JP2003056473A - Internal gear type rotary pump - Google Patents

Internal gear type rotary pump

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Publication number
JP2003056473A
JP2003056473A JP2002232315A JP2002232315A JP2003056473A JP 2003056473 A JP2003056473 A JP 2003056473A JP 2002232315 A JP2002232315 A JP 2002232315A JP 2002232315 A JP2002232315 A JP 2002232315A JP 2003056473 A JP2003056473 A JP 2003056473A
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JP
Japan
Prior art keywords
gear
tooth
circle
point
generated
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.)
Granted
Application number
JP2002232315A
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Japanese (ja)
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JP2003056473A5 (en
JP4251831B2 (en
Inventor
Toshiyuki Kosuge
敏行 小菅
Original Assignee
Sumitomo Electric Ind Ltd
住友電気工業株式会社
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Priority to JP23956297 priority Critical
Priority to JP9-239562 priority
Application filed by Sumitomo Electric Ind Ltd, 住友電気工業株式会社 filed Critical Sumitomo Electric Ind Ltd
Priority to JP2002232315A priority patent/JP4251831B2/en
Publication of JP2003056473A publication Critical patent/JP2003056473A/en
Publication of JP2003056473A5 publication Critical patent/JP2003056473A5/ja
Application granted granted Critical
Publication of JP4251831B2 publication Critical patent/JP4251831B2/en
Expired - Lifetime legal-status Critical Current
Anticipated expiration legal-status Critical

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Abstract

PROBLEM TO BE SOLVED: To improve discharge efficiency and a service life and reduce noise and tooth surface wear by dissolving nonuniformity of inter-tooth clearances of an internal gear type pump. SOLUTION: In this internal gear type pump, the space 3 of an outer gear 1 and the addendum 6 of an opposed inner gear 2 have an epicycloidal shape, and the addendum 4 of the outer gear 1 and the space 5 of the opposed inner gear 2 have a hypocycloidal shape. In this constitution, the cycloid is formed by four generating circles rolling on the pitch circle of each gear. An inter-tooth clearance C1 in the deepest mesh position of the outer gear 1 and inner gear 2 and an inter-tooth clearance C2 in the shallowest mesh region of the outer gear and inner gear are almost equal.

Description

【発明の詳細な説明】 【0001】 【発明の属する技術分野】本発明は、モータ等の駆動源
により駆動されて液体又は気体を圧縮して吐出する回転
ポンプに関し、特に液体ポンプに好適な内接歯車式ポン
プに関する。 【0002】 【従来の技術】内燃機関および自動モータによる車両伝
動装置に使用される内歯車ポンプのほとんどはトロコイ
ド歯のものが用いられる。トロコイド歯とは、アウター
ギアとインナーギアのどちらか一方の歯面が円弧状に制
限され、もう一方のギアの歯面が、円弧により規定され
た一方のギアの歯のノンスリップ回転により規定される
ものをいう。 【0003】本発明が改良する内接歯車式ポンプは、内
燃機関および自動伝動装置において、液体又は気体を送
出するために、サイクロイド歯形を具体的に使用するも
のであり、例えば、1925年の英国特許第23342
3号公報や、独国特許第3938346号公報に記載さ
れている。上記独国特許によるポンプは、互に歯数の異
なるアウターギア(アウターロータ)とインナーギア
(インナーロータ)とを有する内接歯車ポンプにおい
て、完全なサイクロイド歯形を有する歯および歯溝の優
れた運動学的特性を用いている。 【0004】上記アウターギアの歯は、エンジンのクラ
ンクシャフトまたは自動ギアボックスの主シャフト(主
軸)により駆動されるインナーギアの歯に噛合してい
る。この内接歯車式ポンプでは、駆動軸であるクランク
シャフト等の比較的明白な半径方向の動きは、アウター
ギアの周面とハウジングとの間のクリアランスを適当に
設定する(アウターギアの径方向振れを許容する遊びを
つける)ことによって補償される。また、その補償は、
アウターギアをほとんど遊びなしで取り付け、その後、
インナーギアの軸受とインナーギアとの間に相応の大き
な遊びを設けることによっても可能である。この場合に
は、その後、インナーギアの歯をアウターギアの歯と噛
合させる。このようなポンプは、本発明の技術の好適な
適用対象となる。 【0005】図4は、特開平5−256268号公報で
提案されている平坦化されたサイクロイド歯形のモデル
図を表している。 【0006】特開平5−256268号は、周知のポン
プに見られる送出流脈動に起因する雑音の発生、ポンプ
の効率低下及びキャビティーション雑音を低減する目的
で各ギアのサイクロイド歯形を平坦化してアウターギア
とインナーギアが最も深く噛合する位置での歯間隙間を
縮小している。図4のfhは、ギアのピッチ円P上の点
z0を起点として生成円reがピッチ円上を転動し、そ
の生成円reの円周上の一点の軌跡によって画かれる本
来のエピサイクロイド、frは、ピッチ円P上の点z0
を起点として生成円rhがピッチ円上を転動し、その生
成円rhの円周上の一点の軌跡によって画かれる本来の
ハイポサイクロイド、fh3、rh3は平坦化後のエピ
サイクロイドとハイポサイクロイドである。 【0007】 【発明が解決しようとする課題】作動流体の圧力脈動、
即ち、送出流脈動が発生すると、アウターギアとインナ
ーギアに起振力が働き、両ギアの歯が半径方向および接
線方向に互いに打ち合って望ましくない雑音が発生す
る。 【0008】特開平5−256268号は、その雑音を
抑制しようとしているが、同公報の技術によると、アウ
ターギアとインナーギアが最も深く噛み合う点における
各ギアの歯間隙間は非常に小さく、両ギアの噛み合いが
最も浅くなる領域において各ギア間の歯間隙間は大きく
形成され、隙間が不均一なものになっている。これは、
送出流脈動が発生すると、アウターギアとインナーギア
が最も深く噛み合う位置で両ギアの歯が互いに打ち合う
ことを意味し、雑音の抑制効果が充分に引き出されな
い。 【0009】さらに、歯形の一部に尖点(図4のZ1、
Z2)を生じるために、ヘルツ応力に代表される面圧の
増大、尖点のチッピングが発生し、歯面摩耗も促進され
る。 【0010】なお、上記の現象の発生原因は、送出流脈
動のみではない。通常の内接歯車式ポンプは、インナー
ギアに嵌合している駆動軸の振れによっても騒音、摩耗
が引き起こされる。駆動軸の振れはそのままインナーギ
アに伝達されるため、インナーギアに起振力が発生して
いるのと同義であり、隙間の不均一性によってインナー
ギアとアウターギアの歯が互いに打ち合う。 【0011】さらに、ポンピングチャンバ内における液
泡、気泡の破懐により発生するキャビテーションによる
送出流脈動の顕著な増大は、歯の打ち合いが起こり易い
構造の場合、その打ち合いを助長し、雑音、歯面摩耗を
一層促進させる。 【0012】本発明は、このような事情に鑑みてなされ
たものであり、雑音発生を減少させ、更には機械効率お
よび寿命の向上が図れる内接歯車式ポンプを提供するこ
とを目的とする。 【0013】 【課題を解決するための手段】本発明の歯車ポンプは、
液体又は気体圧送用のポンプに使用される内接歯車式ポ
ンプであって、下記の構成を採用したところに特徴を有
している。即ち、アウターギアと該アウターギアに内接
して噛み合うインナーギアとこれ等のギアを収納するハ
ウジングを具備し、アウターギアの歯溝とこれと対向す
るインナーギアの歯先はエピサイクロイド形状を有し、
アウターギアの歯先とこれと対向するインナーギアの歯
溝はハイポサイクロイド形状を有する内接歯車式ポンプ
において、アウターギアのエピサイクロイド形状(fh
1)はピッチ円上を転がる第1の生成円(re1)の円
周上の一点の軌跡で形成され、インナーギアのエピサイ
クロイド形状(fh2)はピッチ円上を転がる第2の生
成円(re2)の円周上の一点の軌跡で形成され、アウ
ターギアのハイポサイクロイド形状(fr1)はピッチ
円上を転がる第3の生成円(rh1)の円周上の一点の
軌跡で形成され、インナーギアのハイポサイクロイド形
状(fr2)はピッチ円上を転がる第4の生成円(rh
2)の円周上の一点の軌跡で形成され、生成円(re
1、re2、rh1、rh2)の各半径は各々異なり、
アウターギアの歯先とこれと対向するインナーギアの歯
溝間の隙間が、第3、第4の生成円(rh1、rh2)
の直径差に略等しく、アウターギアの歯溝とこれと対向
するインナーギアの歯先間の隙間が、第1、第2の生成
円の(re1、re2)の直径差に略等しく、アウター
ギアとインナーギアがもっとも深く噛み合う点における
アウターギアとインナーギア間の隙間と、アウターギア
とインナーギアの噛み合いがもっとも浅くなる領域での
アウターギアとインナーギアの歯先間の隙間とが略等し
くなる構成にして上記の目的を達成するものである。 【0014】 【発明の実施の形態】図1に本発明の好ましい実施の形
態を示す。fh1、fr1は図2に示すアウターギア1
の歯溝3、歯先4の形状を規定するエピサイクロイド、
ハイポサイクロイドを示す。fh1は、ピッチ円P上の
点z0を起点として生成円re1がピッチ円上を転動
し、その生成円の円周上の一点の軌跡として形成され
る。fr1は同じく、ピッチ円上の点z0を起点として
生成円rh1がピッチ円上を転動し、その生成円の円周
上の一点の軌跡として形成される。 【0015】fh2、fr2は図2に示すインナーギア
2の歯先6、歯溝5の形状を規定するエピサイクロイ
ド、ハイポサイクロイドを示す。fh2は、ピッチ円P
上の点z0’を起点として生成円re2がピッチ円上を
転動し、その生成円の円周上の一点の軌跡として形成さ
れる。fr2は同じく、ピッチ円上の点z0’を起点と
して生成円rh2がピッチ円上を転動し、その生成円の
円周上の一点の軌跡として形成される。 【0016】尚、ピッチ円Pは図2のアウターギア1と
インナーギア2のそれぞれのピッチ円を意味するが、図
1においては便宜上同一のピッチ円として表示してあ
る。アウターギア1とインナーギア2間の隙間CRは、
生成円re1、re2、rh1、rh2直径の差によっ
て生じるので、アウターギア1とこれと対向するインナ
ーギア2間には両者がもっとも深く噛み合う領域では略
等しい隙間が生じることになる。 【0017】本発明の内接歯車式ポンプは、図3に示さ
れるように、アウターギア1とアウターギアよりも歯数
の少ないインナーギア2がハウジング10内に設けられ
(ハウジングの蓋は図示せず)、インナーギア2がアウ
ターギア1の回転中心より偏心した位置に回転中心をも
つように配置され、そのインナーギア2と同軸に配され
る駆動シャフト(図示せず)により回転駆動される構造
を有する。ハウジング10は、通常のポンプと同じく吸
引口7、吐出口8を有している。インナーギア2とアウ
ターギア1間には両ギアの回転により容積変化を生じる
チャンバ(ポンピングチャンバ)9が作り出され、その
チャンバ9が吸引口7と連通している位置でチャンバ9
内に液体または気体が吸入され、その液体又は気体が圧
縮工程に移ったチャンバ内で圧縮されて吐出口8から送
り出される。 【0018】通常、回転ポンプを使用すると、製造誤差
等により駆動軸に振れが発生する。駆動軸の振れはその
ままインナーギア2に伝達され、インナーギア2の歯面
と噛み合うことによりアウターギア1に伝達される。こ
れにより、駆動軸の振れは理論上の両歯車の噛み合いか
らのズレを生じさせ、両歯車に予期せぬ歯の摩耗が発生
するとともに、両歯車の歯同志が当たることで雑音を生
じさせる。さらに、アウターギア1とハウジング10と
が機械的に押しつけられ、最悪の場合はギアの破損とい
う事態になる。 【0019】この結果、従来技術においては、歯間隙間
の不均一性によって生じる上記の不具合を無くすため
に、駆動軸の振れを厳密な製造を行って小さく抑える
か、もしくはアウターギア1とハウジング10間の隙間
を大きなものにする必要があった。 【0020】しかしながら、アウターギア1とハウジン
グ10間の隙間を大きくする行為は、ポンプの吐出量を
低下させる行為に他ならない。何故ならば、ギアの回転
によるチャンバ9の容積縮小により圧縮された流体がそ
の隙間を通って高圧部分から低圧部分に逆流するためで
ある。 【0021】本発明は、アウターギア1とインナーギア
2がもっとも深く噛み合う点(最深噛合部)における各
ギア歯間の隙間と、アウターギア1とインナーギア2の
噛み合いがもっとも浅くなる領域での各ギア歯間の隙間
とが略等しくなる構成にして歯間隙間の不均一性を解消
する。 【0022】いうまでもなく、歯間隙間の均一性は4個
の生成円の直径に適宜差を設けて達成される。 【0023】その結果、歯形形状の連続性を損なうこと
なく、言い換えれば歯形形状の一部に尖点を生じること
なく滑らかな歯形を実現して尖点を起点とする歯面摩耗
の発生を押さえることができる。 【0024】ところで、本発明ではインナーギア2の歯
数、アウターギア1の歯数、エピサイクロイドを生成す
る生成円の直径とハイポサイクロイドを生成する生成円
の直径およびその比には何等拘束されず、歯間隙間の均
一性と歯形形状の連続性が保証される。また、歯間隙間
の量(大きさ)もポンプの必要吐出量に応じて選択され
るべきものである。 【0025】 【実施例】図2に本発明の内接歯車式ポンプの歯車の噛
合状態を示す。図2(a)は、インナーギア2の歯先6
とアウターギア1の歯溝3の最深噛合状態を示し、図2
(b)は、インナーギア2の歯溝5とアウターギア1の
歯先4の最深噛合状態を示す。 【0026】1はアウターギア、2はインナーギア、
3、4はアウターギア1の歯溝、歯先を示す。5、6は
インナーギア2の歯溝、歯先を示す。また、C は、
アウターギア1とインナーギア2の最深噛合部における
歯先と歯溝間の隙間、C は、噛み合いがもっとも浅
くなる領域(最深噛合部の反対領域)におけるアウター
ギア1とインナーギア2の歯先間の隙間を示す。C
は、アウターギア1とインナーギア2の軸心の偏心量を
示す。 【0027】次に、本発明のポンプにおけるインナーギ
ア、アウターギアの代表的な寸法諸元を示す。 インナーギア歯数:10枚 インナーギアピッチ円径:φ64.00mm インナーギアエピサイクロイド生成円径:φ2.50m
m インナーギアハイポサイクロイド生成円径:φ3.90
mm アウターギア歯数:11枚 アウターギアピッチ円径:φ70.40mm アウターギアエピサイクロイド生成円径:φ2.56m
m アウターギアハイポサイクロイド生成円径:φ3.84
mm インナーギアとアウターギアの軸心の偏心量:3.20
mm 【0028】上記諸元にて歯形を作成しその隙間を測定
すると、アウターギア1とインナーギア2がもっとも深
く噛み合う点における歯間の隙間(図2(a)もしくは
図2(b)のC )は略0.06mmとなり、アウタ
ーギア1とインナーギア2の噛み合いがもっとも浅くな
る領域での歯間の隙間(図2(a)もしくは図2(b)
のC )は前者とほぼ等しく略0.06mmになる。 【0029】また、歯形形状の一部を拡大すると、エピ
サイクロイドの開始点もしくは終了点と、ハイポサイク
ロイドの開始点もしくは終了点が尖点を生じることなく
連続性を確保しているのが判る。 【0030】図3に、図1、図2の内接歯車をハウジン
グ10に収納した状態を示す。7は吸引口、8は排出
口、9はチャンバ、10はハウジングである。ハウジン
グ10には、歯車収納室を封止する蓋(図示せず)が取
付けられる。 【0031】なお、試作品による試験結果から、本発明
の構造を有する内接歯車式ポンプは、従来技術の同種の
ポンプに比較して寿命、機械効率ともに飛躍的に向上す
ることがわかった。 【0032】 【発明の効果】本発明によれば、アウターギアとインナ
ーギアがもっとも深く噛み合う点における歯間の隙間
と、アウターギアとインナーギアの噛み合いがもっとも
浅くなる領域での歯間の隙間とが略等しくなるようにし
たので、圧縮効率および寿命の向上、ひいては雑音の低
減、歯面摩耗の低減が図れる。
Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary pump which is driven by a drive source such as a motor and compresses and discharges a liquid or a gas. The present invention relates to a contact gear pump. 2. Description of the Related Art Most of internal gear pumps used in a vehicle transmission device using an internal combustion engine and an automatic motor have trochoid teeth. With the trochoid tooth, one of the tooth surfaces of the outer gear and the inner gear is limited to an arc shape, and the tooth surface of the other gear is defined by the non-slip rotation of the tooth of the one gear defined by the arc. A thing. An internal gear pump improved by the present invention specifically uses a cycloidal tooth profile for delivering liquid or gas in an internal combustion engine and an automatic transmission. Patent No. 23342
No. 3 and German Patent No. 3938346. The pump according to the above-mentioned German patent is an internal gear pump having an outer gear (outer rotor) and an inner gear (inner rotor) having different numbers of teeth, and excellent movement of teeth and tooth spaces having a perfect cycloid tooth profile. Using biological characteristics. [0004] The teeth of the outer gear mesh with the teeth of an inner gear driven by a crankshaft of an engine or a main shaft (main shaft) of an automatic gearbox. In this internal gear pump, relatively clear radial movement of the drive shaft, such as the crankshaft, appropriately sets the clearance between the outer peripheral surface and the housing (radial runout of the outer gear). To allow play). The compensation is
Attach the outer gear with almost no play,
It is also possible to provide a correspondingly large play between the bearing of the inner gear and the inner gear. In this case, the teeth of the inner gear are then meshed with the teeth of the outer gear. Such a pump is a preferred application of the technology of the present invention. FIG. 4 shows a model diagram of a flattened cycloid tooth profile proposed in Japanese Patent Application Laid-Open No. 5-256268. Japanese Patent Application Laid-Open No. 5-256268 discloses a flattening cycloid tooth profile of each gear for the purpose of generating noise due to the delivery flow pulsation found in a known pump, reducing the efficiency of the pump and reducing cavitation noise. The gap between the teeth at the position where the outer gear and the inner gear mesh most deeply is reduced. Fh in FIG. 4 is an original epicycloid defined by a locus of one point on the circumference of the generated circle re, with the generated circle re rolling on the pitch circle starting from a point z0 on the pitch circle P of the gear; fr is a point z0 on the pitch circle P.
, The generated circle rh rolls on the pitch circle, and the original hypocycloid defined by the locus of one point on the circumference of the generated circle rh, and fh3 and rh3 are epicycloid and hypocycloid after flattening. . [0007] The pressure pulsation of the working fluid,
That is, when the outflow pulsation occurs, the outer gear and the inner gear exert a vibrating force, and the teeth of the two gears strike each other in the radial direction and the tangential direction, generating undesirable noise. Japanese Unexamined Patent Application Publication No. 5-256268 attempts to suppress the noise. However, according to the technique disclosed in the publication, the gap between the teeth of each gear at the point where the outer gear and the inner gear mesh most deeply is very small. In the region where the gear meshing is the shallowest, the interdental gap between the gears is formed large, and the gap is uneven. this is,
When the delivery flow pulsation occurs, it means that the teeth of the two gears strike each other at the position where the outer gear and the inner gear mesh most deeply, and the noise suppression effect is not sufficiently obtained. Further, cusps (Z1, Z1 in FIG. 4)
In order to cause Z2), an increase in surface pressure typified by Hertz stress, chipping of cusps occurs, and tooth surface wear is promoted. [0010] The cause of the above-mentioned phenomenon is not limited to the outflow pulsation. In a normal internal gear pump, noise and wear are also caused by runout of a drive shaft fitted to an inner gear. Since the run-out of the drive shaft is transmitted to the inner gear as it is, this is synonymous with the generation of a vibrating force in the inner gear, and the unevenness of the gap causes the teeth of the inner gear and the outer gear to strike each other. Further, the remarkable increase in the pulsation of the delivery flow due to the cavitation caused by the breakage of the liquid bubbles and bubbles in the pumping chamber promotes the striking of the teeth in a structure in which the striking of the teeth is likely to occur. Is further promoted. The present invention has been made in view of such circumstances, and an object of the present invention is to provide an internal gear pump that can reduce noise and improve mechanical efficiency and life. [0013] The gear pump of the present invention comprises:
An internal gear pump used for a liquid or gas pressure pump, which is characterized by employing the following configuration. That is, an outer gear, an inner gear that is in contact with and meshes with the outer gear, and a housing for accommodating these gears are provided, and the tooth groove of the outer gear and the tooth tip of the inner gear opposed thereto have an epicycloid shape. ,
In the internal gear type pump having a hypocycloid shape, the tooth tip of the outer gear and the tooth groove of the inner gear facing the outer gear have an epicycloid shape (fh) of the outer gear.
1) is formed by a locus of one point on the circumference of the first generated circle (re1) rolling on the pitch circle, and the epicycloid shape (fh2) of the inner gear is formed on the second generated circle (re2) rolling on the pitch circle. ), And the hypocycloid shape (fr1) of the outer gear is formed by the locus of one point on the circumference of the third generated circle (rh1) rolling on the pitch circle. Is a fourth generated circle (rh) rolling on a pitch circle.
The generated circle (re) is formed by a locus of one point on the circumference of 2).
1, re2, rh1, rh2) have different radii,
The gap between the tooth tip of the outer gear and the tooth groove of the inner gear opposed thereto is the third and fourth generated circles (rh1, rh2).
And the gap between the tooth groove of the outer gear and the tooth tip of the inner gear facing the outer gear is substantially equal to the diameter difference of (re1, re2) of the first and second generated circles. The gap between the outer gear and the inner gear at the point where the gear and the inner gear mesh most deeply, and the gap between the teeth of the outer gear and the inner gear in the region where the engagement between the outer gear and the inner gear is the shallowest are approximately equal This achieves the above object. FIG. 1 shows a preferred embodiment of the present invention. fh1 and fr1 are outer gears 1 shown in FIG.
Epicycloid which defines the shape of the tooth space 3 and the tooth tip 4 of
Indicates a hypocycloid. fh1 is formed as a locus of one point on the circumference of the generated circle, with the generated circle re1 rolling on the pitch circle starting from the point z0 on the pitch circle P. Similarly, fr1 is formed as a locus of one point on the circumference of the generated circle, with the generated circle rh1 rolling on the pitch circle starting from the point z0 on the pitch circle. Fh2 and fr2 denote epicycloids and hypocycloids which define the shape of the tooth tip 6 and the tooth space 5 of the inner gear 2 shown in FIG. fh2 is the pitch circle P
The generated circle re2 rolls on the pitch circle starting from the upper point z0 ′, and is formed as a locus of one point on the circumference of the generated circle. Similarly, fr2 is formed as a locus of one point on the circumference of the generated circle, with the generated circle rh2 rolling on the pitch circle starting from the point z0 ′ on the pitch circle. The pitch circle P means the pitch circle of each of the outer gear 1 and the inner gear 2 in FIG. 2, but is shown as the same pitch circle for convenience in FIG. The gap CR between the outer gear 1 and the inner gear 2 is
Since it is caused by the difference between the diameters of the generated circles re1, re2, rh1, and rh2, a substantially equal gap is generated between the outer gear 1 and the inner gear 2 facing the outer gear 1 in a region where the two mesh deepest. As shown in FIG. 3, the internal gear pump according to the present invention includes an outer gear 1 and an inner gear 2 having fewer teeth than the outer gear. The inner gear 2 is arranged so as to have a center of rotation at a position eccentric from the center of rotation of the outer gear 1, and is driven to rotate by a drive shaft (not shown) coaxial with the inner gear 2. Having. The housing 10 has a suction port 7 and a discharge port 8 as in a normal pump. Between the inner gear 2 and the outer gear 1, a chamber (pumping chamber) 9 that produces a volume change by the rotation of both gears is created, and the chamber 9 is located at a position where the chamber 9 communicates with the suction port 7.
Liquid or gas is sucked into the inside, and the liquid or gas is compressed in the chamber which has moved to the compression step, and is sent out from the discharge port 8. Normally, when a rotary pump is used, the drive shaft oscillates due to a manufacturing error or the like. The deflection of the drive shaft is transmitted to the inner gear 2 as it is, and is transmitted to the outer gear 1 by meshing with the tooth surface of the inner gear 2. As a result, the run-out of the drive shaft causes a deviation from the theoretical meshing of the two gears, causing unexpected wear of the teeth of the two gears and generating noise due to the contact of the teeth of the two gears. Further, the outer gear 1 and the housing 10 are mechanically pressed, and in the worst case, the gear may be damaged. As a result, in the prior art, in order to eliminate the above-mentioned inconvenience caused by the non-uniformity between the tooth gaps, the run-out of the drive shaft is strictly manufactured to reduce it, or the outer gear 1 and the housing 10 The gap between them had to be large. However, the act of increasing the gap between the outer gear 1 and the housing 10 is nothing less than the act of reducing the discharge of the pump. This is because the fluid compressed by the reduction of the volume of the chamber 9 due to the rotation of the gear flows back from the high pressure portion to the low pressure portion through the gap. According to the present invention, the gap between the gear teeth at the point where the outer gear 1 and the inner gear 2 mesh most deeply (the deepest meshing portion), and the gap between the outer gear 1 and the inner gear 2 in the region where the engagement between the outer gear 1 and the inner gear 2 is the shallowest. A configuration in which the gap between the gear teeth is substantially equal eliminates the non-uniformity between the tooth gaps. Needless to say, the uniformity between the tooth gaps is achieved by appropriately providing the diameters of the four generated circles. As a result, a smooth tooth profile can be realized without impairing the continuity of the tooth profile, in other words, without generating cusps in a part of the tooth profile, thereby suppressing the occurrence of tooth surface wear starting from the cusps. be able to. In the present invention, the number of teeth of the inner gear 2, the number of teeth of the outer gear 1, the diameter of a generating circle for generating an epicycloid, the diameter of a generating circle for generating a hypocycloid, and their ratio are not restricted at all. In addition, uniformity between tooth gaps and continuity of the tooth profile are guaranteed. Also, the amount (size) between the tooth gaps should be selected according to the required discharge amount of the pump. FIG. 2 shows a meshing state of gears of an internal gear pump according to the present invention. FIG. 2A shows the tooth tip 6 of the inner gear 2.
FIG. 2 shows a state in which the tooth groove 3 of the outer gear 1 is in the deepest meshing state.
(B) shows the deepest meshing condition between the tooth groove 5 of the inner gear 2 and the tooth tip 4 of the outer gear 1. 1 is an outer gear, 2 is an inner gear,
Reference numerals 3 and 4 denote tooth grooves and tooth tips of the outer gear 1. Reference numerals 5 and 6 denote tooth grooves and tooth tips of the inner gear 2. Also, C 1 is
Gap between the tooth tips and tooth grooves of the deepest meshing portions of the outer gear 1 and the inner gear 2, C 2, the meshing outer gear 1 and the tooth tip of the inner gear 2 in the most shallow a region (an opposite region of the deepest meshing portions) The gap between them is shown. C 3
Indicates the amount of eccentricity of the axis of the outer gear 1 and the inner gear 2. Next, typical dimensions of the inner gear and the outer gear in the pump of the present invention will be described. Number of inner gear teeth: 10 Inner gear pitch circle diameter: φ64.00 mm Inner gear epicycloid generation circle diameter: φ2.50 m
m Inner gear hypocycloid formation circle diameter: φ3.90
mm Number of outer gear teeth: 11 Outer gear pitch circle diameter: φ70.40 mm Outer gear epicycloid generation circle diameter: φ2.56 m
m Outer gear hypocycloid formation circle diameter: φ3.84
mm Eccentricity of the axis of the inner gear and the outer gear: 3.20
mm When the tooth profile is created based on the above specifications and the gap is measured, the gap between the teeth at the point where the outer gear 1 and the inner gear 2 mesh deepest (C in FIG. 2 (a) or FIG. 2 (b)) 1 ) is approximately 0.06 mm, and the gap between the teeth in the region where the engagement between the outer gear 1 and the inner gear 2 is the shallowest (FIG. 2A or FIG. 2B).
C 2 ) is approximately equal to the former and is approximately 0.06 mm. Further, when a part of the tooth profile is enlarged, it can be seen that the start point or the end point of the epicycloid and the start point or the end point of the hypocycloid maintain continuity without generating a cusp. FIG. 3 shows a state in which the internal gear of FIGS. 1 and 2 is housed in a housing 10. 7 is a suction port, 8 is a discharge port, 9 is a chamber, and 10 is a housing. A lid (not shown) for sealing the gear storage chamber is attached to the housing 10. From the test results of the prototypes, it was found that the internal gear pump having the structure of the present invention dramatically improved in both the service life and the mechanical efficiency as compared with the same type pump of the prior art. According to the present invention, the gap between the teeth at the point where the outer gear and the inner gear mesh most deeply, and the gap between the teeth at the area where the engagement between the outer gear and the inner gear is shallowest are obtained. Are made substantially equal, so that compression efficiency and life can be improved, noise can be reduced, and tooth surface wear can be reduced.
【図面の簡単な説明】 【図1】 本発明のポンプのインナーギアとアウターギ
アの噛み合い軌跡を示す説明図。 【図2】 本発明の内接歯車式ポンプのインナーギアと
アウターギアの噛合状態を示す正面図。 【図3】 本発明の内接歯車式ポンプをハウジングの蓋
を外した状態にして示す正面図。 【図4】 平坦化されたサイクロイド歯形のモデル図。 【符号の説明】 1 アウターギア、2 インナーギア、3 アウターギ
アの溝、4 アウターギアの歯、5 インナーギアの
溝、6 インナーギアの歯、7 吸引口、8 排出口、
9 チャンバ、10 ハウジング。
BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an explanatory diagram showing the engagement locus of an inner gear and an outer gear of a pump according to the present invention. FIG. 2 is a front view showing a meshing state of an inner gear and an outer gear of the internal gear pump according to the present invention. FIG. 3 is a front view showing the internal gear pump according to the present invention with a cover of a housing removed. FIG. 4 is a model diagram of a flattened cycloid tooth profile. [Description of Signs] 1 outer gear, 2 inner gear, 3 outer gear groove, 4 outer gear teeth, 5 inner gear groove, 6 inner gear teeth, 7 suction port, 8 discharge port,
9 chambers, 10 housings.

Claims (1)

  1. 【特許請求の範囲】 【請求項1】 アウターギアと当該アウターギアに内接
    して噛み合うインナーギアと、これ等のギアを収納する
    ハウジングを具備し、アウターギアの歯溝とこれと対向
    するインナーギアの歯先はエピサイクロイド形状を有
    し、アウターギアの歯先とこれと対向するインナーギア
    の歯溝はハイポサイクロイド形状を有する内接歯車式ポ
    ンプにおいて、 アウターギアのエピサイクロイド形状はアウターギアの
    ピッチ円上を転がる第1の生成円の円周上の一点の軌跡
    で形成され、インナーギアのエピサイクロイド形状はイ
    ンナーギアのピッチ円上を転がる第2の生成円の円周上
    の一点の軌跡で形成され、アウターギアのハイポサイク
    ロイド形状はアウターギアのピッチ円上を転がる第3の
    生成円の円周上の一点の軌跡で形成され、インナーギア
    のハイポサイクロイド形状はインナーギアのピッチ円上
    を転がる第4の生成円の円周上の一点の軌跡で形成さ
    れ、生成円の各半径は各々異なり、アウターギアの歯先
    とこれと対向するインナーギアの歯溝間の隙間が、第
    3、第4の生成円の直径差に略等しく、アウターギアの
    歯溝とこれと対向するインナーギアの歯先間の隙間が、
    第1、第2の生成円の直径差に略等しく、アウターギア
    とインナーギアがもっとも深く噛み合う点におけるアウ
    ターギアとインナーギア間の隙間と、アウターギアとイ
    ンナーギアの噛み合いがもっとも浅くなる領域でのアウ
    ターギアとインナーギアの歯先間の隙間とが略等しいこ
    とを特徴とする内接歯車式ポンプ。
    Claims: 1. An outer gear comprising: an outer gear; an inner gear which is in contact with and meshes with the outer gear; and a housing for accommodating these gears, wherein a tooth groove of the outer gear and an inner gear opposed thereto are provided. In the internal gear pump, the tip of the outer gear has an epicycloid shape, the tooth of the outer gear and the tooth groove of the inner gear opposed thereto have a hypocycloid shape, the epicycloid shape of the outer gear is the pitch of the outer gear. The epicycloid shape of the inner gear is formed by the locus of one point on the circumference of the first generated circle rolling on the circle, and the locus of one point on the circumference of the second generated circle rolling on the pitch circle of the inner gear. The hypocycloid shape of the outer gear is formed by a locus of one point on the circumference of a third generated circle rolling on the pitch circle of the outer gear. The hypocycloid shape of the inner gear is formed by a locus of one point on the circumference of the fourth generated circle rolling on the pitch circle of the inner gear, and each radius of the generated circle is different, and the tip of the outer gear faces the tooth tip of the outer gear. The gap between the tooth grooves of the inner gear is substantially equal to the diameter difference between the third and fourth generated circles, and the gap between the tooth groove of the outer gear and the tooth tip of the inner gear facing the outer gear groove is
    The gap between the outer gear and the inner gear at the point where the outer gear and the inner gear mesh most deeply with the diameter difference between the first and second generated circles, and the area where the outer gear and the inner gear mesh most shallowly An internal gear pump characterized in that the gap between the tooth tips of the outer gear and the inner gear is substantially equal.
JP2002232315A 1997-09-04 2002-08-09 Internal gear oil pump Expired - Lifetime JP4251831B2 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP23956297 1997-09-04
JP9-239562 1997-09-04
JP2002232315A JP4251831B2 (en) 1997-09-04 2002-08-09 Internal gear oil pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2002232315A JP4251831B2 (en) 1997-09-04 2002-08-09 Internal gear oil pump

Related Child Applications (1)

Application Number Title Priority Date Filing Date
JP10545494 Division

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JP2003056473A true JP2003056473A (en) 2003-02-26
JP2003056473A5 JP2003056473A5 (en) 2006-03-02
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ID=26534310

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WO2008030004A1 (en) * 2006-09-03 2008-03-13 S & T Daewoo Co., Ltd Tooth profile of internal gear
JP2008138601A (en) * 2006-12-01 2008-06-19 Sumitomo Denko Shoketsu Gokin Kk Inscribed gear pump
JP2009013832A (en) * 2007-07-03 2009-01-22 Sumitomo Denko Shoketsu Gokin Kk Pump rotor and internal gear pump using it
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JP2005036735A (en) * 2003-07-15 2005-02-10 Sumitomo Denko Shoketsu Gokin Kk Internal gear pump and inner rotor of the pump
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WO2005015022A1 (en) * 2003-08-12 2005-02-17 Mitsubishi Materials Corporation Oil pump rotor
US7476093B2 (en) 2003-08-12 2009-01-13 Mitsubishi Materials Pmg Corporation Oil pump rotor assembly
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JP2007085256A (en) * 2005-09-22 2007-04-05 Aisin Seiki Co Ltd Oil pump rotor
WO2007034888A1 (en) * 2005-09-22 2007-03-29 Aisin Seiki Kabushiki Kaisha Oil pump rotor
US8579617B2 (en) 2005-09-22 2013-11-12 Aisin Seiki Kabushiki Kaisha Oil pump rotor
US8096795B2 (en) 2005-09-22 2012-01-17 Aisin Seiki Kabushki Kaisha Oil pump rotor
WO2008030004A1 (en) * 2006-09-03 2008-03-13 S & T Daewoo Co., Ltd Tooth profile of internal gear
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