WO2008070932A1 - Améliorations d'amortisseur de choc de véhicule - Google Patents

Améliorations d'amortisseur de choc de véhicule Download PDF

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Publication number
WO2008070932A1
WO2008070932A1 PCT/AU2007/001941 AU2007001941W WO2008070932A1 WO 2008070932 A1 WO2008070932 A1 WO 2008070932A1 AU 2007001941 W AU2007001941 W AU 2007001941W WO 2008070932 A1 WO2008070932 A1 WO 2008070932A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
fluid
spring
shock absorber
passageway
Prior art date
Application number
PCT/AU2007/001941
Other languages
English (en)
Inventor
Vilo Niumeitolu
Original Assignee
Hot Shocks Pty 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
Priority claimed from AU2006906956A external-priority patent/AU2006906956A0/en
Application filed by Hot Shocks Pty Ltd filed Critical Hot Shocks Pty Ltd
Publication of WO2008070932A1 publication Critical patent/WO2008070932A1/fr

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
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages

Definitions

  • the present disclosure relates to a vehicle shock absorber and a valve for a vehicle shock absorber.
  • the present disclosure generally relates to twin tube design.
  • the twin tuoe design has two separate tubes, namely the pressure tube and the reserve tube, which are fitted between upper and lower mounting brackets with fluid as a working media filling the enclosed cavities.
  • a piston assembly is fitted within the pressure tube interior, which is an enclosed cavity, with a rod end connected to the vehicle chassis, and the other (lower) end of the shock absorber connected to the vehicle wheel assembly.
  • the piston of the shock absorber reciprocates inside the enclosed pressure tube cavity as the vehicle rides over a bump, forcing the fluid in and out via two restrictor valving systems, namely the rebound valve at the piston end and the compression valve at the pressure tube base, thereby converting fluid kinetic energy to heat energy. It is an object of the present of the disclosure to provide a shock absorber, and a ' valve for a " shock absorber, that at the very least, provide useful alternatives to known shock absorbers.
  • One aspect of the present disclosure includes a valve for a hydraulic shock absorber including a body having a fluid passageway passing there-through, a coil or helical tension spring comprising at least two windings positioned and retained in said fluid passageway, so that when the spring is unloaded, there is no gap between the windings thereof and the spring is thereby adapted to block the passage of fluid through said fluid passageway.
  • valve selectively permits fluid flow through the passageway when sufficient fluid pressure is reached that the fluid forces the successive windings of the spring apart.
  • valve is part of a shock absorber assembly, and its fluid passageway extends between a pair of fluid cavities in the shock absorber.
  • one of the cavities is a pressure tube of the shock absorber, and the other is a reservoir of the shock absorber.
  • valve body includes an inner portion and an outer portion, which toget ⁇ er define a cavity there-between.
  • spring is positioned in the cavity between the inner and outer— portions of the vaive body.
  • valve further includes an intermediated member located in the cavity between the inner and outer portions of the valve body.
  • the spring is positioned between the intermediate member and the inner portion of the valve body.
  • each of the intermediate member and the inner portion of the valve body there is at least one hole passing through each of the intermediate member and the inner portion of the valve body, said holes forming part of the fluid passageway, and being adapted to permit fluid flow between the pressure chamber and the cavity in the valve body,
  • the holes in the intermediate member and the inner portion of the valve body are substantially aligned.
  • valve is adapted so that fluid flow past the spring is maintained in a direction that is substantially perpendicular to the longitudinal axis of the spring.
  • the disclosure includes a hydraulic shock absorber including a valve as claimed in any one of the preceding claims.
  • the disclosure includes a shock absorber including a valve that is adapted to control fluid flow between a pressure tube and a reservoir of the same, and to act as a rebound valve when fluid flows in a first direction between the two, and a compression valve when fluid flows in the opposite direction.
  • the disclosure includes a valve for a shock absorber that is adapted to control fluid flow between a pressure tube and reservoir of the same, and to act as a rebound valve when fluid flows in a first direction, and a compression vaJve when fluid flows in the opposite direction.
  • valve includes means for preloading the coil or helical tension spring so as to increase the fluid flow pressure required before fluid can pass this.
  • valve includes adjustment means for adjusting the degree of preload applied by the means for preloading the coil or helical tension spring.
  • valve includes a fluid bypass passageway which permits at least a portion of the fluid to bypass the coil or helical tension spring when fluid flows in a given direction.
  • valve includes a non-return valve that prevents flow of fluid through the bypass passageway when fluid flow is reversed.
  • the coil or helical tension spring is made from a material that adapts it to act as an armature under the influence of an electromagnetic field, and the resultant electromagnetic force may be used to preload the spring by either placing this in compression or under tension.
  • the electromagnetic field is created by an electromagnetic coil or solenoid.
  • the disclosure includes a shock absorber assembly including a valve as disclosed above.
  • this shock absorber includes two valves as disclosed above, one serving to regulate compression, and the other rebound.
  • the disclosure includes a valve for a hydraulic shock absorber including a body having a fluid passageway passing there-through, the body flexibly retaining a coil or helical tension spring comprising at least two windings by its ends so that this is positioned in said fluid passageway so the direction of fluid flow is maintained substantially perpendicular to the springs longitudina ⁇ axis, and wherein in use, when the spring is unloaded, there is no gap between the windings thereof and the spring is thereby adapted to block the passage of fluid through said fluid passageway, until sufficient fluid pressure is reached that the fluid forces the successive windings of the spring apart.
  • the coil or helical tension spring is made from wire of substantially constant cross-sectional shape.
  • the cross-sectional shape of the wire is one of round, square, or a combination of these, such as an arch or u-shape.
  • Figure 1 is a cross sectional side view through an exemplary shock absorber
  • Figure 2 is a cross sectional view through the exemplary valve assembly of the exemplary shock absorber in Figure 1 ;
  • Figure 3 is an isometric detailed view of the helical spring in the valve assembly
  • Figure 4 is an enlarged partial view of the spring wire in Figure 3;
  • Figure 5 is an isometric detailed view of the helical spring in the valve assembly according to a further aspect
  • Figure 6 is an enlarged partial view of the spring wire in Figure 5;
  • Figure 7 is an isometric detailed view of the helical spring in the valve assembly according to a further aspect;
  • Figure 8 is an enlarged partial view of the spring wire in Figure 7;
  • Figure 9 is a perspective view of an exemplary valve according to a further aspect, this valve incorporating adjustment means;
  • Figure 10 is a cross-sectional view through the valve illustrated in Figure 9;
  • Figure 11 is a side view of an exemplary shock absorber assembly including two of the valves of the type illustrated in Figures 9 and 10;
  • Figure 12 rs a cross-sectional view through the shock absorber assembly in Figure 11 , taken along line AA;
  • Figure 13 is a cross-sectional view through the shock absorber assembly in Figure 11 , taken along line BB;
  • Figure 14 is a cross-sectional view through the shock absorber assembly in Figure 11, taken along line CC;
  • Figure 15 is a cross-sectional view through an exemplary valve assembly according to a further aspect
  • Figure 16 is a cross-sectional view through an exemplary valve assembly according to yet a further aspect, this valve assembly incorporating an electromagnetic coil;
  • Figure 17 Is a cross-sectional view through a shock absorber assembly
  • the hydraulic shock absorber includes a rod end eye clevis 1 that is adapted to be connected to a vehicle chassis, a piston rod 3 that connects to piston 8, which in turn fits inside the pressure tube 9 with a sliding fit and reciprocates in the central cavity 9a.
  • the valve assembly 11 is adapted to be fitted to a lower mounting bracket 12.
  • valve body of the valve assembly 11 includes an inner portion 15 and an outer portion 14, which together define a cavity there- between.
  • the valve further includes an intermediated member 16 located in the cavity between the inner 15 and outer portions 14 of the valve body.
  • the spring 20 is positioned in the cavity, between the intermediate member 16 and the inner portion 15 of the valve body, and is substantially enclosed and flexibly retained by these.
  • Figure 2 shows a sectional view of the valve assembly 11 where 14, 15 and 16 are the components of the valve body assembly. Items 15a and 16a are holes for fluid entry and exit from the cavity containing the helical spring 20, and which thereby form part of the fluid passageway through the valve. The resultant fluid flow direction then is maintained perpendicular to the helical tension springs longitudinal axis during entry and exit from the helical spring coil body.
  • the fluid fiow 17a and 17b is reversible and it can pass through a spring gap 20a between successive windings of the spring wire when fluid pressure is high enough to force the windings of the spring apart.
  • the neat fit of the helicaf spring 20 between the intermediate member 16 and the inner portion 15 of the valve body minimises the fluid leakage at the longitudinal ends of the helical spring.
  • the valve assembly 11 selectively- permits fluid flow through the passageway when sufficient fluid pressure is reached that the fluid forces the successive windings of the spring 20 apart.
  • the diameter (A) 1 the wire diameter (B) and the pitch dimension (C) of the helical spring can therefore be varied to achieve required damping force in the shock absorber unit.
  • the pressure tube 9 and the reserve tube 10 of the shock absorber may be an extruded profile body.
  • the bottom mounting brackets 12 allow the fitting of the valve assembly 11 in the bottom end thereof.
  • the valve 11 acts as a rebound valve when fluid flows in one direction, and a compression valve when the fluid flows in the opposite direction.
  • the valve 11 controls the flow of the working fluid to and from the pressure tube cavity 9 to reservoir cavities 10 and converts the fluid kinetic energy to heat energy.
  • the pitch dimension between two spring coils or windings described hereafter is, in preference, equal to the spring wire cross sectional height that is parallel to the spring longitudinal axis, which promotes no gap in between spring coils during the inert condition, hence preventing the fluid flow, unless the fluid flow has sufficient energy to force the spring coils open and create a gap between the helical spring coils for the fluid to flow through resulting in damping forces.
  • the gap between spring coils is in a spiral shape, which may affect the resultant, damping force.
  • the cross section of the helical spring wire may be circular, oval or square with corners that are predetermined radii, which assist in minimising the fluid flow turbulence as well as determining the resultant opening forces from the fluid flow.
  • a combination of two or more helical tension springs arranged in either parallel, arrangement or series arrangement adjacent to each other may be used to achieve the required damping forces. This combination may include springs of different material strength and spring index according to Hooke's law, or with different cross sectional shapes to regulate the relationship between damping forces produced against the displacement and velocity of the moving piston.
  • shock absorbers that are presently available are difficult to control the fluid flow rate, and hence these have limited control over damping forces, as it is needed.
  • shock absorbers that are presently available are capable of providing limited frequency adjustment when the frequency of wheel oscillation is high and damping forces are low, and when the frequency of wheel oscillation is low and the damping forces high.
  • valve 40 for a shock absorber the valve incorporating adjustment means.
  • the adjustment means includes a knob 42, the stem of which 44 is threaded into the upper valve housing 46 so that the valve 40 may be adjusted by turning this knob 42.
  • a preload spring 48 is positioned between the nose of the knob's stem 45 and a stem 52 of an upper valve spring guide (hereinafter referred to as the upper spring guide 54).
  • the knob stem 44, the preload spring 48 and the stem 52 of the upper valve spring guide 54 are all retained by a spacer 56 having a central bore passing therethrough.
  • apertures 62 there are a series of apertures 62 in the upper valve housing 46, and these are sized so as to permit fluid passage. When fluid passes in through these apertures 62, this may travel through slotted fluid passageways 64 in the lower housing portion 66 where it is met by a non return valve 70, which is biased (by a spring 72) into a position that prevents fluid flow in this direction unless fluid pressure is great enough to compress this spring 72 (hereinafter referred to as the non return spring 72). If fluid flow pressure in this direction is high enough, fluid may pass through the non-return valve 70 and escape from the valve assembly 40 via the central fluid passageway 76 in the valve assembly 40, thereby having bypassed the valve spring 60 entirely.
  • the non return valve 70 will not permit the passage of fluid via the slotted fluid passageways 64 in the lower housing portion 66, as the fluid pressure in this direction will help seal the non-return valve 70 against its seat. Instead, all fluid will be forced to try and pass the valve spring 60 before it can escape the valve assembly 40 via the apertures 62 in the upper valve housing 46. Moreover, the return of the valve spring 60 to its unloaded and closed position is slowed by fluid backpressure in the slotted fluid passageways 64.
  • valve assemblies 100 and 102 have been mounted in a shared housing 106 at the bottom end of the shock absorber assembly 104, the valve assemblies being connected by a fluid passageway 108 that extends between them, and which is best illustrated in Figure 14.
  • Figures 12 and 13 where the piston 1 10 in the shock absorber 104 is illustrated travelling upward, and fluid is being drawn into the pressure cavity 1 12.
  • the valve assembly 100 illustrated in Figure 12 is passing fluid via the non-return valve 114, i.e. via the slotted fluid passageways 1 16 in the lower housing portion.
  • valve assembly 102 illustrated in Figure 13 is receiving fluid from the reserve tube 118 via it's central fluid passageway 120.
  • the non-return valve 122 in this valve assembly 102 then is forcing fluid to try and pass the valve spring 124 before it can escape the valve via the apertures 126 in the upper valve housing and pass through the passageway 108 between the two valve assemblies to the other valve assembly 100.
  • This valve assembly 102 then is the 'rebound valve', as this is the valve assembly controlling fluid flow during the rebound stroke of the piston, the other valve assembly 100 is merely bypassing fluid.
  • valve assembly 100 and 102 would be the reverse of that illustrated in Figures 12 and 13, so that the valve assembly 102 illustrated in Figure 13 would be bypassing fluid, and the valve assembly 100 illustrated in Figure 12 would be controlling *luid flow, and this valve assembly would be the 'compression valve'.
  • shock absorber assembly 104 An advantage of the above described shock absorber assembly 104, is that its compression and rebound characteristics can be easily and finely tuned by turning the knob of the relevant valve assembly.
  • the knob may be substituted with a screw or socket, which might be adjustable using a special tool.
  • valve assembly 150 that is an adaptation of the valve assembly 40 illustrated in Figures 9 and 10.
  • the upper spring guide 151 includes a centrally positioned bore 152
  • the lower housing portion 154 includes a spigot 156 that is aligned with the bore 152, and which is sized so as to be received in the bore 152 with a sliding fit.
  • the spigot 156 In use, when fluid forces itself between the successive windings of the valve spring 158-, the spigot 156 is freed from the bore 152, and fluid may enter the bore. As fluid pressure drops, the gaps between the windings of the spring 158 close and the spigot 156 re-enters the bore 152 and meets resistance from the fluid trapped therein, which is then forced out of the bore via a vent passageway 160 that connects up with the valve spring seat 162 in the upper housing portion 164. In this way, the return of the valve spring 158 (i.e. the closure of the gaps between the successive windings of the spring) is slowed by fluid pressure acting on the spigot and valve spring ends, thereby creating a less damping force.
  • the return of the valve spring 158 i.e. the closure of the gaps between the successive windings of the spring
  • a restrictor fluid valve may be incorporated in the vent passageway 160 so that the rate of valve spring 158 return to the closed position may be tuned.
  • valve assembly 200 incorporating a ring shaped electromagnetic coil 202 that is used to externally preload the valve spring 204 (by either placing this under compression or in tension) so that the fluid pressure required to open the gap between the windings of the valve spring 204 is either increased or decreased.
  • This then allows the valve assembly 200 to be remotely adjustable, enabling the driver to tune the ride of the vehicle at will, while the vehicle is being operated.
  • Figure 17 illustrates a shock absorber assembly 220 utilising two of the valve assemblies 200 described directly above, one serving to regulate compression, and the other rebound.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Damping Devices (AREA)
  • Vehicle Body Suspensions (AREA)

Abstract

L'invention concerne une soupape pour un amortisseur de choc. La soupape comprend un corps ayant un passage de fluide passant à travers celui-ci, un ressort de traction à boudin ou hélicoïdal comprenant au moins deux enroulements placés dans ledit passage de fluide, de telle sorte que, lorsque le ressort est à vide, il n'y ait aucun espace entre les enroulements, et que le ressort soit de cette façon capable de bloquer le passage du fluide à travers ledit passage de fluide. Divers aspects de cette soupape sont divulgués. L'invention concerne également un amortisseur de choc comprenant un ou plusieurs aspects de cette soupape.
PCT/AU2007/001941 2006-12-14 2007-12-14 Améliorations d'amortisseur de choc de véhicule WO2008070932A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AU2006906956 2006-12-14
AU2006906956A AU2006906956A0 (en) 2006-12-14 The improvement of vehicle shock absorber

Publications (1)

Publication Number Publication Date
WO2008070932A1 true WO2008070932A1 (fr) 2008-06-19

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2999478A1 (fr) * 2012-12-19 2014-06-20 Emc Amortisseur hydraulique de vehicule supprimant les grincements

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU448866B2 (en) * 1970-03-26 1972-09-02 Girling Limited Improvements in or relating to fluid flow control valves
US4088207A (en) * 1975-05-23 1978-05-09 Tokico Ltd. Damping force generating device in hydraulic shock absorber
US4325468A (en) * 1979-01-31 1982-04-20 The United States Of America As Represented By The Secretary Of The Army Suspension control valve using coned spring disks
GB2231122A (en) * 1989-04-20 1990-11-07 Tokico Ltd Damping force adjusting hydraulic shock absorber
US5522486A (en) * 1993-11-13 1996-06-04 Delphi France Automotive Systems Damping valve for shock absorber
US5921360A (en) * 1997-06-05 1999-07-13 General Motors Corporation Digressive damper valve
GB2376514A (en) * 2001-06-13 2002-12-18 Delphi Tech Inc A hydraulic damper for a vehicle suspension system

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU448866B2 (en) * 1970-03-26 1972-09-02 Girling Limited Improvements in or relating to fluid flow control valves
US4088207A (en) * 1975-05-23 1978-05-09 Tokico Ltd. Damping force generating device in hydraulic shock absorber
US4325468A (en) * 1979-01-31 1982-04-20 The United States Of America As Represented By The Secretary Of The Army Suspension control valve using coned spring disks
GB2231122A (en) * 1989-04-20 1990-11-07 Tokico Ltd Damping force adjusting hydraulic shock absorber
US5522486A (en) * 1993-11-13 1996-06-04 Delphi France Automotive Systems Damping valve for shock absorber
US5921360A (en) * 1997-06-05 1999-07-13 General Motors Corporation Digressive damper valve
GB2376514A (en) * 2001-06-13 2002-12-18 Delphi Tech Inc A hydraulic damper for a vehicle suspension system

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2999478A1 (fr) * 2012-12-19 2014-06-20 Emc Amortisseur hydraulique de vehicule supprimant les grincements

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