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EP1212546A1 - Soupape de commande et amortisseur hydraulique - Google Patents

Soupape de commande et amortisseur hydraulique

Info

Publication number
EP1212546A1
EP1212546A1 EP00954772A EP00954772A EP1212546A1 EP 1212546 A1 EP1212546 A1 EP 1212546A1 EP 00954772 A EP00954772 A EP 00954772A EP 00954772 A EP00954772 A EP 00954772A EP 1212546 A1 EP1212546 A1 EP 1212546A1
Authority
EP
European Patent Office
Prior art keywords
control valve
valve
force
damper
flow
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Withdrawn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
EP00954772A
Other languages
German (de)
English (en)
Inventor
James Edward Er Fluid Developments Ltd STANGROOM
Peter Richard Er Fluid Developments Ltd KERMODE
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.)
ER Fluid Developments Ltd
Original Assignee
ER Fluid Developments 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 ER Fluid Developments Ltd filed Critical ER Fluid Developments Ltd
Publication of EP1212546A1 publication Critical patent/EP1212546A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/53—Means for adjusting damping characteristics by varying fluid viscosity, e.g. electromagnetically
    • F16F9/532—Electrorheological [ER] fluid dampers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/005—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion using electro- or magnetostrictive actuation means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
    • F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
    • F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/53—Means for adjusting damping characteristics by varying fluid viscosity, e.g. electromagnetically

Definitions

  • This invention relates to a control valve for the modulation of the flow of an oil or water- based working fluid, and to a hydraulic damper incorporating such a valve.
  • Electro-rheological (ER) fluids are concentrated suspensions of finely divided solid particles in a base liquid which show large reversible increases in flow resistance when they are exposed to electric fields. Since their response is proportional to the applied field, and virtually instantaneous, and their consumption of electrical power is relatively small, ER fluids have been proposed as an interface between electrical control signals and many forms of mechanical device, including linear dampers. Several workers have proposed a conventional single-ended damper filled with ER fluid, with an "ER valve” between the chambers above and below the piston.
  • ER valve is basically a pair of parallel fixed electrodes electrically insulated from each other, so that a voltage can be applied between them. This voltage controls the flow resistance of the ER fluid, and hence the pressure drop across the valve.
  • ER valves can take many forms:- they can be a stack of parallel flat plates, an array of concentric cylinders or even a simple rod mounted concentrically in a tube.
  • the simple ER damper described above has several serious disadvantages: - 1.
  • the ER valves must be quite long to generate the maximum pressures achieved in normal dampers.
  • these ER valves must be quite wide, with large gaps between the electrodes, to keep the no-field pressure drop down to acceptable levels at maximum flow rates.
  • the overall result is that the ER valve required to achieve realistic performance using the ER fluids currently available must be very large. Such valves require large, heavy, dangerous and costly high voltage power supplies.
  • a basic object of the present invention is the provision of an improved control valve and hydraulic damper incorporating such a valve.
  • a control valve for modulating the flow of a conventional oil- or water-based working liquid, the valve comprising an element movable with respect to an orifice through which the working fluid is adapted to flow, with the force on the movable element, due to the pressure of the working liquid, being reduced by the provision of a fixed element on or in which the movable element is adapted to slide.
  • the invention provides a variable orifice valve which is itself controlled preferably by an ER device, which, by the presence of the fixed element and the slidable relationship reduces the force necessary to displace the movable element against the pressure and flow of the working fluid so that, when applied to a hydraulic damper, it is possible to fill the main body of the damper with conventional hydraulic liquid, thus reducing the amount of ER fluid required. Since the main energy dissipation takes place in the conventional liquid rather than the ER fluid, the latter can be isolated from the resultant increases in temperature.
  • Figure 1 illustrates the basic principle of a variable orifice control valve
  • Figure 2 is a diagrammatic sectional view through a first embodiment of control valve in accordance with the first aspect
  • Figures 3 and 4 correspond to Figure 2 but show second and third embodiments;
  • Figure 5 is a diagrammatic sectional view through a first embodiment of hydraulic damper in accordance with the second aspect.
  • FIGS 6 and 7 correspond to Figure 5 but show second and third embodiments.
  • valve member 2 enters a movable valve member 2 in the form of an inverted cup, whose radius is R.
  • the valve member 2 is displaceable towards or away from the valve seat 1 along an axis 20, so as to vary the flow of working fluid through the orifice, so that the gap h between rim 21 of the valve member 2 and the valve seat 1 increases or decreases.
  • P is the difference in pressure between the inside and outside of the valve member 2
  • Q is the volume flow rate through the valve
  • p is the density of the working liquid:
  • the value of P is set by the area of the cup ( ⁇ R 2 ), and the downward force upon it. If for instance the latter is generated by an ER device, it can be controlled independent of h the latter will vary in response to changes in flow rate, but this need not directly affect the pressure. Thus, the pressure drop across the control valve, and hence the force exerted by the damper as a whole, is determined purely by eg the ER system and can be varied as required.
  • valve member 2A is a short length tube, and a top 21 is perforated to become a "spider".
  • valve member 2A slides in a fixed position element 3 in which there is a sliding seal for an operating rod 4.
  • the valve member 2A experiences a net downward force, since its annulus side 22 is at full supply pressure, whereas its inside 23, which forms the control orifice, is at roughly half this pressure. However, this force can be balanced out by the effect of the supply pressure on the operating rod 4, which acts as a plunger.
  • By choosing the cross-sectional area of the operating rod 4 to suit the valve member 2A a good force balance can be achieved.
  • Figure 3 is shown another way in which the force on the valve member 2B can be reduced.
  • valve member 2B in the form of a sleeve, is adapted to slide over a fixed rod 24 with an enlarged head 5 retained in a position by the rod 24 passing through the valve seat 1.
  • Working liquid which escapes in this way will leave through the vents 25 in the top of the sleeve, but the majority will pass through the gap between the rim 21 of valve member 2B and the valve seat 1 as previously discussed.
  • Figure 4 is essentially the same as Figure 3, except that fixed rod 24 A passes through an opening 26 in the valve member 2B and is attached above it (not shown).
  • control valve 13 described above can be made quite light, to reduce inertia, and the hydrostatic forces upon it will be small. Furthermore, since the flow rate varies as the square of the gap (h), the required travel is small. The resulting low power requirement of the valves of
  • Figures 2 - 4 will be reflected in the size of the eg ER actuator, and its power supply.
  • Several workers have described bi-directional ER actuators based on a four-arm bridge, and in PCT/GB97/01679 is described one which requires only two ER valves. Either of these could be used to operate the control valve.
  • the control valve 13 can be arranged to be biassed in one direction and a uni-directional ER actuator used to oppose this bias. Such an arrangement is much simpler than a bi-directional actuator. It consists of two ER valves in series with a piston or diaphragm at the mid point.
  • the two ER valves operate like a potential divider chain, so that the pressure at the mid-point can be set to any value virtually up to the supply pressure.
  • the system relies on the out of balance force on the control valve 13 to return it and may be sluggish if used in conjunction with a hydraulic damper having low stroking speeds.
  • a return spring improves this aspect, but the power of an ER actuator must be increased to overcome it.
  • the mechanical power to drive an ER actuator can be provided externally, for example by a small motor-driven pump.
  • this power is derived from the movement of the hydraulic damper itself.
  • the simplest way of doing this is to provide a second piston and cylinder, in parallel with the main hydraulic damper, which acts as a double- acting pump, taking ER fluid from a low pressure reservoir, and driving it through the actuator back to the reservoir. This is clumsy, and the flow rate will be very variable, since it will be directly linked to the stroking speed of the hydraulic damper.
  • the piston rod 7 passes through a sliding seal 27 and is attached to the piston 8 which moves inside the cylinder 9, which is filled with the working liquid.
  • the piston has one-way valves 10 set into it, and there is a further one-way valve 11 in the base of the cylinder.
  • An external pipe 28 connects this one-way valve to a port 12, and the control valve 13 is connected into the pipe 28.
  • a side-branch 29 between the one way valve 11 and the control valve 13 connects to a compliant reservoir 14.
  • the cross-sectional area of the piston rod 7 is roughly half that of the piston 8.
  • valves 10 close, so that the liquid contained in annulus 35 around the piston rod is expelled through the port 12 and the control valve 13.
  • valve 11 opens, allowing the working liquid in the reservoir 14 to return to the cylinder 9.
  • FIG. 6 shows a variant in which the one-way valves are flaps (10A and 11A) of spring steel, and the low pressure reservoir is connected to a pneumatic spring 30. This allows the damper 31 and spring to be combined into a single unit. If it is required to have greater damping on the extension stroke than in compression - this is usually required in vehicle suspension systems - this can be achieved by adjusting the ratio of the cross-sectional area of the piston rod 7 to that of the piston itself.
  • the flow of working liquid into and out of the low pressure reservoir can be used to operate a pump to provide the energy for the ER actuator. If such a pump is sized to provide sufficient flow from the small movements of the damper 31 running on a smooth surface, the flow provided during large excursions of the damper 31 on rough terrain will be excessive and lead to an undesirable temperature rise in the ER fluid.
  • the flow of working liquid passes into and out of the compliant reservoir 14 in Figure 6 through connections A and B. As it does so, it drives the piston 15 up and down.
  • This piston is lightly loaded by springs 32 towards the centre and is connected via light piston rods 33 to the rolling diaphragms 16 and 17.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fluid Mechanics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

L'invention concerne une soupape de commande (13) permettant de faire varier l'écoulement d'un liquide de travail conventionnel à base d'huile ou d'eau. Cette soupape de commande comprend un élément de soupape (2A, 2B) mobile par rapport à un orifice (19) à travers lequel le fluide de travail est amené à s'écouler, avec la force sur l'élément de soupape (2A, 2B), exercée par le pression du liquide de travail, réduite par la fourniture d'un élément fixe (3, 5) sur lequel ou dans lequel l'élément de soupape (2A, 2B) est amené à coulisser.
EP00954772A 1999-08-28 2000-08-25 Soupape de commande et amortisseur hydraulique Withdrawn EP1212546A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GBGB9920311.9A GB9920311D0 (en) 1999-08-28 1999-08-28 Improvements in or relating to linear dampers controlled by electro-rheological fluids
GB9920311 1999-08-28
PCT/GB2000/003267 WO2001016503A1 (fr) 1999-08-28 2000-08-25 Soupape de commande et amortisseur hydraulique

Publications (1)

Publication Number Publication Date
EP1212546A1 true EP1212546A1 (fr) 2002-06-12

Family

ID=10859917

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00954772A Withdrawn EP1212546A1 (fr) 1999-08-28 2000-08-25 Soupape de commande et amortisseur hydraulique

Country Status (4)

Country Link
EP (1) EP1212546A1 (fr)
AU (1) AU6712700A (fr)
GB (1) GB9920311D0 (fr)
WO (1) WO2001016503A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10143980A1 (de) 2001-09-07 2003-03-27 Bosch Rexroth Ag Magneto-Rheologischer Dämpfer
GB0129588D0 (en) * 2001-12-11 2002-01-30 Reactec Ltd Improvements in or relating to skis
DE10223216B4 (de) * 2002-05-24 2005-10-27 Siemens Ag Vorrichtung zur Stoßdämpfung mittels eines Piezoaktoren
EP1908985A1 (fr) * 2006-10-02 2008-04-09 Delphi Technologies, Inc. Amortisseur magnétorhéologique bi-tube
DE102010051872B4 (de) * 2010-11-22 2021-10-28 Hitachi Astemo, Ltd. Schwingungsdämpferanordnung
DE102012016948A1 (de) * 2012-08-28 2014-03-06 Inventus Engineering Gmbh Dämpfer mit Einwegkreislauf und Verfahren

Family Cites Families (9)

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Publication number Priority date Publication date Assignee Title
IT208326Z2 (it) * 1986-11-07 1988-05-28 Altecna Azienda Della Weber S Elettrovalvola regolatrice di pressione particolarmente per circuiti ad alta pressione di impianti di iniezione del combustibile per motori a combustione interna
US5161653A (en) * 1989-04-18 1992-11-10 Hare Sr Nicholas S Electro-rheological shock absorber
US5158109A (en) * 1989-04-18 1992-10-27 Hare Sr Nicholas S Electro-rheological valve
US5099884A (en) * 1991-05-24 1992-03-31 Ntn Technical Center (U.S.A.), Inc. Electrorheological fluid plate valve
DE69332868T2 (de) * 1992-06-18 2003-12-11 Lord Corp., Erie Magnetorheologische Flüssigkeitsvorrichtungen
DE4431405A1 (de) * 1994-09-02 1996-03-07 Wilhelm Steinhoff Nachf Gmbh Hydraulisches Servo-Wegeventil
GB9613239D0 (en) * 1996-06-25 1996-08-28 Er Fluid Dev Improvements in or relating to high speed actuators and vibrators based on electro-rheological fluids
DE19714045B4 (de) * 1997-04-05 2005-03-10 Continental Teves Ag & Co Ohg Piezoelektrisches Fluidventil mit Druckausgleich
DE19725685B4 (de) * 1997-06-18 2006-11-30 Fludicon Gmbh Fluid-Pumpe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0116503A1 *

Also Published As

Publication number Publication date
WO2001016503A1 (fr) 2001-03-08
AU6712700A (en) 2001-03-26
GB9920311D0 (en) 1999-11-03

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