CN102465992A

CN102465992A - Damper

Info

Publication number: CN102465992A
Application number: CN2010105466692A
Authority: CN
Inventors: P·希武萨尔茨基; W·威德拉; O·克拉兹维斯基
Original assignee: BWI Co Ltd SA
Current assignee: BWI Co Ltd SA
Priority date: 2010-11-11
Filing date: 2010-11-11
Publication date: 2012-05-23
Also published as: CN106122344A; CN106122344B

Abstract

The invention discloses a linear hydraulic damper. The hydraulic damper comprises a main pipe which is divided by a piston rod extending through an expansion chamber. The damper is also provided with a hydraulic resilience stop which is named HRS and is fixed in the extension chamber and comprises HRS pipes which limit the main pipes, a bottom, inlets, and HRS pistons; and the HRS pistons are freely and slidably arranged on the rod, and the diameters of the HRS pistons are adjusted to form the HRS pipes, the HRS pistons are provided with at least one fluid passage with a directed basic axial direction. The axial displacement of the HRS pistons is limited between the resilience stop and HRS rings; and the HRS pistons, the resilience stop and the HRS rings are all fixed on the rod. When the pistons are pressed against the HRS rings, the fluid passages are opened to ensure that fluid flows; and when the pistons are pressed against the resilience stop, the fluid passages are sealed. The HRS is also provided with at least one fluid passage which ensures that an HRS chamber is connected with the extension chamber, and provides outlets through which the fluid leaves for fluid, so HRS damping is generated; the HRS damping can be adjusted, and when the HRS pistons penetrates the HRS pipes, the HRS damping changes; and the relative position of the HRS pistons and the HRS pipes determines the sizes of the outlets.

Description

Vibration damper

Technical field

The present invention relates to a kind of dydraulic shock absorber, it can be used for automobile or motorcycle, is more especially to relate to a kind of hydraulic pressure resilience stopper.

Background technique

Dydraulic shock absorber is usually designed to like this, and the degree of damping that is provided by vibration damper becomes higher in the end of resilience and compression stroke.To prevent metal and the backing sound of Metal Contact between stopping suddenly of piston rod operation and each parts in vibration damper at the additional damping that end provides.Proposed various mechanism and higher degree of damping is provided at two terminals.For example, WO2005/106282 has proposed a kind of hydraulic pressure resilience stopper, is called HRS, and it comprises the coaxial hydraulic damper that is assemblied in the extended cavity chamber interior of vibration damper, and only reaches when extending completely at vibration damper and just operate.Such device comprises the inner HRS pipe of pipe that is fixed on vibration damper.The HRS pipe is provided with the import of cutting sth. askew and is assemblied in the HRS coupling piston on the mobile jib.The HRS piston is provided at an outer portion with circular groove; The elastic opening ring of annular is arranged in this circular groove; This elastic opening ring can freely endwisely slip between two flanges at said groove on the HRS piston; When vibration damper extends or during compression, because the fluid of operation makes said ring in groove, be compelled to carry out axial displacement in opposite direction.Encircle and self be provided with than major path, should be designed to especially like this than major path, when compression, ring is against first flange of groove; This passage will be opened, and pass through thereby make fluid to move at an easy rate, when extending; Ring is against relative flange, and passage is by this flange seal, thereby anti-fluid is sent back to.

Under normal circumstances, when complete extended position was left in the vibration damper operation, the HRS piston was positioned at the outside of HRS pipe, and HRS and inoperation.When vibration damper when extending fully, the HRS piston penetrates in the HRS pipe through the opening of cutting sth. askew of HRS pipe, therefore makes some hydraulic fluids in the HRS chamber be under the pressure.The elastic opening ring that is assemblied on the pipe roundedly slides in that pipe is inner contiguously, still against the flange of groove, thus fluid-encapsulated passage.Because ring is opened, therefore the two ends of ring export thereby produce the demarcation that is used for fluid against each other.This demarcation outlet is that the fluid that in the HRS chamber, is under the pressure can leave the unique path in the main chamber that returns vibration damper, and therefore the final mean annual increment movement for piston rod provides additional damping.When end of travel, provide finally by the rubber pad in being fixed on the piston or being responsible for to stop.It has avoided metal and Metal Contact when extending fully.When compression was returned, ring to be moving in groove against the mode of relative flange, thereby opened big fluid passage, therefore cancelled any additional damping function.

Such device and the similar scheme that is used as one-way valve owing to the various holes that in the HRS piston, provide all no longer adapt to the expection in market.The additional damping that when near end of travel, is provided by HRS is constant, and is confirmed by the cross section of demarcating outlet.And, contact with the final of metal in order to prevent metal, still be forced to and use rubber pad.This has increased parts and complexity.

Summary of the invention

The objective of the invention is through providing a kind of dydraulic shock absorber that is equipped with hydraulic pressure resilience stopper to solve these problems; This hydraulic pressure resilience stopper is called HRS; It provides the damping of end of travel, and variable function is followed in the damping of the trip end, and it is desirable to may be adjusted to the artificer.In addition, the present invention avoids contacting with metal inside at the metal of end of travel without any need for the device of pad type, and this has simplified manufacturing and assembling, has improved reliability simultaneously and has reduced overall cost.

The present invention is a kind of linear hydraulic vibration damper, and it comprises: be responsible for, this person in charge defines the main chamber that is full of fluid; Piston, this piston has bar, and this bar extends axially the extending end that passes the person in charge, and this piston is slidably mounted in the main chamber, and operates between the axial position of axial position that extends fully and compression fully with compact model and extension mode.Vibration damper also is provided with hydraulic pressure resilience stopper, and this hydraulic pressure resilience stopper is called HRS, and it is arranged among the person in charge, and comprises: the HRS pipe, and this HRS pipe is fixed among the person in charge, and this HRS pipe has the wall that internal surface is provided, and this internal surface is called the HRS pipe internal surface; And the HRS piston, this HRS piston is adjusted to the HRS pipe internal surface, and is installed on the bar.When vibration damper is in extension mode and during near complete extended position, the HRS piston gets into the HRS pipe through the import of HRS pipe, so that make extending end and the fluid between the HRS piston at the HRS pipe be under the pressure, more this stage of high compression is called the HRS damping stage.HRS also is provided with the fluid separating device, is used at the inner fluid that is under the pressure of HRS pipe the outlet of leading to main chamber being provided.

In addition, HRS comprises the device that is used for changing in the HRS damping stage HRS damping level.This exports through the change fluid and realizes.The HRS piston has been confirmed the fluid output of whole fluid separating device with respect to the position to axial of HRS pipe.

Preferably, this device provides the continuous increase of damping level in the HRS damping stage.

Be more especially, the fluid separating device is arranged in the cylindrical wall of HRS pipe, and extends towards the HRS pipe is inner from the import of HRS pipe.

HRS also is provided with the fluid inlet device, and when vibration damper was in compact model, this fluid inlet device was opened, thereby makes fluid can be passed to the inside of HRS pipe from main chamber.When vibration damper was in extension mode, the fluid inlet device was closed, and therefore stoped fluid to be passed to HRS pipe inside from main chamber.And the fluid inlet device is in the HRS piston.

More particularly, the fluid inlet device comprises at least one hole.Also have, the HRS piston is slidably mounted on the bar between compression stop surface and extension stop surface.When vibration damper was in compact model, HRS piston axial translation became against the compression stop surface, and this makes the hole open.When vibration damper was in extension mode, HRS piston axial translation became against extending stop surface, and this closes this hole.

And the HRS piston is provided with the inner radial convex shoulder, and this inner radial convex shoulder forms recess, like this, in compact model, the HRS piston in the at of recess against the compression stop surface.

Preferably, for the HRS damping that obtains to change, the fluid separating device has been confirmed a cross section, and fluid leaves through this cross section, and this cross section axis is to variation.

An also advantage of the present invention is in the end sections of HRS pipe, not have the fluid separating device, and like this, vibration damper reached its maximum and extends before any interior metal and Metal Contact, because some fluids are limited and can not leave.

Also have, the import of HRS pipe is provided with oblique cutting part, and is inner thereby guiding HRS piston gets into the HRS pipe.

Another of HRS pipe possibly embodiment comprise a plurality of fluid separating devices with different length.This can advantageously make things convenient for the manufacturing of HRS pipe.

Also have, the fluid separating device can comprise at least one groove, and this groove is arranged in the HRS wall vertically, and manages inside from the import of HRS pipe towards HRS and extend, and inside has bigger cross section to this groove than managing more at HRS in HRS pipe inlet.

Also one possibly embodiment be that fluid output is the annular space between HRS pipe internal surface and HRS outer surface of piston.The HRS pipe internal surface is a convergent, and bigger in HRS pipe inlet, therefore when the HRS piston further is bonded on HRS pipe inside, changes the cross section of annular space.

Also can select, cavity can be between the person in charge and HRS pipe.Cavity leads to the extension chamber.Like this, the fluid separating device comprises at least one through hole, and this through hole is in the HRS wall, and the inside that makes HRS manage is connected with cavity.In this structure, fluid is through the hole and leave to extending chamber through cavity then.

Preferably, for easy manufacturing, because the HRS pipe is fixed on the person in charge, so it also can be integral with the person in charge.

Description of drawings

In conjunction with the drawings with reference to following detailed description, will be easy to and understand other advantage of the present invention better, in the accompanying drawing:

Fig. 1 is in the vehicle suspension system of compression fully.

Fig. 2 is in the vehicle suspension system that extends fully.

Fig. 3 is the front view of the inside detail of vibration damper.

Fig. 4 is the section S 1 of HRS pipe.

Fig. 5 is the section S 2 of HRS pipe.

Fig. 6 is the sectional view of vibration damper under compressive state;

The sectional view that Fig. 7 is a vibration damper when extending fully;

Fig. 8 is the sectional view of HRS when extending.

Fig. 9 is the section S 3 of HRS.

Figure 10 is the view of getting in touch of HRS pipe and HRS damping.

Figure 10 a is the sectional view of HRS pipe.

Figure 10 b is the plotted curve of groove along the cross section of axis A.

Figure 10 c is the plotted curve of HRS damping along axis A.

Figure 11 is the view that is provided with the HRS pipe of conical slit.

Figure 12 is the view of HRS pipe that is provided with the slit of all lengths.

Figure 13 is the sectional view of HRS, in the HRS pipe, has cavity and hole.

Figure 14 is the sectional view of conical HRS pipe.

Figure 15 is and the sectional view of being responsible for all-in-one-piece HRS pipe.

Embodiment

Fig. 1 and 2 has represented the suspension system of vehicle 10, and this suspension system comprises vibration damper 20, and this vibration damper 20 makes wheel steering joint (knuckle) 12 or cantilever be connected with automobile body 14 along axis A.The scope of the total length L of vibration damper 20 is for from being attached at the bottom mounting points 16 of cantilever or wheel steering joint on 12 to the top mounting points 18 (being called body end 18) that is attached on the automobile body 14.In Fig. 1, system representation is for being in compression (FC) position fully, and vibration damper 20 is in its shortest length L, and wheel 12 is as much as possible near automobile body 14.In Fig. 2, system representation extends (FE) position fully for being in, and vibration damper 20 is in its extreme length L, and wheel 12 is as much as possible away from automobile body 14.

For easy explanation, axis A is orientated from wheel 12 towards automobile body 14.

As Fig. 3 roughly shown in, dydraulic shock absorber 20 comprises is responsible for 22, the piston 32 that is fixed on the tail end of bar 36 can endwisely slip and be installed among this person in charge 22 (along axis A).Bar 36 axially stretches out towards automobile body 14 to be responsible for outside 22, and this bar 36 is attached on the automobile body 14.

The person in charge 22 inside is limited by the inner cylindrical surface 24 of confirming main chamber 38, and this inner cylindrical surface 24 has inside diameter D 1.Piston 32 has the outside cylindrical surface 74 that diameter is D2, and this diameter D2 and inside diameter D 1 are joined.Bar 36 has shank diameter D3.

Piston 32 is divided into main chamber 38 compression chamber 40 and extends chamber 42, and this compression chamber 40 has the compressed ends of being confirmed by road wheel end 16 26, and this extension chamber 42 has the extending end of being confirmed by body end 18 28.Compressed ends 26 sealings.Extending end 28 has the hole, is used to make bar 36 to protrude outwardly to automobile body 14.The sealing system (not shown) is around bar 36 sealing extending ends 28.Be responsible for 22 and be full of hydraulic fluid 44.When the length L of vibration damper 20 changed, piston 32 had been responsible for 22 inner axial translations, thereby made fluid 44 superchargings in

chamber

40 and 42, so cushioned the displacement of wheel 12 with respect to automobile body 14.

This specification is based on single-tube shock absorber 20, wherein, and in master cylinders 22, because cubage compensation is carried out in the compression of the unsteady gas cap (not shown) of gas through sealing main vapour 22.The present invention also can be used for dual tube shock absorber 20; Wherein, Master cylinders 22 comprises exterior tube and the inner tube by the sealing of base portion valve (not shown); Like this, when piston 32 when being responsible for 22 inner translations, can be transferred to another

chamber

40,42 from a chamber through the for example control bypass (not shown) between bar 36 and bar guide at vibration damper 20 inner fluids 44.

Hydraulic pressure resilience stopper 50 (being called HRS 50) is arranged in to be responsible for 22 inside and to be positioned at extending end 28.

HRS 50 comprises pipe 52 (being called HRS pipe 52), piston 70 (being called HRS piston 70), stopper 84 (being called resilience stopper 84) and ring 86 (being called HRS ring 86).

HRS pipe 52 be fixed on be responsible for 22 inner and at extending end 28 places.HRS pipe 52 has wall 54 (being called HRS wall 54), and this wall 54 has internal surface 56 (being called HRS pipe internal surface 56), and this internal surface 56 has diameter D4 (being called HRS bore D4), and this diameter D4 is less than inside diameter D 1.HRS pipe 52 58 extends axially to opening 60 from the bottom, and this bottom 58 is called HRS bottom 58, is positioned to against the extending end 28 of being responsible for 22; And have the hole, so that make bar 36 to stretch out, this opening 60 is called the import 60 of HRS pipe; Be oriented towards compressed ends 26, and be provided with oblique cutting part 62.HRS pipe 52 also is provided with groove 64, and this groove 64 is in HRS wall 54.Groove 64 extends axially towards HRS bottom 58 from the import 60 of HRS pipe.Groove 64 finished before arriving HRS bottom 58.Each groove 64 has cross section 68.As shown in Figure 3 and Fig. 4 (section S 1) and Fig. 5 (section S 2) in detail shown in, cross section 68 is because HRS pipe import 60 (section S 1) and bigger, and HRS bottom 58 (section S 2) near, reduces continuously during measurement.

HRS piston 70 has thick dish type geometrical shape; It has inner cylindrical surface 72 and outside cylindrical surface 74 and two

parallel surfaces

76,78, and these two

parallel surfaces

76,78 are expressed as stop surface 76 and the ring surface 78 that barrel surface 72 internally extends to outside cylindrical surface 74.Ring surface 78 is provided with the inner radial convex shoulder that forms recess 79, these recess 79 contiguous inner cylindrical surface 72.Inner cylindrical surface 72 has diameter D6, is called HRS piston inner diameter D6, and it is greater than shank diameter D3.Outside cylindrical surface 74 has diameter D5, is called HRS piston external diameter D5, and it is conditioned, and D4 is little than the HRS bore.HRS piston 70 also is provided with at least one penetration channel 80, is called fluid inlet 80, and it makes stop surface 76 be connected with ring surface 78.In stop surface 76, the opening of fluid inlet 80 is whole, and to be included in round C8 inner, and this circle C8 has axis A and diameter D8 (being called C diameter D8) (Fig. 9).

HRS piston 70 is installed on the bar 36, and the poor portion between HRS piston inner diameter D6 and shank diameter D3 makes that HRS piston 70 can be along bar 36 axial translation freely, and can compensate the radial missing between HRS piston 70, bar 36 and HRS pipe 52.HRS piston 70 is arranged between stopper 84 (being called resilience stopper 84) and the ring 86 (being called HRS ring 86), and this stopper 84 all is fixed on the bar 36 with ring 86.Resilience stopper 84 encircles 86 more near piston 32 than HRS.When in place, stop surface 76 is towards resilience stopper 84, and ring surface 78 is towards HRS ring 86.

Resilience stopper 84 is radially to extend to D outer diameter 7 flat disc of (being called resilience stopper diameter D7) from bar 36.As shown in Figure 7, resilience stopper diameter D7 is less than HRS piston external diameter D5, and greater than C diameter D8.

When vibration damper 20 leaves complete extended position (FE) when (Fig. 2) mediating, like Fig. 3 and shown in Figure 6, HRS piston 70 is in the outside of HRS pipe 52.

Fig. 3 has represented that vibration damper 20 is in extension mode ME, shown in arrow DE.Fluid 44 in extending chamber 42 applies axial direction power F78 on ring surface 78, this axial direction power F78 promotes HRS piston 70, and like this, its stop surface 76 is against the extension stop surface 85 of resilience stopper 84.Resilience stopper diameter D7 is greater than C diameter D8, and fluid inlet 80 is by extending stop surface 85 sealings.Fluid 44 can not flow through fluid inlet 80, and can only be along in the outside cylindrical surface 74 of HRS piston be responsible for that the fluid stream F1 around HRS piston 70 flows between 22.

Fig. 6 has represented that vibration damper 20 is in compact model MC, shown in arrow DC.Fluid 44 in extending chamber 42 applies axial direction power F76 on stop surface 76, this axial direction power F76 promotes HRS piston 70.HRS piston 70 slides on bar 36, like this, and the compression stop surface 87 of the base abuts HRS of recess 79 ring 86, and HRS ring 86 is fully in recess 79 inside, and the axial thickness of HRS ring 86 is less than the axial depth of recess 79.This makes fluid inlet 80 open, and be present in the fluid 44 that extends in the chamber 42 can be along in the outside cylindrical surface 74 of HRS piston be responsible for that the fluid stream F2 around HRS piston 70 flows between 22, it also can flow through fluid inlet 80 simultaneously.

HRS piston 70 is used as one-way valve, thereby when compression, opens fluid inlet 80, when extending, closes fluid inlet 80.

Fig. 7 has represented to extend when vibration damper 20 structure of ME and the HRS 50 when extending FE fully.HRS piston 70 engages in HRS pipe 52.Oblique cutting part 62 helps this joint.HRS piston inner diameter D6 is greater than shank diameter D3, and oblique cutting part 62 guiding HRS pistons 70 get into HRS pipe 52.This can smoothly get into, thereby avoids obstruction or HRS piston 70 firmly against (hard abutment) HRS pipe 52.

HRS chamber 88 (some fluids 44 are in this HRS chamber 88) at this moment is formed at HRS and manages 52 inside, and between the HRS piston 70 of HRS bottom 58 and entering, extends.

Fig. 8 has represented HRS 50 structures when vibration damper 20 is in extension mode ME and on the state shown in Fig. 7, further extend.HRS piston 70 advances HRS pipe 52.The fluid 44 that is present in the HRS chamber 88 is under the pressure, and it onlyly possibly export 66 (being called HRS outlet 66) depend on the groove 64 above the HRS piston 70, and fluid 44 is by force through this groove 64, and longshore current body stream F3 gets into and extends chamber 42.

This produces damping 90, is called HRS damping 90.HRS damping 90 is superimposed upon in the damping that is normally provided by vibration damper 20.HRS piston 70 can be near HRS bottom 58, as long as the fluid 44 that is under the pressure can leave HRS chamber 88.When the end of HRS piston 70 arrival slots 64, the fluid 44 that is retained in the HRS chamber 88 still can (because foozle) leave through the bypass (not shown) with between the outside cylindrical surface 74 and HRS pipe internal surface 54 of HRS piston 70.

Operational phase when HRS provides HRS damping 90 is called the HRS damping stage.

The power of HRS damping 90 is functions of the cross section of HRS outlet 66, and fluid 44 flows through HRS piston 70 (Fig. 9-section S 3) through this HRS outlet 66.The relative velocity that the viscosity of fluid 44 and HRS piston 70 join in the HRS pipe 52 also influences HRS damping 90.Because the variable cross-section 68 of groove 64, fluid 44 are left during than this end when the HRS damping stage begins in stage more easily.This has produced variable force HRS damping 90.

When at full speed extending, the extension of vibration damper 20 preferably stopped before reaching interior metal and Metal Contact, because groove 64 stopped before arriving HRS bottom 58.

When extending with unusual low speed, vibration damper 20 can further extend.HRS ring 86 is hidden in recess 79 inside fully.The fluid 44 that is present in the HRS chamber 88 can leave through the bypass (not shown) with between the outside cylindrical surface 74 of HRS piston 70 and HRS pipe internal surface 54.Extension can be proceeded, up to and till metal between the HRS piston 70 of being responsible for 22 extending end 28 and the Metal Contact.Therefore, the maximum extended length L of the measurement of vibration damper 20 is identical with the standard vibration damper that does not have HRS 50.When being in metal and Metal Contact, the power that arrives the person in charge 22 from bar 36 will be transmitted through HRS piston 70, rather than transmit through HRS ring 86.

Figure 10 is three parts, i.e. Figure 10 a, Figure 10 b and Figure 10 c.It has represented that HRS damping 90 is as the function of HRS piston 70 with respect to the position of HRS pipe 52.

Figure 10 a is the sectional view (HRS piston 70 not shown) of HRS 50 along axis A.HRS pipe 52 is provided with the groove 64 of variable cross section, and this groove 64 provides variable HRS outlet 66, and this HRS outlet is managed at entering HRS and reduced in 52 o'clock.

Figure 10 b has represented changes of section relevant with Figure 10 a, HRS outlet 66.Longitudinally position and the HRS of axis A export 66 cross sections along axis of pitch A66 on Figure 10 b, to have represented to manage 52 inside at HRS by HRS piston 70.The cross section that Figure 10 b has represented HRS outlet 66 further gets into HRS at HRS piston 70 and manages and reduced in 52 o'clock.

Figure 10 c has represented the HRS damping 90 relevant with 10b with Figure 10 a.Figure 10 c longitudinally axis A and axis of pitch A90 representes, wherein can confirm the power of HRS damping 90.In the system of axis A-A 90, the HRS damping curve has loop shape, has path E that when extending, in the HRS damping stage, follows and the path C that when compression, follows.Only represented a curve among Figure 10 c, all other parameters are considered to constant (viscosity and speed).

Figure 10 c is explained as follows:

To putting P2, HRS piston 70 penetrates HRS pipe 52 along path E from a P1, and the power of HRS damping 90 reduces along with HRS outlet 66 and increases.Fluid inlet 80 is closed.

To putting P3, HRS piston 70 leaves HRS pipe 52 along path C from a P2, HRS damping 90 minimums, and this is because fluid inlet 80 is opened.

Introduce several optional embodiment of the present invention below.

Figure 11 is an another embodiment of the present invention, and wherein, groove 64 is replaced by V-arrangement slit 64, and this V-arrangement slit 64 is big opening owing to oblique cutting part 62 has, and near HRS bottom 58 time, reduces.Preferably, V-arrangement slit 64 is at two barrel surface split sheds of HRS wall 54.

Figure 12 is an another embodiment of the present invention.In HRS pipe 52, groove 64 is replaced by a plurality of straight slit 64 with different length.In this embodiment, HRS outlet 66 is confirmed with a plurality of slits that extend chamber 42 64 by connecting HRS chamber 88.This number further penetrates at HRS piston 70 and reduces when HRS manages in 52, thereby reduces HRS outlet 66, therefore can have variable HRS damping 90.Preferably, slit 64 is opened in two barrel surfaces of HRS wall 54.

Figure 13 is an another embodiment of the present invention.Cavity 92 extends towards extending end 28 from extending chamber 42 between the person in charge 22 and HRS pipe 52.HRS pipe 52 also is provided with a plurality of radial direction through hole 94, and these radial direction through hole 94 make HRS chamber 88 be connected with cavity 92.The fluid 44 that is present in the HRS chamber 88 can leave to cavity 92 through these holes 94, and the final extension chamber 42 that gets into, shown in arrow F4.In this embodiment, HRS outlet 66 confirms that by a plurality of holes 94 fluid 44 can leave through these holes.This number further joins at HRS piston 70 and reduces when HRS manages in 52.In this embodiment, cavity 92 can adopt various geometrical shapies, for example the groove of axial orientation, a plurality of groove or annular space.

Figure 14 is an another embodiment of the present invention.The internal surface of HRS pipe 52 is conical, and therefore, the cross section of HRS outlet 66 joins at HRS piston 70 and reduces when HRS manages in 52.Shown in arrow F5, through the fluid 44 generation HRS dampings 90 of HRS outlet 66.

Figure 15 is an another embodiment of the present invention.HRS pipe 52 is integral with the person in charge 22.This can advantageously reduce part count, and makes and assemble processing easily.

A plurality of different embodiments can adapt to the HRS piston 70 as one-way valve.For example, HRS piston 70 can be fixed on the bar 36, and safety check is set.Safety check can comprise bead or dish, and this bead or dish are closed in the cone of fluid import 80 that is provided with in the HRS piston 70 when vibration damper extends, and when vibration damper 20 compressions, opens this fluid inlet.This safety check also can comprise elastic device, and spring for example is so that promote bead or dish.

Also have, fluid inlet 80 is introduced and is the hole.Also can select, fluid inlet 80 can comprise groove, and this groove and extends to ring surface 78 from stop surface 76 in inner cylindrical surface 72.

Claims

1. a linear hydraulic vibration damper (20), it comprises: be responsible for (22), the said person in charge limits the main chamber (38) that is full of fluid (44); Piston (32); Said piston has the bar (36) of the extending end (28) that extends through the said person in charge (22) vertically; Said piston (32) can be slidably mounted in the said main chamber (38), and is extending axial position (FE) fully and compressing fully between the axial position (FC) with compact model (MC) and extension mode (ME) operation;

Said vibration damper (20) also is provided with hydraulic pressure resilience stopper (50), and said hydraulic pressure resilience stopper is called HRS (50), and it is arranged among the said person in charge (22) and comprises:

HRS manages (52), and said HRS pipe is fixed on the said person in charge (22), and said HRS pipe (52) has wall (54), and said wall (54) is provided with the internal surface (56) that is called as HRS pipe internal surface (56); And

HRS piston (70); Said HRS piston is adjusted to said HRS pipe internal surface (56) and is installed on the said bar (36); Make when said vibration damper (20) is in said extension mode (ME) and approaching extended position (FE) fully; Said HRS piston (70) gets in the said HRS pipe (52) through HRS pipe import (60), so that be under the pressure at the extending end (58) of said HRS pipe (52) and the fluid (44) between the said HRS piston (70), the stage of this higher compression is called the HRS damping stage;

Said HRS (50) also is provided with fluid separating device (64), and being used for provides the outlet of leading to said main chamber (38) to the said fluid (44) that the inside at said HRS pipe (52) is under the pressure;

It is characterized in that: said HRS (50) comprises and is used for changing the device (66,64,70) of HRS damping level in the said HRS damping stage through the output that changes said fluid (44), the output of the fluid (44) of whole said fluid separating device (64) is confirmed in the position to axial that said HRS piston (70) is managed (52) with respect to said HRS.

2. linear hydraulic vibration damper according to claim 1 (20) is characterized in that: said device (66) provides increasing continuously of damping level in the said HRS damping stage.

3. according to aforementioned any described linear hydraulic vibration damper of a claim (20), it is characterized in that: said fluid separating device (64) is arranged in the cylindrical wall (56) of said HRS pipe (52).

4. according to aforementioned any described linear hydraulic vibration damper of a claim (20), it is characterized in that: said fluid separating device (64) extends the inside towards said HRS pipe (52) from said HRS pipe import (60).

5. according to aforementioned any described linear hydraulic vibration damper of a claim (20); It is characterized in that: said HRS (50) also is provided with fluid inlet device (80); When said vibration damper (20) is in said compact model (MC); Said fluid inlet device (80) is opened, thereby makes said fluid (44) can be sent to the inside of said HRS pipe (52) from said main chamber (38), when said vibration damper (20) is in said extension mode (ME); Said fluid inlet device (80) is closed, thereby stops said fluid (44) to be sent to the inside of said HRS pipe (52) from said main chamber (38).

6. linear hydraulic vibration damper according to claim 5 (20) is characterized in that: said fluid inlet device (80) is in the said HRS piston (70).

7. linear hydraulic vibration damper according to claim 6 (20); It is characterized in that: said fluid inlet device (80) comprises at least one hole (80); Said HRS piston (70) can be slidably mounted on the said bar (36) between compression stop surface (87) and extension stop surface (85), and when said vibration damper (20) was in said compact model (MC), said HRS piston (70) translation vertically became against said compression stop surface (87); This makes said hole (80) open; When said vibration damper (20) was in said extension mode (ME), said HRS piston (70) translation vertically became against said extension stop surface (85), and this closes said hole (80).

8. linear hydraulic vibration damper according to claim 7 (20); It is characterized in that: said HRS piston (70) also is provided with the inner radial convex shoulder that forms recess (79); Thereby in said compact model (MC), said HRS piston (70) is at the said compression stop surface of the base abuts of said recess (79) (87).

According to aforementioned any described linear hydraulic vibration damper of a claim (20) of claim 4 combination; It is characterized in that: said fluid separating device (64) limits cross section (68); Said fluid (44) leaves through said cross section, and said cross section (68) changes vertically.

10. according to aforementioned any described linear hydraulic vibration damper of a claim (20), it is characterized in that: in said HRS pipe (52), comprise pipe inlet part and bottom part, said fluid separating device (64) only is arranged in the said pipe inlet part.

11. according to aforementioned any described linear hydraulic vibration damper of a claim (20), it is characterized in that: said HRS pipe import (60) is provided with oblique cutting part (62).

12. according to aforementioned any described linear hydraulic vibration damper of a claim (20); It is characterized in that: said fluid separating device (64) comprises at least one groove (64); Said at least one groove is arranged in the said HRS wall (54) and the extension of the inside towards said HRS pipe (52) from said HRS pipe import (60) vertically, and the cross section (68) that said groove (64) is located in said HRS pipe import (60) is bigger than the more inner cross section of locating at said HRS pipe (52).

13. according to any described linear hydraulic vibration damper (20) in the claim 1 to 11; It is characterized in that: said fluid output (64) is the annular space (96) that is positioned between said HRS pipe internal surface (56) and the said HRS outer surface of piston (74); Said HRS pipe internal surface (56) is a convergent; And locate greatlyyer in said HRS pipe import (60), therefore further join the cross section (68) that changes said annular space (96) when HRS manages the inside of (52) to when said HRS piston (70).

14. according to any described linear hydraulic vibration damper (20) in the claim 1 to 11; It is characterized in that: between the said person in charge (22) and said HRS pipe (52), have cavity (92); Said cavity (92) leads to said extension chamber (42); Said fluid separating device (64) comprises at least one through hole (94), and said through hole is arranged in said HRS wall (54), and makes the inside of said HRS pipe (52) be connected with said cavity (92).

15. according to aforementioned any described linear hydraulic vibration damper of a claim (20), it is characterized in that: said HRS pipe (52) is integral with the said person in charge (22).