WO2014122318A1 - Amortisseur ayant une caractéristique d'amortissement auto-adaptative - Google Patents

Amortisseur ayant une caractéristique d'amortissement auto-adaptative Download PDF

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Publication number
WO2014122318A1
WO2014122318A1 PCT/EP2014/052603 EP2014052603W WO2014122318A1 WO 2014122318 A1 WO2014122318 A1 WO 2014122318A1 EP 2014052603 W EP2014052603 W EP 2014052603W WO 2014122318 A1 WO2014122318 A1 WO 2014122318A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
piston
pressure line
component
damper
Prior art date
Application number
PCT/EP2014/052603
Other languages
German (de)
English (en)
Inventor
Andreas Gantioler
Martin Franzel
Peter Russell
Original Assignee
m-craft technologies ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by m-craft technologies ltd. filed Critical m-craft technologies ltd.
Publication of WO2014122318A1 publication Critical patent/WO2014122318A1/fr

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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
    • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
    • F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
    • F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
    • F16F9/5126—Piston, or piston-like valve elements

Definitions

  • the invention relates to a device for damping the movement of a
  • hydraulic shock absorbers have been used for a long time in order to allow the shocks and forces acting on the chassis to decay as quickly as possible.
  • the movement of the chassis is usually transmitted by means of a piston rod to a hydraulic damper.
  • a hydraulic damper In an axial movement of the piston rod relative to the cylinder is the
  • Hydraulic fluid such as oil, displaced and then has to flow through narrow channels and valves in the damper. The kinetic energy of the piston is converted into a warming of the oil.
  • dampers In some known dampers, the damping characteristic of the damper can be adjusted by the user. Such dampers are therefore also referred to as dampers with "Adjuster".
  • the adjuster 1 shown here may e.g. be mounted on a rear swingarm or a suspension fork of a motorcycle.
  • the adjuster 1 has a first side (in the figure below), which in the mounted state is in communication with the hydraulic system of the suspension and is subjected to hydraulic pressure upon compression of the piston, and an opposite side (in the figure above), with adjusting elements 18, 20 for adjusting the damping characteristic.
  • On the hydraulic side is initially a valve 2, which opens when a predetermined pressure level is exceeded and a flow cross-section is free.
  • the valve 2 comprises a plurality of arranged in the housing of the adjuster 1
  • Openings 36 by means of several spring-loaded discs 35 - also shims called - are closed.
  • the disks 35 are pressed against the openings 36 by means of a spring 5, which is supported on an adjusting element 18 on the opposite side. If the hydraulic pressure increases due to a piston movement, the discs 35 return and give one
  • Hydraulic fluid also from the high pressure side 6 through a secondary line 34, in which a needle valve 12 is arranged, in an external expansion tank (not shown).
  • the damping characteristic of the adjuster 1 at greater compression speeds can be regulated by means of the adjustment element 18.
  • Bias of the spring 5 can be increased or decreased.
  • the valve 2 will therefore open sooner or later accordingly.
  • Increasing the preload means a firmer, harder chassis with higher damping, and a reduction in the preload a softer, more comfortable suspension with less damping.
  • the needle 20 of the needle valve 12 may be e.g. be adjusted by means of a screwdriver in the longitudinal direction 32. By appropriate rotation of the screw in or
  • a reduction of the valve cross section means a higher damping and an increase of the
  • Valve cross section a lower damping.
  • From DE 1 455 823 A is a hydraulic damper for damping the
  • the known damper comprises a valve with a
  • Piston element leading pressure line wherein the piston member, when it is acted upon via the pressure line with hydraulic pressure, closing acts on the valve.
  • a damper is not adjustable.
  • dampers that are adjusted to different operating conditions can be.
  • the damper should be simple and include as few components.
  • a hydraulic damper comprising at least the following elements: a valve with a spring-loaded closure part, a movably mounted piston element which is coupled via a spring arrangement with the closure part, and a pressure line which from a high pressure side of the damper to the piston element leads, so that the piston element when it over the
  • Pressure line is subjected to hydraulic pressure, closing on the closure part acts.
  • the piston element is designed annular and slidably mounted on a component.
  • Such a damper has the significant advantage that it automatically adapts to different environmental and driving conditions.
  • the damper according to the invention shows a relatively soft and comfortable damping behavior; on harder surfaces or strong impacts, the damper on the other hand shows a tighter and harder
  • damper is relatively simple and includes only a few components.
  • the damper according to the invention can, for example, in a
  • Shock absorber system of motor vehicles or commercial vehicles such as e.g. Cars or
  • the pressure line is a secondary line, which runs past the valve and bridges it in the form of a bypass.
  • the pressure line is thus arranged in terms of circuitry parallel to the main valve.
  • the pressure line preferably extends from a high-pressure side of the valve to a side remote from the valve rear side of the piston element. It preferably ends in a chamber which is partially bounded by the piston element.
  • the pressure line at least in sections has a smaller cross section than the effective effective area of the valve, d. H. that surface which, when acted upon by pressure, exerts a force component opening the valve. Namely, the smaller cross-section results in an acceleration of the hydraulic fluid, which causes the
  • Piston member is preferably smaller than the effective effective area of the valve, which exerts a valve opening force component on the closure member. At low pressure changes or in stationary case, the valve can therefore open.
  • the effective effective area of the piston element could also be of the same size or larger than the effective effective area of the valve. According to a preferred embodiment of the invention runs the
  • the closure part may, for example, have a channel which forms a section of the pressure line.
  • the closure member has a conical portion which cooperates with a correspondingly shaped valve seat.
  • the closure part comprises one or more discs which close at least one passage opening provided in the housing of the damper.
  • the above-mentioned pressure line is at least partially preferably in a member extending within the damper housing in a longitudinal direction.
  • the component can be designed such that it also forms a rear stop for the piston element.
  • the component may be designed to be fixed or adjustable in the longitudinal direction of the damper, so that the voltage of the spring assembly is adjustable. In the latter case, it may therefore also be referred to as an adjustment.
  • the component can, for. B. have an external thread which cooperates with a housing provided on the inner thread and by means of which it in
  • Longitudinal direction of the damper is adjustable. Upon rotation of the component or adjusting element in or counterclockwise, it moves in the longitudinal direction of the damper, whereby the bias of the spring can be increased or decreased. With the help of such a setting element can be particularly the damping behavior in fast, highly dynamic
  • the adjustment member preferably includes at its rear end a portion at which a user can hold a tool, such as a tool.
  • Wrench can attach to turn the adjustment.
  • the closure part of the main valve is preferably mounted on a valve-side end of the component.
  • the closure part of the main valve z. B. have a projecting away in the opening direction portion which is formed, for example, cylindrical. This section of the closure part can, for example, be immersed in a chamber provided on the valve-side end of the channel or setting element.
  • the closure member may also be stored differently on the component or adjusting, z. B. by means of a sliding bearing.
  • one or more second valves may be formed on the closure part of the main valve.
  • the second valve or valves are preferably formed from one or more passage openings provided in the closure part, which are in communication with the high-pressure side of the valve and are closed on the low-pressure side by means of at least one spring-loaded second closure part.
  • the second valve or valves preferably open in the same low-pressure-side chamber as the first valve and are thus
  • circuitry arranged parallel to the first valve.
  • a further valve is provided, by means of which the flow rate through the pressure line to
  • Rear of the piston can be regulated.
  • the second valve can
  • the second valve may be designed as a needle valve and is preferably via a second adjustment of
  • the second valve is preferably within the above
  • the piston element is preferably slidably mounted in the opening or closing direction of the main valve.
  • the piston element is annular and preferably surrounds said pressure line or a component in which the pressure line is arranged.
  • the pressure line extends in this case through the piston element.
  • the piston element is preferably arranged concentrically to the pressure line or the component.
  • the pressure line preferably ends in a chamber which is at least partially disposed on a side facing away from the main valve of the piston member.
  • the above-mentioned component preferably comprises at least one through-channel, which is part of the pressure line.
  • the channel can extend obliquely at least at one section with respect to the opening and closing direction and opens into the chamber delimited by the piston element at the rear side of the piston element.
  • the damper is designed as a unitary component which has means for attachment to another part, e.g. a part of a hydraulic suspension, comprising.
  • the valve, the piston element and the pressure line are preferably arranged in a common housing.
  • the damper according to the invention is preferably rotationally symmetrical
  • a spring arrangement according to the invention z.
  • Figure 1 is a known from the prior art hydraulic damper with a high-speed adjustment and a low-speed adjustment.
  • Fig. 2 is a schematic representation of a hydraulic according to the invention
  • FIG. 3a shows a first embodiment of a hydraulic according to the invention
  • Fig. 3b shows the hydraulic damper of Fig. 3a in another
  • Fig. 4 is a sectional view of a hydraulic damper according to
  • Figures 5a-5c are various perspective views of a damper according to the first or second embodiment of the invention.
  • FIG. 6 shows a hydraulic damper according to a third embodiment of the invention.
  • Fig. 7 shows a hydraulic damper according to a fourth embodiment of the invention embodiments of the invention
  • FIG. 2 shows a schematic representation of the basic principle of a
  • Hydraulic damper 1 according to the invention.
  • the damper 1 or adjuster is here part of a hydraulically damped suspension, such. one
  • valve 2 can open again and release a larger flow cross-section, which softens the suspension and improves traction again.
  • a hydraulic damper with negative feedback can thus automatically adapt to different environmental and driving conditions.
  • the pressure line 7 preferably has a smaller cross section than a pressure line leading to the valve 2. In a springing movement of the piston 1 1, the hydraulic fluid in the pressure line 7 is therefore accelerated faster than in the pressure line leading to the valve 2, so that the piston 4 is acted upon with a higher dynamics with pressure. This circumstance helps to keep the valve 2 relatively closed at highly dynamic compression events and to delay the time until the valve 2 rises.
  • 3a shows a first embodiment of a damper according to the invention in a sectional view.
  • Fig. 3b shows the same component in another
  • the damper or adjuster 1 comprises a housing 16a, 16a, which by means of an external thread 19 on another component, such as. on a suspension fork or a rear swing arm of a motorcycle, can be attached.
  • the damper is formed here rotationally symmetrical and includes a front side facing the hydraulic (in the picture on the right) and an externally accessible side (pictured left), where the damping characteristic of the damper can be set by the user.
  • the spacer element 17 has a central passage opening through which the hydraulic fluid can reach a valve 2 arranged at the front end of the damper (see arrow 40).
  • the valve 2 here comprises a conically formed closure part 3 which cooperates with a valve seat 25 machined out in the housing part 16b.
  • the closure member 3 is movably mounted in the axial direction 46 and can move between the illustrated closed position and an open position back and forth.
  • the closing and opening direction of the valve 2 extends in the axial direction 46 of the damper. 1
  • the valve 2 will open and release an opening cross-section between cone 3 and valve seat 25.
  • the hydraulic fluid is then through the valve 2 in a low-pressure side chamber 8 in the housing part 16 b, and from there via
  • the closure part 3 of the valve 2 further has a passage 46 a continuous in the axial direction 46, which forms a portion of the pressure line 7 and through which the Hydraulic fluid can pass through different pressure line sections 7b-7e in a chamber 7f.
  • the chamber 7f is bounded on one side by a movably mounted piston 4, which can move in the opening or closing direction 46 of the valve 2 in the housing part 16b and which is coupled via a spring arrangement 5 with the closure part 3 of the valve 2.
  • the spring assembly 5 is shown as a coil spring.
  • other springs such as e.g. Leaf springs, be provided.
  • the piston 4 When the hydraulic pressure is increased, the piston 4 is driven in the direction of the valve 2 - in this case to the right - and exerts a force on the closure part 3 via the spring arrangement 5, which force acts on the valve 2 in a closing manner.
  • the piston 4 and the closure part 3 of the valve 2 are thus counter-coupled and work according to the basic principle already described with reference to FIG.
  • the piston 4 is designed as an annular piston which is mounted on a component 18 for adjusting
  • Bias of the spring assembly 5 is slidably mounted.
  • the pressure line 7 extends through the piston element 4 therethrough.
  • the component 18 comprises an external thread 41, which cooperates with a corresponding internal thread on the housing part 16 a and by a
  • Screwing movement in the opening or closing direction 46 of the valve 2 - here to the left or right - can be moved.
  • the tension of the spring 5 and thus the basic damping behavior of the damper 1 can be set at greater compression speeds (high-speed adjustment).
  • the component 18 has on its back (in the picture on the left) a hexagon on which a tool can be attached.
  • the component 18 extends here over more than half of the damper. 1
  • a piston chamber 27 is formed, in which a cylindrical extension 45 of the
  • Locking parts 3 dips.
  • the valve facing portion of the component 18th and the closure part 3 are thereby coupled together via a sliding bearing.
  • In the interior of the component 18 are also different passages and
  • Openings 7b-7e are provided which form further sections of the pressure line 7. Specifically, these sections 7b-7e are: a chamber 7b bounded by the closure part 3 and the end section of the component 18, from which the hydraulic fluid passes via a further valve 12 and a channel 7c into a chamber 7d. From the chamber 7d then lead several channels 7e to the limited volume of the piston 4 chamber 7f at the back of the piston 4. The through the component 18th
  • Passing channels 7e thereby extend partially obliquely with respect to the opening and closing direction 46.
  • the chamber 7d is arranged further in the opening direction than the chamber 7f delimited by the piston 4.
  • the arranged in the pressure line 7a-7f valve 12 includes a valve needle 14 with an external thread 15 which cooperates with a corresponding internal thread in the component 18.
  • the valve needle is adjustable via an adjusting element 20, which is arranged at least partially in the interior of the first component 18, in the opening or loosening direction 46.
  • the adjusting element 20 has for this purpose at its rear end means for applying a tool, such. a slot for a screwdriver.
  • the front tip of the valve needle 14 cooperates with a correspondingly shaped valve seat formed in the component 18. By a screwing movement of the valve needle 14, the opening cross-section of the valve 12 can be increased or decreased.
  • the valve 12 thus offers a further possibility for adjusting the damping characteristic of the
  • valve needle 14 and the component 18 are designed here as separate components, which are rotatably connected to each other.
  • the adjusting element 20 is fixed in the axial direction and rotatably received in the first component 18 in the direction of rotation. As can be seen, this is supported
  • a sliding bearing is provided between the adjusting element 20 and the valve needle 14.
  • the plain bearing includes an am
  • the valve needle 14 can thus move along the pin in the axial direction.
  • the pin 21 has a corresponding profile, such as e.g. a Kant profile, wherein the recess of the
  • Valve needle 14 is formed correspondingly.
  • a groove 23 is further provided in each case, in which a sealing ring is arranged.
  • the component 18 also comprises an outer, circumferential groove 24 in which a seal is arranged.
  • a latching device 22 which comprises a spring with which a latching element is pressed against the inner wall of the housing part 16a and there can engage in latching recesses which are provided at certain intervals.
  • the latching device 22 gives the user an acoustic and / or haptic feedback about the angle of rotation about which the component 18 has been rotated, and thus about the setting of the damper 1.
  • At the closure part 3 of the main valve 2 here are a plurality of second valves
  • Closing part 30 - here a disc - is closed.
  • the second valves 30,31 open into the same low-pressure side chamber 8 as the first valve 2 and are therefore connected fluidically parallel to the main valve 2.
  • the hydraulic fluid is thus dependent on the pressure conditions on the High-pressure side 6 either through the first valve 2 and / or the second valves 30,31 flow into the chamber 8.
  • the second valve or valves 30, 31 are arranged in this embodiment on the closure part 3 of the valve 2, but could also be provided elsewhere.
  • the second closure part 30 is connected via a further spring arrangement 29 in FIG.
  • the spring assembly 29 comprises here a
  • Coil spring which is arranged coaxially to the spring 5 and the valve side is supported on a disc 28, which in turn presses against the closure part 3 of the valve 2.
  • the spring 29 is supported on the component 18.
  • Fig. 4 shows an alternative embodiment of a damper according to the invention in a sectional view.
  • the damper 1 shown here corresponds essentially to the damper shown in FIGS. 3a and 3b.
  • the spring assembly 5 but includes a leaf spring instead of a coil spring.
  • the low-speed adjustment mechanism consisting of the
  • FIGS. 5a-5c show various perspective views of a hydraulic damper 1 according to the invention.
  • the two housing parts 16a, 16b, a spacer element 17 and the component 18 are clearly visible.
  • the housing part 16b are a plurality of outlet openings 39, 50th
  • the openings 50 are in the region of the valve seat 25 in
  • Housing part 16b arranged. They form open passageways 51, through which the hydraulic fluid from the high-pressure side 6, on the main valve 2 over, can escape directly into the expansion tank.
  • Fig. 6 shows a third embodiment of a damper 1 according to the invention, which is constructed very similar to the two first embodiments of Fig. 3a, 3b and 4.
  • the main valve 2 comprises a plurality of provided in the housing part 16b
  • Inlet openings 36 in the form of through-holes formed by so-called shims 47, e.g. Spring steel washers, to be closed.
  • the shims 47 in this case form the closure part of the main valve 2.
  • the shims 47 are biased by a spring arrangement 5 in the closing direction and are coupled via the spring arrangement 5 with the slidingly mounted piston 4. in the
  • FIG. 7 shows a fourth embodiment of a damper 1 according to the invention.
  • Like elements are again denoted by the same reference numerals.
  • a depression or recess is provided on the rear surface of the annular piston 4, so that the chamber 7f fails larger.
  • the recess could also be formed in the rearwardly adjacent component 18 or housing part.
  • the spring tension of the spring 5 is no longer subsequently adjustable by the user.
  • the component 18 is still present, but no longer comprises elements on which a tool can be attached.
  • the component 18 is screwed in this case via a thread on the housing 16b, where it can be positioned closer to or further away from the closure member.
  • the spring tension can be preset by the manufacturer. It can not be changed afterwards during operation.
  • the component 18 could, of course, also be stationary, ie not adjustable, or, as in the other embodiments, designed to be adjustable.
  • Back pressure line 7 (with the sections 7a-7f) branching line 7g provided, through which the fluid flowing to the chamber 7f can be diverted.
  • the branch line 7 g is arranged here in the component 18. It preferably opens out on the outside of the housing or component 18, so that the branched fluid can flow outward out of the housing 18 in the direction of a container.
  • the valve 12 is preferably arranged so that from the
  • Counterpressure 7-flowing portion - and thus indirectly also flowing into the chamber 7 f fluid flow - can be regulated.
  • the reaction time and the back pressure of the piston can be subsequently adjusted via the valve 12.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Damping Devices (AREA)
  • Axle Suspensions And Sidecars For Cycles (AREA)

Abstract

La présente invention concerne un dispositif pour amortir le mouvement d'un élément (11) dans un système hydraulique, notamment d'un piston (11) d'une suspension hydraulique. L'amortisseur (1) selon l'invention comprend : une soupape (2) présentant une partie de fermeture (3, 35) sollicitée par ressort ; un élément de piston (4) monté mobile et couplé à la partie de fermeture (3, 35) par un dispositif de rappel (5); et une conduite sous pression (7, 7a-7f) qui mène d'un côté haute pression (6) de la soupape (2) à l'élément de piston (4) de sorte qu'une pression hydraulique agit sur l'élément de piston (4) et sollicite la soupape (2) en direction de fermeture. Un tel amortisseur (1) présente l'avantage de s'adapter automatiquement aux différentes conditions régnant au niveau du véhicule et de son environnement.
PCT/EP2014/052603 2013-02-11 2014-02-11 Amortisseur ayant une caractéristique d'amortissement auto-adaptative WO2014122318A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201310002425 DE102013002425B3 (de) 2013-02-11 2013-02-11 Stoßdämpfer mit einer sich automatisch anpassenden Dämpfungscharakteristik
DE102013002425.0 2013-02-11

Publications (1)

Publication Number Publication Date
WO2014122318A1 true WO2014122318A1 (fr) 2014-08-14

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DE (1) DE102013002425B3 (fr)
WO (1) WO2014122318A1 (fr)

Cited By (1)

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US11448282B2 (en) 2018-06-20 2022-09-20 N10Z Performance Shocks LLC Shock absorber assembly

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Publication number Priority date Publication date Assignee Title
DE102014210705A1 (de) * 2014-06-05 2015-12-17 Zf Friedrichshafen Ag Frequenzabhängige Dämpfventilanordnung
DE102014210704B4 (de) * 2014-06-05 2016-11-24 Zf Friedrichshafen Ag Frequenzabhängige Dämpfventilanordnung
US10830366B2 (en) 2016-12-30 2020-11-10 Safran Landing Systems Canada Inc. Hydraulic valve for dampening pressure spikes, and associated systems and methods

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DE4417796A1 (de) * 1993-05-20 1994-12-01 Tokico Ltd Hydraulischer Stoßdämpfer mit einstellbarer Dämfpungskraft
DE19724328C1 (de) * 1997-06-10 1998-10-29 Mannesmann Sachs Ag Dämpfventil mit einstellbarer Dämpfkraft
EP2439424A2 (fr) * 2010-10-11 2012-04-11 Reinhard Dr. Hölscher Amortisseur d'oscillations en fonction de la fréquence dans une construction à deux tuyaux

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FR2651553B1 (fr) * 1989-09-06 1991-12-13 Sirven Jacques Valve pour fluide hydraulique et amortisseur comportant une telle valve.
DE9202402U1 (fr) * 1992-02-25 1992-04-23 Haber, Horst, Dipl.-Ing., 6781 Ruppertsweiler, De
DE19542293B4 (de) * 1994-12-03 2006-08-31 Zf Sachs Race Engineering Gmbh Schwingungsdämpfer mit einstellbarer Dämpfkraft
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DE4417796A1 (de) * 1993-05-20 1994-12-01 Tokico Ltd Hydraulischer Stoßdämpfer mit einstellbarer Dämfpungskraft
DE19724328C1 (de) * 1997-06-10 1998-10-29 Mannesmann Sachs Ag Dämpfventil mit einstellbarer Dämpfkraft
EP2439424A2 (fr) * 2010-10-11 2012-04-11 Reinhard Dr. Hölscher Amortisseur d'oscillations en fonction de la fréquence dans une construction à deux tuyaux

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11448282B2 (en) 2018-06-20 2022-09-20 N10Z Performance Shocks LLC Shock absorber assembly
US11913519B2 (en) 2018-06-20 2024-02-27 N10Z Performance Shocks LLC Shock absorber assembly

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