WO2014203962A1 - Radial piston hydraulic pump - Google Patents
Radial piston hydraulic pump Download PDFInfo
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- WO2014203962A1 WO2014203962A1 PCT/JP2014/066264 JP2014066264W WO2014203962A1 WO 2014203962 A1 WO2014203962 A1 WO 2014203962A1 JP 2014066264 W JP2014066264 W JP 2014066264W WO 2014203962 A1 WO2014203962 A1 WO 2014203962A1
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- 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
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/047—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the outer ends of the cylinders
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- 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
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
- F04B1/107—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders
- F04B1/1071—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders with rotary cylinder blocks
Definitions
- the present invention relates to a radial piston type hydraulic pump.
- a casing having a cylindrical inner surface, an eccentric shaft disposed in the casing by a predetermined amount from the axial center of the casing, and provided with an intake port and a discharge port therein, and rotatably disposed on the eccentric shaft
- a radial piston type hydraulic pump is known (Patent Documents 1 and 2).
- the hydraulic pump whose working fluid is water has no risk of environmental pollution or fire even if leakage occurs. Furthermore, water is harmless to the human body and can be applied to medical and food fields. For this reason, water pressure drive systems (aqua drive systems), which are composed of water pressure pumps, water pressure actuators, water pressure control valves, etc., have very high needs in the industrial field where demands for the environment and sanitation are high. It is attracting attention as a fourth drive system along with hydraulic, pneumatic and electric.
- a radial piston type hydraulic pump sucks and discharges hydraulic fluid as the piston reciprocates in the cylinder.
- the piston is constantly pressed by a sliding plate at one end, while maintaining liquid tightness. Slide on this plate. Due to such a structure, when water is used as the hydraulic fluid, there is a problem of wear and seizure between the piston and the sliding plate, and this problem is particularly noticeable when the pump discharge pressure is high.
- an object of the present invention is to provide a radial piston type hydraulic pump capable of continuous operation at a high discharge pressure.
- a casing having a cylindrical inner surface;
- An eccentric shaft disposed in the casing by a predetermined amount from the axial center of the casing, and provided with a suction port and a discharge port therein;
- a cylinder barrel that is rotatably arranged on the eccentric shaft, and in which cylinders are radially formed;
- An intake / exhaust port formed in the cylinder barrel having one end opened to the cylinder and the other end communicated with the suction port or the discharge port;
- a piston that is slidably disposed in the cylinder, one end of which is in sliding contact with a sliding plate disposed on a cylindrical surface of the casing, and the other end that reciprocates in the cylinder in accordance with the rotation of the cylinder barrel.
- a collar portion is provided on the piston end surface on the sliding plate side.
- rotating means that the cylinder barrel rotates relative to the eccentric shaft, and not only rotating the cylinder barrel with the eccentric shaft fixed, It also includes rotating the eccentric shaft in a fixed state. Further, the cylinder barrel and the eccentric shaft may be rotated with different speeds.
- the flange provided at one end of the piston can increase the pressure balance (details will be described later) of the sliding surface portion of the piston that is in sliding contact with the sliding plate.
- a water film is easily formed between the plates. For this reason, seizure, wear, etc. due to sliding resistance can be reduced, and the durability of these parts, and thus the durability of the pump itself can be improved.
- the radial piston type hydraulic pump concerning this invention presupposes water as a hydraulic fluid, you may add a lubricant etc. as needed.
- the piston may have a tapered sliding surface with the cylinder inclined at an angle ⁇ toward the sliding plate.
- the piston of a radial piston type hydraulic pump is subject to friction on the sliding surface between the piston and cylinder due to sliding with the sliding plate, which applies a greater force in the radial direction toward the sliding plate side of the piston.
- the radial force applied to the piston is distributed over the entire sliding surface between the piston and the cylinder, and the contact resistance when the piston slides can be reduced. Therefore, the durability of the piston and cylinder barrel can be improved, and the sliding efficiency of the piston can be improved.
- FIG. 2 is an explanatory view showing the internal structure of the radial piston type hydraulic pump 20 according to the present embodiment
- FIG. 7 is a view showing the eccentric shaft 2.
- the eccentric shaft 2 includes a suction port 2A and a discharge port 2B inside, and includes an eccentric portion 2C and non-eccentric portions 2D and 2E.
- the eccentric portion 2C of the eccentric shaft 2 is engaged with the cylinder barrel 3 in the casing 1, the non-eccentric portion 2D is engaged with the rear case 11 and the bearing 12, and the non-eccentric portion 2E is engaged with the bearing 13.
- the eccentric portion 2C of the eccentric shaft 2 is eccentric by a predetermined amount e from the axis of the non-eccentric portions 2D and 2E, that is, the axis of the casing 1.
- FIG. 3A is a view of the hydraulic pump 20 according to the present embodiment as viewed from the direction B in FIG. 2, and FIG. 3B is a view as viewed from the direction C in FIG.
- the eccentric shaft 2 is fixed and the front case 14 is rotated.
- the front case 14 has a structure that can be connected to an electric motor such as an electric servo motor or an inverter motor.
- the cylinder barrel 3 is synchronized with the front case 11 by the timing pin 15 and the timing ring 16.
- the hydraulic pump 20 according to the present embodiment can obtain the same pump effect by fixing the front case 14 and rotating the eccentric shaft 2.
- FIG. 1 is an explanatory view showing the AA cross section of FIG.
- the casing 1 has a cylindrical inner surface.
- the cylinder barrel 3 is rotatably disposed on the eccentric portion 2C of the eccentric shaft 2, and rotates eccentrically by the eccentric amount e of the eccentric shaft 2.
- An intake / exhaust port 3 ⁇ / b> A is formed in the cylinder barrel 3.
- One end of the suction / discharge port 3A opens to the cylinder 3B, and the other end can communicate with the suction port 2A or the discharge port 2B of the eccentric shaft 2.
- the piston 4 is slidably and liquid-tightly disposed.
- the piston 4 reciprocates while one end is in sliding contact with the sliding plate 5 disposed on the inner cylindrical surface of the casing 1.
- the piston 4 is pressed against the sliding plate 5 by a spring 17.
- FIG. 4 is a view showing the piston 4, wherein (a) is a top view, (b) is a front view, and (c) is a bottom view.
- FIG. 5 is a DD cross-sectional view of FIG.
- the piston 4 is provided with a linear groove 4C and a circular groove 4D for forming a hydraulic fluid film between the piston 4 and the sliding plate 5 in addition to the hydraulic fluid through hole 4B.
- hydraulic fluid means oil in the case of a hydraulic pump
- water in the case of a hydraulic pump and “hydraulic fluid film” means an oil film in the case of a hydraulic pump. In the case of a hydraulic pump, it shall mean a water film.
- water is broadly understood as a concept opposite to conventional oil, and means a liquid having low viscosity and poor lubricity compared to oil.
- the piston 4 reciprocates in the cylinder 3B according to the eccentric rotation of the cylinder barrel 3.
- the volume of the cylinder chamber defined by the cylinder barrel 3, the piston 4, and the sliding plate 5 is increased or decreased sequentially, and the pump action is generated, whereby the suction and discharge of the hydraulic fluid is realized.
- the pressure balance of the sliding surface portion of the piston is the ratio of the force with which the piston 4 is pushed back from the sliding plate 5 side by the hydraulic pressure to the force with which the piston 4 is pressed against the sliding plate 5 (unit [%]). .
- the piston 4 is pressed against the sliding plate 5 by the reaction force of the spring 17, the centrifugal force due to the rotation of the piston 4 itself, and the pressure of the hydraulic fluid. However, when the pump 20 is operated, the pressure of the hydraulic fluid becomes dominant. .
- pressure balance K p of the sliding surface of the piston, a circle for forming a hydraulic fluid film between the outer diameter d 1, the piston 4 and the sliding plate 5 of the end face of the sliding plate 5 side of the piston 4 The outer diameter d 2 of the groove 4D and the outer diameter d of the end surface of the piston 4 on the eccentric shaft 2 side can be obtained by the following calculation formula.
- K p (d 1 2 + d 1 d 2 + d 2 2 ) / 3d 2 ⁇ 100 (1)
- pressure balance simply refers to the pressure balance of the sliding surface portion of the piston.
- radial piston hydraulic pumps that use oil as hydraulic fluid are designed with a pressure balance of about 80%.
- water has a low viscosity and poor lubricity compared to oil, so that the sliding surface is sufficient. Slidability cannot be ensured, and wear and seizure are likely to occur.
- the piston 4 in the present embodiment is partly changed from the piston 4 used in the hydraulic pump, and provided with a collar portion 4A on the end face of the piston 4 on the side sliding with the sliding plate 5. That is, the shape of the piston 4 was changed so as to enlarge d 1 in FIG. 6 (d 2 and d were not changed). By doing so, the contact area between the piston 4 and the sliding plate 5 increases, and the piston 4 is pushed back from the sliding plate 5 side by the hydraulic pressure without changing the force with which the piston 4 is pressed against the sliding plate 5. Force can be increased and the pressure balance can be increased. That is, the collar part 4A functions as a pressure balance adjustment part.
- FIG. 5 is a view for explaining the shape of the piston 4.
- FIG. 5B is an enlarged view of the E portion of FIG. 5A, and shows the shape in the vicinity of the collar portion 4A, that is, in the vicinity of the end surface of the piston 4 on the sliding plate 5 side.
- the piston 4 has a tapered sliding surface with the cylinder 3B that is inclined at an angle ⁇ toward the sliding plate 5.
- the hydraulic pump 20 according to the present embodiment can be continuously operated for 1000 hours or more at a discharge pressure exceeding 100 atm.
- FIGS. 8 to 10 are diagrams illustrating the operating principle of the pump.
- the casing 1 is assumed to rotate counterclockwise.
- the cylinder barrel 3 rotates eccentrically by a predetermined amount e with respect to the axial center of the casing 1 in the downward direction of the drawing.
- the piston 41 slides in the cylinder 3B in the direction of the sliding plate 51 as the cylinder barrel 3 rotates counterclockwise, and the cylinder barrel 3, the piston 41, and the sliding plate.
- the volume of the cylinder chamber 61 partitioned by 51 increases.
- the cylinder chamber 61 is kept fluid-tight except for an opening communicating with the intake / exhaust port 3A.
- the hydraulic fluid is sucked from the intake port 2A via the intake / exhaust port 3A.
- the hydraulic fluid is also drawn into the cylinder chamber 62 on the same principle.
- the piston 43 slides in the cylinder barrel 3B toward the eccentric shaft 2 due to the eccentric rotation of the cylinder barrel 3, and the volume of the cylinder chamber 63 decreases. Therefore, the hydraulic fluid is discharged to the discharge port 2B through the suction / discharge port 3A by the pressure of the piston 43 and the sliding plate 53. The hydraulic fluid is discharged from the cylinder chamber 64 on the same principle.
- the piston 45 is located at a position where the volume of the cylinder chamber 65 becomes the smallest (so-called bottom dead center), does not perform suction or discharge, and the opening of the cylinder chamber 65 does not communicate with either the suction port 2A or the discharge port 2B. .
- bottom dead center the volume of the cylinder chamber 65 becomes the smallest
- top dead center the volume of the cylinder chamber is the largest
- FIGS. 8B, 9C, 9D, and 10E show a state when the casing 1 is rotated counterclockwise by 72 degrees from the state of FIG. 8A.
- FIG. Table 1 summarizes the suction and discharge states of each piston in these states.
- the hydraulic pump 20 in the present embodiment can switch the suction / discharge direction in the suction port 2A and the discharge port 2B by changing the rotation direction of the casing 1, that is, the front case 14.
- FIG. 11 is a view for explaining the flow of water in the pump 20.
- Each piston in FIG. 11A is in the same state as in FIG.
- FIG. 11B is a cross-sectional view taken along the line HH in FIG.
- the pistons 41 and 42 are in the suction process, and the pistons 43 and 44 are in the discharge process.
- the pistons 41 and 42 communicate with the suction port 2A of the eccentric shaft 2 through the opening 3A of the cylinder barrel, and hydraulic fluid is sucked from the suction port 2A by the suction action of the pistons 41 and 42 (FIG. 9).
- the pistons 43 and 44 communicate with the discharge port 2BA of the eccentric shaft 2 through the opening 3A of the cylinder barrel, and hydraulic fluid is discharged from the suction port 2B by the discharge action of the pistons 43 and 44. (The downward slanted line in FIG. 9).
- the piston 45 located at a so-called bottom dead center does not perform suction or discharge, and does not communicate with either the suction port 2A or the discharge port 2B.
- the hydraulic pump 20 in this embodiment is provided with the five pistons 4, you may increase / decrease as needed.
- the larger the number of pistons 4, the more the pulsation widths at the suction port 2A and the discharge port 2B of the eccentric shaft 2 can be reduced.
- the number of pistons 4 an odd number, the phase of suction / discharge can be shifted, and the same pulsation can be reduced.
- the number of pistons 4 is increased, the number of parts increases and the structure becomes complicated, so it is not realistic to increase the number of pistons 4 too much.
- the change from the hydraulic pump to the hydraulic pump 20 is attempted by changing the shape of the piston 4 in the conventional radial piston type hydraulic pump.
- the material may be changed or the surface treatment may be performed. Good.
- the radial piston type hydraulic pump 20 may further include a bearing member 18 made of resin between the eccentric shaft 2 and the cylinder barrel 3.
- FIG. 12 is a view for explaining the internal structure of the radial piston type hydraulic pump 30 according to this modification.
- the resin used for the bearing member 18 include phenolic resin, fluororesin, and carbon, but it is preferable to use phenolic resin in terms of excellent wear resistance and load resistance.
- the shape of the cylinder barrel 3 is not limited to that shown in the drawings, and can be appropriately changed within a range that exhibits its operational effects in consideration of workability during manufacturing.
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Abstract
Description
筒状内面を有するケーシングと、
前記ケーシング内に該ケーシングの軸心より所定量偏心して配設され、内部に吸入ポート、及び吐出ポートを備える偏心シャフトと、
前記偏心シャフト上に回転自在に配設され、内部にシリンダを放射状に形成したシリンダバレルと、
前記シリンダバレル内に形成され、一端が前記シリンダに開口し、他端が前記吸入ポート又は吐出ポートに連通可能な吸排口と、
前記シリンダ内に摺動自在に配設され、その一端がケーシングの円筒面に配設された摺動プレートと摺接し、他端が前記シリンダバレルの回転に応じて前記シリンダ内を往復動するピストンとを備えたラジアルピストン型水圧ポンプにおいて、
前記摺動プレート側のピストン端面につば部を設けたことを特徴とする。 In the radial piston type hydraulic pump according to the present invention,
A casing having a cylindrical inner surface;
An eccentric shaft disposed in the casing by a predetermined amount from the axial center of the casing, and provided with a suction port and a discharge port therein;
A cylinder barrel that is rotatably arranged on the eccentric shaft, and in which cylinders are radially formed;
An intake / exhaust port formed in the cylinder barrel, having one end opened to the cylinder and the other end communicated with the suction port or the discharge port;
A piston that is slidably disposed in the cylinder, one end of which is in sliding contact with a sliding plate disposed on a cylindrical surface of the casing, and the other end that reciprocates in the cylinder in accordance with the rotation of the cylinder barrel. In the radial piston type hydraulic pump with
A collar portion is provided on the piston end surface on the sliding plate side.
前記ピストンは、前記摺動プレートに向かって角度θで傾斜するテーパー状の、前記シリンダとの摺動面を有してもよい。 In the above configuration,
The piston may have a tapered sliding surface with the cylinder inclined at an angle θ toward the sliding plate.
図2は本実施形態にかかるラジアルピストン型水圧ポンプ20の内部構造を示す説明図であり、図7は偏心シャフト2を示す図である。偏心シャフト2は、内部に吸入ポート2A、及び吐出ポート2Bを備え、偏心部2Cと非偏心部2D及び2Eで構成される。偏心シャフト2の偏心部分2Cはケーシング1内のシリンダバレル3と係合し、非偏心部2Dはリアケース11及びベアリング12と、非偏心部2Eはベアリング13と係合する。 (Configuration of this embodiment)
FIG. 2 is an explanatory view showing the internal structure of the radial piston type
ポンプ20作動時は、ピストン4と摺動プレート5との間に作動液膜が形成され、ピストン4と摺動プレート5は作動液膜を介して摺動する。この場合、作動液膜の形成されやすさは、ピストンの摺動面部の圧力バランスにより決まる。 (Piston pressure balance)
When the
Kp=(d1 2+d1d2+d2 2)/3d2×100 ・・・・・(1) “The pressure balance of the sliding surface portion of the piston” is the ratio of the force with which the
K p = (d 1 2 + d 1 d 2 + d 2 2 ) / 3d 2 × 100 (1)
図5は、ピストン4の形状を説明する図である。図5(b)は同図(a)のE部を拡大したものであり、つば部4A近傍、すなわち摺動プレート5側のピストン4端面付近の形状を示している。この図に示すように、ピストン4は、前記摺動プレート5に向かって角度θで傾斜するテーパー状の、前記シリンダ3Bとの摺動面を有している。 (About the taper shape of the piston)
FIG. 5 is a view for explaining the shape of the
図8~10はポンプの作動原理を説明した図である。ケーシング1は反時計回りに回転するものとする。シリンダバレル3はケーシング1の軸心に対し、図面下方向に所定量eだけ偏心して回転する。 (About the operating principle of the pump)
8 to 10 are diagrams illustrating the operating principle of the pump. The
図11はポンプ20内の水の流れを説明する図である。図11(a)における各ピストンは図8(a)と同じ状態にある。図11(b)は同図(a)のH-H断面図である。図8(a)を用いて説明したように、ピストン41・42が吸入工程、ピストン43・44が吐出工程にある。 (About the flow of water in the pump)
FIG. 11 is a view for explaining the flow of water in the
変形例として、上述の実施形態にかかるラジアルピストン型水圧ポンプ20において、さらに、偏心シャフト2とシリンダバレル3との間に、樹脂からなる軸受部材18を備えてもよい。図12は、本変形例にかかるラジアルピストン型水圧ポンプ30の内部構造を説明する図である。軸受部材18が偏心シャフト2とシリンダバレル3との間に配設されることにより、ポンプ作動時の偏心シャフト2とシリンダバレル3との摩擦による疲労や発熱を抑制でき、これらの部品の耐久性を向上させることができる。軸受部材18に用いられる樹脂としては、フェノール樹脂、フッ素樹脂、カーボン等が例示されるが、耐摩耗性及び耐荷重性に優れるという点でフェノール樹脂を用いることが好ましい。 (Modification)
As a modification, the radial piston type
Note that the shape of the
2 偏心シャフト
2A 吸入ポート
2B 吐出ポート
2C 偏心部
2D 非偏心部
2E 非偏心部
3 シリンダバレル
3A 吸排口
3B シリンダ
4 ピストン
4A つば部
4B 貫通孔
4C 溝
4D 溝
5 摺動プレート
11 リアケース
12 ベアリング
13 ベアリング
14 フロントケース
15 タイミングピン
16 タイミングリング
17 スプリング
18 軸受部材
20,30 水圧ポンプ
41,42,43,44,45 ピストン
51,52,53,54,55 摺動プレート
61,62,63,64,65 シリンダ室 DESCRIPTION OF
Claims (3)
- 筒状内面を有するケーシングと、
前記ケーシング内に該ケーシングの軸心より所定量偏心して配設され、内部に吸入ポート、及び吐出ポートを備える偏心シャフトと、
前記偏心シャフト上に回転自在に配設され、内部にシリンダを放射状に形成したシリンダバレルと、
前記シリンダバレル内に形成され、一端が前記シリンダに開口し、他端が前記吸入ポート又は吐出ポートに連通可能な吸排口と、
前記シリンダ内に摺動自在に配設され、その一端がケーシングの円筒面に配設された摺動プレートと摺接し、他端が前記シリンダバレルの回転に応じて前記シリンダ内を往復動するピストンとを備えたラジアルピストン型水圧ポンプにおいて、
前記摺動プレート側のピストン端面につば部を設けたことを特徴とするラジアルピストン型水圧ポンプ。 A casing having a cylindrical inner surface;
An eccentric shaft disposed in the casing by a predetermined amount from the axial center of the casing, and provided with a suction port and a discharge port therein;
A cylinder barrel that is rotatably arranged on the eccentric shaft, and in which cylinders are radially formed;
An intake / exhaust port formed in the cylinder barrel, having one end opened to the cylinder and the other end communicated with the suction port or the discharge port;
A piston that is slidably disposed in the cylinder, one end of which is in sliding contact with a sliding plate disposed on a cylindrical surface of the casing, and the other end that reciprocates in the cylinder in accordance with the rotation of the cylinder barrel. In the radial piston type hydraulic pump with
A radial piston type hydraulic pump characterized in that a flange is provided on an end face of the piston on the sliding plate side. - 前記ピストンは、前記摺動プレートに向かって角度θで傾斜するテーパー状の、前記シリンダとの摺動面を有することを特徴とする請求項1に記載のラジアルピストン型水圧ポンプ。 The radial piston type hydraulic pump according to claim 1, wherein the piston has a tapered sliding surface that is inclined at an angle θ toward the sliding plate.
- 前記偏心シャフトと前記シリンダバレルとの間に、樹脂からなる軸受部材を備えることを特徴とする請求項1又は2に記載のラジアルピストン型水圧ポンプ。 3. A radial piston hydraulic pump according to claim 1 or 2, wherein a bearing member made of resin is provided between the eccentric shaft and the cylinder barrel.
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JP2015522972A JP6130913B2 (en) | 2013-06-21 | 2014-06-19 | Radial piston type hydraulic pump |
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Cited By (1)
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CN106930916A (en) * | 2017-04-25 | 2017-07-07 | 中国海洋大学 | A kind of dynamic shell type multiaction water hydraulic radial plunger pump |
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EP0099372B1 (en) * | 1982-01-19 | 1989-12-20 | Unipat Ag | Hydraulic radial piston machines |
US4920859A (en) * | 1986-08-01 | 1990-05-01 | Eaton Corporaton | Radial piston pump and motor |
DE19635164A1 (en) * | 1996-08-30 | 1998-03-05 | Bosch Gmbh Robert | Piston pump |
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2014
- 2014-06-19 WO PCT/JP2014/066264 patent/WO2014203962A1/en active Application Filing
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JPS6246860Y2 (en) * | 1979-11-06 | 1987-12-21 | ||
JPH03978A (en) * | 1989-05-25 | 1991-01-07 | Shimadzu Corp | Radial pump or motor |
JP2005054574A (en) * | 2001-07-11 | 2005-03-03 | Yasuo Kita | Rotary type fluid energy converter |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
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CN106930916A (en) * | 2017-04-25 | 2017-07-07 | 中国海洋大学 | A kind of dynamic shell type multiaction water hydraulic radial plunger pump |
CN106930916B (en) * | 2017-04-25 | 2019-03-15 | 中国海洋大学 | A kind of dynamic shell type multiaction water hydraulic radial plunger pump |
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JP6130913B2 (en) | 2017-05-17 |
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