JPS6344954B2 - - Google Patents
Info
- Publication number
- JPS6344954B2 JPS6344954B2 JP55167161A JP16716180A JPS6344954B2 JP S6344954 B2 JPS6344954 B2 JP S6344954B2 JP 55167161 A JP55167161 A JP 55167161A JP 16716180 A JP16716180 A JP 16716180A JP S6344954 B2 JPS6344954 B2 JP S6344954B2
- Authority
- JP
- Japan
- Prior art keywords
- crescent
- hole
- internal gear
- seal member
- pressure plate
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
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
- F04C2/101—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 with a crescent-shaped filler element, located between the inner and outer intermeshing members
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Description
【発明の詳細な説明】
（産業上の利用分野）
この発明は、内接ギヤポンプ又はモータのプレ
ツシヤーローデイングに最適な機構に関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a mechanism optimal for pressure loading of an internal gear pump or motor.
（従来の技術）
第１，２図に示したローデイング機構は、三日
月形シール部材１の側面にプレツシヤープレート
２，３を当接させていた。(Prior Art) In the loading mechanism shown in FIGS. 1 and 2, pressure plates 2 and 3 are brought into contact with the side surfaces of a crescent-shaped seal member 1.
しかし、このような構成では、例えばピニオン
４やインターナルギヤ５の側面が摩耗してその歯
幅が狭くなつたとき、三日月形シール部材１があ
るためにプレツシヤープレート２，３がそれに追
随できない。 However, in such a configuration, when the side surfaces of the pinion 4 or internal gear 5 wear out and their tooth width becomes narrow, for example, the crescent-shaped seal member 1 causes the pressure plates 2 and 3 to follow suit. Can not.
この点を解決するために、当該プレツシヤープ
レート２，３に通し孔を形成し、この通し孔に三
日月形シール部材１を貫通させるとともに、これ
らプレツシヤープレート２，３を軸方向に移動可
能にする構成も従来から知られている。 In order to solve this problem, through holes are formed in the pressure plates 2 and 3, and the crescent-shaped seal member 1 is passed through the through holes, and the pressure plates 2 and 3 are moved in the axial direction. Configurations that enable this are also known from the prior art.
（本発明が解決しようとする問題点）
上記のようにプレツシヤープレート２，３を軸
方向に移動可能にするためには、上記通し孔の寸
法精度を正確にし、この通し孔と三日月形シール
部材１とのすき間を最小に保たなければ、そのす
き間からの漏れが多くなる。したがつて、この場
合には当該通し孔の寸法を正確にしなければなら
ず、それだけ寸法管理が難しくなるという問題が
あつた。(Problems to be Solved by the Invention) In order to make the pressure plates 2 and 3 movable in the axial direction as described above, the dimensional accuracy of the through holes must be made accurate, and the through holes must be shaped like a crescent. If the gap with the sealing member 1 is not kept to a minimum, leakage from the gap will increase. Therefore, in this case, the dimensions of the through hole must be made accurate, which poses the problem of making dimension control that much more difficult.
一方、通し孔の寸法を正確にし、三日月形シー
ル部材１とのすき間を最小にすると、当該ポンプ
又はモータの組み付け時に、この三日月形シール
部材１を通し孔に貫通させにくくなるとう問題も
あつた。 On the other hand, if the dimensions of the through hole were made accurate and the gap with the crescent seal member 1 was minimized, there was a problem in that it became difficult to penetrate the crescent seal member 1 into the through hole when assembling the pump or motor. .
この発明の目的は、プレツシヤープレートの組
み付けを簡単にするとともに、通し孔と三日月形
シール部材との間からの漏れも少なくした内接ギ
ヤポンプ又はモータのローデイング機構を提供す
ることである。 SUMMARY OF THE INVENTION An object of the present invention is to provide a loading mechanism for an internal gear pump or motor that simplifies assembly of a pressure plate and reduces leakage between a through hole and a crescent-shaped seal member.
（問題点を解決する手段）
この発明は、インターナルギヤと、それにかみ
合うピニオンと、これらインターナルギヤとピニ
オンとの間の所定位置であつてそれらの歯溝をシ
ールする三日月形シール部材と、インターナルギ
ヤ及びピニオンの側面に設けたプレツシヤープレ
ートとを備えてなり、しかも、前記プレツシヤー
プレートには、三日月形シール部材を貫通させる
通し孔を形成して、プレツシヤープレートを軸方
向に移動可能とするとともに、この三日月形シー
ル部材をケーシングに固定してなる内接ギヤポン
プ又はモータを前提にするものである。(Means for Solving the Problems) The present invention includes an internal gear, a pinion that meshes with the internal gear, a crescent-shaped seal member that is located at a predetermined position between the internal gear and the pinion, and seals a tooth gap between the internal gear and the pinion. The pressure plate is provided with an internal gear and a pressure plate provided on the side surface of the pinion, and a through hole is formed in the pressure plate to allow a crescent-shaped seal member to pass through, so that the pressure plate can be attached to the shaft. The present invention is based on an internal gear pump or motor in which the crescent-shaped seal member is fixed to a casing and is movable in this direction.
そして、上記内接ギヤポンプ又はモータを前提
にしつつ、この発明は、上記通し孔の全長を三日
月形シール部材よりも長くするとともに、その吸
込側端部を先細りにし、その最も細い先端箇所で
三日月形シール部材と通し孔との間に形成される
すき間が最小になる構成にし、ポンプ内の圧力が
上昇し、通し孔端部の圧力バランスがくずれてプ
レツシヤプレートがギヤの回転方向に回転したと
き、前記吸込側端部が三日月形シール部材とのす
き間を小さくした点に特徴を有する。 Based on the above-mentioned internal gear pump or motor, the present invention makes the entire length of the through-hole longer than the crescent-shaped sealing member, and makes the suction side end tapered, so that the narrowest point is shaped like a crescent. The structure minimizes the gap formed between the sealing member and the through hole, and the pressure inside the pump increases, causing the pressure balance at the end of the through hole to collapse and causing the pressure plate to rotate in the direction of rotation of the gear. The present invention is characterized in that the gap between the suction side end and the crescent-shaped seal member is reduced.
（本発明の作用）
この発明は、上記のように構成したので、プレ
ツシヤープレートにローデイング力が作用したと
きには、このプレツシヤープレートが軸方向に移
動する。(Operation of the present invention) Since the present invention is configured as described above, when a loading force is applied to the pressure plate, the pressure plate moves in the axial direction.
また、ポンプ内の圧力が上昇し、通し孔端部の
圧力バランスがくずれてプレツシヤプレートがギ
ヤの回転方向に回転したとき、通し孔の最も細い
部分が三日月形シール部材の端部に接触すること
になる。 Also, when the pressure inside the pump increases and the pressure balance at the end of the through hole is disrupted, causing the pressure plate to rotate in the direction of rotation of the gear, the narrowest part of the through hole will come into contact with the end of the crescent-shaped seal member. I will do it.
（本発明の実施例）
第３，４図に示したポンプはケーシングをカバ
ー１１及びマウンテイングフランジ１２から構成
している。そしてこのカバー１１には、インター
ナルギヤ１３を内装するボア１４を形成するとと
もに、このボア１４内所定個所に三日月形シール
部材１５を削り残している。すなわち三日月形シ
ール部材１５を、カバー１１と一体的に形成して
いる。(Embodiment of the present invention) The pump shown in FIGS. 3 and 4 has a casing composed of a cover 11 and a mounting flange 12. The cover 11 is formed with a bore 14 in which the internal gear 13 is housed, and a crescent-shaped seal member 15 is left uncut at a predetermined location within the bore 14. That is, the crescent-shaped seal member 15 is formed integrally with the cover 11.
またカバー１１及びマウンテイングフランジ１
２のそれぞれには、インターナルギヤ１３にかみ
合うピニオン１６の軸受孔１７，１８を形成して
いる。 Also, cover 11 and mounting flange 1
2 are formed with bearing holes 17 and 18 for a pinion 16 that engages with the internal gear 13, respectively.
一方第５図に示した他の実施例であるポンプ
は、本体１９の両側をカバー２０及びマウンテイ
ングフランジ２１でふさぐとともに、それら両者
間所定個所に三日月形シール部材２２をかけ渡し
ている。 On the other hand, in a pump according to another embodiment shown in FIG. 5, both sides of the main body 19 are covered with a cover 20 and a mounting flange 21, and a crescent-shaped sealing member 22 is stretched between the two at a predetermined location.
そしてこの発明においては、上記いずれのケー
シングであつても、それに用いるプレツシヤープ
レート２３，２４は同一構造となるので、以下に
は第３，４図に示したポンプを基に説明する。 In the present invention, the pressure plates 23 and 24 used in any of the above-mentioned casings have the same structure, so the following explanation will be based on the pump shown in FIGS. 3 and 4.
しかして上記プレツシヤープレート２３は、第
６〜８図に示すように、前記ボア１４にぴつたり
とはまる外径を有するとともに、吐出孔２５、吸
込孔２６及び三日月形シール部材１５を貫通させ
る通し孔２７を形成している。 As shown in FIGS. 6 to 8, the pressure plate 23 has an outer diameter that fits snugly into the bore 14, and allows the discharge hole 25, the suction hole 26, and the crescent-shaped seal member 15 to pass through it. A through hole 27 is formed.
そして、前記ボア１４内にプレツシヤープレー
ト２３、インターナルギヤ１３及びピニオン１６
を順次組込んでマウンテイングフランジ１２でふ
さぐが、プレツシヤープレート２３は、その通し
孔２７に三日月形シール部材１５を貫通させて、
軸方向への移動を可能にしている。したがつてイ
ンターナルギヤ１３及びピニオン１６側面が摩耗
しても、当該プレツシヤープレート２３はそれに
追随することになる。 A pressure plate 23, an internal gear 13 and a pinion 16 are provided in the bore 14.
are sequentially assembled and closed with the mounting flange 12, and the pressure plate 23 has its through hole 27 penetrated by the crescent-shaped sealing member 15.
Allows movement in the axial direction. Therefore, even if the side surfaces of the internal gear 13 and pinion 16 wear out, the pressure plate 23 will follow suit.
ただし上記の場合、通し孔２７を三日月形シー
ル部材１５にぴつたりはまる大きさにすると、当
該プレツシヤープレート２３をボア１４内に組込
む作業が難しくなる。そこで当該通し孔２７を三
日月形シール部材１５の外形より少し大きめに形
成すれば、上記組付け上の難点が解消される。 However, in the above case, if the through hole 27 is sized to fit snugly into the crescent-shaped seal member 15, it becomes difficult to assemble the pressure plate 23 into the bore 14. Therefore, if the through hole 27 is formed to be slightly larger than the outer shape of the crescent-shaped seal member 15, the above-mentioned difficulty in assembly can be solved.
そしてこの場合に、通し孔２７の形状を次のよ
うにすれば、その通し孔と三日月形シール部材１
５との隙間からの漏れも少なくなる。 In this case, if the shape of the through hole 27 is made as follows, the through hole and the crescent-shaped seal member 1
Leakage from the gap with 5 is also reduced.
すなわち第１０図に示すように、通し孔２７の
外径R1は、三日月形シール部材１５の外径R0よ
りわずかに大きくする。 That is, as shown in FIG. 10, the outer diameter R 1 of the through hole 27 is made slightly larger than the outer diameter R 0 of the crescent-shaped seal member 15.
またこの通し孔の内径は中心を異にする２つの
弧からなるもので、その詳細は次のとおりであ
る。 The inner diameter of this through hole consists of two arcs with different centers, and the details are as follows.
つまり、吸込側の内径r1は、三日月形シール部
材１５の内径r0よりわずかに小さくするととも
に、その中心をQ1にしている。この中心Q1は、
前記ピニオンの軸心Qpとインターナルギヤの軸
心Qiとの軸間距離ｅに等しく、かつそれら軸心
Qp，Qiを結ぶ線から微小角θ1だけずれた位置にし
ている。 That is, the inner diameter r 1 on the suction side is made slightly smaller than the inner diameter r 0 of the crescent-shaped seal member 15, and its center is set at Q 1 . This center Q 1 is
Equal to the interaxial distance e between the pinion axis Q p and the internal gear axis Q i , and
The position is shifted by a small angle θ 1 from the line connecting Q p and Q i .
また吐出側の内径r2も前記三日月形シール部材
の内径r0よりわずかに小さく、かつ前記軸心Qp，
Qiを結ぶ線に対して対称な点Q2を中心としてい
る。 Further, the inner diameter r 2 on the discharge side is also slightly smaller than the inner diameter r 0 of the crescent-shaped seal member, and the axis Q p ,
It is centered at a point Q 2 that is symmetrical with respect to the line connecting Q i .
しかも通し孔全体の長さも、三日月形シール部
材より長くしている。 Moreover, the entire length of the through hole is also longer than that of the crescent-shaped seal member.
上記のようにして開けられた通し孔２７は、前
記三日月形シール部材１５よりも大きくなるとと
もに、吸込側においてやや先細りとなる。 The through hole 27 opened as described above is larger than the crescent-shaped sealing member 15 and is slightly tapered on the suction side.
したがつて当該プレツシヤープレート２３を組
付ける際に、通し孔２７に三日月形シール部材１
５を通しやすくなり、前記した難点も解消され
る。 Therefore, when assembling the pressure plate 23, the crescent-shaped seal member 1 is inserted into the through hole 27.
5 becomes easier to pass through, and the above-mentioned difficulties are also solved.
また当該ポンプ内の圧力が上昇すると、通し孔
２７両端の圧力バランスがくずれるので、プレツ
シヤープレート２３はその外径中心Qiを回転中心
として、ギヤの回転方向（第１０図矢印方向）に
回転し、第１０図波線位置に達する。このように
プレツシヤープレート２３が回転すると、前記の
ように先細りにした通し孔の吸込側端部２７ａが
三日月形シール部材１５の吸込側端部１５ａに密
接する。したがつて第１０図に示すＬの範囲で
は、通し孔２７と三日月形シール部材１５とのす
き間がごく狭く保たれ、そのすき間からの漏れが
非常に少なくなる。特にインターナルギヤ１３及
びピニオン１６は、前記したＬの範囲でシールさ
れれば足りるので、前記のような通し孔２７の形
状はきわめて有効である。 Furthermore, when the pressure inside the pump increases, the pressure balance at both ends of the through hole 27 is lost, so the pressure plate 23 rotates around its outer diameter center Q i in the direction of rotation of the gear (in the direction of the arrow in FIG. 10). It rotates and reaches the position shown by the dotted line in Figure 10. When the pressure plate 23 rotates in this manner, the suction side end 27a of the through hole, which is tapered as described above, comes into close contact with the suction side end 15a of the crescent-shaped seal member 15. Therefore, within the range L shown in FIG. 10, the gap between the through hole 27 and the crescent-shaped seal member 15 is kept very narrow, and leakage from the gap is extremely reduced. In particular, since the internal gear 13 and pinion 16 only need to be sealed within the range L described above, the shape of the through hole 27 as described above is extremely effective.
次に前記プレツシヤープレート２３の裏面、す
なわちギヤとは反対側面の構造であるが、それは
第７，８図に示すとおりである。 Next, the structure of the back side of the pressure plate 23, that is, the side opposite to the gear, is as shown in FIGS. 7 and 8.
すなわちこのプレツシヤープレート２３の高圧
エリヤＨ周囲には、第１２図に示すシール部材２
８をはめ込む。また吐出孔２５の周囲には、隔壁
２９を設けるとともに、この隔壁２９の所定個所
に高圧導入切欠部３０を形成している。ただし、
通し孔２７は、その吐出側端部２７ｂが前記した
ように三日月形シール部材１５の吐出側端部１５
ｂから離隔し、高圧油はこの部分から流入するの
で、当該通し孔２７の形状によつては、前記高圧
導入切欠部３０は不要となる。 That is, around the high pressure area H of this pressure plate 23, there is a seal member 2 shown in FIG.
Insert 8. Further, a partition wall 29 is provided around the discharge hole 25, and a high pressure introduction notch 30 is formed at a predetermined location of the partition wall 29. however,
The discharge side end 27b of the through hole 27 is connected to the discharge side end 15 of the crescent-shaped sealing member 15 as described above.
b, and high pressure oil flows in from this portion, so depending on the shape of the through hole 27, the high pressure introduction notch 30 is unnecessary.
さらに前記のように通し孔２７の形状を特定し
たとしても、三日月形シール部材１５との間にわ
ずかなすき間が残るが、本件のようなローデイン
グ機構では、そのわずかなすき間も密閉し、前記
高圧エリヤＨの油が漏れないようにしなければな
らない。 Furthermore, even if the shape of the through hole 27 is specified as described above, a slight gap remains between it and the crescent-shaped sealing member 15, but in the loading mechanism of the present invention, even that slight gap is sealed, and the high pressure Elijah H's oil must be kept from leaking.
そのために、前記高圧エリヤＨ内において、三
日月形シール部材１５周囲にシール材３１，３２
を組込んでいる。 For this purpose, sealing materials 31 and 32 are placed around the crescent-shaped sealing member 15 in the high-pressure area H.
It incorporates.
そして上記シール材３１は、第１１図に示すよ
うに、そのシール材３１の吸込側端部３１ａの形
状を、三日月形シール部材の吸込側端部１５ａに
一致させるとともに、当該シール部材３１の孔幅
を、三日月形シール部材の幅よりもわずかに狭く
なるようにし、かつ吐出側端部３１ｂは切り離し
ている。 As shown in FIG. 11, the sealing material 31 has a suction side end 31a that matches the shape of the suction side end 15a of the crescent-shaped sealing member, and a hole in the sealing member 31. The width is made slightly narrower than the width of the crescent-shaped seal member, and the discharge side end 31b is separated.
しかしてこれらのシール部材３１，３２を組み
込むことによつて、高圧エリヤＨは完全にシール
されることになる。 By incorporating these seal members 31 and 32, the high pressure area H is completely sealed.
（本発明の効果）
この発明の内接ギヤポンプ又はモータのローデ
イング機構は、通し孔の最も細い部分の大きさを
三日月形シール部材の端部に合わせれば、他の部
分は当該三日月形シール部材よりもやや大きめに
形成できるので、その寸法管理が楽になるととも
に、三日月形シール部材を通し孔に貫通させる作
業も簡単になる。(Effects of the present invention) In the internal gear pump or motor loading mechanism of the present invention, if the size of the narrowest part of the through hole is adjusted to the end of the crescent-shaped seal member, the other parts are smaller than the crescent-shaped seal member. Since it can be formed into a slightly larger size, it is easier to manage its dimensions, and the work of penetrating the crescent-shaped seal member into the through hole is also easier.
また、上記のように通し孔を三日月形シール部
材よりも大きめに形成しても、それら両者間のす
き間が小さくなるので、そのすき間から圧油が漏
れたりせず、当該ポンプ又はモータの効率を低下
させるようなこともない。 In addition, even if the through hole is made larger than the crescent-shaped seal member as described above, the gap between the two will be small, so pressure oil will not leak from the gap and the efficiency of the pump or motor will be improved. There's nothing to make it worse.
図面第１，２図は従来の機構を示すケーシング
を省略した内部構造図とその−線断面図、第
３〜第１２図はこの発明の実施例を示すもので、
第３図は第４図−線断面図、第４図は第３図
−線断面図、第５図は他の実施例の第４図に
対応する図、第６図はプレツシヤープレートの一
側面図、第７図は同じく他側面図、第８図は第７
図−線断面図、第９図は三日月形シール部材
部分の拡大断面図、第１０図は三日月形シール部
材とプレツシヤープレートの通し孔との関係を示
す説明図、第１１，１２図はシール部材の正面図
である。
１３……インターナルギヤ、１５，２２……三
日月形シール部材、１６……ピニオン、２３，２
４……プレツシヤープレート、２７……通し孔、
２７ａ……吸込側端部。
Figures 1 and 2 are internal structural diagrams with the casing omitted, showing a conventional mechanism, and cross-sectional views thereof taken along the line 1, and Figures 3 to 12 show embodiments of the present invention.
3 is a cross-sectional view taken along the line shown in FIG. 4, FIG. 4 is a cross-sectional view taken along the line taken from FIG. 3, FIG. 5 is a view corresponding to FIG. 4 of another embodiment, and FIG. One side view, Figure 7 is the other side view, Figure 8 is the 7th side view.
Figure-9 is an enlarged sectional view of the crescent-shaped seal member, Figure 10 is an explanatory diagram showing the relationship between the crescent-shaped seal member and the through hole of the pressure plate, and Figures 11 and 12 are It is a front view of a sealing member. 13... Internal gear, 15, 22... Crescent seal member, 16... Pinion, 23, 2
4...Pressure plate, 27...Through hole,
27a... Suction side end.
Claims (1)
ンと、これらインターナルギヤとピニオンとの間
の所定位置であつてそれらの歯溝をシールする三
日月形シール部材と、インターナルギヤ及びピニ
オンの側面に設けたプレツシヤープレートとを備
えてなり、しかも、前記プレツシヤープレートに
は、三日月形シール部材を貫通させる通し孔を形
成して、プレツシヤープレートを軸方向に移動可
能にするとともに、この三日月形シール部材をケ
ーシングに固定してなる内接ギヤポンプ又はモー
タにおいて、上記通し孔の全長を三日月形シール
部材よりも長くするとともに、その吸込側端部を
先細りにし、その最も細い先端箇所で三日月形シ
ール部材と通し孔との間に形成されるすき間が最
小になる構成にし、ポンプ内の圧力が上昇し、通
し孔端部の圧力バランスがくずれてプレシヤプレ
ートがギヤの回転方向に回転したとき、前記吸込
側端部が三日月形シール部材とのすき間を小さく
するようにした内接ギヤポンプ又はモータのロー
デイング機構。1 An internal gear, a pinion that meshes with the internal gear, a crescent-shaped seal member that is located at a predetermined position between the internal gear and the pinion and seals the tooth spaces between them, and a plate provided on the sides of the internal gear and the pinion. and a pressure plate, furthermore, the pressure plate is formed with a through hole through which the crescent-shaped sealing member passes through, so that the pressure plate can be moved in the axial direction, and the crescent-shaped In an internal gear pump or motor in which a sealing member is fixed to a casing, the overall length of the through hole is longer than that of the crescent-shaped sealing member, and the suction side end thereof is tapered, so that the crescent-shaped seal is formed at the narrowest point. The structure is such that the gap formed between the member and the through hole is minimized, and when the pressure inside the pump increases and the pressure balance at the end of the through hole is lost and the pressure plate rotates in the direction of rotation of the gear, A loading mechanism for an internal gear pump or motor, wherein a gap between the suction side end and a crescent-shaped seal member is reduced.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16716180A JPS5791391A (en) | 1980-11-27 | 1980-11-27 | Loading mechanism for inscribed gear pump or motor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16716180A JPS5791391A (en) | 1980-11-27 | 1980-11-27 | Loading mechanism for inscribed gear pump or motor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5791391A JPS5791391A (en) | 1982-06-07 |
| JPS6344954B2 true JPS6344954B2 (en) | 1988-09-07 |
Family
ID=15844544
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP16716180A Granted JPS5791391A (en) | 1980-11-27 | 1980-11-27 | Loading mechanism for inscribed gear pump or motor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5791391A (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4550645A (en) * | 1984-04-27 | 1985-11-05 | Sundstrand Corporation | Thin valve plate for a hydraulic unit |
| DE102010063313A1 (en) * | 2010-12-17 | 2012-06-21 | Robert Bosch Gmbh | Axial disc for a gear pump and gear pump with such an axial disc |
| DE102010064130A1 (en) * | 2010-12-23 | 2012-06-28 | Robert Bosch Gmbh | Axial disc and gear pump with axial disc |
| JP6485305B2 (en) * | 2015-09-24 | 2019-03-20 | アイシン精機株式会社 | Variable oil pump |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS496725U (en) * | 1972-04-20 | 1974-01-21 | ||
| JPS54152209A (en) * | 1978-05-20 | 1979-11-30 | Tokico Ltd | Gear pump |
-
1980
- 1980-11-27 JP JP16716180A patent/JPS5791391A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5791391A (en) | 1982-06-07 |
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