EP2770218A2 - Unité d'actionneur rotatif bidirectionnel électro-hydraulique autonome - Google Patents

Unité d'actionneur rotatif bidirectionnel électro-hydraulique autonome Download PDF

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Publication number
EP2770218A2
EP2770218A2 EP14156685.1A EP14156685A EP2770218A2 EP 2770218 A2 EP2770218 A2 EP 2770218A2 EP 14156685 A EP14156685 A EP 14156685A EP 2770218 A2 EP2770218 A2 EP 2770218A2
Authority
EP
European Patent Office
Prior art keywords
duct
hydraulic
pump
cylinder
valve
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.)
Withdrawn
Application number
EP14156685.1A
Other languages
German (de)
English (en)
Other versions
EP2770218A3 (fr
Inventor
Eddy Schuurman
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Enerpac Tool Group Corp
Original Assignee
Actuant Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Actuant Corp filed Critical Actuant Corp
Publication of EP2770218A2 publication Critical patent/EP2770218A2/fr
Publication of EP2770218A3 publication Critical patent/EP2770218A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F15B15/18—Combined units comprising both motor and pump
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/025—Installations or systems with accumulators used for thermal compensation, e.g. to collect expanded fluid and to return it to the system as the system fluid cools down
    • 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
    • F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
    • F15B15/06—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement
    • F15B15/065—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement the motor being of the rack-and-pinion type
    • 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
    • F15B15/24—Other details, e.g. assembly with regulating devices for restricting the stroke
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/3051—Cross-check valves
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3052—Shuttle valves
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves

Definitions

  • the present invention relates to a self-contained electro-hydraulic bidirectional rotary actuator unit adapted for limited arc actuation of an object.
  • the unit is adapted for quarter turn actuation, e.g. of a valve, e.g. of a pipeline valve.
  • the present invention provides a self-contained electro-hydraulic bidirectional rotary actuator unit according to claim 1.
  • the inventive unit due to the absence of air in the hydraulic circuit, can be mounted in any desired orientation.
  • the unit can be mounted above a valve, below a valve, or with the unit mainly in vertical orientation.
  • the hydraulic fluid may be a biodegradable hydraulic fluid.
  • the absence of air warrants that the biodegradable fluid will not deteriorate due to oxidation.
  • the thermal pressure relief valves are set in practice to open at such a pressure that no damage is done to any seals, e.g. around the pistons, so that no leakage will occur in case of the unit becoming very hot, e.g. when exposed to the sun.
  • the opening pressure of these valves is set at about 300 bars.
  • an additional pressure relief valve is connected to the first duct and an additional pressure relief valve is connected to the second duct.
  • Each of these additional pressure relief valves is connected to the low pressure duct, and each of these additional pressure relief valves is embodied to open at a hydraulic pressure in the respective first or second duct which is significantly below the hydraulic pressure at which the respective first and second thermal expansion pressure relief valves open.
  • the additional pressure relief valves act to govern the maximum torque that can be caused by means of the unit, and the thermal expansion relief valves act as a safeguard in case of excessive pressure built-up due to overheating of the unit.
  • the additional pressure relief valves are set to open at a hydraulic pressure that is between 50 and 125 bars below the opening pressure of the thermal expansion pressure relief valves, e.g. said additional pressure relief valves being embodied to open at a pressure between 150 and 225 bars.
  • the hydraulic circuit comprises a manually operable relief valve interconnecting, when opened manually, the first and second ducts between the respective pilot-operated check valve and respective hydraulic cylinder.
  • a manually operable relief valve interconnecting, when opened manually, the first and second ducts between the respective pilot-operated check valve and respective hydraulic cylinder.
  • This allows direct displacement of hydraulic fluid from the one cylinder to the other as the pinion, and thereby the rack, is moved by external force.
  • the pinion shaft has a protruding portion with parallel faces adapted to apply a wrench on the pinion shaft in order to rotate the pinion shaft in an emergency, e.g. loss of electric power or failure of the motor and/or pump.
  • the accumulator comprises a bore and a spring loaded piston therein defining the variable volume chamber, e.g. said accumulator being formed in the pump housing.
  • the electric motor is arranged parallel to an axis through the linearly aligned first and second cylinders.
  • the pump housing is bolted onto a lateral side of the cylinder housing.
  • the electric motor is located along said same lateral side of the cylinder housing.
  • first and second thermal expansion relief valves are arranged in the cylinder housing, and the pilot-operated check valves and - if present - the additional pressure relief valves are arranged in the pump housing.
  • the pump is a radial piston pump.
  • the shaft supporting the pinion is further provided with an angle limiter member providing two abutment faces at a defined angular spacing relative to the shaft axis, wherein the cylinder housing is provided with two threaded bores each having threaded angle adjuster rod therein, each adjuster rod being engageable by one of said abutment faces to determine an angular limit position of the pinion shaft, wherein screwing an angle adjuster rod into or out of the corresponding threaded bore adjusts the angular limit position relative to the cylinder housing.
  • the cylinder housing is a rectangular aluminum block and the first and second cylinders are formed by one circular bore extending between opposed end faces of the block, wherein the bore is closed at each end thereof by an end cap having one or more sealing rings thereon.
  • the invention also relates to the combination of a unit as described herein and a valve, e.g. a pipeline valve, a valve stem of the valve being connected to the pinion shaft.
  • a valve e.g. a pipeline valve
  • a self-contained electro-hydraulic bidirectional rotary actuator unit 1 adapted for limited arc actuation of an object will be discussed.
  • the unit 1 is adapted for quarter turn actuation of a valve, e.g. a pipeline valve.
  • the unit 1 comprises a hydraulic rotary actuator with a cylinder housing 2 having two linearly aligned, opposed, single-acting first and second hydraulic cylinders 3, 4 therein.
  • the housing 2 is a rectangular aluminum block.
  • the first and second cylinders 3, 4 are formed by one circular bore extending between opposed end faces of the block.
  • the bore is closed at each end thereof by an end cap 3a, 4a having one or more sealing rings thereon, which end caps defined the bottom of the respective cylinder 3, 4.
  • Each cylinder is provided with a piston 5, 6 that sealingly fits in the bore in the housing 2.
  • These two aligned pistons 5, 6 are interconnected by a rod 7 that forms a toothed rack.
  • the cylinder housing 2 supports a pinion 8 that meshes with the rack on the rod 7.
  • the pinion is supported on a rotary shaft 9 in the cylinder housing 2.
  • This shaft 9 has an output end 10 that is adapted for connection to an object to be rotated about a limited arc.
  • the output end 10 has a blind hole into which a stem, e.g. a valve stem, can be inserted.
  • the unit 1 further comprises a bidirectional hydraulic pump 15, here a radial piston pump, having a pump housing 16.
  • the pump housing is an aluminum block that is bolted, e.g. by bolt 17, directly onto a lateral side of the cylinder housing 2.
  • the unit 1 also comprises an electric motor 20 that is connected to the pump housing and drives the pump 15.
  • the hydraulic circuit of the unit 1 comprises ducts that are provided in the pump housing 16 and the cylinder housing 2. As the pump housing 16 is connected directly to the cylinder housing 2 any hydraulic fluid ducts in the pump housing 16 and cylinder housing 2 interconnect directly without intermediate tubing.
  • the bidirectional hydraulic radial piston pump 15 has a first pump port 17 and a second pump port 18. In operation of the unit, one port acts as pressure port and discharges pressurized hydraulic fluid into the connected first or second duct and the other as suction port depending on the rotation direction of the electric motor 20.
  • the hydraulic circuit comprises a first duct 30 connecting the first pump port 17 through the pump housing and the cylinder housing to the first cylinder 3.
  • a second duct 31 through the pump housing and the cylinder housing connects the second pump port 18 to the second cylinder 4.
  • a first pilot operated check valve 33 is arranged in the first duct 30.
  • a second pilot operated check valve 34 is arranged in the second duct 31.
  • Each of these pilot operated check valves has a pilot line 33a, 34a to the other of said first and second ducts 30, 31, so that the one check valve opens if the other duct is used to supply pressurized hydraulic fluid to one cylinder and hydraulic fluid can flow out of the other cylinder via the opened pilot-operated check valve.
  • the pilot line 33a connects to the duct 31 between the pump port 18 and the check valve 34.
  • the other pilot line 34a connects to the duct 30 between the check valve 34 and the cylinder 3.
  • the line 34a connects to the duct 30 between the pump port 17 and the check valve 33, which may be done to achieve a more rapid closing action of the check valve 34 upon stopping of the pump, e.g. halfway through actuation of a pipeline valve.
  • an additional manually operable relief valve in addition to valve 70, may be provided for between a pilot line 33a, 34a on the one hand and a high pressure duct between the check valve and a cylinder on the other hand. This allows for opening of a check valve and will then render one of the valves 44, 45 active to limit the actual fluid pressure, e.g. if any imbalance is present between the two cylinders.
  • a first thermal expansion pressure relief valve 40 is connected to the first duct 30, between the first pilot-operated check valve 34 and the first cylinder 3 as this part of the duct 30 is effectively sealed by the check valve 34 during standstill of the shaft 9 of the unit 1. Thermal effects may then cause the trapped hydraulic fluid to develop an excessive pressure, potentially causing leakage, e.g. along the piston of the respective cylinder, which is now prevented due to the valve 40.
  • a second thermal expansion pressure relief valve 41 is connected to the second duct 31 between the second pilot-operated check valve 34 and the second cylinder 4.
  • the hydraulic circuit further comprises a low pressure duct 46 to which these first and second thermal expansion pressure relief valves 40, 41 each connect, such that upon opening of one or both of said thermal expansion pressure relief valves 40, 41 due to thermal expansion hydraulic fluid is relieved from the respective first or second duct into this low pressure duct 46.
  • the hydraulic circuit further comprises a suction shuttle valve 50, which is arranged between this low pressure duct 46 on the one hand and each of the first and second pump ports 17, 18 on the other hand.
  • This suction shuttle valve 50 is adapted to allow the suction port to retrieve hydraulic fluid from the low pressure duct 46 and separates the actual pressure port of the pump 15 from the low pressure duct 46.
  • the hydraulic circuit further comprises an accumulator 60 having a spring loaded variable hydraulic chamber 61 connecting to the low pressure duct 46. This accumulator absorbs changes in hydraulic fluid volume due to thermal expansion.
  • the hydraulic circuit is completely filled with hydraulic fluid and is devoid of air.
  • an additional pressure relief valve 44 is connected to the first duct 30 and an additional pressure relief valve 45 is connected to the second duct 31. These additional pressure relief valves 44, 45 are each connected to the low pressure duct 46.
  • Each of these additional pressure relief valves 44, 45 is embodied to open at a hydraulic pressure in the respective first or second duct 30, 31 which is significantly below the hydraulic pressure at which the first and second thermal expansion pressure relief valves 40, 41 open.
  • these additional pressure relief valves 44, 45 are set to open at a hydraulic pressure that is between 50 and 125 bars below the opening pressure of the thermal expansion pressure relief valves 40, 41.
  • these additional pressure relief valves are set to open at a pressure between 150 and 225 bars.
  • the hydraulic circuit comprises a manually operable relief valve 70 interconnecting, when opened manually, the first and second ducts 30, 31 between the respective pilot-operated check valve 33, 34 and the respective hydraulic cylinder 3, 4 so that hydraulic fluid may flow directly from the one cylinder into the other cylinder.
  • the shaft 9 is provided with a protrusion 9b outside the housing 2 which may e.g. have parallel faces to be engaged by a wrench.
  • the accumulator 60 comprises a bore and a spring loaded piston 62 therein defining the variable volume chamber 61.
  • the accumulator is formed in the pump housing 16, in the alternative one could arrange the accumulator within the cylinder housing 2.
  • a metallic spring is preferred to load the piston 62, but in an alternative a gas spring may be provided.
  • the volume of the chamber 61 can be very small, e.g. as small as 1.5 cc.
  • the electric motor 20 is arranged alongside a lateral side of the cylinder housing 2, parallel to an axis through the linearly aligned first and second cylinders 3, 4.
  • the pump housing 16 is bolted onto the same lateral side of the cylinder housing 2.
  • first and second thermal expansion relief valves 40, 41 are arranged in the cylinder housing 2.
  • the pilot-operated check valves 33, 34 and the additional pressure relief valves 44, 45 are arranged in the pump housing 16.
  • the shaft 9 supporting the pinion 8 is further provided with an angle limiter member 80 providing two abutment faces 81, 82 at a defined angular spacing relative to the shaft axis.
  • the cylinder housing is provided with two threaded bores 83, 84 each having a threaded angle adjuster rod 85, 86 therein.
  • Each adjuster rod is with its inner end engageable by one of the abutment faces in order to determine an angular limit position of the pinion shaft 9.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve Device For Special Equipments (AREA)
  • Actuator (AREA)
EP14156685.1A 2013-02-26 2014-02-26 Unité d'actionneur rotatif bidirectionnel électro-hydraulique autonome Withdrawn EP2770218A3 (fr)

Applications Claiming Priority (1)

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US201361769363P 2013-02-26 2013-02-26

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EP2770218A2 true EP2770218A2 (fr) 2014-08-27
EP2770218A3 EP2770218A3 (fr) 2017-04-26

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104500492A (zh) * 2014-12-17 2015-04-08 北京航空航天大学 双蝶形协同配流泵驱动的电静液作动器
EP3425213A1 (fr) * 2017-07-03 2019-01-09 LEONARDO S.p.A. Soupape de sécurité et procédé de commande d'un circuit hydraulique
US10982743B2 (en) 2016-09-16 2021-04-20 Bosch Rexroth Corporation Rotary electrohydraulic actuator
WO2021112750A1 (fr) * 2019-12-05 2021-06-10 Saab Ab Actionneur linéaire électro-hydraulique et procédé de commande du fonctionnement d'un tel actionneur
US11384777B2 (en) 2018-08-21 2022-07-12 Siemens Energy, Inc. Double-acting hydraulic actuator with different pumps for each actuation direction
WO2022148668A1 (fr) * 2021-01-08 2022-07-14 Robert Bosch Gmbh Unité de transmission hydraulique, en particulier pour une utilisation en haute mer
CN115324949A (zh) * 2022-07-20 2022-11-11 中国兵器装备集团上海电控研究所 多功能负载模拟与能量回收装置
CN115853931A (zh) * 2023-03-03 2023-03-28 太原矿机电气股份有限公司 一种限速值可调的限速制动控制系统

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3605409A (en) 1969-04-01 1971-09-20 Hydra Power Inc Hydraulic actuator

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US4630441A (en) * 1984-09-04 1986-12-23 The Boeing Company Electrohydraulic actuator for aircraft control surfaces
DE9406760U1 (de) * 1994-04-22 1994-08-18 Paul Pleiger Maschinenfabrik GmbH & Co KG, 58452 Witten Kompakte Antriebseinheit für Armaturen, insbesondere im Schiffbau
CA2279435A1 (fr) * 1999-07-30 2001-01-30 Michael Alexander Duff Actionneur lineaire
US6446539B1 (en) * 2000-12-14 2002-09-10 Leopold J. Niessen Dual end stop actuator and method
EP1548289A1 (fr) * 2003-12-22 2005-06-29 Young & Franklin Actionneur électro-hydrostatique
JP4820552B2 (ja) * 2005-01-19 2011-11-24 カヤバ工業株式会社 油圧制御装置、及びその油圧制御装置を備える油圧駆動ユニット
US7640736B2 (en) * 2005-07-22 2010-01-05 Ashradan Holdings Ltd. Self-contained hydraulic actuator system

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3605409A (en) 1969-04-01 1971-09-20 Hydra Power Inc Hydraulic actuator

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104500492A (zh) * 2014-12-17 2015-04-08 北京航空航天大学 双蝶形协同配流泵驱动的电静液作动器
CN104500492B (zh) * 2014-12-17 2016-11-30 北京航空航天大学 双蝶形协同配流泵驱动的电静液作动器
US10982743B2 (en) 2016-09-16 2021-04-20 Bosch Rexroth Corporation Rotary electrohydraulic actuator
US10935052B2 (en) 2017-07-03 2021-03-02 Leonardo S.P.A. Safety valve and method for controlling a hydraulic circuit
CN110753795A (zh) * 2017-07-03 2020-02-04 列奥纳多股份公司 用于控制液压回路的安全阀和方法
KR20200055688A (ko) * 2017-07-03 2020-05-21 레오나르도 에스피에이 유압 회로 제어를 위한 안전밸브 및 방법
WO2019007815A1 (fr) * 2017-07-03 2019-01-10 Leonardo S.P.A. Soupape de sûreté et procédé de commande de circuit hydraulique
EP3425213A1 (fr) * 2017-07-03 2019-01-09 LEONARDO S.p.A. Soupape de sécurité et procédé de commande d'un circuit hydraulique
RU2755853C2 (ru) * 2017-07-03 2021-09-22 ЛЕОНАРДО С.п.А. Предохранительный клапан и способ управления гидравлическим контуром
US11384777B2 (en) 2018-08-21 2022-07-12 Siemens Energy, Inc. Double-acting hydraulic actuator with different pumps for each actuation direction
WO2021112750A1 (fr) * 2019-12-05 2021-06-10 Saab Ab Actionneur linéaire électro-hydraulique et procédé de commande du fonctionnement d'un tel actionneur
WO2022148668A1 (fr) * 2021-01-08 2022-07-14 Robert Bosch Gmbh Unité de transmission hydraulique, en particulier pour une utilisation en haute mer
US20240052944A1 (en) * 2021-01-08 2024-02-15 Robert Bosch Gmbh Hydraulic Transmission Unit, Particularly for Deep-Sea Use
CN115324949A (zh) * 2022-07-20 2022-11-11 中国兵器装备集团上海电控研究所 多功能负载模拟与能量回收装置
CN115853931A (zh) * 2023-03-03 2023-03-28 太原矿机电气股份有限公司 一种限速值可调的限速制动控制系统

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