WO2014080691A1 - 流体圧ポンプ - Google Patents
流体圧ポンプ Download PDFInfo
- Publication number
- WO2014080691A1 WO2014080691A1 PCT/JP2013/075840 JP2013075840W WO2014080691A1 WO 2014080691 A1 WO2014080691 A1 WO 2014080691A1 JP 2013075840 W JP2013075840 W JP 2013075840W WO 2014080691 A1 WO2014080691 A1 WO 2014080691A1
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- WIPO (PCT)
- Prior art keywords
- piston
- cam
- cam surface
- rotating
- rotation axis
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Classifications
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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
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
- F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
- F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams
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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
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
Definitions
- the present invention relates to a fluid pressure pump, and more particularly, to a fluid pressure pump configured to operate a piston with a driving force of an electric motor.
- Patent Document 1 discloses a pump that converts rotational motion of a motor shaft of an electric motor into reciprocating motion by an eccentric bearing and sends oil by operating a piston (a plunger in the literature). It is shown.
- Patent Document 2 has a cylinder block in which a swash plate is provided on the output shaft of the electric motor, a plurality of pistons that operate when the swash plate rotates, and a plurality of cylinders that accommodate the plurality of pistons are formed. The pump is shown.
- the pump of Patent Document 2 is configured as an axial piston type in which a swash plate rotates integrally with an output shaft of an electric motor, and a plurality of pistons are advanced and retracted.
- Patent Document 3 discloses a pump in which a piston is disposed on a coaxial core with an output shaft (rotary shaft in the literature) of an electric motor, and the piston is rotatably accommodated around the output shaft axis. Has been.
- Some vehicles that run on an engine include a hydraulic pump that is driven by the engine, and hydraulic equipment that operates with oil supplied from the hydraulic pump. Many of these vehicles include a speed change mechanism in which a clutch is intermittently operated by hydraulic pressure as a hydraulic device, and a variable valve timing system that sets intake timing by hydraulic pressure.
- an electric oil pump is used to supply oil to the hydraulic equipment in a situation where the engine is stopped as described in Patent Document 2. I have.
- the oil pump only needs to maintain the oil pressure supplied to the hydraulic equipment, and is configured to be relatively small.
- the pump described in Patent Document 3 is reduced in size because an electric motor and a piston are arranged on a coaxial core and does not require a mechanism such as an eccentric bearing for reciprocating the piston. Is possible.
- this pump requires a configuration in which the piston and the cylinder rotate relative to each other, and requires a predetermined accuracy to engage the engaging pin with the cam groove on the outer periphery of the piston, so there is room for improvement.
- An object of the present invention is to make a pump that is operated by a driving force of an electric motor small.
- a feature of the present invention is that a piston that is arranged on the same axis as the rotation axis of the output shaft of the electric motor and that can reciprocate along the rotation axis, and the rotational force of the output shaft along the rotation axis.
- a cam mechanism that operates the piston in the forward movement direction by converting it into a pressing force in a direction, and a spring that operates the piston in the backward movement direction opposite to the forward movement direction,
- the cam mechanism has a rotating member that rotates integrally with the output shaft, and a cam surface that cannot rotate around the rotating shaft core and contacts the rotating member, and reciprocates along the rotating shaft core. It is in the point provided with the free cam member.
- the rotating member rotates integrally with the output shaft, and when the rotating member comes into contact with the cam surface, the cam member operates in a direction along the rotating shaft core.
- the piston is operated in the forward direction in cooperation. Further, when the pressing force by the cam member is released, the piston operates in the backward movement direction by the biasing force of the spring.
- a plurality of the rotating members are arranged at a plurality of locations in a circumferential area centered on the rotation axis, and the cam member has the cam surface with which the plurality of rotating members simultaneously contact,
- the direction of the resultant force acting on the cam member from the plurality of rotating members may be set so as to be located on the rotating shaft core.
- the plurality of rotating members simultaneously apply a pressing force to a plurality of locations on the cam surface of the cam member.
- the acting direction of the resultant force of the pressing force acting on a plurality of locations on the cam surface is located on the rotation axis, no force is applied to the cam member or the piston in a direction away from the rotation axis. Energy is not wasted and uneven wear is not caused.
- the shape of the cam surface in a state where the cam member is developed in the circumferential direction may be wavy.
- the backward side cam surface that operates the piston in the backward direction is steeper than the forward side cam surface that applies a pressing force to the piston in the forward direction. May be set.
- FIG. 3 is a cross-sectional view of a fluid pressure pump. These are sectional drawings of a cam mechanism and a pump part in the state which sends out oil. Is a cross-sectional view taken along line III-III in FIG.
- FIG. 3 is an exploded perspective view of a fluid pressure pump. These are sectional drawings of the fluid pressure pump of another embodiment (a). These are exploded perspective views of the fluid pressure pump of another embodiment (a).
- a fluid pressure pump is configured by including an electric motor M, a cam mechanism C, and a pump part P.
- a cam mechanism C and a pump part P are arranged on the same axis as the rotation axis X of the output shaft 2 of the electric motor M.
- the hydraulic clutch switches from the transmission state to the cutoff state as the hydraulic pressure decreases when the engine is stopped.
- the hydraulic clutch returns to the transmission state as the hydraulic pressure rises, and a shock may be generated at the start of traveling. This tendency is particularly remarkable in a vehicle in which idle stop control is performed.
- the fluid pressure pump of the present invention is provided in a vehicle in which idle stop control is performed, and maintains oil supply to hydraulic equipment by operating when the engine is stopped.
- the vehicle may be provided with hydraulic equipment such as a variable valve timing system for setting the intake timing, and oil may be supplied from the fluid pressure pump.
- the fluid pressure pump of the present invention may be used to send out fluids such as water and gas in addition to oil.
- the electric motor M supports the output shaft 2 so as to be rotatable about the rotation axis X inside the motor case 1, and includes a field coil 3 on the inner periphery of the motor case 1, and a permanent magnet is provided on the output shaft 2.
- the rotor 4 is provided.
- the electric motor M is configured as a brushless DC motor, and the rotation of the output shaft 2 is controlled by supplying electric power to the field coil 3 from a dedicated motor control circuit.
- the unit case 10 is connected to the end of the electric motor M.
- a large-diameter portion 11 that accommodates the cam mechanism C and a small-diameter portion 12 that constitutes the pump portion P are integrally formed, and a partition wall portion 13 is formed at the end of the small-diameter portion 12.
- the large-diameter portion 11 of the unit case 10 is integrally formed with a flange connected to the electric motor M, and is formed with a cam mechanism housing space 11S having a cylindrical inner surface coaxial with the rotary shaft X. Yes.
- the small-diameter portion 12 is formed with a pump space 12S having a cylindrical inner surface coaxial with the rotation axis X.
- the cam mechanism C includes a rotating member 21 that rotates integrally with the output shaft 2 of the electric motor M, and a cam member 23 having a cam surface 23S with which the rotating member 21 contacts, and these are cam mechanisms. It is accommodated in the accommodating space 11S.
- the rotating member 21 is composed of ball bearings supported at both ends of a shaft body 22 provided in a posture orthogonal to the rotation axis X with respect to the protruding end portion of the output shaft 2.
- the inner race is fitted and connected to the shaft body 22, and the outer race freely rotates with respect to the shaft body 22.
- the cam surface 23S is formed in a ring shape with a predetermined width centered on the rotation axis X when viewed in the direction along the rotation axis X. Further, the cam member 23 makes the outer periphery of the rotating member 21 point-contact with the cam surface 23S by smoothly projecting a part of the ring-shaped cam surface 23S in the width direction over the entire circumference.
- the rotating member 21 since the outer periphery of the rotating member 21 has a smooth circumferential shape, for example, when the surface of the cam surface 23S is smooth in the width direction, the rotating member 21 and the cam surface 23S come into contact with each other on a wide surface. Accordingly, when the rotating member 21 rotates about the rotation axis X, the speed between the center side and the outer peripheral side of the rotation axis X of the cam surface 23S even if the rotation member 21 rotates about the shaft body 22. It was considered that slipping was caused by the difference, leading to heat generation and wear. In response to such a problem, the cam surface 23S and the rotating member 21 are brought into a point contact state by smoothly projecting a part of the cam surface 23S in the width direction over the entire circumference, thereby suppressing the slip.
- the rotating member 21 is point-contacted with the cam surface 23S by forming the rotating member 21 into a shape projecting to the outer periphery at the center of the thickness (for example, the shape of a abacus ball). You may comprise so that it may do.
- the cam member 23 has a columnar shape with a cam surface 23S that contacts the pair of rotating members 21 formed at the end, and is fitted in the cam mechanism accommodating space 11S so as to be movable in the direction along the rotation axis X.
- a pair of guide recesses 24 are formed in the outer peripheral portion of the cam member 23 along the direction along the rotation axis X, and a pair of guide pins 25 engaged with the guide recesses 24 connects the large diameter portion 11 of the unit case 10. It is provided in a penetrating state.
- the cam surface 23S is formed in a wavy shape that is, for example, a sine curve in a state where the cam surface 23S is deployed in the circumferential direction, and the pair of rotating members 21 are simultaneously contacted with equal pressure. Further, the cam member 23 is formed with a through-hole 26 that is coaxial with the rotational axis X, and a fitting portion 27 into which the end of the piston 31 is fitted is formed on the cam member 23 on the opposite side of the cam surface 23S. ing.
- the pump portion P is a piston 31 that is movably fitted to the small diameter portion 12 of the unit case 10 in a direction along the rotational axis X, and a backward movement direction (see FIG. 1) that is opposite to the forward movement direction. And a coil spring 32 for urging in the left direction). Further, the pump portion P includes a first ball valve 34 supported by the first holder 33 with respect to the piston 31 and a second ball valve 36 supported by the second holder 35 with respect to the partition wall portion 13 of the unit case 10. And is configured.
- the outer peripheral surface of the piston 31 is in intimate contact with the inner peripheral surface of the pump space 12S. With this configuration, the small-diameter portion 12 into which the piston 31 is fitted functions as a cylinder in the unit case 10.
- An outer channel 31A having a groove shape is formed at an end portion of the piston 31 facing the cam member 23, and a protruding portion 31B is formed at the other end portion.
- An oil circulation space 31S is formed in a through hole shape on the same axis as the rotation axis X from the end of the piston 31 facing the cam member 23 to the protruding end of the protruding portion 31B.
- the first ball valve 34 described above is movably provided at a position where the opening of the end portion of the protruding portion 31B of the piston 31 is closed and a position where it is opened, and is urged in the closing direction by a spring.
- the second ball valve 36 described above is provided movably between a position where the opening formed in the partition wall 13 of the unit case 10 is closed and a position where the opening is opened, and is biased in the closing direction by a spring. .
- a suction port 14 for supplying oil to the oil circulation space 31S of the piston 31 is formed in the large-diameter portion 11 of the unit case 10 and discharged to a portion where the oil is sent out from the second holder 35 provided at the end of the unit case 10. Port 15 is formed.
- the inner peripheral diameter of the fitting portion 27 of the cam member 23 is set to be slightly larger than the outer peripheral diameter of the piston 31, and the piston 31 is fitted into the fitting portion 27.
- a gap is formed between the inner circumference of the fitting portion 27 and the outer circumference of the piston 31 in the fitted state as described above, and this gap is connected to the oil circulation space 31S via the external flow path 31A.
- the large-diameter portion 11 of the unit case 10 is formed with a supply / exhaust port 16 communicating with a fitting space in which the piston 31 is fitted into the cam member 23 in the cam mechanism accommodating space 11S.
- the fluid pressure pump is disposed below the oil level inside the transmission. As a result, a pipe that guides oil from the discharge port 15 to the hydraulic equipment is required, but a pipe that supplies oil to the suction port 14 is not necessary, and the oil inside the transmission is connected to the suction port 14. Supplied directly.
- the two (multiple) rotating members 21 are arranged at positions in contact with two places (a plurality of places) in the circumferential area around the rotation axis X on the cam surface 23S, and the pair of rotating members 21 are cams.
- the cam surface 23S of the member 23 is simultaneously contacted with equal pressure.
- the two rotating members 21 come into contact with the cam surface 23S at positions facing each other with the rotation axis X interposed therebetween.
- the rotating member 21 rotates about the rotation axis X
- the resultant force acting on the cam member 23 from the two cam surfaces 23S with which the rotating member 21 contacts acts on the rotation axis. That is, no force is applied to the cam member 23 or the piston 31 in the direction away from the rotation axis X, and the force is applied linearly along the rotation axis X, so that energy is not wasted. It does not cause uneven wear.
- the shaft body when rotating about the rotation axis X, the shaft body is in a state where the outer outer race is in contact with the cam surface 23S of the cam member 23. It rotates around the 22 axis. Thereby, the resistance when the rotating member 21 rotates about the rotation axis X is extremely reduced.
- the cam member 23 since the guide pin 25 is fitted to the guide recess 24 of the cam member 23, the cam member 23 does not rotate even when the rotating member 21 rotates about the rotation axis X, and the rotating shaft Move linearly along the core X.
- the first ball valve 34 closes the opening of the protruding portion 31B as the internal pressure of the pump space 12S increases, and the second ball valve 36 The opening of the part 13 is opened. As a result, the oil in the pump space 12S is sent out from the discharge port 15 to the outside.
- the pair of rotating members 21 simultaneously contact the cam surface 23S of the cam member 23 with the same pressure, so that the pair of rotating members from the two cam surfaces 23S with which the rotating member 21 contacts.
- the equal pressure is applied to 21 and the cam member 23 is operated in a linear direction along the rotation axis X, and the piston 31 is also operated linearly in conjunction with this.
- the first ball valve 34 opens the projection 31B and the second ball valve 36 opens the partition wall 13 as the internal pressure of the pump space 12S decreases. Occlude. Thereby, the oil from the suction port 14 is introduced into the oil circulation space 31S from the introduction opening 31C of the piston 31 and supplied to the pump space 12S.
- This fluid pressure pump applies the rotational operation of the output shaft 2 of the electric motor M to the piston 31 from the cam mechanism C so as to move the piston 31 in the forward movement direction and send out oil from the discharge port 15.
- the piston 31 is operated in the backward movement direction by the urging force of the coil spring 32 to suck oil from the suction port 14. By repeating this oil feeding and suction, it functions as a pump.
- the rotating member 21 is comprised by the rod material penetrated and supported by the attitude
- the piston 31 is integrally formed.
- the cam member 23 is configured by forming the cam surface 23 ⁇ / b> S at an end portion close to the electric motor M of the cylindrical member, and the piston 31 is configured at a portion connected thereto.
- a long hole-shaped guide recess 24 is formed in the cylindrical member, and the rotation of the rotation axis X while preventing the rotation of the cylindrical member around the rotation axis X by engaging the guide pin 25 therewith. It is possible to operate in the direction along.
- the cylindrical member (the cam member 23 and the piston 31) is continued along the rotation axis X in the forward movement direction and the backward movement direction by driving the electric motor M. It is possible to repeatedly perform the operation of sending the oil from the discharge port 15 and sucking the oil to the suction port 14.
- only one rotating member 21 may be provided as the cam mechanism C, or three or more may be provided. That is, even if the rotation member 21 is single, it functions, and even if it is three or more, it functions.
- the rotating member 21 by disposing the rotating member 21 so as to contact a plurality of locations that equally divide the circumferential area around the rotation axis X on the cam surface 23S, The acting direction of the resultant force acting on the cam member 23 from the plurality of rotating members 21 can be made to act on the rotation axis.
- the backward side cam surface that operates the piston 31 in the backward direction is steeper than the forward side cam surface that applies a pressing force to the piston 31 in the forward direction. Mold to be a gradient.
- a reed valve is used that controls the flow of oil by swinging a plate-like flexible material with oil pressure.
- this reed valve the structure is simple and the cost is reduced as compared with the ball valve.
- the present invention can be used for a fluid pressure pump configured to operate a piston by a driving force of an electric motor.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Abstract
Description
〔基本構成〕
図1~図4に示すように、電動モータMと、カム機構Cと、ポンプ部Pとを備えて流体圧ポンプが構成されている。この流体圧ポンプは、電動モータMの出力軸2の回転軸芯Xと同軸芯上にカム機構Cとポンプ部Pとを配置している。
電動モータMは、モータケース1の内部に回転軸芯Xを中心に回転自在に出力軸2を支承すると共に、モータケース1の内周に界磁コイル3を備え、出力軸2に永久磁石を有するロータ4を備えて構成されている。この電動モータMはブラシレスDCモータとして構成され、界磁コイル3に対して専用のモータ制御回路から電力を供給することにより、出力軸2の回転が制御される。
カム機構Cは、電動モータMの出力軸2と一体的に回転する回転部材21と、この回転部材21が接触するカム面23Sを有するカム部材23とを有して構成され、これらがカム機構収容空間11Sに収容されている。
ポンプ部Pは、ユニットケース10の小径部12に対し回転軸芯Xに沿う方向に移動自在に嵌め込まれたピストン31と、このピストン31を往動方向と逆向きとなる復動方向(図1で左方向)に付勢するコイルスプリング32とを備えている。更に、ポンプ部Pは、ピストン31に対して第1ホルダ33により支持された第1ボール弁34と、ユニットケース10の隔壁部13に対して第2ホルダ35により支持された第2ボール弁36とを備えて構成されている。
この流体圧ポンプはトランスミッションの内部でオイルの液面下に配置される。これにより吐出ポート15からのオイルを油圧機器に導く管路は必要とするが、吸引ポート14に対してオイルを供給する管路は不要であり、吸引ポート14に対してトランスミッションの内部のオイルが直接供給される。
本発明は、上記した実施形態以外に以下のように構成しても良い。
Claims (4)
- 電動モータの出力軸の回転軸芯と同軸芯上に配置され前記回転軸芯に沿って往復作動自在なピストンと、
前記出力軸の回転力を、前記回転軸芯に沿う方向への押圧力に変換して作用させることで前記ピストンを往動方向に作動させるカム機構と、
前記ピストンを前記往動方向と逆向きとなる復動方向に作動させるスプリングとを備えると共に、
前記カム機構が、前記出力軸と一体的に回転する回転部材と、前記回転軸芯を中心にする回転が不能で前記回転部材が接触するカム面を有し前記回転軸芯に沿って往復作動自在なカム部材とを備えて構成されている流体圧ポンプ。 - 複数の前記回転部材が前記回転軸芯を中心とする円周領域の複数箇所に配置され、
前記カム部材が、複数の前記回転部材が同時に接触する前記カム面を有し、
複数の前記回転部材が回転する際には、複数の前記回転部材から前記カム部材に作用する合力の作用方向が、前記回転軸芯上に位置するように設定されている請求項1記載の流体圧ポンプ。 - 前記カム部材を周方向に展開した状態での前記カム面の形状が波状である請求項2記載の流体圧ポンプ。
- 前記カム面のうち、前記ピストンを前記復動方向へ作動させる復動側カム面が、前記ピストンに対して前記往動方向へ押圧力を作用させる往動側カム面より急勾配に設定されている請求項2又は3記載の流体圧ポンプ。
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201390000891.XU CN204663787U (zh) | 2012-11-21 | 2013-09-25 | 流体压力泵 |
US14/435,804 US20150292493A1 (en) | 2012-11-21 | 2013-09-25 | Fluid-pressure pump |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012255598A JP2014101843A (ja) | 2012-11-21 | 2012-11-21 | 流体圧ポンプ |
JP2012-255598 | 2012-11-21 |
Publications (1)
Publication Number | Publication Date |
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WO2014080691A1 true WO2014080691A1 (ja) | 2014-05-30 |
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ID=50775881
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PCT/JP2013/075840 WO2014080691A1 (ja) | 2012-11-21 | 2013-09-25 | 流体圧ポンプ |
Country Status (4)
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US (1) | US20150292493A1 (ja) |
JP (1) | JP2014101843A (ja) |
CN (1) | CN204663787U (ja) |
WO (1) | WO2014080691A1 (ja) |
Families Citing this family (5)
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US10113538B1 (en) * | 2016-06-17 | 2018-10-30 | The United States Of America As Represented By The Secretary Of The Navy | Impulse pump |
EP3379084B1 (en) * | 2017-03-23 | 2019-12-18 | Xylem Europe GmbH | De-blocking device for a hydraulic pump |
CN110560336A (zh) * | 2019-09-25 | 2019-12-13 | 深圳市海润智能机械有限公司 | 结构简单的输送结构 |
US11703039B2 (en) * | 2020-08-07 | 2023-07-18 | Ridge Tool Company | Wobble plate pump drive with gear box |
CN114837792A (zh) | 2021-03-10 | 2022-08-02 | 美普盛(上海)汽车零部件有限公司 | 一种带膨胀补偿密封件的电动冷却液泵 |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS50131110A (ja) * | 1974-04-03 | 1975-10-17 | ||
JPS5927162U (ja) * | 1982-08-11 | 1984-02-20 | 三菱重工業株式会社 | 往復動圧縮機 |
JPS62288374A (ja) * | 1986-06-04 | 1987-12-15 | Nippo Giken Kogyo Kk | カム駆動によるピストンポンプ |
JPH0226780U (ja) * | 1988-08-10 | 1990-02-21 | ||
JPH04175474A (ja) * | 1990-11-08 | 1992-06-23 | Matsushita Electric Works Ltd | ウォーターポンプ |
JPH06229369A (ja) * | 1992-05-22 | 1994-08-16 | Tatsuji Motomiya | 送液ポンプ |
JPH10318128A (ja) * | 1997-05-21 | 1998-12-02 | Nippon Soken Inc | ポンプ |
JP2001263223A (ja) * | 2000-03-23 | 2001-09-26 | Kyoritsu Kiko Kk | 二連プランジャポンプ |
JP2011052549A (ja) * | 2009-08-31 | 2011-03-17 | Oken Ltd | ピストンポンプおよびその設置方法 |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7743847B2 (en) * | 2000-08-15 | 2010-06-29 | Wave Craft Limited | Cam operated devices |
-
2012
- 2012-11-21 JP JP2012255598A patent/JP2014101843A/ja active Pending
-
2013
- 2013-09-25 WO PCT/JP2013/075840 patent/WO2014080691A1/ja active Application Filing
- 2013-09-25 US US14/435,804 patent/US20150292493A1/en not_active Abandoned
- 2013-09-25 CN CN201390000891.XU patent/CN204663787U/zh not_active Expired - Fee Related
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS50131110A (ja) * | 1974-04-03 | 1975-10-17 | ||
JPS5927162U (ja) * | 1982-08-11 | 1984-02-20 | 三菱重工業株式会社 | 往復動圧縮機 |
JPS62288374A (ja) * | 1986-06-04 | 1987-12-15 | Nippo Giken Kogyo Kk | カム駆動によるピストンポンプ |
JPH0226780U (ja) * | 1988-08-10 | 1990-02-21 | ||
JPH04175474A (ja) * | 1990-11-08 | 1992-06-23 | Matsushita Electric Works Ltd | ウォーターポンプ |
JPH06229369A (ja) * | 1992-05-22 | 1994-08-16 | Tatsuji Motomiya | 送液ポンプ |
JPH10318128A (ja) * | 1997-05-21 | 1998-12-02 | Nippon Soken Inc | ポンプ |
JP2001263223A (ja) * | 2000-03-23 | 2001-09-26 | Kyoritsu Kiko Kk | 二連プランジャポンプ |
JP2011052549A (ja) * | 2009-08-31 | 2011-03-17 | Oken Ltd | ピストンポンプおよびその設置方法 |
Also Published As
Publication number | Publication date |
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US20150292493A1 (en) | 2015-10-15 |
CN204663787U (zh) | 2015-09-23 |
JP2014101843A (ja) | 2014-06-05 |
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