CN101243266A

CN101243266A - Asymmetrical intake damper valve

Info

Publication number: CN101243266A
Application number: CNA2006800298616A
Authority: CN
Inventors: 乔安·皮兹曼; 沃尔特·斯皮里斯特; 弗兰克·高曼斯; 迈克尔·图泰乐斯
Original assignee: Tenneco Automotive Operating Co Inc
Current assignee: Tenneco Automotive Operating Co Inc
Priority date: 2005-08-15
Filing date: 2006-08-10
Publication date: 2008-08-13

Abstract

A valve assembly progressively opens to provide a smooth transition from a closed position to an open position. The fluid pressure reacts against a valve plate in a non-symmetrical manner to progressively open the valve. The valve can include a plurality of varying sized fluid passages or valve lands can be positioned eccentrically to each other to provide a non-symmetrical pressure area.

Description

Asymmetric intake damper valve

Technical field

Present application/patent relates generally to hydraulic bjuffer or vibration damper, is used for suspension system, for example is used for the suspension system of motor vehicle.More specifically, present application/patent relates to a kind of asymmetric intake damper valve, to reduce pressure oscillation when opening and closing valve.

Background technique

Statement in this part only provides the background information about present disclosure, may not constitute prior art.

Vibration damper uses with automobile suspension system, to absorb the undesirable vibration that occurs in the process of moving.In order to absorb undesirable vibration, vibration damper is connected between the band spring section (vehicle body) and no spring section (suspension) of vehicle usually.Piston is positioned at the pressure tube of vibration damper, and pressure tube is connected to the no spring section of vehicle.Piston is connected to the band spring section of automobile by the piston rod that extends through pressure tube.Piston is divided into pressure tube last active chamber and the following active chamber that all is filled with hydraulic fluid.Because piston is when vibration damper compression or stretching, can be limited in flowing of hydraulic fluid between the upper and lower active chamber by valve, so vibration damper can produce the damping force of offsetting vibration, this vibration might be sent to the band spring section from the no spring section of vehicle.In dual-tube shock absorber, reservoir or reserve chamber are limited between pressure tube and the reserve tube.Bottom valve also is used to produce damping force to offset the vibration that might be sent to the band spring section of automobile from the no spring section of vehicle between following active chamber and reserve chamber.

As mentioned above, for dual-tube shock absorber, when producing cushion load, be limited in flowing of buffer fluid between the upper and lower active chamber at the valve on the piston when shock absorber.When producing cushion load, be limited in flowing of the buffer fluid between the active chamber and reserve chamber down at the valve on the bottom valve when vibration damper compression.For mono-tube shock absorber, when producing cushion load, be limited in flowing of buffer fluid between the upper and lower active chamber at the valve on the piston when shock absorber or compression.In the process of moving, suspension system moves in vibrations (compression) and resilience (stretching).In the shock motion process, vibration damper compression and cause buffer fluid to move through bottom valve in dual-tube shock absorber is perhaps by the piston valve in mono-tube shock absorber.The orifice valve that is positioned on bottom valve or the piston is controlled flowing of buffer fluid, thereby produces cushion effect.In the resilience movement process, shock absorber and cause buffer fluid to move through piston in dual-tube shock absorber and mono-tube shock absorber.Be positioned at the cushion effect that flows and produced of the damped valve control buffer fluid on the piston.

In dual-tube shock absorber, piston and bottom valve generally comprise a plurality of pressure channels and a plurality of drawing passageway.In the shock motion process in dual-tube shock absorber, the pressure channel that orifice valve or bottom valve are opened in the bottom valve flows and the generation cushion load with the control fluid.Safety check on the piston is opened the pressure channel in the piston, and replacing the buffer fluid in the active chamber, but this safety check is not used in the generation cushion load.In the compression movement process, the drawing passageway of the orifice valve closure piston on the piston, and the drawing passageway of the closure of check ring bottom valve on the bottom valve.In the resilience movement process of dual-tube shock absorber, the drawing passageway that the orifice valve on piston is opened in the piston flows and the generation cushion load with the control fluid.Safety check on bottom valve is opened drawing passageway in the bottom valve replacing the buffer fluid in active chamber down, but this safety check and be not used in the generation cushion load.

In mono-tube shock absorber, piston generally comprises a plurality of pressure channels and a plurality of drawing passageway.As be known in the art, vibration damper also comprises the mode of the bar amount flow that is used for compensator fluid.In the shock motion process of mono-tube shock absorber, the compression damper valves on the piston is opened the pressure channel in the piston, flows and the generation cushion load with the control fluid.In the shock motion process, the drawing passageway of the stretching orifice valve closure piston on piston.In the resilience movement process of mono-tube shock absorber, the drawing passageway that the stretching orifice valve on piston is opened in the piston flows and the generation cushion load with the control fluid.In the resilience movement process, the pressure channel of the compression damper valves closure piston on the piston.

For most of buffer, even some valves may comprise the stream of releasing of buffer fluid, orifice valve still is designed to the valve of normal close.Because this close/open design may produce pressure oscillation.This pressure oscillation can cause the dither by the vibration damper generation, and this may form undesirable interference.

Summary of the invention

The valve assembly that is used for vibration damper comprises the biasing element that valve plate is produced the axisymmetric loads distribution.Valve plate is closed non-axisymmetrical pressure area.This geometrical property makes and to realize seamlessly transitting from valve to the valve of opening of closing, to eliminate and/or to reduce the pressure oscillation relevant with the normal close/open design of valve.

Further application will become apparent by description provided herein.It should be understood that description and concrete example just for purposes of illustration, do not attempt to limit the scope of the present disclosure.

Description of drawings

Accompanying drawing as described herein does not attempt to limit by any way the scope of the present disclosure only for purposes of illustration.

Fig. 1 is the schematic representation with the automobile that comprises the vibration damper that designs according to valve of the present invention;

Fig. 2 is the partial side view in cross section that comprises the dual-tube shock absorber of the Fig. 1 that designs according to valve of the present invention;

Fig. 3 is that side cross-sectional view is amplified in the part of the piston assembly of vibration damper shown in Figure 2;

Fig. 4 is that side cross-sectional view is amplified in the part of the bottom valve assembly of vibration damper shown in Figure 2;

Fig. 5 A and 5B are the planimetric map of the piston of piston assembly shown in Figure 3;

Fig. 6 A and 6B are the planimetric map of the valve body of bottom valve shown in Figure 5;

Fig. 7 is for comprising the planimetric map of the valve of non-axisymmetrical pressure area according to another embodiment of the present invention;

Fig. 8 is the planimetric map according to the valve that comprises non-axisymmetrical pressure area of further embodiment of this invention;

Fig. 9 is the partial side view in cross section that comprises according to the mono-tube shock absorber of valve design of the present invention;

Figure 10 is that side cross-sectional view is amplified in the part of piston assembly shown in Figure 9; With

Figure 11 A and 11B are the planimetric map of piston of the piston assembly of Figure 10.

Embodiment

Following description only is example in essence, does not attempt to limit the disclosure, its application or use.Vehicle shown in Fig. 1 comprises the suspension system with vibration damper, and each vibration damper comprises that according to piston assembly of the present invention vehicle is by reference character 10 expressions.Vehicle 10 comprises rear suspension 12, front suspension 14 and vehicle body 16.Rear suspension 12 comprises the rear axle assemblies (not shown) of horizontal expansion, is suitable for effectively supporting pair of rear wheels 18.Rear axle is connected to vehicle body 16 by a pair of vibration damper 20 and a pair of spring 22.Similarly, front suspension 14 comprises the preceding shaft assembly (not shown) of horizontal expansion, is used for effectively supporting a pair of front-wheel 24.Preceding shaft assembly is connected to vehicle body 16 by a pair of vibration damper 26 and a pair of spring 28.

Vibration damper

20 and 26 be used for to the no spring (unsprung) of vehicle 10 partly (for example, forward and backward suspension 12,14) with respect to band spring (sprung) partly the motion of (for example, vehicle body 16) cushion.Although shown vehicle 10 is the passenger vehicle that comprises preceding shaft assembly and rear axle assemblies, but

vibration damper

20 and 26 can be used for the vehicle of other type or the application of other types, comprise, but be not limited to, the vehicle that comprises non-independent front suspension and/or non-independent rear suspension, comprise the vehicle of independent front suspension and/or independent rear suspension, or comprise the vehicle of other suspension systems well known in the prior art.Further, employed here term " vibration damper (shock absorber) " is meant common buffer (damper), thereby will comprise Mai Kabosen support (McPherson struts) and other Cushioning Design well known in the prior art.

With reference now to Fig. 2,, vibration damper 20 is shown in more detail.Although Fig. 2 only illustrates vibration damper 20, it should be understood that vibration damper 26 also comprises the valve design at vibration damper 20 as described below.Vibration damper 26 only is with the difference of vibration damper 20: it is suitable for being connected to the band spring and the no spring section of vehicle 10.Vibration damper 20 comprises pressure tube 30, piston assembly 32, piston rod 34, reserve tube 36 and bottom valve assembly 38.

Pressure tube 30 limits active chamber 42.Piston assembly 32 is slidably disposed in the pressure tube 30, and active chamber 42 is divided into active chamber 44 and following active chamber 46.Sealing 48 is arranged between piston assembly 32 and the pressure tube 30, can not produce excessive frictional force to allow piston assembly 32 with respect to pressure tube 30 sliding movements, and will go up active chamber 44 and be sealed in down active chamber 46.Piston rod 34 is connected to piston assembly 32, and extends through active chamber 44 and pass the upper end cap 50 that is used for occlusion pressure solenoid 30 upper ends.Sealing system is sealed in the interface between upper end cap 50, reserve tube 36 and the piston rod 34.Piston rod 34 be adapted to fasten to the band spring section of vehicle 10 with piston assembly 32 opposing ends.In the movement process of piston assembly 32 in pressure tube 30, the fluid motion in the valve control in piston assembly 32 between active chamber 44 and the following active chamber 46.Because 34 in piston rod extends through active chamber 44 and do not pass down active chamber 46, so piston assembly 32 causes fluid flow and the fluid flow in descending active chamber 46 in last active chamber 44 there are differences with respect to the motion of pressure tube 30.The residual quantity of this fluid flow is known as " bar amount (rod volume) ", and flows through bottom valve assembly 38.

Reserve tube 36 centers on pressure tube 30 to limit the fluid storage chamber 52 between pipe 30 and 36.The bottom of reserve tube 36 is closed by the end cup 54 of the no spring section that is suitable for being connected to vehicle 10.The upper end of reserve tube 36 is connected to upper end cap 50.Bottom valve assembly 38 is arranged on down between active chamber 46 and the storage chamber 52 and flows with the fluid between control chamber 46 and 52.When vibration damper 20 stretches along its length, because the notion of " bar amount " is needing more flow in the active chamber 46 down.Like this, fluid will flow to down the worker by bottom valve assembly 38 from storage chamber 52 and cross chamber 46 (seeing for details hereinafter).When vibration damper 20 compressed along its length, because the notion of " bar amount ", unnecessary fluid must be from shifting out the active chamber 46 down.Like this, fluid will flow to storage chamber 52 (seeing for details hereinafter) by bottom valve assembly 38 from following active chamber 46.

With reference now to Fig. 3,, piston assembly 32 comprises piston body 60, compression valve assembly 62 and resilience valve assembly 64.Shoulder 66 on the compression valve assembly 62 abuts against plunger bars 34 is installed.Piston body 60 is installed against compression valve assembly 62, and resilience valve assembly 64 abuts against plunger bodies 60 are installed.Nut 68 is fastened to piston rod 34 with these parts.

Piston body 60 limits a plurality of pressure channels 70 and a plurality of rebound channel 72.Sealing 48 comprises a plurality of ribs 74 that cooperate with a plurality of circular grooves 76, so that piston assembly 32 can sliding movement.

Compression valve assembly 62 comprises holding part 78, valve disc 80 and spring 82.Holding part 78 is at the one end and take on 66 adjacency, and in its other end and piston body 60 adjacency.Valve disc 80 and piston body 60 be in abutting connection with closes compression passage 70, and keep rebound channel 72 to open simultaneously.Spring 82 is arranged between holding part 78 and the valve disc 80, the abuts against plunger body 60 so that valve disc 80 is setovered axisymmetrically.In compression stroke, the fluid pressurized in following active chamber 46 and cause hydrodynamic pressure to react on valve disc 80.When the hydrodynamic pressure of pressing to valve disc 80 surpassed the offset placed load of spring 82, valve disc 80 separated with piston body 60, thereby opened pressure channel 70 and allow fluid to flow to active chamber 44 from following active chamber 46.Usually, 82 on spring applies lighter axisymmetric loads on valve disc 80, and compression valve assembly 62 is as the safety check between the chamber 46 and 44.In compression stroke, the damping characteristics of vibration damper 20 is controlled by bottom valve assembly 38, because the notion of " bar amount ", bottom valve assembly 38 allows from active chamber 46 is mobile to the fluid of storage chamber 52 down.In rebound stroke, pressure channel 70 is closed by valve disc 80.

Resilience valve assembly 64 comprises separating part 84, a plurality of valve disc 86, holding part 88 and Belleville spring 90.Separating part 84 is carried on the piston rod 34 by engage thread, and is arranged between piston body 60 and the nut 68.Separating part 84 keeps piston body 60 and compression valve assemblies 62, and allows fastening nut 68 simultaneously and do not compress valve disc 80 or valve disc 86.Holding part 78, piston body 60 and separating part 84 provide continuously and firmly are connected to help that separating part 84 and piston rod 34 are tightened and be fastened to nut 68 between shoulder 66 and nut 68.Valve disc 86 is carried on the separating part 84 slidably, and with piston body 60 in abutting connection with closing rebound channel 72, and keep pressure channel 70 to open simultaneously.Holding part 88 also is carried on the separating part 84 slidably, and with valve disc 86 adjacency.Belleville spring 90 is installed on the separating part 84, and is arranged on holding part 88 and is carried on threadably between the nut 68 on the separating part 84.Belleville spring 90 is setovered axisymmetrically against valve disc 86 holding part 88, and makes valve disc 86 abuts against plunger bodies 60.When hydrodynamic pressure puts on dish 86 the time, dish 86 outside perimeter edge place elastic deflection to open resilience valve assembly 64.Liner 108 between nut 68 and Belleville spring 90 with control Belleville spring 90 preload and pressure discharges, as described below.Like this, can be to separate the calibration of resilience valve assembly 64 release characteristics with calibration to compression valve assembly 62.

In rebound stroke, the fluid pressurized in last active chamber 44 and cause hydrodynamic pressure to react on valve disc 86.When the hydrodynamic pressure that reacts on valve disc 86 surpasses the flexural load of valve disc 86, valve disc 86 elastic deflections, thus open rebound channel 72, allow fluid to flow to down active chamber 46 from last active chamber 44.The intensity of valve disc 86 and the size of rebound channel will be determined the damping characteristics of vibration damper 20 in resilience.When the hydrodynamic pressure in the last active chamber 44 arrives predeterminated level, hydrodynamic pressure will cause holding

part

88 and 86 axial motions of a plurality of valve disc above the offset placed load of Belleville spring 90.Rebound channel 72 is opened in the axial motion of holding part 88 and valve disc 86 fully, thereby the buffer fluid that allows significant quantity is by discharging to form hydrodynamic pressure, and this is needed in order to prevent vibration damper 20 and/or vehicle 10 infringements.

With reference to figure 4, bottom valve assembly 38 comprises valve body 92, compression valve assembly 94 and resilience valve assembly 96.Compression valve assembly 94 and resilience valve assembly 96 uses bolts 98 and nut 100 and is connected to valve body 92.Fastening nut 100 and compression valve assembly 94 setovered axisymmetrically rely on valve body 92.Valve body 92 limits a plurality of pressure channels 102 and a plurality of rebound channel 104.

Compression valve assembly 94 comprises a plurality of valve discs 106, and valve disc 106 is biased against valve body 92 by bolt 98 and nut 100 and axisymmetrically.In compression stroke, the fluid pressurized in the following active chamber 46, the hydrodynamic pressure in pressure channel 102 will be used for resilience valve assembly 64 similar mode deflexion disks 106 and finally open compression valve assembly 94 by adopting with above-mentioned.Compression valve assembly 94 will allow from active chamber 46 is mobile to the fluid of last active chamber 44 down, and have only " bar amount " to flow through compression valve assembly 94.The damping characteristics of vibration damper 20 is determined by the design of the compression valve assembly 94 of bottom valve assembly 38.

Resilience valve assembly 96 comprises valve disc 108 and axisymmetric valve spring 110.Valve disc 108 and valve body 92 adjacency, and close rebound channel 104.Valve spring 110 is arranged between nut 100 and the valve disc 108, so that valve disc 108 biased against valve body 92 axisymmetrically.In rebound stroke, the hydrodynamic pressure in the following active chamber 46 reduces, and causes the pressure in the storage chamber 52 to react on valve disc 108.When the hydrodynamic pressure of pressing to valve disc 108 surpassed the offset placed load of valve spring 110, valve disc 108 separated with valve body 92, thereby opens rebound channel 104, allowed fluid to flow to down active chamber 46 from storage chamber 52.Usually, valve spring 110 only applies lighter axisymmetric loads on valve disc 108, and compression valve assembly 94 is as the safety check between storage chamber 52 and following active chamber 46.The damping characteristics of rebound stroke is controlled (as detailed above) by resilience valve assembly 64.

With reference now to Fig. 5 A and 5B,, piston body shown in it 60.Fig. 5 A shows the top of piston body 60, wherein is shown specifically the outlet of pressure channel 70, and Fig. 5 B shows the bottom of piston body 60, wherein is shown specifically the outlet of rebound channel 72.Shown in Fig. 5 A and 5B, three pressure channels 70 and three rebound channel 72 are arranged.Shown in Fig. 5 A, the size difference of each pressure channel 70, each pressure channel 70 comprises the seal area (land) 120 of himself.Valve disc 80 engages to close each pressure channel 70 respectively with each seal area 120.Like this, the surface area that is limited by seal area 120 on valve disc 80 changes according to circumferential location.In compression stroke, the hydrodynamic pressure in the passage 70 reacts on valve disc 80.Hydrodynamic pressure in the passage 70 of largest cross-sectional sized is deflection valve disc 80 at first, then is the passage 70 of second largest sectional dimension, then is the passage 70 of smallest cross-sectional size again.This provides the level and smooth transition between the closed position of compression valve assembly 62 and fully open position.Shown in Fig. 5 B, the size difference of each rebound channel 72, each rebound channel 72 has the seal area 122 of himself.Valve disc 86 engages to close each rebound channel 72 respectively with each seal area 120.Like this, the surface area that is limited by seal area 122 on valve disc 86 changes according to circumferential location.In rebound stroke, the hydrodynamic pressure in the passage 72 reacts on valve disc 86.Hydrodynamic pressure in the passage 72 of largest cross-sectional sized is deflection valve disc 86 at first, then is the passage 72 of second largest sectional dimension, then is the passage 72 of smallest cross-sectional size again.This provides the level and smooth transition between the closed position of resilience valve assembly 64 and fully open position.

With reference now to Fig. 6 A and 6B,, valve body shown in it 92.Fig. 6 A shows the top of valve body 92, wherein is shown specifically the outlet of rebound channel 104, and Fig. 6 B shows the bottom of valve body 92, wherein is shown specifically the outlet of pressure channel 102.Shown in Fig. 6 A and 6B, there are three pressure channels 102 and three rebound channel 104.As shown in Figure 6A, the size difference of each rebound channel 104, each rebound channel 104 has the seal area 124 of himself.Valve disc 108 engages to close each rebound channel 104 respectively with each seal area 124.Like this, the surface area that is limited by seal area 124 on valve disc 108 changes according to circumferential location.In rebound stroke, the hydrodynamic pressure in path 10 4 reacts on valve disc 108.Hydrodynamic pressure in the path 10 4 of largest cross-sectional sized is deflection valve disc 108 at first, then is the path 10 4 of second largest sectional dimension, then is the path 10 4 of smallest cross-sectional size again.This is provided at seamlessly transitting between the closed position of resilience valve assembly 96 and the fully open position.Shown in Fig. 6 B, the size difference of each pressure channel 102, each pressure channel 102 has the seal area 126 of himself.Valve disc 106 engages to close each pressure channel 102 respectively with each seal area 126.Like this, the surface area that is limited by seal area 126 on the valve disc 106 changes according to circumferential location.In compression stroke, the hydrodynamic pressure in the path 10 2 reacts on valve disc 106.Hydrodynamic pressure in the path 10 2 of largest cross-sectional sized is deflection valve disc 106 at first, then is the path 10 2 of second largest sectional dimension, then is the path 10 2 of smallest cross-sectional size again.This is provided at seamlessly transitting between the closed position of compression valve assembly 94 and the fully open position.

With reference now to Fig. 7,, valve body shown in it 192.Although Fig. 7 only illustrates the top and the rebound channel 104 of valve body 192, but it should be understood that, have the valve body 192 of pressure channel 102 downside, have pressure channel 70 piston body 60 the top side and have the bottom side of the piston body 60 of rebound channel 72, the asymmetric design that is used for valve body 192 and rebound channel 104 shown in can comprising.

The rebound channel 104 that a plurality of equivalent size are arranged as shown in Figure 7.External sealed district 130 and interior seal area 132 are arranged on eccentric position, its off-centring, and the feasible larger cross-section zone that reacts on the fluid of valve disc 108 is present in a side of valve body 192.Like this, the surface area that is limited by

seal area

130 and 132 on valve disc 108 changes according to circumferential location.In rebound stroke, because the off-centre of

seal area

130 and 132 location, the hydrodynamic pressure that reacts on valve disc 108 is with uneven mode effect.Hydrodynamic pressure in the zone, maximum cross-section is deflection valve disc 108 at first, and final hydrodynamic pressure is removed valve disc 108 fully from seal area 130 and 132.This is provided for seamlessly transitting between the closed position of valve assembly and open position.

With reference now to Fig. 8,, valve body 292 is shown.Although Fig. 8 only illustrates the top and the rebound channel 104 of valve body 292, but it should be understood that, have the valve body 292 of pressure channel 102 downside, have pressure channel 70 piston body 60 the top side and have the bottom side of the piston body 60 of rebound channel 72, the asymmetric design that is used for valve body 292 and rebound channel 104 shown in can comprising.

The rebound channel 104 that a plurality of different sizes are arranged as shown in Figure 8.Discrete seal area 140 each independent path 10 4 of sealing.Valve disc 104 engages to close each rebound channel 104 respectively with each seal area 140.Like this, the surface area that is limited by seal area 140 on the valve disc 104 changes according to circumferential location.In rebound stroke, the hydrodynamic pressure in the path 10 4 reacts on valve disc 104.Hydrodynamic pressure in the path 10 4 of largest cross-sectional sized is deflection valve disc 104 at first, then is the path 10 4 of second largest sectional dimension, then is the passage of the third-largest sectional dimension again, or the like, separate fully with valve body 292 up to valve disc 104.This is provided for seamlessly transitting between the closed position of valve assembly and fully open position.

With reference now to Fig. 9-11B,, illustrates according to mono-tube shock absorber 320 of the present invention.By changing the mode that it is suitable for being connected to the band spring section of vehicle and/or does not have spring section, vibration damper 320 can replace vibration damper 20 or vibration damper 26.Vibration damper 320 comprises pressure tube 330, piston assembly 332 and piston rod 334.

Pressure tube 330 limits active chamber 342.Piston assembly 332 is slidably disposed in the pressure tube 330, and active chamber 342 is divided into active chamber 344 and following active chamber 346.Sealing 348 is arranged between piston assembly 332 and the pressure tube 330, makes piston assembly 332 can not produce excessive frictional force with respect to pressure tube 330 sliding movements, and will go up active chamber 344 and be sealed in down active chamber 346.Piston rod 334 is connected to piston assembly 332, and extends through active chamber 344 and upper end cap or bar guide portion 350 by being used for occlusion pressure solenoid 330 upper ends.Sealing system is sealed in the interface between bar guide portion 350, pressure tube 330 and the piston rod 334.The end opposite with piston assembly 332 of piston rod 334 is adapted to fasten to the band spring section of vehicle 10.The end opposite with bar guide portion 350 of pressure tube 330, the end cup 354 of the no spring section by being suitable for being connected to vehicle 10 is closed.

In the compression movement process of piston assembly 332 in pressure tube 330, be connected to the following active chamber 346 of compression valve assembly 362 controls of piston assembly 332 and the fluid motion between the last active chamber 344.In compression stroke, the damping characteristics of the design of compression valve assembly 362 control vibration damper 320.In the stretching or resilience movement process of piston assembly 332 in pressure tube 330, the fluid motion between active chamber 344 and the following active chamber 346 is gone up in stretching valve assembly 364 controls that link to each other with piston assembly 332.In stretching or rebound stroke, the damping characteristics of the design of stretching valve assembly 364 control vibration damper 320.

Because 334 in piston rod extends through active chamber 344 by following active chamber 346, so piston assembly 332 causes fluid flow and the fluid flow in following active chamber 346 in last active chamber 344 there are differences with respect to the motion of pressure tube 330.The residual quantity of fluid flow is known as " bar amount ", and the compensation that is used for this fluid realizes by the piston 370 that is slidably disposed in the pressure tube 330 and between following active chamber 346 and compensated cavity 372.Usually, compensated cavity 372 is filled with superheated steam, and piston 370 moves with balancing lever amount factor in pressure tube 330.

With reference now to Figure 10,, piston assembly 332 comprises piston body 360, compression valve assembly 362 and resilience valve assembly 364.Shoulder 366 on the compression valve assembly 362 abuts against plunger bars 334 is installed.Piston body 360 is installed against compression valve assembly 362, and resilience valve assembly 364 abuts against plunger bodies 360 are installed.Nut 368 is fastened to piston rod 334 with these parts.

Piston body 360 defines a plurality of pressure channels 370 and a plurality of rebound channel 372.Sealing 348 comprises a plurality of ribs 374 that cooperate with a plurality of circular grooves 376, to allow piston assembly 332 sliding movements.

Compression valve assembly 362 comprises holding part 378, valve disc 380 and spring 382.Holding part 378 is in one end and shoulder 366 adjacency, in its other end and piston body 360 adjacency.Valve disc 380 and valve body 360 be in abutting connection with closes compression passage 370, and keep rebound channel 372 to open simultaneously.Spring 382 is arranged between holding part 378 and the valve disc 380 the abuts against plunger body 360 so that valve disc 380 is setovered axisymmetrically.In compression stroke, the fluid pressurized in the following active chamber 346 and cause hydrodynamic pressure to react on valve disc 380.When the hydrodynamic pressure of pressing to valve disc 380 surpassed the offset placed load of spring 382, valve disc 380 separated with valve body 360, to open pressure channel 370, allowed fluid to flow to active chamber 344 from following active chamber 346.In compression stroke, the damping characteristics of vibration damper 320 is by 362 controls of compression valve assembly.In rebound stroke, pressure channel 370 is closed by valve disc 380.

Resilience valve assembly 364 comprises: separating part 384, a plurality of valve disc 386, holding part 388 and Belleville spring 390.Separating part 384 is carried on the piston rod 334 by engage thread, and is arranged between piston body 360 and the nut 368.Separating part 384 keeps piston body 360 and compression valve assemblies 362, allows fastening nut 368 simultaneously and does not compress valve disc 380 or valve disc 386.Holding part 378, piston body 360 and separating part 384 are provided at continuous between shoulder 366 and the nut 368 and firmly are connected, and help separating part 384 and piston rod 334 are tightened and be fastened to nut 368.Valve disc 386 is carried on the separating part 384 slidably, and with piston body 360 in abutting connection with closing rebound channel 372, and keep pressure channel 370 to open simultaneously.Holding part 388 also is carried on the separating part 384 slidably, itself and valve disc 386 adjacency.Belleville spring 390 is installed on the separating part 384, and is arranged on holding part 388 and is carried between the nut 368 on the separating part 384 by engage thread.Belleville spring 390 is setovered axisymmetrically against valve disc 386 holding part 388, and makes valve disc 386 abuts against plunger bodies 360.When hydrodynamic pressure is applied to dish 386 the time, dish 386 outside perimeter edge place elastic deflection to open resilience valve assembly 364.Liner 408 between nut 368 and Belleville spring 390 with control Belleville spring 390 preload and release pressure (seeing for details hereinafter).Like this, can be to separate at the calibration of resilience valve assembly 364 release characteristics with calibration at compression valve assembly 362.

In rebound stroke, the fluid pressurized in last active chamber 344 causes hydrodynamic pressure to react on valve disc 386.When the hydrodynamic pressure that reacts on valve disc 386 surpassed the flexural load of valve disc 386, valve disc 386 elastic deflections to be opening rebound channel 372, thereby allowed fluid to flow to down active chamber 346 from last active chamber 344.The intensity of valve disc 386 and the size of rebound channel will be determined the damping characteristics of vibration damper 320 in the resilience.When the hydrodynamic pressure in the last active chamber 344 arrives predeterminated level, hydrodynamic pressure will cause holding part 388 and 386 axial motions of a plurality of valve disc above the offset placed load of Belleville spring 390.Rebound channel 372 is opened in the axial motion of holding part 388 and valve disc 386 fully, passes through with the buffer fluid that allows significant quantity, discharges thereby form hydrodynamic pressure, and this is needed in order to prevent vibration damper 320 and/or vehicle 10 infringements.

With reference now to Figure 11 A and Figure 11 B,, piston body 360 is shown.Figure 11 A illustrates the top of piston body 360, wherein is shown specifically the outlet of pressure channel 370, and Figure 11 B illustrates the bottom of piston body 360, wherein is shown specifically the outlet of rebound channel 372.Shown in Figure 11 A and 11B, there are three pressure channels 370 and three rebound channel 372.Shown in Figure 11 A, the size difference of each pressure channel 370, and each pressure channel 370 has the seal area 420 of himself.Valve disc 380 engages to close each pressure channel respectively with each seal area 420.Like this, the surface area that is limited by seal area 420 on valve disc 380 changes according to circumferential location.In compression stroke, the hydrodynamic pressure in the passage 370 reacts on valve disc 380.Hydrodynamic pressure in the passage 370 of largest cross-sectional sized is deflection valve disc 380 at first, then is the passage 370 of second largest sectional dimension, then is the passage 370 of smallest cross-sectional size again.This provides seamlessly transitting between the closed position of compression valve assembly 362 and fully open position.Shown in Figure 11 B, the size difference of each rebound channel 372, each rebound channel 372 has the seal area 422 of himself.Valve disc 386 engages to close each rebound channel 372 respectively with each seal area 420.Like this, the surface area that is limited by seal area 422 on valve disc 386 changes according to circumferential location.In rebound stroke, the hydrodynamic pressure in the passage 372 reacts on valve disc 386.Hydrodynamic pressure in the passage 372 of largest cross-sectional sized is deflection valve disc 386 at first, then is the passage 372 of second largest sectional dimension, then is the passage 372 of smallest cross-sectional size again.This is provided at seamlessly transitting between the closed position of resilience valve assembly 364 and the fully open position.

Claims

1, a kind of vibration damper comprises:

Pressure tube;

Be arranged on the valve assembly in the described pressure tube, described valve assembly comprises:

Valve body, its qualification extend through a plurality of first passages of described valve body;

Be arranged on a plurality of first seal areas on first side of described valve body;

Engage to close first valve disc of at least one described first passage with described a plurality of first seal areas;

Wherein, the surface area on described first valve disc that is limited by described a plurality of first seal areas changes according to circumferential location.

2, vibration damper according to claim 1, wherein, each in described a plurality of first passages by single seal area institute around, at least two different surfaces zones that are limited on described first valve disc in described a plurality of first seal areas.

3, vibration damper according to claim 2, wherein, each in described a plurality of first seal areas limits the different surfaces zone of described first valve disc.

4, vibration damper according to claim 1, wherein, at least two in described a plurality of first passages have different sectional areas.

5, vibration damper according to claim 4, wherein, each in described a plurality of first passages by single seal area institute around, at least two different surfaces zones that are limited on described first valve disc in described a plurality of first seal areas.

6, vibration damper according to claim 5, wherein, each in described a plurality of first seal areas limits the different surfaces zone of described first valve disc.

7, vibration damper according to claim 1, wherein, each in described a plurality of first passages has different sectional areas.

8, vibration damper according to claim 7, wherein, each in described a plurality of first passages by single seal area institute around, at least two different surfaces zones that are limited on described first valve disc in described a plurality of first seal areas.

9, vibration damper according to claim 8, wherein, each in described a plurality of first seal areas limits the different surfaces zone of described first valve disc.

10, vibration damper according to claim 1, wherein, seal area and external sealed district in described a plurality of first seal areas comprise, described a plurality of first passages are arranged between described interior seal area and the external sealed district.

11, vibration damper according to claim 10, wherein, the misalignment of described interior seal area is in the center in described external sealed district.

12, vibration damper according to claim 1 further comprises:

Extend through a plurality of second channels of described valve body;

Be arranged on a plurality of second seal areas on second side of described valve body;

Engage to close second valve disc of at least one described second channel with described a plurality of second seal areas.

13, vibration damper according to claim 12, wherein, the surface area on described second valve disc that is limited by described a plurality of second seal areas changes according to circumferential location.

14, vibration damper according to claim 13, wherein, each in described a plurality of second channels by single seal area institute around, at least two different surfaces zones that are limited on described second valve disc in described a plurality of second seal areas.

15, vibration damper according to claim 14, wherein, each in described a plurality of second seal areas limits the different surfaces zone of described second valve disc.

16, vibration damper according to claim 13, wherein, at least two in described a plurality of second channels have different sectional areas.

17, vibration damper according to claim 16, wherein, each in described a plurality of second channels by single seal area institute around, at least two different surfaces zones that are limited on described second valve disc in described a plurality of second seal areas.

18, vibration damper according to claim 17, wherein, each in described a plurality of second seal areas limits the different surfaces zone of described second valve disc.

19, vibration damper according to claim 1, wherein, each in described a plurality of second channels has different sectional areas.

20, vibration damper according to claim 19, wherein, each in described a plurality of second channels by single seal area institute around, at least two different surfaces zones that are limited on described second valve disc in described a plurality of second seal areas.

21, vibration damper according to claim 20, wherein, each in described a plurality of second seal areas limits the different surfaces zone of described second valve disc.

22, vibration damper according to claim 13, wherein, seal area and external sealed district in described a plurality of second seal areas comprise, described a plurality of first passages are arranged between described interior seal area and the external sealed district.

23, vibration damper according to claim 22, wherein, the misalignment of described interior seal area is in the center in described external sealed district.

24, vibration damper according to claim 1, wherein, described valve body is the piston body that is used for piston assembly, described piston assembly is slidingly arranged in the described pressure tube.

25, vibration damper according to claim 1, wherein, described valve body is incorporated in the bottom valve assembly, and described bottom valve assembly is secured to described pressure tube.