EP0860612A2 - Schieberventil mit regelbarer Überdeckung - Google Patents

Schieberventil mit regelbarer Überdeckung Download PDF

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Publication number
EP0860612A2
EP0860612A2 EP98301136A EP98301136A EP0860612A2 EP 0860612 A2 EP0860612 A2 EP 0860612A2 EP 98301136 A EP98301136 A EP 98301136A EP 98301136 A EP98301136 A EP 98301136A EP 0860612 A2 EP0860612 A2 EP 0860612A2
Authority
EP
European Patent Office
Prior art keywords
valve
relative
drive spindle
control
spool
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
EP98301136A
Other languages
English (en)
French (fr)
Other versions
EP0860612B1 (de
EP0860612A3 (de
Inventor
Richard John Mckay
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.)
ZF International UK Ltd
Original Assignee
Lucas Industries Ltd
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 Lucas Industries Ltd filed Critical Lucas Industries Ltd
Publication of EP0860612A2 publication Critical patent/EP0860612A2/de
Publication of EP0860612A3 publication Critical patent/EP0860612A3/de
Application granted granted Critical
Publication of EP0860612B1 publication Critical patent/EP0860612B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves

Definitions

  • This invention relates to hydraulic control valves particularly, but not exclusively for use in the control of the position of aircraft flight control surfaces.
  • a conventional hydraulic control valve construction includes a valve body incorporating at least one fluid inlet port and at least one fluid outlet port, a control member moveable within the valve body to make and break fluid flow communication between said inlet port and said outlet port, and a drive element moveable relative to the valve body between rest and operative positions to move the control member to make and break said fluid flow communication.
  • the operating characteristics of the conventional valve and the system controlled thereby are determined directly by the position of the drive element relative to the valve body, and it is an object of the present invention to provide an hydraulic control valve wherein at least one operating characteristic can be adjusted independently of control inputs to the valve control member by way of the drive element.
  • an hydraulic control valve comprising a valve body having an inlet port and an outlet port, a valve member moveable within the valve body to make or break communication between the inlet and outlet ports, a drive element coupled to said valve member for moving said valve member relative to the valve body to operate the valve and, means for moving the valve member relative to the valve body and the drive element to effect an adjustment in the position of the valve member relative to said inlet port and/or said outlet port.
  • valve member is a valve spool
  • drive element is a drive spindle upon which said spool is slidably mounted.
  • said spool is urged to a first operative position relative to said spindle by a resilient device, and is moveable from said first position against the action of said resilient device to a second operative position by hydraulic pressure acting on the spool.
  • an hydraulic control valve having an elongate valve body including longitudinally spaced first and second inlet ports, and longitudinally spaced first and second outlet ports, a drive spindle extending longitudinally within the valve body, first and second control spools slidably mounted on the drive spindle, resilient means acting between the control spools and the drive spindle to urge the control spools to occupy respective first positions relative to the drive spindle, and means for applying hydraulic pressure to the control spools to move them to occupy a second position, against the action of said resilient means, relative to the drive spindle.
  • the movement of the control spools relative to the drive spindle alters the positioning of lands of the drive spools relative to respective ports of the valve body, in a predetermined position of the drive spindle.
  • the hydraulic control valve illustrated is a spool valve primarily, but not exclusively, intended for use in a standby rudder power control unit of an aircraft.
  • the standby rudder power control unit (SRPCU) is employed in combination with a main rudder power control unit (MRPCU) to control the position of the aircraft rudder in accordance with control inputs provided by the pilot, and generally the SRPCU has three possible operating modes, Bypass; Normal; and Rudder Assist.
  • the SRPCU In the Bypass position the SRPCU is inoperative in that it provides no power assistance to the MRPCU in driving the rudder.
  • the SRPCU takes control of the rudder from the MRPCU which may actually be inoperative at that time.
  • the SRPCU includes an hydraulic actuator in the form of a double-acting hydraulic ram, which links the aircraft structure and the moveable control surface of the rudder and supplies power to move the rudder either alone, or in combination with a similar actuator of the MRPCU.
  • the supply of hydraulic fluid to the actuator is controlled at least in part by a control valve of the kind illustrated in Figures 1 and 2, the control spool assembly of the valve being moveable in response to the pilot's movements of a rudder control member.
  • the hydraulic control valve includes a valve body 11 having a cylindrical bore 12 slidably receiving a spool assembly 13.
  • the valve body may be defined by a valve housing or by a guide member formed with the bore 12 and received in a valve housing.
  • the spool assembly 13 includes an elongate spindle 14 through which mechanical control inputs derived from the pilot's rudder control are transmitted to the assembly 13.
  • first and second substantially identical control spools 15, 16 each of which has a reduced diameter region intermediate its ends such that each spool has a land (indicated by the suffix a) at one end, and an identical land (indicated by the suffix b) at its opposite axial end, the lands being in sliding, sealing engagement with the wall of the bore 12, and defining between them, in the bore 14, respective annular chamber 15 c , 16 c .
  • One end of the spindle 14 protrudes from the spool 15 and is formed with an integral head 17 against which an axial end of the land 15a abuts.
  • a cylindrical spacer 18 is slidably disposed on the spindle 14 between the spools 15, 16.
  • the end of the spindle 14 remote from the head 17 is formed with a further integral head 19 and a helical compression spring 21 acts between the head 19 and an axial end of the land 16 b of the spool 16.
  • the spring 21 urges the spool 16, the spacer 18 and the spool 15 towards the head 17 so that the spool 15 abuts the head 17 and the spacer 18 is trapped between the spools 15, 16.
  • the valve body 11 contains a port 22 communicating with the bore 12, and through which pressurized hydraulic fluid can be supplied to the chamber 22 a within the bore 12 defined between the spools 15, 16 and around the spacer 18. Moreover, adjacent the spool 15 the valve body has a supply port 24, a return port 23, and a control port 25 all communicating with the bore 12, and correspondingly associated with the spool 16 is a supply port 27, a return port 26 and a control port 28.
  • a passage 31 within the valve body interconnects the supply ports 24, 27 so that they can receive hydraulic fluid under pressure from a common supply line 31 a , and a further passage 29 in the valve body interconnects the return ports 23, 26 with a common return line 29 a .
  • the port 25 is connected to one side of the hydraulic actuator ram for the rudder control surface, the port 28 being connected to the opposite side of the ram.
  • the control spool assembly 14, 15, 16 has a centralised position usually referred to as the null position, and this is the position of the assembly illustrated in both Figure 1 and Figure 2. It can be seen that the dimensioning of the spool lands 15 b , 16 a and the spacer 18 is such, in relation to the positioning of the return ports 23, 26 that with the spool assembly in its null position and the chamber 22 a vented, the land 15 b only partially closes the port 23, and the land 16 a similarly only partially closes the port 26. Thus there is communication between the return line 29a and one side of the actuator ram by way of the port 23, the annular chamber 15 c and the port 25.
  • Underlapping of the return ports provides particular operating characteristics of the control valve and the system associated with the control valve.
  • the ports 23, 26 underlapped in the null position of the control spool assembly fluid flow communication exists between opposite ends of the associated ram and thus fluctuations in pressure at one end of the ram will be reflected at the opposite end.
  • the ram be driven physically by an external force, then it is not hydraulically locked and fluid displaced from one end of the ram by such a movement flows to the opposite end of the ram.
  • valve is used in an SRPCU then in the Normal operating mode of the SRPCU the chamber 22 a will be vented so that the spools 15, 16 will be in the position shown in Figure 1 and thus the SRPCU will be passive around the null position of the control valve thereby minimising the possibility of a "force fight" between the SRPCU and the MRPCU when both are operative.
  • the MRPCU will not exhibit the same operating characteristics, and thus in effect will be in primary control of the rudder control surface position in those situations where the SRPCU control valve is in its null position.
  • Figure 2 illustrates the valve of Figure 1 but in the configuration it occupies when sufficient hydraulic pressure is applied to the chamber 22a to displace the spools 15, 16 outwardly relatively to one another against the action of the spring 21. It can be seen that while the spool 15 remains in abutment with the head 17 of the spindle 14 a clearance exists between the spacer 18 and the spool 16 and the spring 21 has been compressed until the spool 16 abuts a spacer collar 21 a positioned beneath the spring 21, and in turn abutting the head 19. It will be recognised that the increased spacing of the spools 15, 16 is relatively small, and the corresponding displacement of the spindle 14 generated by the spool movement is half the increased spacing between the spools.
  • a solenoid valve will ensure that the chamber 22 a is vented in the Normal operating mode, and pressurized only in the Rudder Assist operating mode.
  • the valve does not, in the Rudder Assist mode, exhibit a region around the null position with zero pressure gain the "force fight" problem does not arise as the MRPCU is inoperative.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Multiple-Way Valves (AREA)
  • Mechanically-Actuated Valves (AREA)
EP19980301136 1997-02-25 1998-02-17 Schieberventil mit regelbarer Überdeckung Expired - Lifetime EP0860612B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB9703890 1997-02-25
GBGB9703890.5A GB9703890D0 (en) 1997-02-25 1997-02-25 Valves

Publications (3)

Publication Number Publication Date
EP0860612A2 true EP0860612A2 (de) 1998-08-26
EP0860612A3 EP0860612A3 (de) 1999-05-12
EP0860612B1 EP0860612B1 (de) 2002-10-02

Family

ID=10808270

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19980301136 Expired - Lifetime EP0860612B1 (de) 1997-02-25 1998-02-17 Schieberventil mit regelbarer Überdeckung

Country Status (3)

Country Link
EP (1) EP0860612B1 (de)
DE (1) DE69808348T2 (de)
GB (1) GB9703890D0 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1541874A3 (de) * 2003-12-12 2006-01-18 Goodrich Actuation Systems Ltd. Hydraulische Steuerventilvorrichtung
DE102017008562A1 (de) * 2017-09-12 2019-03-14 Daimler Ag Hydraulikventil, insbesondere für ein hydraulisches Parksperrensystem, und hydraulisches Parksperrensystem mit dem Hydraulikventil

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3106939A (en) * 1960-05-19 1963-10-15 Flick Reedy Corp Actuator valve structure
GB8713304D0 (en) * 1987-06-06 1987-07-08 Lucas Ind Plc Fluid control valve
GB9211898D0 (en) * 1992-06-05 1992-07-15 Vickers Systems Ltd Two-stage hydraulic valves

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1541874A3 (de) * 2003-12-12 2006-01-18 Goodrich Actuation Systems Ltd. Hydraulische Steuerventilvorrichtung
US7306009B2 (en) 2003-12-12 2007-12-11 Goodrich Actuation Systems Limited Hydraulic control valve
DE102017008562A1 (de) * 2017-09-12 2019-03-14 Daimler Ag Hydraulikventil, insbesondere für ein hydraulisches Parksperrensystem, und hydraulisches Parksperrensystem mit dem Hydraulikventil
DE102017008562B4 (de) * 2017-09-12 2026-02-12 Mercedes-Benz Group AG Hydraulikventil, insbesondere für ein hydraulisches Parksperrensystem, und hydraulisches Parksperrensystem mit dem Hydraulikventil

Also Published As

Publication number Publication date
DE69808348D1 (de) 2002-11-07
GB9703890D0 (en) 1997-04-16
DE69808348T2 (de) 2003-06-18
EP0860612B1 (de) 2002-10-02
EP0860612A3 (de) 1999-05-12

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