EP2325499A1 - Druckentlastungsventil für zwei parallel funktionierende Zylinder - Google Patents

Druckentlastungsventil für zwei parallel funktionierende Zylinder Download PDF

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Publication number
EP2325499A1
EP2325499A1 EP09425475A EP09425475A EP2325499A1 EP 2325499 A1 EP2325499 A1 EP 2325499A1 EP 09425475 A EP09425475 A EP 09425475A EP 09425475 A EP09425475 A EP 09425475A EP 2325499 A1 EP2325499 A1 EP 2325499A1
Authority
EP
European Patent Office
Prior art keywords
conduit
tract
valve
obturator
piloting
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Withdrawn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
EP09425475A
Other languages
English (en)
French (fr)
Inventor
Andrea Storci
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.)
Bosch Rexroth Oil Control SpA
Original Assignee
Bosch Rexroth Oil Control SpA
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 Bosch Rexroth Oil Control SpA filed Critical Bosch Rexroth Oil Control SpA
Priority to EP09425475A priority Critical patent/EP2325499A1/de
Publication of EP2325499A1 publication Critical patent/EP2325499A1/de
Withdrawn legal-status Critical Current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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/226—Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7114—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators
    • F15B2211/7128—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators the chambers being connected in parallel

Definitions

  • each of these cylinders be equipped with a device of its own, typically a block and control valve of the load descent, in order to avoid uncontrolled falls in a case of breakage of the oil pipes. It follows that in order to activate the descending or lowering movement of the load, the command system of the machine has to send a signal, for example a piloting pressure, which contemporaneously opens the two block and control devices of the descent in each of the two cylinders.
  • a signal for example a piloting pressure
  • each cylinder affords small-diameter choke orifices, in general comprised between 0.8 and 1.0 mm, such as very much to limit any oil leakage in a case of pipe breakage.
  • These chokes enable only static pressure balance, as the limited oil flow which they allow through is not sufficient to guarantee balance under dynamic conditions too.
  • the aim of the present invention is to provide a device which enables the drawbacks in the balancing circuits of known type to be obviated.
  • the set aim is attained by a pressure balancing valve for two cylinders activated in parallel according to the present invention.
  • An advantage of the valve is that is provides excellent response characteristics in both static conditions and dynamic load conditions.
  • a further advantage of the valve is that in case of a breakage of the connecting conduit between the two cylinders, the loss of oil is limited to very small amounts.
  • the valve of the present invention is particularly useful internally of a hydraulic control circuit for two cylinders 31, 32 activated in parallel.
  • This circuit comprises a first supply conduit circuit V2-C2 predisposed for supplying an operating fluid to supply port C2 of the base of the two cylinders 31, 32, with the aim of causing extension of the stem of the two cylinders and, consequently, raising of a load.
  • a second conduit circuit V1, C1 is predisposed to supply the operating fluid to the supply port C1 of the annular chamber (the chamber in which the stem is arranged) of the two cylinders, with the aim of determining return of the stems and consequently the descent of the load.
  • valves 33, 34 for control of the descent are interposed between the supply port C2 of the base of the two cylinders and the pressurised fluid source, indicated by V2 in the figures.
  • the valves 33, 34 widely available on the market, have the function of preventing the discharge of the operating fluid from the bottom of the respective cylinder in the absence of a load descent command, such as to guarantee that the load stays in a stationary position.
  • the valves 33, 34 for load descent control enable a controlled discharge of the fluid from the bases of the two cylinders, such that the descent of the load is initially done at a contained speed.
  • the load decent control valves 33, 34 are provided with shaped obturators which can take on a closed position, in which they do not enable discharge of the operating fluid from the base of the cylinders, and an open position, in which they enable discharge of the fluid from the bases of the cylinders 31, 32.
  • Elastic means push the two obturators towards the closed position, while the displacement towards the open position is normally determined by means of a piloting pressure exerted by a piloting fluid supplied via a conduit Pil.
  • the piloting fluid could be directly sourced from the conduit V1-C1.
  • the balancing valve 1 of the present invention comprises a main conduit 21, 22 predisposed to be connected to a first cylinder and to be connected to a balancing conduit 40 which, in turn, is predisposed to connect to a second cylinder 32.
  • the balancing tube 40 can comprise a flexible tract, or can be entirely flexible.
  • the obturator 3 is mobile between a closed position, in which the first and the second tract of main conduit 21, 22 are not in mutual communication and the main conduit 21, 22 is closed to fluid passage, and an open position, in which the first and the second tract of the main conduit 21, 22 are in mutual communication.
  • the main conduit 21, 22 is open to fluid passage such that the base of the first cylinder 31 and the balancing conduit are in mutual communication.
  • Thrust means 4 preferably of an elastic type, are predisposed to push the obturator 3 towards the closed position.
  • the thrust means 4 are constituted by an spring having an adjustable or fixed calibration, located in a low-pressure environment by means of an opening to air or a connection to the operating fluid tank, as illustrated in the figures.
  • Piloting means 5, 6 are predisposed to push the obturator 3 towards the open position, exerting an antagonistic action to that of the thrust means 4 by means of a piloting pressure. In the absence of a piloting pressure, the piloting means 5, 6 exert no thrust, so that the obturator 3 is brought into a closed position by effect of the thrust exerted by the thrust means 4.
  • the piloting means comprise a first piloting conduit 5 which places the second tract 22 of the main conduit 21, 22 in communication with a thrust surface of the obturator 3, such that the pressure internally of the second tract 22 of the main conduit 21, 22 exerts a force which acts on the thrust surface of the obturator in order to push the obturator 3 towards the open position.
  • the presence of pressurised fluid internally of the balancing conduit 40 which is in communication with the second tract 22 of the main conduit 21, 22 of the valve, maintains the obturator 3 in an open position.
  • the base of the first cylinder 31 is in communication with the balancing conduit 40 and, consequently, it is in communication with the base of the second cylinder 32.
  • pressurised fluid internally of the balancing conduit 40 is typical of a condition in which there is a load present which is acting on the two cylinders 31, 32 and creating pressure internally of the bases of the two cylinders .
  • This pressure is transmitted to the obturator 3 which stays in the open position such that the bases of the two cylinders 31, 32 are in communication with one another and the pressures present internally thereof equal out perfectly.
  • the perfect equalling-out between the pressures present internally of the two bases enables a perfectly similar response to be given to the two cylinders 31, 32 to a command to descend.
  • the pressure in the balancing conduit 40 drops and with it also the piloting pressure which, via the first piloting conduit 5, acts on the obturator 3.
  • the drop in piloting pressure which acts on the obturator 3 leads to the obturator 3 itself moving into the closed position by effect of the thrust exerted by the thrust means 4. In this way, the fluid in the base of the first cylinder 31 cannot discharge through the balancing conduit 40.
  • a second balancing valve 1a is interposed between the second cylinder 32 and the balancing chamber 40 in a same way as for the first balancing valve 1.
  • the obturator 3 of the second balancing valve 1a too is brought into the closed position by effect of the thrust exerted by the thrust means 4. If, on the contrary, there are no leakages from the balancing conduit and internally thereof there is pressurised fluid, both the obturators 3 are kept in the open position and perfect fluid communication is maintained between the bases of the two cylinders 31, 32.
  • the piloting means 5, 6 preferably comprise a second piloting conduit 6 which places the first tract 21 of the main conduit in communication with the first piloting conduit 5.
  • the second piloting conduit 6 might be afforded through the valve body, but alternatively might be afforded through the obturator body 3, or it could be constituted by a small passage of fluid between the obturator 3 and the sliding seat of the obturator 3.
  • the presence of the second piloting conduit 6 enables a very rapid opening of the obturator 3 to be obtained, as soon as the operating fluid is supplied to the bases of the two cylinders 31, 32, even in a case in which the pressure internally of the bases and the balancing conduit 40 is initially nil, as happens for example when the load is rested on the ground.
  • the second piloting conduit 6 is provided with a fixed choke 7 ( figures 1 and 2 ) or a flow rate regulator 7a ( figure 3 ) predisposed to limit the flow of fluid which can transit through the second piloting conduit 6.
  • a fixed choke 7 figures 1 and 2
  • a flow rate regulator 7a figure 3
  • the flow rate regulator 7a can be compensated, i.e. able to limit the maximum flow rate of fluid that can discharge from the second piloting conduit 6 independently of the fluid pressure in the base of the cylinder 31, 32.
  • the first tract 21 of the main conduit 21, 22 can also be provided with a fixed choke 8 ( figure 1 ) or a flow rate regulator 8a ( figures 2 and 3 ), possibly of the compensated type, predisposed to limit the fluid flow rate which can transit through the first tract 21 of the main conduit 21, 22.
  • the choke 8 or flow rate regulator 8a enable excessive movement of oil between the two cylinders to be limited.
  • the choke 8 or the flow regulator 8a of the first tract 21 of the main conduit 21, 22 can be combined equally with the choke 7 or the flow regulator 7a of the second piloting conduit 6.
  • the valve of the present invention can be provided with a by-pass conduit 9 provided with a check valve 10.
  • the check valve allows the operating fluid to flow only from the second cylinder 32 towards the first cylinder 31.
  • the check valve 10 allows fluid to flow only from the first cylinder 31 towards the second cylinder 32.
  • the by-pass conduit is arranged in parallel with the main conduit 21, 22 of the valve.
  • the valve can greatly limit any fluid leakage due to a breakage of the balancing conduit. This is due to the presence of the obturator 3, piloted to open by the pressure internally of the balancing conduit which, should there be a drop in pressure due to breakage of the balancing conduit, is rapidly brought into the closed position, blocking the transmission of the fluid towards the balancing conduit.
  • the very small leakage of residual oil is discharged via the first piloting conduit 5 of the obturator, which fluid leakage can be further reduced with the use of the fixed choke 7 or the compensated flow regulator 7a.
  • the valve is further simple to use and install, as it can be applied directly to the bases of the two cylinders.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
EP09425475A 2009-11-19 2009-11-19 Druckentlastungsventil für zwei parallel funktionierende Zylinder Withdrawn EP2325499A1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP09425475A EP2325499A1 (de) 2009-11-19 2009-11-19 Druckentlastungsventil für zwei parallel funktionierende Zylinder

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP09425475A EP2325499A1 (de) 2009-11-19 2009-11-19 Druckentlastungsventil für zwei parallel funktionierende Zylinder

Publications (1)

Publication Number Publication Date
EP2325499A1 true EP2325499A1 (de) 2011-05-25

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EP09425475A Withdrawn EP2325499A1 (de) 2009-11-19 2009-11-19 Druckentlastungsventil für zwei parallel funktionierende Zylinder

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EP (1) EP2325499A1 (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103486105A (zh) * 2013-10-14 2014-01-01 徐州重型机械有限公司 一种先导滑阀的控制装置
CN104088843A (zh) * 2014-07-05 2014-10-08 福州大学 一种低泄漏高频响大流量高速开关阀
CN104140045A (zh) * 2014-06-30 2014-11-12 徐州重型机械有限公司 一种起重机及其重力下落控制方法、控制系统
CN108019391A (zh) * 2017-12-08 2018-05-11 重庆红江机械有限责任公司 一种板式连接可调阻尼的单向平衡阀
CN109555743A (zh) * 2018-12-11 2019-04-02 中联重科股份有限公司 用于油缸的控制系统及工程机械
IT201800007167A1 (it) * 2018-07-13 2020-01-13 Dispositivo di equilibratura
CN113048104A (zh) * 2021-04-22 2021-06-29 贵州大学 一种液压负载作业平台能量回收系统

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4080994A (en) * 1976-01-16 1978-03-28 Robert Bosch Gmbh Control arrangement for supplying pressure fluid to at least two hydraulically operated consumer devices
US4682931A (en) 1986-09-22 1987-07-28 Cascade Corporation Lift truck clamp for handling stacked loads of different sizes
US6431816B1 (en) * 1998-10-07 2002-08-13 Cascade Corporation Adaptive load-clamping system
US20070017364A1 (en) * 2005-07-04 2007-01-25 Veneziani Luciano Hydraulic control unit for the arms of a grip and grip including said hydraulic unit

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4080994A (en) * 1976-01-16 1978-03-28 Robert Bosch Gmbh Control arrangement for supplying pressure fluid to at least two hydraulically operated consumer devices
US4682931A (en) 1986-09-22 1987-07-28 Cascade Corporation Lift truck clamp for handling stacked loads of different sizes
US6431816B1 (en) * 1998-10-07 2002-08-13 Cascade Corporation Adaptive load-clamping system
US20070017364A1 (en) * 2005-07-04 2007-01-25 Veneziani Luciano Hydraulic control unit for the arms of a grip and grip including said hydraulic unit

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103486105A (zh) * 2013-10-14 2014-01-01 徐州重型机械有限公司 一种先导滑阀的控制装置
CN103486105B (zh) * 2013-10-14 2016-02-24 徐州重型机械有限公司 一种先导滑阀的控制装置
CN104140045A (zh) * 2014-06-30 2014-11-12 徐州重型机械有限公司 一种起重机及其重力下落控制方法、控制系统
CN104140045B (zh) * 2014-06-30 2016-08-24 徐州重型机械有限公司 一种起重机及其重力下落控制方法、控制系统
CN104088843A (zh) * 2014-07-05 2014-10-08 福州大学 一种低泄漏高频响大流量高速开关阀
CN108019391A (zh) * 2017-12-08 2018-05-11 重庆红江机械有限责任公司 一种板式连接可调阻尼的单向平衡阀
CN108019391B (zh) * 2017-12-08 2019-12-13 重庆红江机械有限责任公司 一种板式连接可调阻尼的单向平衡阀
IT201800007167A1 (it) * 2018-07-13 2020-01-13 Dispositivo di equilibratura
CN109555743A (zh) * 2018-12-11 2019-04-02 中联重科股份有限公司 用于油缸的控制系统及工程机械
CN109555743B (zh) * 2018-12-11 2020-05-22 中联重科股份有限公司 用于油缸的控制系统及工程机械
CN113048104A (zh) * 2021-04-22 2021-06-29 贵州大学 一种液压负载作业平台能量回收系统
CN113048104B (zh) * 2021-04-22 2022-07-15 贵州大学 一种液压负载作业平台能量回收系统

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