JPS6112119B2 - - Google Patents
Info
- Publication number
- JPS6112119B2 JPS6112119B2 JP10198875A JP10198875A JPS6112119B2 JP S6112119 B2 JPS6112119 B2 JP S6112119B2 JP 10198875 A JP10198875 A JP 10198875A JP 10198875 A JP10198875 A JP 10198875A JP S6112119 B2 JPS6112119 B2 JP S6112119B2
- Authority
- JP
- Japan
- Prior art keywords
- cover
- pressure
- pinions
- hollow body
- end 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
- 239000012530 fluid Substances 0.000 claims description 19
- 230000005540 biological transmission Effects 0.000 claims description 7
- 230000013011 mating Effects 0.000 claims description 2
- 238000003754 machining Methods 0.000 description 5
- 238000004519 manufacturing process Methods 0.000 description 3
- 238000007789 sealing Methods 0.000 description 3
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000002441 reversible effect Effects 0.000 description 2
- 238000005266 casting Methods 0.000 description 1
- 229920001971 elastomer Polymers 0.000 description 1
- 239000000806 elastomer Substances 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000012858 resilient material Substances 0.000 description 1
Landscapes
- Rotary Pumps (AREA)
- Hydraulic Motors (AREA)
Description
【発明の詳細な説明】
〔発明の技術分野〕
本発明はポンプとしても流体圧モータとしても
用いられ得るギヤを有する可逆転流体圧機に係
り、特に相噛み合う二つのピニオン（ギヤ）の軸
を保持する為の二つの軸受端板（側面受体）を有
し、上記端板が上記ピニオンと接触する側に及ぼ
される作動圧に対抗する流体圧が、上記端板の他
側に与えられる事によつて、上記端板が上記ピニ
オンの両側に接触した状態に保たれる様に構成さ
れた流体圧機に関する。[Detailed Description of the Invention] [Technical Field of the Invention] The present invention relates to a reversible fluid pressure machine having gears that can be used both as a pump and as a fluid pressure motor, and particularly to a reversible fluid pressure machine that holds the shafts of two pinions (gears) that mesh with each other. The bearing has two bearing end plates (side receivers) for the purpose of applying fluid pressure to the other side of the end plate to counteract the operating pressure applied to the side where the end plate contacts the pinion. Therefore, the present invention relates to a fluid pressure machine configured such that the end plate is kept in contact with both sides of the pinion.
この様な流体圧機に於ては、ピニオン及び端板
は両側をカバーにより閉じられた中空本体中に置
かれ、従来上記カバーの端板に面する面にはガス
ケツトの位置ぎめ及び保持の為の種々な溝及び室
（凹部）が作られ、上記溝及び室はそれぞれ、端
板中にあけられた伝達通路を経てピニオンがその
中で回転する作動室の当該の部分と連通する事に
よつて流体圧が発生される隔絶された区域を仕切
るようにされている。
In such a hydraulic machine, the pinion and the end plate are placed in a hollow body closed on both sides by covers, and the surface of the cover facing the end plate conventionally has a structure for positioning and retaining the gasket. Various grooves and chambers (recesses) are made, each said groove and chamber being in communication with the corresponding part of the working chamber in which the pinion rotates through a transmission passage bored in the end plate. It is adapted to demarcate an isolated area in which fluid pressure is generated.
これらの既知の構造はカバーにデリケートな加
工を施す事を要し、上記加工は同じ型の流体圧機
（ポンプまたはモータ）に対しても極めて異つて
くる事が屡々であるが、これは流体圧機を、それ
が装置の一部を形成する全体装置中に適用する際
の要件を満たす為に必要とされるのである。 These known structures require delicate machining of the cover, which is often quite different for the same type of hydraulic machine (pump or motor); is required to meet the requirements of its application in the overall device of which it forms part.
本発明はカバーの機械加工を著るしく簡単化
し、よつて製作を合理化する事を可能にし、しか
も流体圧機の軸受端板の完全な圧力均衡を得る事
を可能にしたギヤを有する流体圧機を提供するこ
とを目的とする。
The present invention significantly simplifies the machining of the cover, thus making it possible to rationalize the production, and also to provide a hydraulic machine with a gear, which makes it possible to obtain a perfect pressure balance of the bearing end plates of the hydraulic machine. The purpose is to provide.
本発明は両方向に回転可能なギヤを有する流体
圧機、例えばポンプあるいはモータであり、両端
開口した中空本体と、中空本体内に配設された端
板に形成されている軸受により支持された軸に取
付けられた２つの相噛み合うピニオンを有し、中
空本体はその両側を中空本体に固定されたカバー
により閉じられ、端板は一方側がピニオンに隣接
し他方側がカバーに面するよう配置されるととも
に、カバーの側面にガスケツトを圧接保持する手
段を備え、さらにガスケツトは端板と隣接するカ
バーとの間にそれぞれ３種の区域を区切り、この
３種の区域の最初のものは作動流体の入口および
出口ダクトとそれぞれ連通する第１および第２の
外側側方区域であり、ポンプあるいはモータが通
常に作動している際、第１の側方区域は低圧下に
あり、第２の側方区域は高圧下にあり、前記３種
の区域の次のものは、圧力伝達通路を経て前記２
つのピニオンの噛み合い側と直径方向に反対側に
あるピニオンの各々の歯間間隙と連通する少なく
とも２つの端部区域であり、前記３種の区域の最
後のものは、側方区域と端部区域により囲まれ、
圧力伝達通路を経てピニオンの噛み合い区域と連
通する中心区域であることを特徴としている。
The present invention relates to a fluid pressure machine, such as a pump or a motor, which has a gear that can rotate in both directions, and has a hollow body that is open at both ends, and a shaft that is supported by a bearing formed in an end plate disposed inside the hollow body. having two mating pinions mounted thereon, the hollow body being closed on both sides by a cover secured to the hollow body, the end plate being arranged with one side adjacent the pinion and the other side facing the cover; Means is provided for holding a gasket against the side of the cover, the gasket further defining three zones between the end plate and the adjacent cover, the first of which is a working fluid inlet and an outlet. first and second outer lateral sections respectively communicating with the duct, the first lateral section being under low pressure and the second lateral section being under high pressure during normal operation of the pump or motor; The next one of the three zones is connected to the second zone through pressure transmission passages.
at least two end sections communicating with the interdental gaps of each of the pinions diametrically opposite the meshing sides of the two pinions, the last of said three sections being a lateral section and an end section; surrounded by
It is characterized by a central area communicating with the meshing area of the pinion via a pressure transmission channel.
本発明によれば、端板を特別な機械加工するこ
となく製造することができ、製造コストの大幅な
低下を図ることができる。また、流体圧機を両方
向に回転可能なポンプあるいはモータとして使用
することができ、この場合において同一の端板を
なんら改造を加えずに用いることが可能である。 According to the present invention, the end plate can be manufactured without special machining, and manufacturing costs can be significantly reduced. It is also possible to use the hydraulic machine as a bidirectionally rotatable pump or motor, in which case the same end plate can be used without any modification.
さらに本発明によれば、カバーの製造が容易で
あり、機械加工を施す部分を最小限とすることが
可能となる。 Further, according to the present invention, the cover is easy to manufacture and the number of parts to be machined can be minimized.
以下添付図面に従い本発明の実施例について説
明する。
Embodiments of the present invention will be described below with reference to the accompanying drawings.
流体圧機は本体（またはケーシング）１を有
し、この本体１は内部に相交わる二つのほぼ円筒
形の室２及び２ａを形成し、該室２，２ａは中間
室３を経て相連結され、この中間室３もまたほぼ
円筒形であつて、流体の入口または出口として用
いられるダクト４，５に連通する。室２，２ａ中
にはそれぞれピニオン６及び７が置かれ、このピ
ニオン６と７とはそれらの中間室３中に置かれた
部分に於て相係合する。 The hydraulic machine has a main body (or casing) 1, which internally forms two intersecting, substantially cylindrical chambers 2 and 2a, which are connected to each other via an intermediate chamber 3, This intermediate chamber 3 is also approximately cylindrical and communicates with ducts 4, 5 which serve as fluid inlets or outlets. Pinions 6 and 7 are placed in the chambers 2 and 2a, respectively, and the pinions 6 and 7 engage with each other in their portions placed in the intermediate chamber 3.
ピニオン６，７の両側面は平らであつて、それ
ぞれ端板８，９の側壁に接触し、この端板８，９
はほぼ眼鏡形であり、軸受体を構成し、中間室３
とともにダクト４，５に連通する室１０，１１を
形成する。 Both sides of the pinions 6 and 7 are flat and contact the side walls of the end plates 8 and 9, respectively.
is almost spectacle-shaped, constitutes a bearing body, and has an intermediate chamber 3.
Together, chambers 10 and 11 communicating with the ducts 4 and 5 are formed.
端板８，９は軸１２及び１３の為の軸受体を構
成し、軸１２，１３はカバー１４及び１５により
本体１内に保たれ、カバー１４，１５はスタツド
１６により中心位置を合わされ、ねじ１７等によ
り本体に固定される。本体１とカバー１４，１５
との間にはシールガスケツト１８が設けられ、こ
のガスケツト１８は例えばカバー１４，１５の溝
中に置かれるが、所望によつては上記溝を本体１
の両端中に作る事も出来る。 The end plates 8, 9 constitute bearing bodies for the shafts 12 and 13, which are kept in the body 1 by covers 14 and 15, which are centered by studs 16 and screwed together. It is fixed to the main body by 17 etc. Main body 1 and covers 14, 15
A sealing gasket 18 is provided between the two parts, and this gasket 18 is placed, for example, in a groove in the covers 14, 15, but if desired, the groove can be inserted into the main body 1.
It can also be made inside both ends.
カバー１４，１５は、軸１２及び１３の両端に
ある室（凹部）１９を形成し、室１９は一方に於
て端板８，９中に作られた潤滑溝２０と連通し、
他方に於てピニオン６，７及び軸１２，１３の周
りの周辺溝２２中に至る通路２１と連通する。こ
の様にして軸受を形成する端板８，９の部分及び
上述した軸の部分の潤滑を保証する為の流体の閉
鎖回路による循環路が与えられる。 The covers 14, 15 form chambers (recesses) 19 at both ends of the shafts 12 and 13, the chambers 19 communicating on one side with lubricating grooves 20 made in the end plates 8, 9;
On the other hand, it communicates with a passage 21 leading into a peripheral groove 22 around the pinions 6, 7 and the shafts 12, 13. In this way a closed circuit circulation of fluid is provided to ensure lubrication of the parts of the end plates 8, 9 forming the bearing and of the shaft mentioned above.
端板８，９はわずかな摩擦を与えられた状態で
本体１内に配置され、この端板８，９は相互に同
形であり、カバー１４，１５に面する側面上に二
組の溝を有し、その第一組は二つの溝２３，２３
ａから成り、この溝２３，２３ａはほぼギリシヤ
文字ωの形をしており、溝２３，２３ａの両端２
３１は図示の如く、ほぼ軸１２及び１３の長手軸
心上に中心を有する半径に沿つて延びる様に連続
的に曲げられている。 The end plates 8, 9 are arranged in the body 1 with slight friction, the end plates 8, 9 are mutually identical and have two sets of grooves on the side facing the covers 14, 15. The first set has two grooves 23, 23.
a, and these grooves 23, 23a are approximately in the shape of the Greek letter ω, and both ends 2 of the grooves 23, 23a are
31 is continuously bent so as to extend along a radius centered approximately on the longitudinal axes of the axes 12 and 13, as shown.
第二組の溝は端板８，９の両端（図に於て上下
端）近くに作られた二つの溝２４，２４ａから成
り、この溝２４，２４ａはそれぞれ軸１２及び１
３と同心の部分及び軸１２及び１３の長手軸心上
に中心を有する半径に沿つて延びる端部２４１を
有する。 The second set of grooves consists of two grooves 24, 24a made near both ends (upper and lower ends in the figure) of the end plates 8, 9, and these grooves 24, 24a are formed near the shafts 12 and 1, respectively.
3 and an end 24 1 extending along a radius centered on the longitudinal axes of the axes 12 and 13 .
二組の溝２３，２３ａ及び２４，２４ａはそれ
ぞれガスケツト２５，２５ａ及び２６，２６ａを
入れる様に作られ、上記ガスケツトの各端は本体
１の内壁に衝接し、上記ガスケツト２５，２５ａ
及び２６，２６ａは如何なる適当な材料製でも可
であり、また予成形されたものでも、されていな
いものでも可であるが、エラストマーのごとき比
較的可撓な弾力性のある材料で作られる事が望ま
しい。 Two sets of grooves 23, 23a and 24, 24a are made to receive gaskets 25, 25a and 26, 26a, respectively, each end of said gasket abuts against the inner wall of body 1, and said gaskets 25, 25a
and 26, 26a may be made of any suitable material and may be preformed or unformed, but may be made of a relatively flexible, resilient material such as an elastomer. is desirable.
第２図は上記二組のガスケツトが側方区域２
７，２７ａ、端部区域２８，２８ａ及び中心区域
３０を仕切る有様を示す。側方区域２７，２７ａ
は、それぞれ、入口及び出口室１０，１１と連通
し、上記室１０，１１中には入口及び出口ダクト
４，５中に存在する流体圧に等しい流体圧が存在
する。次に端部区域２８，２８ａはそれぞれ圧力
伝達通路２９，２９ａを経て、ほぼピニオン６と
７が噛み合う部分の反対側にある両ピニオンの歯
の間の歯間々隙と連通する。軸１２，１３の間お
よびこれらを取囲む中心区域３０は通路２１を介
して室１９と連通している。中心区域３０は圧力
区域であり、通常はドレン通路４０を経て、圧力
流体貯槽に直接連結されている。 Figure 2 shows that the above two sets of gaskets are located in the side area 2.
7, 27a, the end areas 28, 28a and the central area 30 are shown partitioned. Lateral areas 27, 27a
communicate with inlet and outlet chambers 10, 11, respectively, in which a fluid pressure exists which is equal to the fluid pressure present in the inlet and outlet ducts 4, 5. The end sections 28, 28a then communicate via pressure transmission passages 29, 29a, respectively, with the tooth gap between the teeth of the two pinions, approximately opposite the meshing portion of the pinions 6 and 7. A central area 30 between and surrounding the shafts 12, 13 communicates with the chamber 19 via a passage 21. The central area 30 is a pressure area and is connected directly to a pressure fluid reservoir, usually via a drain passage 40.
上述の構造により端板８，９の背面（カバー１
５，１４に面する側）に及ぼされる補償圧（釣合
い圧）は如何なる点に於ても、端板８，９の前面
（即ち、ピニオン６，７と接触する側）に及ぼさ
れる圧力と実質的に同じにされる。実際にこの流
体圧機がポンプとして作動し、ピニオンが第２図
中の矢印の方向に駆動されている場合を考える
と、この時にはダクト５（即ちこの時の入口ダク
ト）中には低い吸入圧力があり、ダクト４（即ち
この時の出口ダクト）中には高圧がある。従つて
この時には区域２７中には低圧が供給され、区域
２７ａ中には高圧が供給され、さらに中心区域３
０中にも低圧が供給され、区域２８，２８ａ中に
は中間圧力が供給される。ピニオンが矢印と反対
の方向に駆動されれば、ダクト４が入口ダクトと
なり、区域２７ａ中は低圧となり、区域２７中は
高圧となるが、常に中心区域３０中は低圧であ
り、区域２８，２８ａ中は中間圧である。 Due to the above structure, the back surface of the end plates 8 and 9 (cover 1
At any point, the compensating pressure (balancing pressure) exerted on the end plates 8, 9 (the side facing the pinions 6, 7) is substantially equal to the pressure exerted on the front surface of the end plates 8, 9 (i.e. the side in contact with the pinions 6, 7). be made the same. Considering the case where this fluid pressure machine actually operates as a pump and the pinion is driven in the direction of the arrow in Fig. 2, at this time there is a low suction pressure in the duct 5 (i.e., the inlet duct at this time). , and there is high pressure in the duct 4 (ie the outlet duct at this time). Therefore, at this time, a low pressure is supplied in the zone 27, a high pressure is supplied in the zone 27a, and also a central zone 3.
0 is also supplied with low pressure and in zones 28, 28a with intermediate pressure. If the pinion is driven in the direction opposite to the arrow, duct 4 becomes the inlet duct, with low pressure in zone 27a and high pressure in zone 27, but always low pressure in central zone 30 and zones 28, 28a. Inside is medium pressure.
この流体圧機がモータとして作動する時にも作
動回路及び補償区域（圧力釣合い区域）の両者中
の圧力関係に於て上述と同様な状態が出現し、よ
つて流体圧機は何等特別の手段を要せずに常に完
全に釣合わされる。 When this fluid pressure machine operates as a motor, a similar situation as described above occurs in the pressure relationship in both the operating circuit and the compensation area (pressure balance area), so the fluid pressure machine does not require any special measures. always perfectly balanced.
端板８，９の背面と前面とにおける圧力が釣合
わされることにより、端板８，９が背面側に移動
して、端板８，９とピニオン６，７との間に大き
な隙間を生ずることはなく、端板８，９の前面か
らの流体の漏洩が防止される。 By balancing the pressures on the back and front surfaces of the end plates 8, 9, the end plates 8, 9 move toward the back side, creating a large gap between the end plates 8, 9 and the pinions 6, 7. This prevents fluid from leaking from the front surfaces of the end plates 8 and 9.
ここに特記するにガスケツトに及ぼされる高
圧、または中間圧、例えばガスケツト２６，２６
ａに及ぼされる高い圧力は、これらのガスケツト
の曲つた部分を、軸１２または１３に最も近い溝
の壁に近づける様に働き、即ちガスケツトを平ら
にしようとする方向に押し、よつて端２４１が本
体１の内壁に押付けられて充分なシール性を与え
られる。この事は他の二つのガスケツト２５，２
５ａの何れに於ても同様である。 It is particularly noted here that high or intermediate pressures exerted on the gaskets, e.g. gaskets 26, 26
The high pressure exerted on a serves to bring the curved portions of these gaskets closer to the wall of the groove nearest the axis 12 or 13, i.e. to push the gaskets in a direction that tends to flatten them, thus forcing the ends 24 1 is pressed against the inner wall of the main body 1 to provide sufficient sealing performance. This also applies to the other two gaskets 25, 2.
The same applies to any of 5a.
第３及び第４図に示す実施例に於ても構造は第
１及び２図のものと殆んど同様であるが、この場
合には二組のガスケツトの端部２３１と２４１と
の間に摺動ピン３１が設けられ、このピン３１は
前後のカバーの孔３２（第４図）中で案内され、
上記孔３２は上記カバーの表面に開口する通路３
３と連通する。従つて区域２７または２７ａ中に
於て端板とカバーとの間に存在する流体圧は通路
３３を経てピン３１の一端に加えられ、このピン
３１は、ピストンとして働いて、ガスケツト２
３，２４の端部２３１との間に押込まれ、端部２
３１と２４１とを押し広げ、両端部を中空本体の
内壁により確実に圧接し、これによりガスケツト
のシール性の向上を図るとともに、例えば区域２
７と区域３０との間に存在する圧力差により生じ
得る漏洩を防ぐ。 The structure of the embodiment shown in FIGS . 3 and 4 is almost the same as that of FIGS. A sliding pin 31 is provided therebetween, and this pin 31 is guided in a hole 32 (FIG. 4) in the front and rear covers;
The hole 32 is a passage 3 that opens on the surface of the cover.
Connects with 3. The fluid pressure existing between the end plate and the cover in the area 27 or 27a is therefore applied via the passage 33 to one end of the pin 31, which acts as a piston and presses the gasket 2.
3 and 24 , and the end 2
3 1 and 24 1 are pushed apart to ensure that both ends are pressed into contact with the inner wall of the hollow body, thereby improving the sealing performance of the gasket and, for example, in area 2.
7 and the area 30 to prevent leakage that may occur due to the pressure difference existing between the area 7 and the area 30.
以上述べた構造に於ては端板８，９は鋳造によ
り容易に作られ得、各溝は特別な機械加工を要せ
ずして作られ得、機械加工を要するのは本体１の
内壁に接触すべき端板の周面のみである。またカ
バー１４，１５はこの流体圧機を他の機器と組合
わせて取付け得る様に如何なる適当な形にも作ら
れ得、さらにカバー壁に補償（圧力釣合い）の為
の特殊な加工を施す事を何等要しない。実際に於
て必要である事は端板及び本体に面するカバーの
面が平滑な面である事を要するのみである。 In the structure described above, the end plates 8, 9 can be easily made by casting, and the grooves can be made without special machining, and the only machining required is on the inner wall of the main body 1. Only the peripheral surface of the end plate should be in contact. Moreover, the covers 14 and 15 can be made in any suitable shape so that the hydraulic machine can be mounted in combination with other equipment, and the cover walls can be specially processed for compensation (pressure balance). I don't need anything. In practice, all that is required is that the end plates and the surfaces of the cover facing the body be smooth.
本発明は上述の二実施例に限定されるものでは
無く、その主旨から脱する事無く種々の改変が行
われ得る。特に端板の軸受部分に設けられたガス
ケツトは溝中に入れる代りにリブにより取付ける
ことができ、これにより端板をさらに軽くする事
が出来る。 The present invention is not limited to the two embodiments described above, and various modifications may be made without departing from the spirit thereof. In particular, the gasket provided in the bearing portion of the end plate can be attached by a rib instead of being placed in a groove, thereby making the end plate even lighter.
第１図は本発明による流体圧機の長手方向断面
図、第２図は第１図の−線方向に見た拡大断
面図、第３図は本発明の第二実施例を示す、第２
図と同様な断面図、第４図は第３図の−線に
よる部分断面図である。
１…中空本体、６，７…ピニオン、８，９…端
板、１２，１３…軸、１４，１５…カバー、２
５，２５ａ，２６，２６ａ…ガスケツト、２７，
２７ａ…側方区域、２８，２８ａ…端部区域、３
０…中心区域。
FIG. 1 is a longitudinal sectional view of a hydraulic machine according to the present invention, FIG. 2 is an enlarged sectional view taken in the - line direction of FIG. 1, and FIG. 3 is a second embodiment of the present invention.
FIG. 4 is a partial sectional view taken along the - line in FIG. 3; 1... Hollow body, 6, 7... Pinion, 8, 9... End plate, 12, 13... Shaft, 14, 15... Cover, 2
5, 25a, 26, 26a...gasket, 27,
27a... Side section, 28, 28a... End section, 3
0...Central area.
Claims (1)
された端板に形成されている軸受により支持され
た軸に取付けられた２つの相噛み合うピニオンと
を有し、前記中空本体はその両端を前記中空本体
に固定されたカバーにより閉じられ、前記端板は
一方の側が前記ピニオンに隣接し他方の側が前記
カバーに面するよう配置されるとともに、それぞ
れ前記ピニオンのほぼ半径方向に向けて中空本体
の内壁まで延びる折り曲げ端部の形成された、前
記カバーの側面にガスケツトを圧接保持するそれ
ぞれほぼω字形およびほぼ円弧状をした２組の溝
を備え、前記カバーには、底部付近にカバーの側
面に開口する圧力伝達通路が連通されている穴が
穿設され、この穴中に、ほぼ半径方向に向けて中
空本体の内壁の内壁まで延びる前記２組のガスケ
ツトの折り曲げ端部の間に向けて配設されたピン
が摺動可能に挿入されており、さらに前記ガスケ
ツトは前記端板と隣接するカバーとの間にそれぞ
れ３種の区域を区切り、前記３種の区域の最初の
ものは作動流体の入口および出口ダクトとそれぞ
れ連通する第１および第２の外側側方区域であ
り、ポンプあるいはモータが通常に作動している
際、第１の側方区域は低圧下にあり、第２の側方
区域は高圧下にあり、前記３種の区域の次のもの
は、圧力伝達通路を経て前記２つのピニオンの噛
み合い側と直径方向に反対側にあるピニオンの
各々の歯間間隙と連通する少なくとも２つの端部
区域であり、前記３種の区域の最後のものは、前
記側方区域と端部区域により囲まれ、圧力伝達通
路を経て前記ピニオンの噛み合い区域と連通する
中心区域であることを特徴とする両方向に回転可
能なギヤを有する流体圧機。1 It has a hollow body with both ends open, and two mating pinions attached to shafts supported by bearings formed in end plates disposed inside the hollow body, and the hollow body has both ends open. The end plate is closed by a cover fixed to the hollow body, and the end plate is arranged such that one side is adjacent to the pinion and the other side faces the cover, and each end plate is oriented generally in a radial direction of the pinion. The cover is provided with two sets of substantially omega-shaped and substantially arc-shaped grooves, respectively, for holding a gasket in pressure contact with the side surface of the cover, each having a bent end extending to the inner wall of the cover, and the cover has a side surface of the cover near the bottom. A hole is drilled into the hole through which a pressure transmission passageway opening into is communicated, extending generally radially to the inner wall of the hollow body between the folded ends of said two sets of gaskets. A disposed pin is slidably inserted therein, and the gasket further defines three zones between the end plate and an adjacent cover, the first of the three zones being injected with a working fluid. first and second outer side sections that communicate with inlet and outlet ducts, respectively, of the pump or motor, the first side section being under low pressure and the second side section being under low pressure during normal operation of the pump or motor; one of the two pinions is under high pressure, and the next of the three zones is in communication with the interdental gap of each of the two pinions diametrically opposite the meshing side of the two pinions via a pressure transmission passage. two end regions, the last of said three regions being a central region surrounded by said lateral regions and end regions and communicating with said meshing region of said pinion via a pressure transmission passage; A hydraulic machine with a gear that can rotate in both directions.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10198875A JPS5226605A (en) | 1975-08-22 | 1975-08-22 | Hydraulic gear pumps |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10198875A JPS5226605A (en) | 1975-08-22 | 1975-08-22 | Hydraulic gear pumps |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5226605A JPS5226605A (en) | 1977-02-28 |
| JPS6112119B2 true JPS6112119B2 (en) | 1986-04-07 |
Family
ID=14315208
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10198875A Granted JPS5226605A (en) | 1975-08-22 | 1975-08-22 | Hydraulic gear pumps |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5226605A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5572681A (en) * | 1978-11-29 | 1980-05-31 | Nippon Air Brake Co Ltd | Gear pump/motor |
-
1975
- 1975-08-22 JP JP10198875A patent/JPS5226605A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5226605A (en) | 1977-02-28 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US2809592A (en) | Rotary pump or motor | |
| US3528756A (en) | Pressure loaded pump | |
| US2676548A (en) | Pump | |
| US3833317A (en) | Rotary gear motor/pump having hydrostatic bearing means | |
| US2321609A (en) | Rotary pump | |
| KR940000218B1 (en) | Gear pump | |
| US2571377A (en) | Rotary displacement pump | |
| US1673259A (en) | Pump | |
| US5378130A (en) | Tandem type gear pump having an integral inner middle partition wall | |
| US3473476A (en) | Gear pump seal | |
| US2923248A (en) | Pump | |
| US3029739A (en) | Gear pump or motor with radial pressure balancing means | |
| US3073251A (en) | Hydraulic machines | |
| US3416459A (en) | Rotary pump or motor | |
| US4177025A (en) | High-pressure rotary fluid-displacing machine | |
| US3043230A (en) | High pressure gear pump | |
| US4337018A (en) | Rotary impeller pump or motor with counterbalancing chamber in thrust plate bearing counterbore | |
| US2864315A (en) | Liquid pump | |
| KR860000960B1 (en) | Apparatus for an hydrostatic compensation of hydraulic pumps and motors of gear type | |
| US5240393A (en) | Hydraulic machine of the gear type | |
| JPS6112119B2 (en) | ||
| EP0018216B1 (en) | Reversible gear pump or motor and diverter plates therefor | |
| US3173374A (en) | Bearing for pumps and motors | |
| US2808007A (en) | Gear pump or motor | |
| JPH10122160A (en) | Gear pump |