EP0160265A2 - Hydraulisches Steuersystem - Google Patents

Hydraulisches Steuersystem Download PDF

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Publication number
EP0160265A2
EP0160265A2 EP85104920A EP85104920A EP0160265A2 EP 0160265 A2 EP0160265 A2 EP 0160265A2 EP 85104920 A EP85104920 A EP 85104920A EP 85104920 A EP85104920 A EP 85104920A EP 0160265 A2 EP0160265 A2 EP 0160265A2
Authority
EP
European Patent Office
Prior art keywords
valve
meter
valves
pressure
actuator
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.)
Granted
Application number
EP85104920A
Other languages
English (en)
French (fr)
Other versions
EP0160265A3 (en
EP0160265B1 (de
Inventor
Vinod Kumar Nanda
Henry Delano Taylor
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.)
Vickers Inc
Original Assignee
Vickers Inc
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 Vickers Inc filed Critical Vickers Inc
Publication of EP0160265A2 publication Critical patent/EP0160265A2/de
Publication of EP0160265A3 publication Critical patent/EP0160265A3/en
Application granted granted Critical
Publication of EP0160265B1 publication Critical patent/EP0160265B1/de
Expired 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

Definitions

  • This invention relates to a hydraulic control system according to the preamble of claim 1.
  • Such hydraulic systems are found, for example, on mobile equipment, such as excavators and cranes, and are used to control an actuator, such as a hydraulic cylinder or hydraulic motor.
  • the actuator normally has two openings or ports to be used alternately as inlet or outlet.
  • a known system of that kind (US-A-4,201,052) has several valves housed in a valve body designed to be mounted directly on the actuator.
  • the valves comprise an independent pilot operated meter-in valve, a pair of load drop check valves, a pair of independently operated, normally closed meter-out valves, a pair of load pressure responsive valves, and a pair of anti-cavitation valves.
  • the meter-in valve functions to direct fluid flow to one or the other of the actuator ports.
  • the normally closed meter-out valves are associated with each of the actuator ports for controlling fluid flow from the port opposite to the actuator port to which the meter-in valve is directing fluid.
  • the meter-out valves function as variable orifices metering fluid between the appropriate actuator port and a low pressure zone such as a reservoir tank.
  • Each of the meter-out valves has associated therewith a load pressure responsive element which acts on the meter-out valves in response to load pressure to enable the meter-out valves to also provide pressure relief protection.
  • the anti-cavitation valves are associated with each of the actuator ports and are adapted to open the appropriate port to tank.
  • the valve body is directly mounted to the actuator port manifold and is supplied by one full flow high pressure line, a pair of pilot pressure lines, and a load sensing line.
  • the operation of the valves is controlled through the pilot lines from a manually operated hydraulic remote control valve.
  • the meter-in valve assumes a centered or neutral position with the check valves, the meter-out elements, the pressure responsive valves, and the anti-cavitation valves, all in closed position.
  • the valve system prevents uncontrolled lowering of loads and in the case of overrunning loads, prevents fluid flow from the high pressure fluid source to the actuator even in the event of a ruptured line. Due to the normally closed meter-out valves, such a hydraulic control system does not lend itself to free float, swing or coast the actuator.
  • the hydraulic control system embodying the invention comprises an actuator 20, herein shown as a linear hydraulic cylinder, having an output shaft 21 that is moved in opposite directions by hydraulic fluid supplied from a variable displacement pump 22 which has load sensing control 79 through 82 as is fully described in EP oo85,962 A3.
  • the hydraulic control system further includes a manually operated controller 23 that directs high or low pilot pressure through pilot port C1 or C2 to a valve system 24 for controlling the direction of movement of the actuator 20.
  • Fluid from the pump 22 is directed through supply lines 25 and 26 and a pump port P to a meter-in valve 27 that functions to direct and control the flow of hydraulic fluid to one or the other actuator lines A or B connected to the actuator 20.
  • pilot ports C1 and C2 lead through pilot control lines 28, 30 and pilot control lines 29, 31, respectively, to the opposed ends of the meter-in valve 27.
  • hydraulic fluid passes through passages 32, 33 and actuator lines A or B to one or the other end of the actuator 20.
  • the hydraulic control system further includes normally closed exhaust valves 34d, 35d, each positioned between lines A or B and a return passage 36 leading to a tank port T.
  • the exhaust.valves 34d, 35d control the return flow of fluid to tank.
  • the hydraulic control system further includes spring loaded poppet valves 37, 38 in the passages 32,33 and spring-loaded anti-cavitation valves 39, 40 which are opened when pressure in the return passage 36 is higher than in the passage 32 or 33.
  • spring loaded poppet valves 41, 42 (Fig. 2) are associated with each valve 34d, 35d acting as pilot operated relief valves.
  • a bleed line 47 having an orifice 49 extends from the return passage 36 to the exhaust valves 34d, 35d and to the pilot control lines 28, 29 through check valves 77, 78 (Fig. 1).
  • the system also includes a back pressure valve 44 connected to the tank port T and associated with the return passage 36.
  • Back pressure valve 44 functions to minimize cavitation when an overrunning or a lowering load tends to drive the actuator 20 down.
  • a charge pump relief valve 45 is provided to take excess flow above the inlet requirements of the pump 22 and apply it to the back pressure valve 44 to augment the fluid available to the actuator.
  • Meter-in valve 27 comprises a bore in which a spool is positioned. At low pilot pressure ("normally") the spool is maintained in a neutral position by springs and blocks the flow from the supply line26 to the passages 32, 33. When high pilot pressure is applied to either end of the spool, the spool moves until a force balance exists among the high pilot pressure, the spring load and the flow forces. The direction of movement determines which of the passages 32, 33 is provided with fluid under pressure from supply line 26.
  • the single meter-in valve 27 may be replaced by two meter-in valves as shown in DE-3,011,088 A1.
  • the meter-out or exhaust valves 34d, 35d are of the poppet type and have back pressure spaces 63a and 63b, respectively, which are connected to the actuator lines A and B through orifices 62a and 62b, respectively, and can be vented by retracting a stem 65a and 65b, respectively, each is connected to a piston 67a and 67b, respectively.
  • pilot pressure is admitted through control line 28, piston 67a and stem 65a are moved and back pressure space 63a vented so that pressure in the return actuator line A opens exhaust valve 34d. Similar operation is carried out with pilot pressure in control line 29 and exhaust valve 35d.
  • the exhaust valves 34d, 35d are also controlled by the poppet valves 41, 42.
  • poppet valves 41, 42 are acted upon, on one side, by pressure in the actuator line A or B, and, on the other side, by the same pressure, yet delayed.
  • a restricted passage 72 through check valve 37 leads to an accumulator volume 72a and to a spring cavity 41a of the poppet valve 41.
  • poppet valve 41 is sensitive for sudden pressure rises in actuator line A and lowers the respond pressure (An videwert) of the exhaust valve 34d for a short time. This is accomplished by venting the back pressure space 63a of exhaust valve 34d to low presure in return passage 36 via a passage 73a.
  • poppet valve 42 including another accumulator volume 72b, orifice 62b and passage 73b.
  • restricted passages 27a, 27b in the valve spool connect pilot line 30 to passage 32 and pilot line 31 to passage 33.
  • a passage 90 is provided to connect passage 32 to the accumulator volume 72a and therethrough to the spring cavity 41a of the poppet valve 41. So low pilot- pressure is extended to spring cavity 41a, i.e. pressure holding the poppet valve 41 closed is reduced and allowing to open valve 41 when a relatively low pressure (approximately 200 psi) is developed in actuator line A. Back pressure in space 63a is vented through passage 73a and pressure in actuator line A is allowed to open the exhaust valve 34d to the return passage 36.
  • valve system 24 provides for a float or coast characteristic of the actuator movement in one direction. If a float or coast characteristic is desired for the other direction of movement, a similar passage (92 in Fig. 1) between passage 33 and the accumulator volume 72b is added which reduces the back pressure of the exhaust valve 35d in the neutral position of the meter-in valve 27. According to the requirements, one or the other or both passages 90, 92 are used to bleed off the back pressure holding the respective poppets of the valves 34d or 35d closed, thus allowing them to p pen in response to low pressures in the actuator lines A or B.
  • Fig. 1 shows an embodiment for one source operated exhaust valve
  • Fig. 2 shows two pilot sources operated exhaust valves, i.e. each back pressure space 63a, 63b can be vented by pilot valves 67a, 67b or 41, 42.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
EP85104920A 1984-04-30 1985-04-23 Hydraulisches Steuersystem Expired EP0160265B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US60560784A 1984-04-30 1984-04-30
US605607 1984-04-30

Publications (3)

Publication Number Publication Date
EP0160265A2 true EP0160265A2 (de) 1985-11-06
EP0160265A3 EP0160265A3 (en) 1986-02-12
EP0160265B1 EP0160265B1 (de) 1989-01-11

Family

ID=24424419

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85104920A Expired EP0160265B1 (de) 1984-04-30 1985-04-23 Hydraulisches Steuersystem

Country Status (5)

Country Link
EP (1) EP0160265B1 (de)
AU (1) AU583504B2 (de)
CA (1) CA1234529A (de)
DE (1) DE3567509D1 (de)
IN (1) IN164362B (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104030163A (zh) * 2014-05-23 2014-09-10 武汉武桥交通装备技术有限公司 一种船用全液压起重机低能耗及低发热恒压系统
WO2017188869A1 (en) * 2016-04-28 2017-11-02 Volvo Construction Equipment Ab Hydraulic system

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110667809B (zh) * 2019-09-27 2021-06-11 北京精密机电控制设备研究所 一种流量精确控制的浮力调节系统

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3011088A1 (de) * 1979-03-26 1980-10-09 Sperry Corp Hydraulische antriebsschaltung
GB2047435A (en) * 1979-03-26 1980-11-26 Sperry Corp Hydraulic control valve system
EP0085962A2 (de) * 1982-02-08 1983-08-17 Vickers Incorporated Hydraulisches Steuersystem,insbesondere für schwenkende Lasten
DE3307582A1 (de) * 1982-03-04 1983-09-22 Kabushiki Kaisha Komatsu Seisakusho, Tokyo Hydraulik-bremsventilanordnung

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2044366A (en) * 1934-11-24 1936-06-16 Pierson Gordon Green Method for separation and recovery of au, pt, pd, se, te, and as by means of mercurous salts
US4201052A (en) * 1979-03-26 1980-05-06 Sperry Rand Corporation Power transmission
US4407122A (en) * 1981-05-18 1983-10-04 Vickers, Incorporated Power transmission

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3011088A1 (de) * 1979-03-26 1980-10-09 Sperry Corp Hydraulische antriebsschaltung
GB2044366A (en) * 1979-03-26 1980-10-15 Sperry Corp Hydraulic Systems for Actuators
GB2047435A (en) * 1979-03-26 1980-11-26 Sperry Corp Hydraulic control valve system
EP0085962A2 (de) * 1982-02-08 1983-08-17 Vickers Incorporated Hydraulisches Steuersystem,insbesondere für schwenkende Lasten
DE3307582A1 (de) * 1982-03-04 1983-09-22 Kabushiki Kaisha Komatsu Seisakusho, Tokyo Hydraulik-bremsventilanordnung

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104030163A (zh) * 2014-05-23 2014-09-10 武汉武桥交通装备技术有限公司 一种船用全液压起重机低能耗及低发热恒压系统
CN104030163B (zh) * 2014-05-23 2016-06-29 武汉武桥交通装备技术有限公司 一种船用全液压起重机低能耗及低发热恒压系统
WO2017188869A1 (en) * 2016-04-28 2017-11-02 Volvo Construction Equipment Ab Hydraulic system

Also Published As

Publication number Publication date
EP0160265A3 (en) 1986-02-12
CA1234529A (en) 1988-03-29
AU4177085A (en) 1985-11-07
AU583504B2 (en) 1989-05-04
DE3567509D1 (en) 1989-02-16
EP0160265B1 (de) 1989-01-11
IN164362B (de) 1989-03-04

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