JPS59131787A - Rotary pump - Google Patents

Rotary pump

Info

Publication number
JPS59131787A
JPS59131787A JP711383A JP711383A JPS59131787A JP S59131787 A JPS59131787 A JP S59131787A JP 711383 A JP711383 A JP 711383A JP 711383 A JP711383 A JP 711383A JP S59131787 A JPS59131787 A JP S59131787A
Authority
JP
Japan
Prior art keywords
rotor
curve
inner rotor
outer rotor
pump
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
Application number
JP711383A
Other languages
Japanese (ja)
Inventor
Aoi Sugimoto
杉本 葵
Yasuyoshi Saegusa
三枝 康能
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.)
Sumitomo Electric Industries Ltd
Original Assignee
Sumitomo Electric Industries 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 Sumitomo Electric Industries Ltd filed Critical Sumitomo Electric Industries Ltd
Priority to JP711383A priority Critical patent/JPS59131787A/en
Publication of JPS59131787A publication Critical patent/JPS59131787A/en
Pending legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/08Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10Rotary-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
    • F04C2/101Rotary-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 with a crescent-shaped filler element, located between the inner and outer intermeshing members

Abstract

PURPOSE:To reduce leakage against low viscosity and high pressure of fluid to be pumped by a method wherein a crescent is provided between an outer rotor and an inner rotor while a paratrochoidal curve is employed to form the shapes of the teeth of both rotors. CONSTITUTION:The shapes of the teeth of the outer rotor 12 and the inner rotor 11 are formed by the paratrochoidal curve and the crescent 5 is provided between the outer rotor 12 and the inner rotor 11. According to this method, the low pressure side and the high pressure side of the pump may be partitioned by surface contacts between the crescent 5 and the inner diameter of the outer rotor 12 as well as the outer diameter of the inner rotor 11, therefore, leakage may be reduced against the low viscosity and the high pressure of the fluid to the pumped.

Description

【発明の詳細な説明】 この発明はエンジン潤滑油供給用オイルポンプや高圧用
あるいは低粘度用ポンプに用いる回転ポンプに関するも
のであり、詳しくのべると内接歯車を使用した回転ポン
プにおいて、アウターローターとインナーローターとの
間にクレセントを設け、かつ歯形状にアウターローター
、インナーローターともにバラトロコイド曲線を用いた
ことを特徴とするものである。
Detailed Description of the Invention The present invention relates to a rotary pump used for an oil pump for supplying engine lubricating oil or a high-pressure or low-viscosity pump.More specifically, in a rotary pump using an internal gear, the outer rotor and A crescent is provided between the rotor and the inner rotor, and both the outer rotor and the inner rotor are characterized by having baratrochoid curves as tooth shapes.

トロコイド曲線Tとは第1図において直径Aなる基礎円
上を直径B=A/n  (nは普通正の整数であって、
インナーの歯数)なる転円が滑らずに転がる時に、この
転円中の転円よりeだけ偏心した定点が描く曲線のこと
である。そしてこのトロコイド曲線上を直径Cの軌跡円
の中心が移動する時にできるこの円群に対する包絡線を
バラトロコイド曲線TCとすると、このバラトロコイド
曲線TCを通常のトロコイド歯形のポンプのインナーロ
ーターの歯の曲線として使用する。
Trochoid curve T is a basic circle with diameter A in Fig. 1 with diameter B = A/n (n is usually a positive integer,
It is a curve drawn by a fixed point that is eccentric from the rolling circle by e when the rolling circle (number of inner teeth) rolls without slipping. If the envelope for this group of circles created when the center of a locus circle with diameter C moves on this trochoid curve is the baratrochoid curve TC, then this baratrochoid curve TC is the shape of the teeth of the inner rotor of a pump with a normal trochoid tooth profile. Use as a curve.

この時アウターローターの曲線は通常直径Cの円弧が(
n+1)個でできていることになる。
At this time, the curve of the outer rotor is usually an arc of diameter C (
It is made up of n+1) pieces.

従来トロコイド曲線を用いたポンプローターは、アウタ
ーローターは軌跡円弧、インナーローターはバラトロコ
イド曲線を用いた内外の歯数差1枚のものが通常であっ
た。
Conventionally, a pump rotor using a trochoid curve has an outer rotor having an arcuate trajectory, and an inner rotor using a baratrochoid curve, with a difference in the number of teeth between the inner and outer rotors of one tooth.

このタイプのローターの欠点は、100に9J以上もの
高圧にするのが非常に回動であり、また低粘度において
は吐出効率が悪くなることである。
The drawbacks of this type of rotor are that it requires a lot of rotation to generate high pressures of 100 to 9 J or more, and that the discharge efficiency is poor at low viscosity.

即ち第2図に示すように、アウターローター1の歯曲線
はインナーローター1の歯数より1個多い円弧からなり
、インナーローターは上述したようにパラトロコイド曲
線でできている。
That is, as shown in FIG. 2, the tooth curve of the outer rotor 1 consists of one more circular arc than the number of teeth of the inner rotor 1, and the inner rotor is made of a paratrochoid curve as described above.

インナーローターとアウターローターは離心量eだけ偏
心している。
The inner rotor and outer rotor are eccentric by an eccentricity e.

そして矢印の方向へインナーローターが回転すると、ア
ウターローターは従動して回転し、インナーローターと
アウターローターで作る空間容積Sは吸入孔側では次第
に大きくなり、最大になった後吐出孔側で次第に小さく
なって行く。
When the inner rotor rotates in the direction of the arrow, the outer rotor follows and rotates, and the space volume S created by the inner rotor and outer rotor gradually increases on the suction port side, reaches its maximum, and then gradually decreases on the discharge port side. It's becoming.

そして吸入孔側から吐出孔側ヘローターが回転する時高
圧側)(Pと低圧側LPを仕切るところは、第3図に示
すようにインナーローターとアウターローターの線接触
部したけ、になり、ここでの漏れが大きいため特に圧力
が高くなったり、低粘度になるとこの影響が著しくなっ
て容積効率が悪くなるという欠点がある。
When the rotor rotates from the suction hole side to the discharge hole side, the place that separates the high pressure side (P) from the low pressure side LP is the line contact area between the inner rotor and the outer rotor, as shown in Figure 3. Since the leakage is large, this effect becomes significant especially when the pressure becomes high or the viscosity becomes low, resulting in a disadvantage that the volumetric efficiency deteriorates.

そこで従来のエンジン潤滑用オイルポンプのエンジン直
結タイプにおいて使用されている第4図の如き内接形イ
ンボリュート歯車に使用されていると同様のクレセント
5を使用することができれば対策をこうじたことになっ
て好ましいが、従来の上記形状のローターではそれが不
可能である。
Therefore, if it were possible to use a crescent 5 similar to that used in the internal involute gear shown in Fig. 4, which is used in the engine-directly connected type of conventional oil pump for engine lubrication, a countermeasure would be taken. However, this is not possible with conventional rotors of the above shape.

この発明は上記の点に鑑みてなされたものであり、アウ
ターローター、インナーローターともにパラトロコイド
曲線を用い、インナーローターおよびアウターローター
の歯先、歯元をそれぞれの回転中心を中心とする円弧形
状とすることによりクレセントを挿入可能にしたことを
特徴とするものである。
This invention was made in view of the above points, and uses a paratrochoid curve for both the outer rotor and the inner rotor, and the tips and roots of the inner rotor and outer rotor are shaped into circular arcs centered on their respective rotation centers. This feature allows the crescent to be inserted.

これによってパラトロコイド歯形を用いたポンプロータ
ーにても低粘度流体用や高圧用のポンプとして使えるこ
とになるのである。
As a result, even a pump rotor using a paratrochoid tooth profile can be used as a pump for low viscosity fluids or high pressures.

例えば最近のエンジンはターボ化など高性能化し、それ
に応じてエンジン周辺の′ljA度が上昇し、オイルの
温度も上り、粘度低下し、そのため充分な吐出量を確保
できないようなことが起るが、このような時にこの発明
の回転ポンプが有効である。
For example, recent engines have become more efficient, such as turbos, and the temperature around the engine increases accordingly, the oil temperature also rises, and the viscosity decreases, making it impossible to ensure sufficient displacement. The rotary pump of the present invention is effective in such cases.

というのはクレセントがあるため低圧側と高圧側の仕切
りがタレセントとアウターローター内径およびインナー
ローター外径との面接触とすることができ、低粘度は勿
論のこと高圧に対しても漏れを小さくできるのである。
Because there is a crescent, the partition between the low pressure side and the high pressure side can make surface contact between the talescent and the inner diameter of the outer rotor and the outer diameter of the inner rotor, which can reduce leakage not only for low viscosity but also for high pressure. It is.

以下この発明の回転ポンプを第5図について説明すると
、インナーローター11の歯数を01、アウターロータ
ー12の歯数をn、 (n、> n、 )とし、転円径
をB mm、軌跡円径をCmm、離心量をe、IIlを
正の整数とした時、 インナーローターはA、  −〇l 、i Bを基礎円
径とする転円径B1軌跡円径C1離心量eをもったトロ
コイド曲線のパラトロコイド曲線を歯曲線とし、アウタ
ーローターはAL=n!、&Bを基礎円径とする転円径
B1軌跡円径C1離心i1eをもったトロコイド曲線の
バラトロコイド曲線を歯曲線とすると、この時にインナ
ーローターとアウターローターとの中心の距離EはE 
= −匹E−勿−Bとなる。
Hereinafter, the rotary pump of the present invention will be explained with reference to FIG. 5. The number of teeth of the inner rotor 11 is 01, the number of teeth of the outer rotor 12 is n, (n, > n, ), the radius of rotation is B mm, and the trajectory circle is When the diameter is Cmm, the eccentricity is e, and IIl is a positive integer, the inner rotor is a trochoid with A, -〇l, i B as the basic circle diameter, rolling circle diameter B1 locus circle diameter C1 eccentricity e The paratrochoid curve of the curve is taken as a tooth curve, and the outer rotor is AL=n! , &B as the base circle diameter, and the baratrochoid curve of the trochoid curve with the radius B1 of the locus circle diameter C1 and the eccentricity i1e is taken as a tooth curve. At this time, the distance E between the centers of the inner rotor and the outer rotor is E
= - E - Of course - B.

2萌t またインナーローター、アウターローターの歯先径をそ
れぞれd3.d2とするとクリアランス零の場^、4゜ 合はタレセントの厚さtはt = −+ Eである。
2. Also, set the tooth tip diameters of the inner rotor and outer rotor to d3. If d2, the thickness t of the talent is t = -+ E when the clearance is zero and 4 degrees.

歯だけをHとするとクリアランス零の場合は以上のよう
にこの発明の回転ポンプはアウターローターとインナー
ローターの間にクレセントを使用できるので高圧もしく
は低粘度でも効率よく使用できるのである。
If only the teeth are H and the clearance is zero, the rotary pump of the present invention can use a crescent between the outer rotor and the inner rotor as described above, so it can be used efficiently even at high pressure or low viscosity.

しかしてこの発明の回転ポンプはエンジン潤滑油供給用
オイルポンプ、高圧用(100kfllJ以上)油圧ポ
ンプ、低粘度流体く水、ガソリン)用ポンプ、自動変速
機用オイルポンプなどとして使用することができるので
ある。
However, the rotary pump of the present invention can be used as an oil pump for supplying engine lubricating oil, a high pressure (over 100 kflJ) hydraulic pump, a pump for low viscosity fluid (water, gasoline), an oil pump for automatic transmissions, etc. be.

【図面の簡単な説明】 第1図はトロコイド曲線諸元の説明図、第2図は従来の
パラトロコイド歯車ポンプの例、第3図は同パラ1−ロ
コイド歯車ポンプ回転時のインナーローターとアウター
ローターの接触部を示す部分拡大図、第4図はインボリ
ュート歯形内接歯車ポンプの正面図、第5図はこの発明
の回転ポンプの実施例を示す正面図である。 5・・・クレセント  11・・・インナーローター1
2・・・アウターローター  13・・・吐出孔14・
・・吸入孔 第1図 第2図         第4図 第5図 手続?■正書(自発) 1、事件の表示 昭和58年特許願第7113号 2、発明の名称 回転ポンプ 3、補正をする者 事件との関係  特許出願人 住  所  大阪市東区北浜5丁目15番地名  称 
 (213)住友電気工業株式会社4、代理人 住  所  大阪市大淀区中津1丁目18番18号若杉
ビル 6、補正の内容 別紙の通り 補正の内容 第1頁19行目 一ローター1」を「インナーローター 2」と副正します0 2、同第5頁3行目 Fnjを「nl」と訂正し1丁。 3、同!g5頁4行目 rnJを「n、」と訂正します。 4、同第5頁7行目 1 [Al= n+/ mB j k [At= B ×j
と訂正します。 5、同第5頁10行目 L r Az= na/mB J ’i r Al= BX
−Jと訂正します。 6、同第5頁14行目 n L   n 1 mB Jを[E = B x −Jと訂正m     
     2m
[Brief explanation of the drawings] Figure 1 is an explanatory diagram of trochoid curve specifications, Figure 2 is an example of a conventional paratrochoid gear pump, and Figure 3 is an illustration of the inner rotor and outer surface of the paratrochoid gear pump when it rotates. FIG. 4 is a front view of an involute tooth type internal gear pump, and FIG. 5 is a front view of an embodiment of the rotary pump of the present invention. 5...Crescent 11...Inner rotor 1
2... Outer rotor 13... Discharge hole 14.
...Suction hole Figure 1 Figure 2 Figure 4 Figure 5 Procedure? ■Authentic document (spontaneous) 1. Indication of the case Patent Application No. 7113 of 1982 2. Name of the invention Rotary pump 3. Person making the amendment Relationship to the case Patent applicant address Address 5-15 Kitahama, Higashi-ku, Osaka name
(213) Sumitomo Electric Industries, Ltd. 4, Agent Address: Wakasugi Building 6, 1-18-18 Nakatsu, Oyodo-ku, Osaka, Contents of Amendment As shown in the attached document, ``Contents of Amendment, Page 1, Line 19, Rotor 1'' Inner rotor 2" is corrected. 0 2, page 5, line 3, Fnj is corrected to "nl". 1. 3. Same! Correct rnJ on page 5, line 4 to "n,". 4, page 5, line 7 1 [Al= n+/ mB j k [At= B ×j
I will correct it. 5, page 5, line 10 L r Az = na/mB J 'i r Al = BX
- Correct as J. 6, page 5, line 14, change n L n 1 mB J to [E = B x −J m
2m

Claims (1)

【特許請求の範囲】[Claims] 内接歯車を使用した回転ポンプにおいて、アウターロー
ターとインナーローターとの間にタレセントを設け、か
つ歯形状にアウターローター、インナーローターともに
バラトロコイド曲線を用いたことを特徴とする回転ポン
プ。
A rotary pump using an internal gear, characterized in that a talent is provided between an outer rotor and an inner rotor, and a baratrochoid curve is used for the tooth shape of both the outer rotor and the inner rotor.
JP711383A 1983-01-18 1983-01-18 Rotary pump Pending JPS59131787A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP711383A JPS59131787A (en) 1983-01-18 1983-01-18 Rotary pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP711383A JPS59131787A (en) 1983-01-18 1983-01-18 Rotary pump

Publications (1)

Publication Number Publication Date
JPS59131787A true JPS59131787A (en) 1984-07-28

Family

ID=11657029

Family Applications (1)

Application Number Title Priority Date Filing Date
JP711383A Pending JPS59131787A (en) 1983-01-18 1983-01-18 Rotary pump

Country Status (1)

Country Link
JP (1) JPS59131787A (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5692888A (en) * 1995-10-24 1997-12-02 Truninger Ag Gear train mechanism having reduced leakage
WO2006086887A1 (en) * 2005-02-16 2006-08-24 Magna Powertrain Inc. Crescent gear pump with novel rotor set
EP1970570A2 (en) * 2007-03-16 2008-09-17 Yamada Manufacturing Co., Ltd. Internal gear pump
EP2050963A2 (en) 2007-10-21 2009-04-22 Yamada Manufacturing Co., Ltd. Method for manufacturing trochoid pump and trochoid pump obtained
EP2050962A2 (en) 2007-10-21 2009-04-22 Yamada Manufacturing Co., Ltd. Method for manufacturing trochoid pump and trochoid pump obtained

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5692888A (en) * 1995-10-24 1997-12-02 Truninger Ag Gear train mechanism having reduced leakage
WO2006086887A1 (en) * 2005-02-16 2006-08-24 Magna Powertrain Inc. Crescent gear pump with novel rotor set
US7766634B2 (en) 2005-02-16 2010-08-03 Magna Powertrain Inc. Crescent gear pump with novel rotor set
EP1970570A2 (en) * 2007-03-16 2008-09-17 Yamada Manufacturing Co., Ltd. Internal gear pump
US7625192B2 (en) 2007-03-16 2009-12-01 Yamada Manufacturing Co., Ltd. Internal gear pump including a crescent
EP1970570A3 (en) * 2007-03-16 2010-01-13 Yamada Manufacturing Co., Ltd. Internal gear pump
EP2050963A2 (en) 2007-10-21 2009-04-22 Yamada Manufacturing Co., Ltd. Method for manufacturing trochoid pump and trochoid pump obtained
EP2050962A2 (en) 2007-10-21 2009-04-22 Yamada Manufacturing Co., Ltd. Method for manufacturing trochoid pump and trochoid pump obtained
US7967586B2 (en) 2007-10-21 2011-06-28 Yamada Manufacturing Co., Ltd. Method for manufacturing trochoid pump and trochoid pump obtained
US7967585B2 (en) 2007-10-21 2011-06-28 Yamada Manufacturing Co., Ltd. Method for manufacturing trochoid pump and trochoid pump obtained

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