圧縮して吐出するオイルポンプにおいて
、前記外歯および／または内歯の歯先面を前記外ロータ
および／または前記内ロータの回転中心を中心として描
かれる円筒の一部周面に倣って形成したことを特徴とす
る。Means for Solving Problem C] In order to achieve this object, the present invention provides a mechanism for expanding and contracting the rotor in the rotational direction by meshing the internal teeth of the inner rotor with the external teeth of the outer rotor and causing the rotor to rotate eccentrically. In an oil pump in which a moving space is formed by the internal teeth of the inner rotor and the external teeth of the external rotor, and the fluid is sucked, compressed, and discharged, the tooth tip surfaces of the external teeth and/or internal teeth are connected to the external teeth. It is characterized in that it is formed to follow a partial peripheral surface of a cylinder drawn around the rotation center of the rotor and/or the inner rotor.
この発明の構成によれば、外ロータの外歯および／また
は内ロータの内歯の歯先面を外ロータおよび／または内
ロータの回転中心を中心として溝かれる円筒の一部周面
に倣って形成することにより、シール性能に影響を与え
るチップクリアランスを所定に確保させつつロータの歯
先面を修正し、ポンプ性能を向上させるとともに、ポン
プ音の発生を低減して静粛性を向上させ、しかも歯形の
修正を容易に行わせることができる。According to the configuration of the present invention, the tooth tip surfaces of the external teeth of the outer rotor and/or the internal teeth of the inner rotor are shaped to follow a partial peripheral surface of the cylinder grooved around the rotation center of the outer rotor and/or the inner rotor. By modifying the tip surface of the rotor while securing a specified tip clearance that affects sealing performance, it improves pump performance, reduces pump noise, and improves quietness. The tooth profile can be easily modified.
以下図面に基づいてこの発明の実施例を詳細且つ具体的
に説明する。Embodiments of the present invention will be described in detail and specifically below based on the drawings.
第１〜７図は、この発明の実施例を示すものである。図
において、２は内燃機関、４はシリンダヘッド、６はシ
リンダブロック、８はオイルパンである。シリンダブロ
ック６に装着されたクランク軸１０には、例えば内燃機
関２の潤滑油等を圧送するオイルポンプ１２が取付けら
れている。このオイルポンプ１２は、オイルパン８内の
潤滑油をオイルストレーナ１４を経て吸入し、そして潤
滑油の圧力を高くしてオイルフィルタ１６側に圧送し、
内燃機関２各部に潤滑油を供給するものである。1 to 7 show embodiments of this invention. In the figure, 2 is an internal combustion engine, 4 is a cylinder head, 6 is a cylinder block, and 8 is an oil pan. An oil pump 12 is attached to a crankshaft 10 attached to the cylinder block 6, which pumps, for example, lubricating oil for the internal combustion engine 2. This oil pump 12 sucks the lubricating oil in the oil pan 8 through the oil strainer 14, increases the pressure of the lubricating oil, and pumps it to the oil filter 16 side.
It supplies lubricating oil to each part of the internal combustion engine 2.
前記オイルポンプ１２は、以下の如く構成される。即ち
、オイルポンプ１２は、第２図に示す如く、トロコイド
曲線によって形成された内歯１８ａを有する内ロータ１
８との外歯２０ａを有する外ロータ２０とが偏心した状
態、つまり互いの軸心を異ならしめた状態でポンプハウ
ジング２２内に組込まれ、−側からポンプガスケット２
４を介してポンププレート２６を取着して構成されてい
る。The oil pump 12 is constructed as follows. That is, as shown in FIG. 2, the oil pump 12 has an inner rotor 1 having inner teeth 18a formed by a trochoidal curve.
8 and the outer rotor 20 having external teeth 20a are assembled into the pump housing 22 in an eccentric state, that is, with their axes different from each other, and the pump gasket 2 is inserted from the negative side.
A pump plate 26 is attached via 4.
前記内ロータ１８の内歯１８ａは、第３．４図に示す如
き形成される。即ち、トロコイド曲線により形成される
内ロータ１８の内歯１８ａは、基礎円の直径、転円の直
径、離心量、軌跡円の直径を設定した時、まず、基礎円
上を滑ることな（転円が転がり、その転円の中心から離
心量だけ離れた転円内の固定点が描く軌跡としてトロコ
イド曲線が得られ、このトロコイド曲線上に中心を有す
る直径の円弧群の包絡線によって描かれた歯形曲線によ
って形成される。The inner teeth 18a of the inner rotor 18 are formed as shown in FIG. 3.4. That is, when the diameter of the base circle, the diameter of the rolling circle, the amount of eccentricity, and the diameter of the locus circle are set, the internal teeth 18a of the inner rotor 18 formed by the trochoid curve must first not slide on the base circle (rolling). When a circle rolls, a trochoidal curve is obtained as the locus drawn by a fixed point within the rolling circle that is separated from the center of the rolling circle by the amount of eccentricity, and is drawn by the envelope of a group of circular arcs with diameters having centers on this trochoidal curve. Formed by a tooth profile curve.
また、この内ロータ１８の内歯ｔａａの歯先面１８Ｃは
、内ロータ１８の回転中心、つまり回転軸２８の軸心０
１を中心として描かれる半径Ｒ１を有する内円筒３０の
一部周面に倣って研摩等で形成される。つまり、第４図
に示す如く、内歯１８ａの歯先面１８ｃは、従来の破線
Ｐの如き形成されていたが、この実施例においては実線
の如き形成される。Further, the tooth tip surface 18C of the internal teeth taa of the inner rotor 18 is located at the rotation center of the inner rotor 18, that is, the axis 0 of the rotating shaft 28.
It is formed by polishing or the like, following a part of the circumferential surface of the inner cylinder 30 having a radius R1 drawn with 1 as the center. That is, as shown in FIG. 4, the tooth tip surface 18c of the internal tooth 18a was formed as shown by a broken line P in the conventional case, but in this embodiment, it is formed as shown by a solid line.
また、前記外ロータ２０の外歯２０ａは、第５．６図に
示す如き形成される。即ち、外ロータ２０の外歯２０ａ
は、内ロータ１８の内歯１８ａの形成時における基礎円
の直径と転円の直径とを加え円の円周上に中心を有する
上述の円の直径の（Ｎ＋１）個の円弧で構成されている
。この外ロータ２０の外歯２０ａの歯先面２０ｃは、外
ロータ２０の回転中心０２を中心として描かれる半径Ｒ
２を有する外円筒３２の一部周面に倣って研摩等で形成
される。つまり、第６図に示す如く、外ロータ１８の外
歯１８ａの歯先面１８Ｃは、従来の破線Ｓの如き形成さ
れていたが、この実施例においては実線の如き形成され
る。Further, the outer teeth 20a of the outer rotor 20 are formed as shown in FIG. 5.6. That is, the outer teeth 20a of the outer rotor 20
is composed of (N+1) arcs having the diameter of the above-mentioned circle, which is the sum of the diameter of the base circle and the diameter of the rolling circle when forming the inner teeth 18a of the inner rotor 18, and has a center on the circumference of the circle. There is. The tooth tip surface 20c of the external tooth 20a of this outer rotor 20 has a radius R drawn around the rotation center 02 of the outer rotor 20.
2 is formed by polishing or the like, following a part of the circumferential surface of the outer cylinder 32. That is, as shown in FIG. 6, the tooth tip surfaces 18C of the external teeth 18a of the outer rotor 18 were formed as shown by the broken line S in the conventional case, but in this embodiment, they are formed as shown by the solid line.
このように構成された内ロータ１８の内歯１８ａと外ロ
ータ２０の外ｍ ２０ ａとを噛合せてポンプハウジン
グのポケット３４内に収容する際には、ポケット３４が
既に研摩仕上げ等で機械加工されており、外ロータ２０
の外歯２０ａは機械加工により一定の精度が補償され、
もって内ロータ１８も、回転中心０１と内ロータ１８の
歯先面１８Ｃも同様に精度が補償される。これにより、
内ロータ１８の内歯１８ａと外ロータ２０と外歯２０ａ
との組合せ間隙（チップクリアランス）ｇは、人動状態
での隙間が焼結歯型の状態で使用した場合よりも精度が
良くなり、適正に確保されるものである。When the internal teeth 18a of the inner rotor 18 and the outer m20a of the outer rotor 20 configured in this way are to be engaged and housed in the pocket 34 of the pump housing, the pocket 34 has already been machined by polishing or the like. and the outer rotor 20
The external teeth 20a have a certain degree of accuracy guaranteed by machining,
As a result, the accuracy of the inner rotor 18 as well as the rotation center 01 and the tooth tip surface 18C of the inner rotor 18 is similarly compensated. This results in
Inner teeth 18a of the inner rotor 18, outer rotor 20, and outer teeth 20a
The combined gap (chip clearance) g in the manual operation state is more accurate than in the case where the sintered tooth type is used, and is appropriately secured.
また、各ロータ１８．２０を歯形のピッチ誤差を見込ん
で製作した場合には、従来チップクリアランスｇを大き
くすることで両ロータ１８．２０間のバソクラソシを確
保して吐出性能を低下させていたが、この実施例によれ
ば、シール性能に影響を与えるチップクリアランスｇを
所定に確保しつつ外ロータ２０の外歯２０．ａの歯形（
主として円弧で形成）を楕円にする等の歯形修正が可能
となるものである（第５図参照）。In addition, when each rotor 18.20 was manufactured taking into account the pitch error of the tooth profile, conventionally the tip clearance g was increased to ensure the spacing between the two rotors 18.20 and reduce the discharge performance. , according to this embodiment, the outer teeth 20 . Tooth profile of a (
It is possible to modify the tooth profile, such as changing the tooth shape (mainly formed by a circular arc) to an ellipse (see Fig. 5).
次に、この実施例の作用を説明する。Next, the operation of this embodiment will be explained.
クランク軸１０の駆動によってオイルポンプ１２の内ロ
ータ１８が回転し、この内ロータ１８の回転によってこ
の内ロータ１８の内歯１８ａが外ロータ２０の外ｍ ２
０ ａ、２Ｏａ間の谷間に入り込んで空間（図示せず）
の容積が変化し、外ロータ２０も内ロータ１８と同一方
向に回転し、空間３２の容積の変化によって吸入ポート
（図示せず）側からの低圧の潤滑油が吐出ポート（図示
せず）側に高圧となって吐出される。The inner rotor 18 of the oil pump 12 rotates due to the drive of the crankshaft 10, and the rotation of the inner rotor 18 causes the inner teeth 18a of the inner rotor 18 to move outward of the outer rotor 20 m2.
The space enters the valley between 0a and 2Oa (not shown)
The volume of the space 32 changes, the outer rotor 20 also rotates in the same direction as the inner rotor 18, and due to the change in the volume of the space 32, low-pressure lubricating oil from the suction port (not shown) side is transferred to the discharge port (not shown) side. It is discharged under high pressure.
ところで、この実施例においては、内ロータ１８の内歯
１８ａの歯先面１８Ｃは、内ロータ１８の回転中心○工
を中心として描かれる内円筒３０の一部周面に倣って研
摩等で形成され、また、外ロータの外歯２０ａの歯先面
２０ｃは、外ロータ２０の回転中心０２を中心として描
かれる外円筒３２の一部周面に倣って研摩等で形成され
ている。By the way, in this embodiment, the tooth tip surface 18C of the internal tooth 18a of the internal rotor 18 is formed by polishing or the like to follow a partial circumferential surface of the internal cylinder 30, which is drawn around the rotation center ○ of the internal rotor 18. Further, the tooth tip surfaces 20c of the external teeth 20a of the outer rotor are formed by polishing or the like to follow a partial circumferential surface of the outer cylinder 32, which is drawn around the rotation center 02 of the outer rotor 20.
この結果、シール性能に影響を与えるチップクリアラン
スｇを所定に確保させつつ内歯１８ａ、外歯２０ａの各
歯形の修正を行わせ、しかも各歯間のバソクラ・ノシＤ
をも所定に担保しく第７図参照）、ポンプ性能を向上さ
せるとともに、歯の干渉を防止してポンプ音の発生を低
減して静粛性を向上させ、しかも歯形の修正を容易に行
わせることができる。As a result, the tooth profiles of the internal teeth 18a and external teeth 20a can be corrected while ensuring a predetermined tip clearance g that affects sealing performance.
(see Fig. 7) to improve pump performance, prevent tooth interference, reduce pump noise, improve quietness, and facilitate modification of tooth profile. Can be done.
なお、この実施例においては、内ロータ１８の内歯１８
ａの歯先面１８Ｃと外ロータ２０の外歯２０ａの歯先面
２０ｃとの双方を修正したが、内ロータ１８の内ＦｉＪ
１８ ａの歯先面１８ｃのみ、あるいは外ロータ２０
の外歯２０ａの歯先面１８Ｃのみを修正することが可能
である。In addition, in this embodiment, the inner teeth 18 of the inner rotor 18
Both the tooth tip surface 18C of the tooth a and the tooth tip surface 20c of the outer tooth 20a of the outer rotor 20 were modified, but the inner FiJ of the inner rotor 18
Only the tooth tip surface 18c of 18a or the outer rotor 20
It is possible to modify only the tooth tip surface 18C of the external tooth 20a.
また、この実施例に係るオイルポンプ１２は、四輪自動
車や自動二輪車のエンジンオイルのポンプ、また、自動
変速機のオイルポンプ、更に、産業機械の油圧ポンプ、
そして医療機器のオイルポンプ等として広い分野で利用
されるものである。The oil pump 12 according to this embodiment can also be used as an engine oil pump for four-wheeled vehicles or motorcycles, an oil pump for automatic transmissions, and a hydraulic pump for industrial machinery.
It is used in a wide range of fields, such as oil pumps for medical equipment.
以上詳細な説明から明らかなようにこの発明によれば、
外ロータの外歯および／または内ロータの内歯の歯先面
を外ロータおよび／または内ロータの回転中心を中心と
して描かれる円筒の一部周面に倣って形成したことによ
り、チソフリリアランスを所定に確保しつつロータの歯
先を修正し、ポンプ性能を向上させ得るとともに、ポン
プ音の発生を低減して静粛性を向上させ、しがも歯形の
修正を容易に果し得る。As is clear from the above detailed description, according to the present invention,
By forming the tooth tip surfaces of the external teeth of the outer rotor and/or the internal teeth of the inner rotor to follow a partial circumferential surface of a cylinder drawn around the rotation center of the outer rotor and/or inner rotor, the titanium free rearance is improved. It is possible to correct the tip of the rotor teeth while ensuring a predetermined value, thereby improving pump performance, reducing pump noise, improving quietness, and easily correcting the tooth profile.
第１〜７図はこの発明の実施例を示し、第１図は内燃機
関の斜視図、第２図はオイルポンプの組立状態の斜視図
、第３図は内ロータの外歯を修正する説明図、第４図は
修正された内歯の歯先面の斜視図、第５図は外ロータを
修正する説明図、第６図は修正された外歯の歯先面の斜
視図、第７図は内歯と外歯との噛合状態を説明する拡大
図である。
第８図は従来における内ロータと外ロータとの噛合状態
の説明図である。
図において、２は内燃機関、１０はクランク軸、１２は
オイルポンプ、１８は内ロータ、１８ａは内歯、１８ｃ
は歯先面、２ｏは外ロータ、２０ａハ外歯、２０ｃは歯
先面、２２はポンプハウジング、２８は回転軸、３０は
内ロータの内円筒、３２は外ロータの外円筒、そして３
４はポケットである。
第 １ 図1 to 7 show embodiments of the present invention, FIG. 1 is a perspective view of an internal combustion engine, FIG. 2 is a perspective view of an assembled oil pump, and FIG. 3 is an explanation of modifying the outer teeth of the inner rotor. 4 is a perspective view of the corrected tooth tip surface of the internal tooth, FIG. 5 is an explanatory diagram for correcting the outer rotor, FIG. 6 is a perspective view of the corrected external tooth tip surface, and FIG. The figure is an enlarged view illustrating the meshing state of internal teeth and external teeth. FIG. 8 is an explanatory diagram of a conventional meshing state between an inner rotor and an outer rotor. In the figure, 2 is an internal combustion engine, 10 is a crankshaft, 12 is an oil pump, 18 is an inner rotor, 18a is an inner tooth, 18c
2o is the tooth tip surface, 2o is the outer rotor, 20a is the external tooth, 20c is the tooth tip surface, 22 is the pump housing, 28 is the rotating shaft, 30 is the inner cylinder of the inner rotor, 32 is the outer cylinder of the outer rotor, and 3
4 is a pocket. Figure 1
Claims (1)
転させることにより前記ロータの回転方向に拡縮しつつ
移動する空間を前記内ロータの内歯と前記外ロータの外
歯とによって形成し、流体を吸入し圧縮して吐出するオ
イルポンプにおいて、前記外歯および／または内歯の歯
先面を前記外ロータおよび／または前記内ロータの回転
中心を中心として描かれる円筒の一部周面に倣って形成
したことを特徴とするオイルポンプ。1. By meshing the internal teeth of the inner rotor with the external teeth of the outer rotor and rotating them eccentrically, a space in which the rotor moves while expanding and contracting in the rotational direction is created by the internal teeth of the inner rotor and the external teeth of the outer rotor. In an oil pump that sucks, compresses, and discharges fluid, the tooth tip surfaces of the external teeth and/or internal teeth are part of a cylinder drawn around the rotation center of the external rotor and/or the internal rotor. An oil pump characterized by being formed to follow the circumferential surface.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24765088A JPH0295787A (en) | 1988-09-30 | 1988-09-30 | Oil pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24765088A JPH0295787A (en) | 1988-09-30 | 1988-09-30 | Oil pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0295787A true JPH0295787A (en) | 1990-04-06 |
Family
ID=17166644
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP24765088A Pending JPH0295787A (en) | 1988-09-30 | 1988-09-30 | Oil pump |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0295787A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2005021969A3 (en) * | 2003-09-01 | 2005-05-06 | Mitsubishi Materials Corp | Oil pump rotor |
| US7052258B2 (en) | 2002-07-11 | 2006-05-30 | Yamada Manufacturing Co., Ltd. | Trochoidal pump |
| EP1674727A1 (en) | 2004-12-27 | 2006-06-28 | Yamada Manufacturing Co., Ltd. | Trochoid oil pump |
| KR101273033B1 (en) * | 2006-05-15 | 2013-06-10 | 현대자동차주식회사 | Oil pump for Transmission |
-
1988
- 1988-09-30 JP JP24765088A patent/JPH0295787A/en active Pending
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7052258B2 (en) | 2002-07-11 | 2006-05-30 | Yamada Manufacturing Co., Ltd. | Trochoidal pump |
| WO2005021969A3 (en) * | 2003-09-01 | 2005-05-06 | Mitsubishi Materials Corp | Oil pump rotor |
| CN100462561C (en) * | 2003-09-01 | 2009-02-18 | 三菱综合材料Pmg株式会社 | Oil pump rotor |
| US7588429B2 (en) | 2003-09-01 | 2009-09-15 | Mitsubishi Materials Pmg Corporation | Oil pump rotor assembly |
| KR101044590B1 (en) * | 2003-09-01 | 2011-06-29 | 가부시키가이샤 다이야멧트 | Oil pump rotor |
| EP1674727A1 (en) | 2004-12-27 | 2006-06-28 | Yamada Manufacturing Co., Ltd. | Trochoid oil pump |
| KR101273033B1 (en) * | 2006-05-15 | 2013-06-10 | 현대자동차주식회사 | Oil pump for Transmission |
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