EP0080135A1 - Hydraulisches Steuersystem für ein hydraulisches Stellglied - Google Patents

Hydraulisches Steuersystem für ein hydraulisches Stellglied Download PDF

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Publication number
EP0080135A1
EP0080135A1 EP82110471A EP82110471A EP0080135A1 EP 0080135 A1 EP0080135 A1 EP 0080135A1 EP 82110471 A EP82110471 A EP 82110471A EP 82110471 A EP82110471 A EP 82110471A EP 0080135 A1 EP0080135 A1 EP 0080135A1
Authority
EP
European Patent Office
Prior art keywords
actuator
valve
meter
pilot
fluid
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
EP82110471A
Other languages
English (en)
French (fr)
Other versions
EP0080135B1 (de
Inventor
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
Sperry Corp
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 Sperry Corp, Vickers Inc filed Critical Sperry Corp
Publication of EP0080135A1 publication Critical patent/EP0080135A1/de
Application granted granted Critical
Publication of EP0080135B1 publication Critical patent/EP0080135B1/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 power transmission in hydraulic systems that are found, for example, on mobile equipment such as excavators and cranes.
  • the valve system disclosed in the aforementioned patent comprises an independent pilot operated meter-in element; a pair of load drop check valves; a pair of independently operated normally closed meter-out elements; a pair of load pressure responsive valves; and a pair of anti-cavitation valves.
  • the meter-in element functions to direct fluid flow to one or the other of the actuator ports.
  • the normally closed meter-out elements 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 element is directing fluid.
  • the meter-out elements 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 elements has associated therewith the load pressure responsive valves which act on the meter-out elements in response to load pressure to enable the meter-out elements 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 system 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 valve system is controlled through the pilot lines from a manually operated hydraulic remote control valve.
  • the meter-in element 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. Since the valve system is a load sensing system, the pump output is made to match that which is required by the load. In contrast, in a non-load sensing system, the pump output may exceed that required by the load with the excess power being dissipated as heat.
  • valve system Under certain conditions, it may not be possible or desirable to mount the valve system directly to an actuator. Such conditions may exist due to space limitations on the actuator or where it is desirable to limit the number of supply and pilot lines, such as to the topmost section of a telescoping boom or when a brake, such as in a winch-type application, is required between the actuator and valve system. Under these conditions, the valve system is mounted on the equipment remote from the actuator with a pair of lines running to the actuator port manifold. -In one of these situations, it may be desirable to interpose a conventional counterbalance valve between one of the actuator port lines and the valve system. The counterbalance valve provides for controlled lowering and holding of the load at the actuator port manifold.
  • pilot operated check valve In another situation when a stable load is involved, it may be desirable to interpose a pilot operated check valve between the actuator port and the valve system.
  • the pilot operated check valve provides for positive holding of the load, that is, holding the load stable with zero drift.
  • valve system disclosed in the aforementioned patent does not lend itself to use in the circuit applications mentioned above; namely, the use of counterbalance valves, pilot operated check valves, brakes and free float or swing of the actuator. This is mainly due to the normally closed condition of the meter-out valve elements.
  • valve system of the aforementioned type which is operable with the use of counterbalance valves, pilot operated check valves, brakes, and free floating or swinging actuators.
  • control valve system is provided with a pair of normally open exhaust valves positioned between a tank passage and actuator ports so that with the meter-in valve in the neutral position, both actuator ports are open to the tank passage through the normally open meter-out valves and the actuator will be free to move, as, for example, in the case of a free coasting boom.
  • pilot pressure is also applied to close the appropriate exhaust valve preventing flow of fluid from the pump to the tank passage with the other exhaust valve remaining open to the tank passage,
  • a counterbalance valve is utilized in association with one opening of an actuator for controlling lowering and holding of a load
  • a single normally open exhaust valve is provided between that actuator opening and the tank passage.
  • an external brake is provided for holding a load
  • a single normally open exhaust valve is also provided between the actuator opening and the tank passage.
  • the hydraulic 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 system 22 which has load sensing control in accordance with conventional construction.
  • the hydraulic system further includes a manually operated controller, not shown, that direct a pilot pressure to a valve system 24 for controlling the direction of movement of the actuator, as presently described.
  • Fluid from the pump 22 is directed to the line 25 and line 26 to a meter-in valve 27-that functions to direct and control the flow of hydraulic fluid to one or the other end of the actuator 20.
  • the meter-in valve 27 is pilot pressure controlled by controller, not shown, through lines 28, 29 and lines 30, 31 to the opposed ends thereof, as presently described.
  • hydraulic fluid passes through lines 32, 33 to one or the other end of the actuator 20.
  • the hydraulic system further includes a normally- open exhaust valve 34, 35 positioned between each end of the actuator in lines 32, 33 and a tank passage 36.
  • the exhaust valves control the flow of fluid between the actuator and tank passage 36, as presently described.
  • the hydraulic system further includes spring loaded poppet valves 37, 38 in the lines 32, 33 and spring-loaded anti-cavitation valves 39, 40 which are adapted to open the lines 32, 33 to the tank passage 36.
  • spring-loaded poppet valves are associated with each valve 34, 35 acting as pilot operated relief valves.
  • a line 47 connects exhaust valve 35 with pilot control line 28 and a line 48 connects valve 34 with pilot control line 29 so that when pilot pressure is applied to one side of meter-in valve 27, the appropriate valve 34, 35 is closed.
  • the system also includes a back pressure valve 44 associated with the return or tank line.
  • Back pressure valve 44 functions to minimize cavitation when an overrunning or a lowering load tends to drive the actuator 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 and in the absence of pilot pressure the spool is maintained in a neutral position by springs.
  • the spool normally blocks the flow from the pressure passage 26 to the passages 32, 33.
  • pilot pressure is applied to either end of the spool, the spool moves until a force balance exists among the 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 passage 26.
  • the same pilot pressure which functions to determine the direction of opening of the meter-in valve and therefor the direction of movement of the actuator also functions to close the appropriate exhaust valve so that the fluid will flow into the actuator.
  • the opposite exhaust valve is not acted on by the pilot pressure therefor remaining open to the tank passage and allowing fluid from the opposite end of the actuator to flow to tank.
  • each valve system 24 includes a line 81 extending to a shuttle valve 80 that receives load pressure from an adjacent actuator through line 79.
  • Shuttle valve 80 senses which of the pressures is greater and shifts to apply the higher pressure to pump 22.
  • each valve system in succession incorporates shuttle valves 80, 82 which compare the load pressure therein with the load pressure of an adjacent valve system and transmit the higher pressure to the adjacent valve system in succession and finally apply the highest load pressure to pump 220
  • the single meter-in valve 27 may be replaced by two meter-in valves as shown in DE-30 11 088 A 1 and having a common assignee with the instant application.
  • one or both of the valves 34, 35 is a normally open exhaust valve rather than normally closed meter-out valves as in the aforementioned United States patent.
  • both exhaust valves are normally open as shown in FIGS. 1 and 2 the exhaust valves are vented, as presently described, through vent lines 47a or 48a.
  • both the exhaust valve 35b or 35c and the normally closed meter-out valve 34b or 34c are vented through a common vent line 29a.
  • both exhaust valves 34, 35 are normally open so that the actuator will be free to move, as in the case of a swinging boom, when the meter-in valve is in a neutral position.
  • pilot pressure is applied through line- 47 or 48 to close the appropriate exhaust valve.
  • the exhaust valve associated with the port to the actuator through which fluid is to be supplied is closed by the pilot signal.
  • the exhaust valve is returned to its normally open position and the actuator is permitted to have a float position in the case of a hydraulic cylinder or to have a free swing or coast position in the case of a rotary hydraulic motor.
  • a pressure control meter-in valve system has feedback pressure of line 83 opposing the pilot pressure at 31 and feedback pressure of line 84 opposing pilot pressure applied at 30. This gives smoother stopping and starting of loads and accurate positioning of loads which would otherwise not be obtained with the flow control meter-in valve system.
  • each normally open exhaust valve 34, 35, 35b, 35c is of identical construction and, for purposes of clarity, only valve 35 is described.
  • the exhaust valve 35 includes a differential area bores 60 and 72 in which a poppet 61 is positioned between supply passage 33 and tank passage 36.
  • the valve includes a passage 62 having an orifice 62a extending from supply passage 33 to a chamber 63 behind the poppet.
  • One or more passages 64 formed within the poppet 61 extend from chamber 63 to the tank passage 36.
  • a stem 65 is adapted to close the connection between chamber 63 and passages 64 under the action of a pilot pressure piston 66 which is positioned between chambers 69 and 71 o
  • a spring 67 in the absence of any pressure in the system, holds stem 65 in the open position and yieldingly urges poppet 61 to the closed position as shown in FI G . 5.
  • valve functions as a normally open valve; to this end the orifice 62a, the spring rate of spring 67, and the differential area of the poppet 66, i.e. the area of bore 60 less the area of bore 72, are selected so that a small and relatively insignificant pressure in line 33 will cause the poppet 61 to open and provide a flow path between passage 33 and tank passage 36.
  • a passage 68 connects chamber 69 to pilot pressure in pilot line 28.
  • the pressure in chamber 69 acts on one end of piston 66.
  • Chamber 71 which is at the other end of piston 66, is vented through a passage 70, which as previously mentioned, connects with the appropriate vent line 48a or 29a as shown in FIGS. 1-4.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Fluid Gearings (AREA)
  • Valve Device For Special Equipments (AREA)
  • Vehicle Body Suspensions (AREA)
EP82110471A 1981-11-12 1982-11-12 Hydraulisches Steuersystem für ein hydraulisches Stellglied Expired EP0080135B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US32044881A 1981-11-12 1981-11-12
US320448 1981-11-12

Publications (2)

Publication Number Publication Date
EP0080135A1 true EP0080135A1 (de) 1983-06-01
EP0080135B1 EP0080135B1 (de) 1986-01-22

Family

ID=23246474

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82110471A Expired EP0080135B1 (de) 1981-11-12 1982-11-12 Hydraulisches Steuersystem für ein hydraulisches Stellglied

Country Status (13)

Country Link
EP (1) EP0080135B1 (de)
JP (1) JPS5884255A (de)
AU (1) AU557058B2 (de)
BR (1) BR8205049A (de)
CA (1) CA1172136A (de)
DE (1) DE3268712D1 (de)
ES (1) ES8402641A1 (de)
FI (1) FI72579C (de)
IN (1) IN156019B (de)
MX (1) MX154560A (de)
NO (1) NO156301C (de)
NZ (1) NZ201541A (de)
ZA (1) ZA825385B (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0066717A2 (de) * 1981-05-18 1982-12-15 Vickers Incorporated Hydraulisches Steuersystem mit Zuflussstromregelventil
EP0089652A2 (de) * 1982-03-22 1983-09-28 Vickers Incorporated Kraftübertragung
EP0209019A2 (de) * 1985-07-12 1987-01-21 Vickers Incorporated Hydraulisches Steuersystem
FR2586463A1 (fr) * 1985-08-26 1987-02-27 Leblon Hubert Valves cartouches a inserer multi-fonctions coaxiales et application a la commande d'un verin a double effet
CN109139577A (zh) * 2017-06-27 2019-01-04 罗伯特·博世有限公司 阀块装置和用于阀块装置的方法

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4201052A (en) * 1979-03-26 1980-05-06 Sperry Rand Corporation Power transmission
DE1601729B2 (de) * 1966-07-06 1980-08-07 Hydraulic Unit Specialties Co., Waukesha, Wis. (V.St.A.) Mit Vorsteuerung arbeitende hydraulische SteuerventUeinrichtung

Family Cites Families (1)

* 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

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1601729B2 (de) * 1966-07-06 1980-08-07 Hydraulic Unit Specialties Co., Waukesha, Wis. (V.St.A.) Mit Vorsteuerung arbeitende hydraulische SteuerventUeinrichtung
US4201052A (en) * 1979-03-26 1980-05-06 Sperry Rand Corporation Power transmission

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0066717A2 (de) * 1981-05-18 1982-12-15 Vickers Incorporated Hydraulisches Steuersystem mit Zuflussstromregelventil
EP0066717A3 (en) * 1981-05-18 1983-10-12 Sperry Corporation Hydraulic control system comprising a meter-in valve means
EP0089652A2 (de) * 1982-03-22 1983-09-28 Vickers Incorporated Kraftübertragung
EP0089652A3 (en) * 1982-03-22 1984-09-05 Vickers, Incorporated Power transmission
EP0209019A2 (de) * 1985-07-12 1987-01-21 Vickers Incorporated Hydraulisches Steuersystem
EP0209019A3 (en) * 1985-07-12 1990-03-14 Vickers, Incorporated Power transmission
FR2586463A1 (fr) * 1985-08-26 1987-02-27 Leblon Hubert Valves cartouches a inserer multi-fonctions coaxiales et application a la commande d'un verin a double effet
US4706547A (en) * 1985-08-26 1987-11-17 Leblon Hubert Coaxial multi-function insertable cartridge valve
CN109139577A (zh) * 2017-06-27 2019-01-04 罗伯特·博世有限公司 阀块装置和用于阀块装置的方法
CN109139577B (zh) * 2017-06-27 2023-05-02 罗伯特·博世有限公司 阀块装置和用于阀块装置的方法

Also Published As

Publication number Publication date
FI822599L (fi) 1983-05-13
AU8667982A (en) 1983-05-19
FI822599A0 (fi) 1982-07-23
ZA825385B (en) 1983-06-29
DE3268712D1 (en) 1986-03-06
JPS5884255A (ja) 1983-05-20
NO156301C (no) 1987-08-26
JPH0341706B2 (de) 1991-06-24
NO156301B (no) 1987-05-18
MX154560A (es) 1987-09-25
AU557058B2 (en) 1986-12-04
BR8205049A (pt) 1983-08-09
EP0080135B1 (de) 1986-01-22
FI72579C (fi) 1987-06-08
NO822687L (no) 1983-05-13
ES515812A0 (es) 1984-03-01
ES8402641A1 (es) 1984-03-01
CA1172136A (en) 1984-08-07
NZ201541A (en) 1985-11-08
IN156019B (de) 1985-04-27
FI72579B (fi) 1987-02-27

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