JPS58128477A - Hydraulic rotary machine - Google Patents
Hydraulic rotary machineInfo
- Publication number
- JPS58128477A JPS58128477A JP57009784A JP978482A JPS58128477A JP S58128477 A JPS58128477 A JP S58128477A JP 57009784 A JP57009784 A JP 57009784A JP 978482 A JP978482 A JP 978482A JP S58128477 A JPS58128477 A JP S58128477A
- Authority
- JP
- Japan
- Prior art keywords
- cylinder
- auxiliary
- piston
- diameter
- 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2064—Housings
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Hydraulic Motors (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は斜板溢、斜粕屋等の液圧ポンプやモータとして
使用される液圧回転機に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic rotary machine used as a hydraulic pump or motor for a swash plate overflow, a slant lees house, etc.
第１図および第２図に従来技術における液圧回転機とし
て斜板型の油圧ボンｆを示す。FIGS. 1 and 2 show a swash plate type hydraulic bong f as a conventional hydraulic rotary machine.
同図において、１はケーシング、２は該ケーシング１内
に軸受３によって支持されて設けられた回転軸、４は該
回転軸２に圧入等の手段で固定されたシリンダプロ、り
である。シリンダブロック４はその軸方向に複数個のシ
リン１５，５・・・が穿股されており、該各シリンダ５
内には一端が斜板（図示せず）に支持されたピストン６
が摺動可能に挿嵌されて、該各ピストン６は回転軸２０
回転によって往復動せしめられる。In the figure, 1 is a casing, 2 is a rotating shaft provided within the casing 1 and supported by a bearing 3, and 4 is a cylinder member fixed to the rotating shaft 2 by means such as press fitting. The cylinder block 4 has a plurality of cylinders 15, 5... bored in its axial direction, and each cylinder 5
Inside is a piston 6 whose one end is supported by a swash plate (not shown).
are slidably inserted into each piston 6, and each piston 6 is connected to a rotating shaft 20.
It is caused to reciprocate by rotation.
７はシリンダブロック４と共に回転する弁板圧ｍｅ構と
しての押圧板で、該押圧板７はその一端開が弁板８に摺
接せしめられる摺動面７Ａｔ有し、他端側には補助ピス
トン部９．９＃・・・が形成され、該各補助ピストン部
９はシリンダブロック４の各シリンダ５内に嵌入せしめ
られている。また骸補助ピストン部９の軸方向には連通
路１０が穿設されており、該各連通路１０は押圧板７の
摺動面７ＡＶＣＨ口している。さらに、各連通路１０の
途中にはばね座１１が設けられ、該ばね座１１とピスト
ン６の端面との間にはばね１２が張設されている。Reference numeral 7 denotes a pressing plate as a valve plate pressure me mechanism which rotates together with the cylinder block 4. The pressing plate 7 has a sliding surface 7At whose one end is opened and is brought into sliding contact with the valve plate 8, and an auxiliary piston at the other end. 9.9#... are formed, and each auxiliary piston part 9 is fitted into each cylinder 5 of the cylinder block 4. Furthermore, communication passages 10 are bored in the axial direction of the skeleton auxiliary piston portion 9, and each communication passage 10 has an opening on the sliding surface 7AVCH of the pressing plate 7. Further, a spring seat 11 is provided in the middle of each communication path 10, and a spring 12 is stretched between the spring seat 11 and the end surface of the piston 6.
次に、弁板８は一側に押圧板７の摺動面７ＡとＷ１接す
る摺動面８Ａを有し、他側はピン１３によりケーシング
１に固定されている。そして、弁板８には吸入＆ −？
１４および吐出／ −） １５が穿設されてお９、該
吸入／−ト１４．吐出ポート１５はそれぞれケーシング
１に穿設された鉄人通路１６、吐出通路１７に常時遅過
すると共に、抑圧板７に穿設した連通路１０と間欠的に
連通するようになっている（第２図参照）。Next, the valve plate 8 has a sliding surface 8A on one side that contacts the sliding surface 7A of the pressing plate 7 W1, and the other side is fixed to the casing 1 by a pin 13. And the valve plate 8 has suction &-?
14 and discharge/-) 15 are drilled 9, and the suction/- port 14. The discharge ports 15 are always delayed to the iron man passage 16 and the discharge passage 17 bored in the casing 1, respectively, and are intermittently communicated with the communication passage 10 bored in the suppression plate 7 (second (see figure).
なお、図中、１８．１８．・・・は補助ピストン部９と
シリンダ５との間に設けたシール部材である。In addition, in the figure, 18.18. . . . is a sealing member provided between the auxiliary piston portion 9 and the cylinder 5.
従来技術による斜板盤の油圧−ンデは前述の構成を有す
るもので、回転軸２がエンジン等の駆動手段（図示せず
）により回転せしめられると、シリンダブロック４が抑
圧板７と共に回転する。このため、シリンダブロック４
０回転軸に対して傾斜して設けた斜板によシピストン６
はシリンダ５内を往復動すると共に、シリンダ５と連通
ずる連通路１０は間欠的に弁板８の吸入ポート１４また
は吐出ポー？１５と連通するから４７１作用が行なわれ
る。The conventional swash plate hydraulic pressure switch has the above-described configuration, and when the rotating shaft 2 is rotated by a driving means (not shown) such as an engine, the cylinder block 4 rotates together with the suppressing plate 7. . For this reason, the cylinder block 4
The piston 6 is mounted on a swash plate that is inclined with respect to the zero rotation axis.
reciprocates within the cylinder 5, and the communication passage 10 that communicates with the cylinder 5 is intermittently connected to the suction port 14 or the discharge port of the valve plate 8. Since it communicates with 15, the 471 action is performed.
而して、ボンデが高負荷状態で駆動せしめられると、吐
出／ −ト１４内は高圧となる。このため、押圧板７に
は該押圧板７を弁板８から離反させようとする開離力が
発生する。この開離力に対してばね１２のばね力とシリ
ンダ５内において補助ピストン部９の端面に作用する流
体圧とによって抑圧板７には弁板８への押圧力が付与さ
れる・そして、この押圧力が前述の開離力より大きくな
るように設計することによって、押圧板７の摺動面７Ａ
と弁板８の摺動面８Ａとの間から流体が漏洩するのを防
止している。ここで、吸排ポート１４゜１５の溝幅をｂ
とし、シリンダ５の直径をｄとしたときに、前述の開離
力は溝幅すにより、また押付力は直径ｄによシ決定され
る。このため、吸排ポート１４．１５の溝幅ｂｔ−シリ
ン１５の直径ｄに対して可及的小さくすることによって
、押付力を大きくシ、流体の過度な漏洩を防止してい友
。When the bonder is driven under a high load, the pressure inside the discharge port 14 becomes high. Therefore, a separating force is generated in the pressing plate 7 that tends to separate the pressing plate 7 from the valve plate 8. In response to this opening force, a pressing force is applied to the suppression plate 7 against the valve plate 8 by the spring force of the spring 12 and the fluid pressure acting on the end face of the auxiliary piston part 9 in the cylinder 5. By designing the pressing force to be larger than the above-mentioned separating force, the sliding surface 7A of the pressing plate 7
This prevents fluid from leaking between the valve plate 8 and the sliding surface 8A of the valve plate 8. Here, the groove width of suction/exhaust port 14°15 is b
When the diameter of the cylinder 5 is d, the above-mentioned separating force is determined by the groove width, and the pressing force is determined by the diameter d. Therefore, by making the groove width bt of the suction/discharge port 14, 15 as small as possible relative to the diameter d of the cylinder 15, the pressing force can be increased and excessive leakage of fluid can be prevented.
しかしながら、前述の従来技術によるボンデにあっては
幾多の欠点があった。まず第１に、連通路１０の直径は
牧排４−ト１４．１５の溝幅すにより制限される。従っ
て、その溝幅ｂ′ｆ：小さくすると、ポンプの高速躯勧
時において、連通路１０の流路抵抗が増大し、圧力損失
が大きくなり、ボンデに大きな貴荷がかかるから、その
機械効率が着しく低下し、またその自吸能力も低下する
欠点があった。第２に、連通路１０内の高圧油はポンプ
吐出行程時にも吐出通路１７には流れず、流体の体積弾
性率による圧縮分のうち、連通路１００体積分はデ、ド
カリ、−ムとなシ、見かけの漏れ量となってしまう、こ
のため、ボンデの容積効率が低下する欠点もあった。そ
して第３に、補助ピストン部９はシリンダ５内に突出し
ているから、ピストン６はその上死点位置において、補
助ピストン部９との接触を避けるために、ピストン６０
ストロークＳが制限されてしまう、そこで、該ピストン
６０ストローク諺を十分大きくするためには、シリンダ
シａ、り４をその軸方向に長くしなければならず、装置
全体が大量化する欠点があった。However, the prior art bonders described above have a number of drawbacks. First of all, the diameter of the communication passage 10 is limited by the groove width of the shedding 4-toe 14,15. Therefore, if the groove width b'f is made smaller, the flow resistance of the communicating passage 10 increases, pressure loss increases, and a large precious load is applied to the bonder, which reduces its mechanical efficiency. There was a drawback that the self-priming ability also decreased. Second, the high-pressure oil in the communication passage 10 does not flow into the discharge passage 17 even during the pump discharge stroke, and the volume of the communication passage 100 out of the compression due to the bulk modulus of the fluid is However, there is also the drawback that the volumetric efficiency of the bonder is reduced due to the apparent amount of leakage. Thirdly, since the auxiliary piston part 9 protrudes into the cylinder 5, the piston 6 has to be inserted into the piston 60 in order to avoid contact with the auxiliary piston part 9 at its top dead center position.
The stroke S is limited. Therefore, in order to make the piston 60 stroke sufficiently large, it is necessary to lengthen the cylinder axle 4 in the axial direction, which has the disadvantage of increasing the volume of the entire device. .
本発明は前述し九ような従来゛技術の欠点を改良したも
ので、その第１の目的はシリンダブロックの端部のシリ
ンダと対応する位置に咳シリンダより大径の凹部を形成
し、抑圧板に形成した補助ピストン部を前記凹部に嵌合
させて、抑圧板の弁板への押圧力を決定する補助ピスト
ン部の外径を大きくすることにより、ポンプの負荷を軽
減させて機械効率を向上させると共に、その自吸能力を
良好ならしめるようにした液圧回転機を提供することに
ある。The present invention is an attempt to improve the above-mentioned nine drawbacks of the conventional technology, and its first purpose is to form a recess with a larger diameter than the cough cylinder at the end of the cylinder block at a position corresponding to the cylinder, and to form a recess in the suppression plate. By fitting the auxiliary piston formed in the recess into the recess and increasing the outer diameter of the auxiliary piston that determines the pressing force of the suppression plate against the valve plate, the load on the pump is reduced and mechanical efficiency is improved. It is an object of the present invention to provide a hydraulic rotary machine which has a good self-priming ability.
本発明の第２の目的は前記抑圧板にピストンの直径より
大径の補助シリンダを穿設することにより、ピストンを
補助シリンダ内に突入可能となし、デッドボリュームを
減少させると共に、補助ピスト／部をピストンのストロ
ークに対する制限とならないようにした液圧回転機を提
供することにあるー
以下、本発明の実施例を第３図および第４図に基づき拝
細に説明する。A second object of the present invention is to make it possible for the piston to enter the auxiliary cylinder by boring an auxiliary cylinder with a diameter larger than the diameter of the piston in the suppression plate, thereby reducing the dead volume and reducing the auxiliary piston/part. An object of the present invention is to provide a hydraulic rotary machine in which the piston stroke is not restricted by the piston stroke.Hereinafter, embodiments of the present invention will be described in detail with reference to FIGS. 3 and 4.
同図において、第１図および第２図と同−構成要素には
同一符号を付してその説明を省略するものとする。シリ
ンダプロ、り２１には各シリンダ２２の端部と対応する
位置に該各シリンダ２２よりも大径の凹部２３が形成さ
れている。一方、押圧板２４に突設され九補助ピストン
部２５は前記凹部２３内に嵌合せしめられている・そし
て、押圧板２４には補助♂ストｙ部２５を貫通してピス
トン６０直径よシ大きい孔径を有する補助シリン／２６
が穿設されている。該補助シリンダ２６社押圧板２４の
弁板８に摺接する摺動面２４Ａに開口し、弁板８に設け
た吸排ポート１４または１５と間欠的に連通せしめられ
る。従って、補助シリンダ２６は、前述の従来技術にお
ける連通鮎１０としての機能を有するほか、ピストン６
がその上死点位置においては該補助シリンダ２６内に突
入することがで龜るようになりているから、シリンダ２
２の一部を構成する機能を併せ有する・図中、２７は回
転軸２に形成された段部２Ａと押圧板２４の段部２４Ｂ
との間に配設し九皿ばねで、該皿ばね２７により押圧板
２４は弁板８に押圧されると共に補助ピストン２５の端
面とシリンダブロック２１０凹部２３底壁との間に流体
圧が作用する間隙δが形成される。２８は補助ピストン
部２５と凹部２３との間に設けたシール部材である。In this figure, the same components as in FIGS. 1 and 2 are given the same reference numerals, and their explanations will be omitted. A recess 23 having a larger diameter than each cylinder 22 is formed in the cylinder protrusion 21 at a position corresponding to the end of each cylinder 22. On the other hand, a nine auxiliary piston part 25 protruding from the pressing plate 24 is fitted into the recess 23.The auxiliary piston part 25 is inserted into the pressing plate 24 through the auxiliary male piston part 25, which is larger than the diameter of the piston 60. Auxiliary cylinder with pore size /26
is drilled. The auxiliary cylinder 26 is opened in a sliding surface 24A of the press plate 24 that slides on the valve plate 8, and is intermittently communicated with the suction/exhaust port 14 or 15 provided on the valve plate 8. Therefore, the auxiliary cylinder 26 not only has the function of the communication ayu 10 in the prior art described above, but also has the function of the piston 6.
Since the cylinder 2 is prevented from entering the auxiliary cylinder 26 at its top dead center position, the cylinder 2
In the figure, 27 indicates a step 2A formed on the rotating shaft 2 and a step 24B of the pressing plate 24.
A nine disc spring disposed between the disc spring 27 presses the pressing plate 24 against the valve plate 8, and fluid pressure acts between the end face of the auxiliary piston 25 and the bottom wall of the recess 23 of the cylinder block 210. A gap δ is formed. 28 is a sealing member provided between the auxiliary piston portion 25 and the recessed portion 23.
本発明に係る液圧回転機は前述の構成を有するもので、
斜板型の油圧ポンプとした場合におけるポンプとしての
作用については前述の従来技術におけるものと格別差異
はない。然るに、押圧板２４Ｈシリン／２２よシ大径の
凹部２３内に嵌入せしめられているから皿ばね２７と共
に、抑圧板２４による弁板８への押付力を決定する補助
ピストン部２５の直径りをシリンダ２２０直径ｄに制約
されることなく適宜大きくすることができる。The hydraulic rotating machine according to the present invention has the above-mentioned configuration,
In the case of a swash plate type hydraulic pump, there is no particular difference in its function as a pump from that in the prior art described above. However, since the pressing plate 24H is fitted into the recess 23 which has a larger diameter than the cylinder 22, the diameter of the auxiliary piston part 25, which determines the pressing force against the valve plate 8 by the pressing plate 24 together with the disc spring 27, is reduced. The diameter of the cylinder 220 can be increased as appropriate without being restricted by the diameter d.
従って、補助ぎストン部２５の直径りを大きくすればす
るほど該補助ピストン部２５の端面２５Ａに形成される
受圧面積が飛躍的に増大し、大きな押付力が得られるか
ら、弁板８に穿設される吸排ポート１４，１５の震幅Ｂ
を太き（して開離力が増大しても流体が摺動面８Ａと２
４Ａとの間から漏出するのを防止することが”できる。Therefore, as the diameter of the auxiliary piston portion 25 is increased, the pressure receiving area formed on the end surface 25A of the auxiliary piston portion 25 increases dramatically, and a large pressing force can be obtained. Seismic amplitude B of the intake and exhaust ports 14 and 15 to be installed
Even if the separation force increases by increasing the thickness of the
4A can be prevented from leaking from between.
このように、吸排ポート１４．１５の溝幅Ｂを大きくす
れば、補助シリンダ２６の直径も大きくすることができ
るから、補助シリンダ２６に訃ける流路抵抗が著しく減
少”し、圧力損失を低減させることができ、ｔｌｌｙｆ
の機械効率を上昇させることができると共に、自吸能力
を向上させ、キャピテーシ、ンの発生を防止することが
できる。In this way, by increasing the groove width B of the intake/discharge port 14.15, the diameter of the auxiliary cylinder 26 can also be increased, so the flow resistance to the auxiliary cylinder 26 is significantly reduced, reducing pressure loss. can be done, tllyf
It is possible to increase the mechanical efficiency of the pump, improve the self-priming ability, and prevent the occurrence of capitation.
次に、補助シリンダー６の直径社ピスト／６の直径より
大径であるから、ピストン６は補助シリン／２６内に突
入することができるようになっている。そこで、ピスト
ン６の哀トロークは補助ピストン２５によそ制約−を受
けることなく、その上死点位置鵞補助シリンダ２６内の
吸排Ｉ−夕１４１５に開口す′る位置近傍に設定するこ
とができ、ピストン６０ストローク１１１−大きくする
ことができると共に、シリ′ンダ２２内で圧縮された流
体はそのはとんどを吐出ポート１５内に吐出させること
ができる・
なお、前述の実施例では本発明に係る液圧回転機を斜板
型の油゛圧ボンデとして用いる場合について説明したが
、油圧七−夕としても使用することができ、ｔた斜軸温
等他の型式のポンプ、モータとしても使用することがで
きるの鉱勿論である。Next, since the diameter of the auxiliary cylinder 6 is larger than the diameter of the piston 6, the piston 6 can plunge into the auxiliary cylinder 26. Therefore, the lower stroke of the piston 6 can be set near its top dead center position, which opens to the intake/exhaust port 1415 in the auxiliary cylinder 26, without being restricted by the auxiliary piston 25. The stroke 111 of the piston 60 can be increased, and most of the fluid compressed in the cylinder 22 can be discharged into the discharge port 15. Although we have described the case where such a hydraulic rotary machine is used as a swash plate type hydraulic bonder, it can also be used as a hydraulic tanabata, and it can also be used as a pump or motor for other types of pumps and motors such as slant shaft temperature. Of course you can.
以上詳細に述べた如く、本発明に係る液圧回転機によれ
ば、まず第１にシリンダプロ、りに穿設されたシリンＩ
と対応する位置に該各シリンダよりも大径の凹部を形成
し、該凹部に抑圧板に突設した補助ピストン部を嵌合さ
せる構成としたから、シリンダと吸排ポートとを連通さ
せる流路の震幅を大きくすることができるから、流路抵
抗による圧力損失、を低下させることができ、液圧回転
機の機械効率を向上させることができると共に、ポンプ
として使用した場合における自吸能力の向上を図ること
ができる。As described in detail above, according to the hydraulic rotating machine according to the present invention, firstly, the cylinder I bored in the cylinder pro
A recess with a diameter larger than that of each cylinder is formed at a position corresponding to the cylinder, and the auxiliary piston part protruding from the suppression plate is fitted into the recess, so that the flow path connecting the cylinder and the suction/exhaust port is Since the vibration amplitude can be increased, pressure loss due to flow path resistance can be reduced, and the mechanical efficiency of hydraulic rotating machines can be improved, as well as improved self-priming ability when used as a pump. can be achieved.
第２に、押圧板にはシリンダ内を摺動するピストンの直
径より大径の補助シリンダを穿設し、ピストンを補助シ
リンダ内に突入させることができるようにしたので、回
転機のデッドゲリ、−ムを著しく少くすることかで亀、
液圧回転機の容積効率を向上させることかで自、特に高
圧作動時における容積効率は極めて良好となる。また、
ピストンの上死点を補助シリンダ内の吸排／−トへの開
口部近傍位置に設定することができるから、ピストンの
ストロークを大きくすることができ、液圧回転機をその
軸方向に短縮させ、装置全体を小屋にすることができる
。Second, an auxiliary cylinder with a diameter larger than the diameter of the piston that slides inside the cylinder is bored in the press plate, and the piston can be pushed into the auxiliary cylinder. By significantly reducing the amount of
By improving the volumetric efficiency of the hydraulic rotary machine, the volumetric efficiency can be extremely improved, especially during high pressure operation. Also,
Since the top dead center of the piston can be set near the opening to the suction/exhaust port in the auxiliary cylinder, the stroke of the piston can be increased, and the hydraulic rotating machine can be shortened in its axial direction. The entire device can be turned into a shed.
第１図は従来技術による液圧回転機の部分縦断面図、第
２図は第１図の■−■矢示方向断面図、第３図は本発明
に係る液圧回転機の部分縦断面図１第４図は第３図のｗ
−ｒｔ矢矢示方向断固図ある。
２・・・回転軸、６・・・ピストン、８・・・弁板、２
１・・・シリン／ ｆ ｏ ｙり、２２・・・シリンダ
、２３・・・凹部１２４・・・押圧板、２５・・・補助
ピストン部、２６・・・補助シリンダ。
第２図
第３図
第４図FIG. 1 is a partial longitudinal sectional view of a hydraulic rotating machine according to the prior art, FIG. 2 is a sectional view taken in the direction indicated by the ■-■ arrow in FIG. 1, and FIG. 3 is a partial vertical sectional view of a hydraulic rotating machine according to the present invention. Figure 1 Figure 4 is Figure 3 w
-rt arrow shows the direction of the arrow. 2... Rotating shaft, 6... Piston, 8... Valve plate, 2
DESCRIPTION OF SYMBOLS 1... Cylinder/foy holder, 22... Cylinder, 23... Recessed part 124... Pressing plate, 25... Auxiliary piston part, 26... Auxiliary cylinder. Figure 2 Figure 3 Figure 4
Claims (1)
ｆ ｏツクをＭし、該シリンダブロックには軸方向に
間ｒＪＰｈをもって複数個のシリンダを穿設し、該各シ
リンノにはピストンを往復動可能に設け、前記シリンダ
ブロックの端部に押圧板を取付け、該押圧板を弁板に摺
動可能に当接させてなる液圧回転＋！ｉにおいて、前記
シリン／ ｆ ａ 、りの端部には前記シリンＩと対応
する位置に該各シリンダより大径の凹部を形成し、前記
抑圧板には前記各凹部に嵌合する補助ピストン部を形成
し、該補助ピストン部に前記シリンダと弁板に穿設した
吸排／−１とを連通する補助シリンダを穿設したこと１
−特徴とする液圧回転儂。 （２）回転軸と該回転軸に固定して設けたシリンダブロ
ックと′ｔ−肩し、該シリンダプロ、りには軸方向に間
隔をもって複数個のシリンダを穿設し、該各シリンダに
はピストンを往復動可能に設け、前記シリンダブロック
の端部に押圧板を取付け、該押圧板を弁板に摺動可能に
当接させてなる液圧回転機において、前記シリンダブロ
ックの端ｓＫは前記シリンダと対応する位置に該各シリ
ンダよりも大径の凹部を形成し、前記抑圧板には前記各
凹部に嵌合する補助ピストン部を形成すると共に前記シ
リンダと連通する補助シリンダを穿設し、該補助シリン
ダの直径を前記ピストンの直径より大径に形成したこと
ｔ−特徴とする液圧回転機。[Claims] 111 A cylinder fixed to the rotating shaft/
A plurality of cylinders are bored in the cylinder block with a distance rJPh in the axial direction, a piston is provided in each cylinder so as to be able to reciprocate, and a pressing plate is provided at the end of the cylinder block. Installation, the pressure plate is brought into sliding contact with the valve plate, resulting in hydraulic rotation +! In i, a concave portion having a diameter larger than that of each cylinder is formed at the end of the cylinder /f a at a position corresponding to the cylinder I, and the suppressing plate has an auxiliary piston portion that fits in each of the concave portions. 1, and an auxiliary cylinder is formed in the auxiliary piston portion to communicate between the cylinder and the intake/exhaust/-1 formed in the valve plate.
-Features hydraulic rotation. (2) A rotary shaft and a cylinder block fixed to the rotary shaft are connected to each other, and a plurality of cylinders are bored in the cylinder block at intervals in the axial direction. In a hydraulic rotating machine in which a piston is provided to be reciprocally movable, a press plate is attached to an end of the cylinder block, and the press plate is slidably abutted on a valve plate, the end sK of the cylinder block is forming a recess with a larger diameter than each cylinder at a position corresponding to the cylinder, forming an auxiliary piston part in the suppressing plate to fit into each recess, and drilling an auxiliary cylinder communicating with the cylinder; A hydraulic rotating machine characterized in that the diameter of the auxiliary cylinder is larger than the diameter of the piston.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57009784A JPS58128477A (en) | 1982-01-25 | 1982-01-25 | Hydraulic rotary machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57009784A JPS58128477A (en) | 1982-01-25 | 1982-01-25 | Hydraulic rotary machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS58128477A true JPS58128477A (en) | 1983-08-01 |
| JPH0251074B2 JPH0251074B2 (en) | 1990-11-06 |
Family
ID=11729853
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP57009784A Granted JPS58128477A (en) | 1982-01-25 | 1982-01-25 | Hydraulic rotary machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58128477A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6165080A (en) * | 1984-09-05 | 1986-04-03 | Hitachi Constr Mach Co Ltd | Fluid pressure rotary machine |
| WO2015071503A1 (en) * | 2013-11-13 | 2015-05-21 | Eco-Sistems Watermakers, S.L. | Hydraulic axial piston pump having a floating rotatory drum |
| DE102019135083A1 (en) * | 2019-12-19 | 2021-06-24 | Danfoss A/S | Hydraulic axial piston machine |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4858403A (en) * | 1971-11-13 | 1973-08-16 | ||
| JPS49129907A (en) * | 1973-04-04 | 1974-12-12 | ||
| JPS509104A (en) * | 1973-05-09 | 1975-01-30 |
-
1982
- 1982-01-25 JP JP57009784A patent/JPS58128477A/en active Granted
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4858403A (en) * | 1971-11-13 | 1973-08-16 | ||
| JPS49129907A (en) * | 1973-04-04 | 1974-12-12 | ||
| JPS509104A (en) * | 1973-05-09 | 1975-01-30 |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6165080A (en) * | 1984-09-05 | 1986-04-03 | Hitachi Constr Mach Co Ltd | Fluid pressure rotary machine |
| WO2015071503A1 (en) * | 2013-11-13 | 2015-05-21 | Eco-Sistems Watermakers, S.L. | Hydraulic axial piston pump having a floating rotatory drum |
| US20160273525A1 (en) * | 2013-11-13 | 2016-09-22 | Eco-Sistems Watermakers, S.L. | Hydraulic axial piston pump having a floating rotatory drum |
| DE102019135083A1 (en) * | 2019-12-19 | 2021-06-24 | Danfoss A/S | Hydraulic axial piston machine |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0251074B2 (en) | 1990-11-06 |
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