WO2015002055A1 - 流体圧シリンダ - Google Patents
流体圧シリンダ Download PDFInfo
- Publication number
- WO2015002055A1 WO2015002055A1 PCT/JP2014/066931 JP2014066931W WO2015002055A1 WO 2015002055 A1 WO2015002055 A1 WO 2015002055A1 JP 2014066931 W JP2014066931 W JP 2014066931W WO 2015002055 A1 WO2015002055 A1 WO 2015002055A1
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- WIPO (PCT)
- Prior art keywords
- piston
- chamber
- fluid pressure
- inner chamber
- pressure cylinder
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1457—Piston rods
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/149—Fluid interconnections, e.g. fluid connectors, passages
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
- B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
- B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
- B66F9/075—Constructional features or details
- B66F9/20—Means for actuating or controlling masts, platforms, or forks
- B66F9/22—Hydraulic devices or systems
Definitions
- the present invention relates to a fluid pressure cylinder.
- a device for raising and lowering a load such as a forklift is provided with a hydraulic cylinder that expands and contracts by supplying and discharging hydraulic pressure.
- the hydraulic cylinder is a single-acting type and expands by supplying hydraulic pressure to the hydraulic chamber in the cylinder tube, and contracts by discharging the hydraulic pressure in the hydraulic chamber.
- JP9-317717A describes a hydraulic cylinder having a cushion function that reduces the impact by suppressing the rising speed of the piston when reaching the stroke end.
- the cushion function is realized by an orifice provided in the vicinity of the piston of the piston rod of the hydraulic cylinder and communicating between the inside and outside of the piston rod. That is, in the vicinity of the stroke end, the cushion oil, which is the hydraulic oil between the cylinder tube and the piston rod, flows into the piston rod through the orifice, thereby creating a flow resistance in the hydraulic oil and increasing the piston rising speed. Reduce.
- the piston has a built-in communication path that connects the inside of the piston rod and the hydraulic chamber, and a check valve that is provided in the communication path and allows only a flow from the inside of the piston rod to the hydraulic chamber.
- the cushion oil passes down the oil seal of the piston and leaks to the hydraulic chamber side.
- the hydraulic oil cannot be supplied from the hydraulic chamber into the piston rod by the action of the check valve, so there is a possibility that the cushion oil is insufficient.
- An object of the present invention is to provide a fluid pressure cylinder capable of preventing a shortage of cushion oil.
- the piston extends upward in response to the supply of the working fluid to the lower drive chamber of the piston sliding in the cylinder tube, and extends before the piston reaches the stroke end of the extension side.
- a single-acting fluid pressure cylinder having a cushion function that suppresses operation, and is connected to the upper part of the piston and defines a rod inner chamber between the piston and the piston rod and the cylinder tube.
- a cushion chamber whose volume decreases as the fluid pressure cylinder extends, a communication passage formed in the piston rod that communicates the cushion chamber and the rod inner chamber, and a cushion passage formed below the communication passage.
- a throttle passage that provides a cushion function by giving resistance to the flow of working fluid to the rod inner chamber, and the rod inner chamber and drive chamber provided in the piston communicate with each other And a check valve that allows only the flow of working fluid from the rod inner chamber to the drive chamber, and a check function that is formed in the piston and guides the pressure in the cushion chamber to the check valve as a pilot pressure. And a pilot passage for releasing the fluid pressure cylinder.
- FIG. 1 is a cross-sectional view showing a fluid pressure cylinder according to a first embodiment of the present invention.
- FIG. 2 is a cross-sectional view showing the fluid pressure cylinder according to the first embodiment of the present invention.
- FIG. 3 is a cross-sectional view showing a fluid pressure cylinder according to a second embodiment of the present invention.
- FIG. 4 is a cross-sectional view showing a fluid pressure cylinder according to a second embodiment of the present invention.
- FIG. 1 is a cross-sectional view showing a fluid pressure cylinder 100 in the present embodiment.
- the fluid pressure cylinder 100 includes a cylindrical cylinder tube 10, a piston 20 slidably fitted in the cylinder tube 10, a piston rod 30 connected to an upper portion of the piston 20, and an upper end of the cylinder tube 10. And a cylinder head 40 that slidably supports the piston rod 30 so as to be slidable.
- the fluid pressure cylinder 100 is used as a lift cylinder that lifts and lowers a load in a lifting device such as a forklift.
- a lifting device such as a forklift.
- the cylinder tube 10 and the piston rod 30 are fixed to a vehicle body (not shown).
- the fluid pressure cylinder 100 is used in a direction in which the piston rod 30 is disposed on the top of the piston 20 and the axial direction of the cylinder tube 10 substantially coincides with the vertical direction.
- the drive chamber 1 is defined below the piston 20 in the cylinder tube 10.
- a supply / discharge passage 50 is connected to the drive chamber 1, and working fluid from a fluid pressure source (not shown) is supplied / discharged to the drive chamber 1 through the supply / discharge passage 50.
- a fluid pressure source not shown
- the working fluid is, for example, oil or other water-soluble alternative liquid.
- the piston rod 30 is formed in a bottomed cylindrical shape in which one end which is an open end is connected to the piston 20 and the other end is located outside the cylinder tube 10.
- a rod inner chamber 2 is defined between the piston rod 30 and the piston 20.
- a reduced diameter portion 31 having an inner diameter smaller than other portions is formed at the bottom of the piston rod 30 (upper end portion in FIG. 1).
- a space defined in the reduced diameter portion 31 is also a part of the rod inner chamber 2.
- the cylinder head 40 is attached to the upper opening end of the cylinder tube 10 and pivotally supports the piston rod 30.
- An annular cushion chamber 3 is defined between the cylinder tube 10 and the outer peripheral surface of the piston rod 30.
- the volume of the cushion chamber 3 decreases as the fluid pressure cylinder 100 extends, and increases as the fluid pressure cylinder 100 contracts.
- the volume of the rod inner chamber 2 is set to be equal to or greater than the volume of the cushion chamber 3 when the fluid pressure cylinder 100 is maximally contracted so that the cushion chamber 3 is maximized.
- a communication passage 32 that connects the cushion chamber 3 and the rod inner chamber 2 is formed on the side surface of the piston rod 30. Further, a throttle passage 33 that connects the cushion chamber 3 and the rod inner chamber 2 is formed on the side surface of the piston rod 30 and below the communication passage 32. The throttle passage 33 provides resistance to the flow of the working fluid from the cushion chamber 3 to the rod inner chamber 2. Thus, a cushion function that suppresses the extension operation of the fluid pressure cylinder 100 before the piston 20 reaches the extension stroke end is exhibited.
- the rod inner chamber 2 in the piston rod 30 accommodates a free piston 60 that can slide up and down the rod inner chamber 2.
- the free piston 60 as the separating member has a sliding contact portion 61 that is in sliding contact with the inner wall surface of the rod inner chamber 2, and a small diameter portion 62 that is disposed below the sliding contact portion 61 and has a smaller diameter than the sliding contact portion 61.
- a seal ring 63 that seals the space above and below the free piston 60 is fitted on the outer periphery of the sliding contact portion 61.
- a working fluid is filled below the free piston 60, and a gas (for example, air) is stored above the free piston 60. That is, the free piston 60 slides up and down in accordance with the level of the working fluid in the rod inner chamber 2 from the lowest point in contact with the upper surface of the piston 20.
- the axial dimension of the small diameter portion 62 is set so that the opening of the communication path 32 faces the small diameter portion 62 when the free piston 60 is at the lowest point.
- a seal ring 21 that seals between the drive chamber 1 and the cushion chamber 3 is fitted on the outer periphery of the piston 20.
- the seal ring 21 suppresses the working fluid in the drive chamber 1 from leaking into the cushion chamber 3 and suppresses the working fluid in the cushion chamber 3 from leaking into the drive chamber 1.
- the piston 20 incorporates a check valve 23 that communicates the rod inner chamber 2 and the drive chamber 1 and has a check function that allows only the flow of the working fluid from the rod inner chamber 2 to the drive chamber 1.
- the check valve 23 is closed by a check function when the working fluid pressure in the rod inner chamber 2 is lower than the working fluid pressure in the driving chamber 1, and the working fluid pressure in the rod inner chamber 2 is set to the working fluid pressure in the driving chamber 1. Opens when higher.
- a pilot passage 24 is formed in the piston 20 to guide the working fluid pressure in the cushion chamber 3 to the check valve 23 as a pilot pressure.
- the pilot pressure supplied from the cushion chamber 3 via the pilot passage 24 exceeds a predetermined valve opening pressure, the check function of the check valve 23 is released and the check valve 23 is opened.
- the space in the cylinder tube 10 is defined inside the drive chamber 1 defined below the piston 20, the cushion chamber 3 defined outside the piston rod 30, and the inside of the piston rod 30. And the rod inner chamber 2.
- the driving chamber 1 is a pressure chamber filled with a working fluid, and the pressure fluctuates according to the supply and discharge of the working fluid supplied from a fluid pressure source.
- the cushion chamber 3 is a pressure chamber filled with a working fluid, and the volume increases and decreases according to the sliding of the piston 20.
- the rod inner chamber 2 is a pressure chamber that is filled with working fluid and air with the free piston 60 as a boundary, and exhibits a pressure accumulation function when the free piston 60 slides according to a change in pressure.
- FIG. 1 shows a state in which the working fluid is supplied from the fluid pressure source to the driving chamber 1 through the supply / discharge passage 50. Supplying the working fluid raises the pressure in the driving chamber 1 and drives the piston 20 and the piston rod 30 upward. As the piston 20 rises, the volume of the cushion chamber 3 decreases, so that the working fluid corresponding to the decreasing volume flows into the rod inner chamber 2 through the communication path 32.
- the pressure in the rod inner chamber 2 increases as the pressure in the cushion chamber 3 increases.
- the free piston 60 slides upward while compressing air.
- the communication path 32 is closed by the cylinder head 40 as shown in FIG.
- the working fluid corresponding to the volume reduction of the cushion chamber 3 due to the rising of the piston 20 flows into the rod inner chamber 2 through the throttle passage 33. Since the throttle passage 33 provides resistance to the flow of the working fluid from the cushion chamber 3 to the rod inner chamber 2, the pressure in the cushion chamber 3 increases and the piston 20 is prevented from rising. Thereby, a cushion function is exhibited. Further, at this time, the free piston 60 rises and high-pressure air is stored in the reduced diameter portion 31.
- the cushion function is exhibited until the top dead center position of the piston 20, that is, the extension stroke end of the fluid pressure cylinder 100 is reached, so that the impact when the piston 20 collides with the cylinder head 40 is reduced.
- the pressure in the cushion chamber 3 is supplied to the check valve 23 through the pilot passage 24.
- the pilot pressure supplied to the check valve 23 exceeds a predetermined valve opening pressure due to an increase in pressure in the cushion chamber 3, the check function of the check valve 23 is released.
- the working fluid in the drive chamber 1 flows into the rod inner chamber 2 via the check valve 23.
- the piston 20 and the piston rod 30 are lowered by their own weight. Since the volume of the cushion chamber 3 increases as the piston 20 descends, the working fluid in the rod inner chamber 2 flows into the cushion chamber 3 via the throttle passage 33 and the communication passage 32. As the liquid level of the working fluid in the rod inner chamber 2 decreases, the free piston 60 slides downward. At this time, the pressure stored in the air when the fluid pressure cylinder 100 is extended promotes the lowering of the free piston 60.
- the piston 20 descends, the working fluid in the rod inner chamber 2 flows into the cushion chamber 3, but the volume of the rod inner chamber 2 is set to be equal to or larger than the volume of the cushion chamber 3.
- the free piston 60 is not lowered to the lowest point before the cylinder 100 is in the most contracted state, and the piston 20 cannot be lowered.
- the working fluid in the drive chamber 1 is supplied to the rod inner chamber via the check valve 23. 2 can be supplied. Therefore, even if the working fluid leaks from the cushion chamber 3 to the drive chamber 1 through the seal ring 21 of the piston 20, the working fluid can be replenished to the rod inner chamber 2 every time the hydraulic cylinder 100 is extended. Therefore, it is possible to prevent the cushioning function from being lowered due to insufficient working fluid in the cushion chamber 3.
- the free piston 60 is accommodated in the rod inner chamber 2 and the free piston 60 separates the rod inner chamber 2 into working fluid and air, the working fluid in the rod inner chamber 2 increases or decreases as the fluid pressure cylinder 100 expands and contracts. It is possible to prevent the working fluid from foaming.
- the rod inner chamber 2 can function as an accumulator, and the free piston 60 accumulates pressure when the fluid pressure cylinder 100 contracts.
- a smooth operation can be promoted by urging the air downward by the air.
- the volume of the rod inner chamber 2 is set to be equal to or larger than the volume of the cushion chamber 3 at the time of the maximum contraction of the fluid pressure cylinder 100 at which the cushion chamber 3 is maximized.
- FIG. 3 is a cross-sectional view showing the fluid pressure cylinder 200 in the present embodiment.
- a boot 170 described later is provided instead of the free piston 60 of the first embodiment, and the structure of the rod inner chamber 2 is different from that of the first embodiment, and other structures are the same. Therefore, below, a different part from 1st Embodiment is demonstrated.
- the piston rod 130 of the present embodiment does not have the reduced diameter portion 31 as in the first embodiment, and is formed in a bottomed cylindrical shape having a uniform inner diameter along the axial direction.
- a boot 170 filled with air is housed in the piston rod 130 instead of the free piston 60.
- the boot 170 as an isolation member is formed of a material that can be expanded and contracted, such as a resin or a thin metal.
- the volume of the boot 170 changes according to the pressure change in the rod inner chamber 2. That is, when the pressure in the rod inner chamber 2 increases, the boot 170 contracts, and when the pressure in the rod inner chamber 2 decreases, the boot 170 expands.
- the vertical dimension of the boot 170 is set so as not to block the opening of the communication path 32. As a result, the communication passage 32 and the throttle passage 33 always open below the boot 170 regardless of the expansion / contraction state of the boot 170.
- FIG. 3 shows a state in which the working fluid is supplied from the fluid pressure source to the driving chamber 1 through the supply / discharge passage 50. Supplying the working fluid raises the pressure in the drive chamber 1 and drives the piston 20 and the piston rod 130 upward. As the piston 20 rises, the volume of the cushion chamber 3 decreases, so that the working fluid corresponding to the decreasing volume flows into the rod inner chamber 2 through the communication path 32.
- the pressure in the rod inner chamber 2 increases as the pressure in the cushion chamber 3 increases.
- the boot 170 contracts while compressing air.
- the communication path 32 is closed by the cylinder head 40 as shown in FIG.
- the working fluid corresponding to the volume reduction of the cushion chamber 3 due to the rising of the piston 20 flows into the rod inner chamber 2 through the throttle passage 33. Since the throttle passage 33 provides resistance to the flow of the working fluid from the cushion chamber 3 to the rod inner chamber 2, the pressure in the cushion chamber 3 increases and the piston 20 is prevented from rising. Thereby, a cushion function is exhibited. Further, at this time, high-pressure air is stored in the boot 170.
- the cushion function is exhibited until the top dead center position of the piston 20, that is, the extension stroke end of the fluid pressure cylinder 200 is reached, so that the impact when the piston 20 collides with the cylinder head 40 is reduced.
- the pressure in the cushion chamber 3 is supplied to the check valve 23 through the pilot passage 24.
- the pilot pressure supplied to the check valve 23 exceeds a predetermined valve opening pressure due to an increase in pressure in the cushion chamber 3, the check function of the check valve 23 is released.
- the working fluid in the drive chamber 1 flows into the rod inner chamber 2 via the check valve 23.
- the piston 20 and the piston rod 130 are lowered by their own weight. Since the volume of the cushion chamber 3 increases as the piston 20 descends, the working fluid in the rod inner chamber 2 flows into the cushion chamber 3 via the throttle passage 33 and the communication passage 32. As the liquid level of the working fluid in the rod inner chamber 2 decreases, the boot 170 expands.
- the volume of the rod inner chamber 2 is set to be equal to or larger than the volume of the cushion chamber 3.
- the boot 170 does not expand until the volume becomes the same as that of the rod inner chamber 2, and the piston 20 cannot be lowered.
- the boot 170 Since the boot 170 is accommodated in the rod inner chamber 2 and the working fluid in the rod inner chamber 2 is separated from the air by the boot 170, the working fluid in the rod inner chamber 2 increases or decreases as the fluid pressure cylinder 200 expands and contracts. It is possible to prevent the working fluid from foaming.
- the rod inner chamber 2 can function as an accumulator, and the rod is compressed by the air accumulated in the boot 170 when the fluid pressure cylinder 200 contracts. Smooth operation can be promoted by causing the working fluid in the inner chamber 2 to flow into the cushion chamber 3 more smoothly.
- the free piston 60 or the boot 170 is used to separate the working fluid in the rod inner chamber 2 from the air is illustrated, but the working fluid and the air may be separated by other structures. Good.
- the free piston 60 or the boot 170 is provided in the rod inner chamber 2 to prevent foaming of the working fluid, but the lack of cushion oil can be prevented without providing these members. It is possible to do.
- the volume of the rod inner chamber 2 is set so that it may become more than the volume of the cushion chamber 3 at the time of the maximum contraction of the fluid pressure cylinders 100 and 200 in which the cushion chamber 3 becomes the maximum, If the fluid pressure cylinder 20 is a type that does not descend to the bottom of the cylinder tube 10, the volume of the rod inner chamber 2 may be smaller than the maximum volume of the cushion chamber 3.
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Abstract
Description
Claims (5)
- シリンダチューブ内を摺動するピストンの下側の駆動室への作動流体の供給に応じて上方に伸長するとともに、前記ピストンが伸側のストローク端に達する前に伸長作動を抑制するクッション機能を有する単動型の流体圧シリンダであって、
前記ピストンの上部に連結されて前記ピストンとの間にロッド内室を画成するピストンロッドと、
前記ピストンロッドと前記シリンダチューブとの間に画成され、前記流体圧シリンダの伸長に応じて容積が減少するクッション室と、
前記ピストンロッドに形成され前記クッション室と前記ロッド内室とを連通する連通路と、
前記連通路より下方に形成され前記クッション室から前記ロッド内室への作動流体の流れに抵抗を与えることで前記クッション機能を発揮する絞り通路と、
前記ピストンに設けられ前記ロッド内室と前記駆動室とを連通するとともに前記ロッド内室から前記駆動室への作動流体の流れのみを許容する逆止機能を有する逆止弁と、
前記ピストンに形成され前記クッション室の圧力をパイロット圧として前記逆止弁に導くことで逆止機能を解除させるパイロット通路と、
を備える流体圧シリンダ。 - 請求項1に記載の流体圧シリンダであって、
前記ロッド内室に収容され前記ロッド内室を作動流体とエアとに隔てるとともに前記ロッド内室の作動流体圧に応じてエアの体積を増減させる隔離部材をさらに備える、
流体圧シリンダ。 - 請求項2に記載の流体圧シリンダであって、
前記隔離部材は、前記ロッド内室を上下に摺動可能であって上方にエアを蓄えるフリーピストンである、
流体圧シリンダ。 - 請求項2に記載の流体圧シリンダであって、
前記隔離部材は、内部にエアを蓄える膨縮可能なブーツである、
流体圧シリンダ。 - 請求項1に記載の流体圧シリンダであって、
前記ロッド内室の容積は、前記流体圧シリンダの最収縮時における前記クッション室の容積以上である、
流体圧シリンダ。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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US14/898,152 US9638221B2 (en) | 2013-07-05 | 2014-06-26 | Fluid pressure cylinder |
CN201480036316.4A CN105358843B (zh) | 2013-07-05 | 2014-06-26 | 流体压缸 |
KR1020157036064A KR101721792B1 (ko) | 2013-07-05 | 2014-06-26 | 유체압 실린더 |
Applications Claiming Priority (2)
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JP2013-141622 | 2013-07-05 | ||
JP2013141622A JP5876855B2 (ja) | 2013-07-05 | 2013-07-05 | 流体圧シリンダ |
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WO2015002055A1 true WO2015002055A1 (ja) | 2015-01-08 |
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PCT/JP2014/066931 WO2015002055A1 (ja) | 2013-07-05 | 2014-06-26 | 流体圧シリンダ |
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US (1) | US9638221B2 (ja) |
JP (1) | JP5876855B2 (ja) |
KR (1) | KR101721792B1 (ja) |
CN (1) | CN105358843B (ja) |
WO (1) | WO2015002055A1 (ja) |
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JP7202170B2 (ja) * | 2018-12-18 | 2023-01-11 | Kyb株式会社 | 流体圧緩衝器 |
CN112855098B (zh) * | 2021-02-19 | 2021-10-29 | 大庆市天德忠石油科技有限公司 | 一种堵水管柱 |
KR102529818B1 (ko) * | 2021-07-30 | 2023-05-08 | 대모 엔지니어링 주식회사 | 콤팩트 파워형 실린더 |
JP2024067462A (ja) * | 2022-11-04 | 2024-05-17 | カヤバ株式会社 | 流体圧シリンダユニット |
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2014
- 2014-06-26 KR KR1020157036064A patent/KR101721792B1/ko active IP Right Grant
- 2014-06-26 WO PCT/JP2014/066931 patent/WO2015002055A1/ja active Application Filing
- 2014-06-26 CN CN201480036316.4A patent/CN105358843B/zh active Active
- 2014-06-26 US US14/898,152 patent/US9638221B2/en active Active
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JPH10122205A (ja) * | 1996-10-21 | 1998-05-12 | Kayaba Ind Co Ltd | 油圧シリンダ |
JP2002003199A (ja) * | 2000-06-27 | 2002-01-09 | Toyota Industries Corp | リフトシリンダおよび該リフトシリンダを備えた産業用車両 |
JP2010242804A (ja) * | 2009-04-02 | 2010-10-28 | Kayaba Ind Co Ltd | 液圧シリンダ |
JP2011047446A (ja) * | 2009-08-26 | 2011-03-10 | Kyb Co Ltd | 液圧シリンダ |
Also Published As
Publication number | Publication date |
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KR20160010615A (ko) | 2016-01-27 |
CN105358843B (zh) | 2017-03-15 |
CN105358843A (zh) | 2016-02-24 |
US9638221B2 (en) | 2017-05-02 |
JP5876855B2 (ja) | 2016-03-02 |
KR101721792B1 (ko) | 2017-03-30 |
JP2015014328A (ja) | 2015-01-22 |
US20160138622A1 (en) | 2016-05-19 |
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