EP0611422A1 - Schwingungsdämpfer - Google Patents
SchwingungsdämpferInfo
- Publication number
- EP0611422A1 EP0611422A1 EP92923357A EP92923357A EP0611422A1 EP 0611422 A1 EP0611422 A1 EP 0611422A1 EP 92923357 A EP92923357 A EP 92923357A EP 92923357 A EP92923357 A EP 92923357A EP 0611422 A1 EP0611422 A1 EP 0611422A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- vibration damper
- spring
- valve body
- damper according
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
- F16F9/446—Adjustment of valve bias or pre-stress
Definitions
- the invention relates to a vibration damper according to the preamble of claim 1.
- a hydraulic vibration damper such as that (as a telescopic shock absorber)
- Vibration or shock absorbers are used in vehicles in connection with the suspension to dampen the shocks or vibrations caused by uneven roads as far as possible in a controlled manner.
- the purpose is to send as few road impulses as possible to the sprung mass of the vehicle Pass on few road impulses to the sprung mass of the vehicle (frame, chassis, body), but without the wheels losing grip.
- damping systems vary greatly according to the different areas of application, which range from (soft-sprung) comfort cars to (hard) racing vehicles.
- the requirements for the damping system are determined by the type and nature of the slopes, but also by vehicle-side parameters such as vehicle mass, mass distribution, wheel suspension, tires and much more, up to the outside and operating temperature, which in particular affects the oil viscosity. flows.
- damping characteristics of a vibration damping system are usually described in a damping characteristic diagram. 9 shows, by way of example, linear and progressive relationships between the deflection speed v (m / s) and the associated pressure damping force F (kN), as are customary for simple applications. Vibration damping systems with such damping characteristics can only be used to a very limited extent for high-performance vehicles (or driving parts).
- Vibration dampers are customary, in which a piston in a cylindrical tube in oil continuously dampens both compressive and tensile forces (compressive and rebound stages) by oil flowing through a bore under impact loads, as a result of which the compressive or tensile pulse is broken down.
- Another function in addition to damping during compression (compression) and rebound (rebound) is the suspension itself, which is usually done by spring elements or air cushions.
- Such a shock absorber is known from DE-A 32 14 599, in which the bore is closed off by spring elements. The damping characteristics that can be achieved in this way depend on the rigidity of the spring elements used.
- Damping characteristics designed operating conditions is constant and can only be changed with considerable effort (by installing completely different systems).
- higher-quality vehicles, in particular high-performance vehicles, as described at the beginning it is, however, required that the damping characteristics can be flexibly adapted to the respective conditions of use.
- the invention is based on the object of further developing a vibration damper of the type mentioned at the outset such that its damping characteristic can be easily adapted to the specified conditions without significantly increasing the unsprung masses. This object is achieved by the features specified in the characterizing part of claim 1.
- An important point of the invention is that adjustment devices are provided, by means of which the force with which the spring acts on the valve body in the direction of the valve seat (with the valve flowing through) can be set from the outside, that is to say without replacing the vibration damper . This allows each vehicle to be adapted to changing circumstances in a very simple manner.
- the valve body preferably comprises a conical section and (adjacent to the side of the larger diameter) a cylindrical section, the diameter of which is smaller than that of the valve seat.
- the valve body lies with its cylindrical section inside the valve seat.
- valve body and / or the spring are preferably designed to be exchangeable.
- installation kits 11 are used, which are color-coded so that it can be seen from the outside which valve body or which spring is inserted, so that the damping characteristic of the system can be recognized from the outside.
- the valve body is slidably mounted on a valve pin. arranges who carries a feather seat. One end of the spring rests on the spring seat, and the other end rests on the valve body.
- the valve pin is preferably adjustable in the direction of the valve body via a thread. In this way, in the case of a valve whose valve body rests on the valve seat under contact in the idle state, the point from which the valve releases an opening can be determined. If the valve described above is used with a conical and a cylindrical section which releases a certain flow cross-section from the beginning, the screw-in depth determines the point (with respect to v) at which the flow cross-section begins to increase. Furthermore, the characteristic in this area of high flow velocities v is also determined at the same time.
- the valve body is designed as a control needle, which is adjustable in the direction of the valve seat (likewise preferably via a thread).
- the valve seat is held so that it can slide against the spring.
- a kinematic reversal of the previously shown embodiment of the invention which is particularly suitable for the case in which the valve is formed in the piston. You can then lead the control needle through the entire length of the piston to the outside.
- a bypass valve to the valve described above is provided, which has a flow cross section that can be adjusted from the outside.
- This valve thus represents a purely throttle bore and is particularly preferred for the case in which the valve closes completely in the idle state by engaging the valve body with the valve seat.
- a throttle valve is provided in series with the aforementioned valve or the assembly consisting of the aforementioned valve and the associated bypass valve for setting the damping force curve in the region of high deflection speeds.
- This - hydraulically - serially arranged throttle valve represents a - in terms of force - parallel-connected damping element. Particularly advantageous is the fact that the damping properties with respect to high deflection speeds can be set almost independently of the damping properties at low deflection speeds.
- a further damper with a second piston or second cylinder can be provided parallel to the first damper (with its valves) with this throttle valve for setting the damping force curve in the region of high deflection speeds.
- This embodiment is particularly suitable for motorcycles in which two dampers are assigned to one wheel.
- This embodiment of the invention is particularly inexpensive and simple.
- scales are preferably provided for reading the setting status in addition to the color or graphic markings for the valve type.
- valve described above the damping properties of which can be adjusted via the control needle, is particularly suitable for the rebound stage, while the other valves are preferably installed in the compression stage.
- FIG. 2-5 detailed representations corresponding to the sections II-V of Fig. 1,
- FIG. 7 shows a modified embodiment of the invention relating to the valve shown in FIG. 4,
- FIG. 8 shows the representation of a double shock absorber systems similar to that of FIG. 1,
- the vibration damper 1 shown in FIG. 1 comprises a first telescopic shock absorber 1 ′ and a second telescopic shock absorber 11 . These belong to a first shock absorber 8 or a second shock absorber 8 *, which can be used, for example, on the front wheel of a motorcycle (or also on the rear wheel).
- the telescopic shock absorber 1 comprises a piston 2 which is slidably received in an oil-filled cylinder 3 in a manner known per se. On the outside, the arrangement is enclosed by a damper bar 9.
- first valve 4 for setting the basic hardness
- second valve 5 which is arranged as a bypass valve to the first valve 4, for Adjustment of the damping provided at low deflection speeds.
- the telescopic shock absorber 1 '' also has a cylinder 3 'and a piston 2 1 , in the piston plate 23 fixed
- the damper l 1 'further comprises a valve 6 which is externally adjustable, being adjustable about this valve 6 of the damping force characteristic in the large Einfederungs Anlagenen.
- the telescopic shock absorber 1 is • *, which corresponds to 4 in terms of forces parallel to the telescopic shock absorber 1 • a hydraulic series circuit of the valve (with the bypass valve 5) to the valve. 6
- valve 17 In the piston 2 of the telescopic shock absorber l 1 is a valve hen 17 vorgese ⁇ to adjust the damping behavior in the rebound, located at what in hydraulic parallel circuit a wei ⁇ teres valve merit ⁇ through holes 10 with it, the spring-loaded valve plate is defined. 11
- the valve 17 represents a fourth adjustable valve, which is also adjustable from the outside by means of a control needle 16. This is also explained in more detail below.
- the valve 4 shown in more detail in FIG. 2a comprises a valve pin 26 which is held by a thread 29 in a valve holder 18 which is attached to the damper bar 9.
- the valve pin 26 also has a spring seat 15 on which a spring 14 is supported with one end. The other end of the spring 14 rests on the rear side of a valve cone 13, which carries a conical section 21 at its front end. With this conical gate 21, the valve cone 13 is seated in the bore of a flow disc 27, which thus forms a valve seat.
- a cylindrical section 20 is provided between the conical section 21 and the rear end of the valve cone 13.
- a flow occurs only at a pressure which is sufficient to lift the valve cone 13 out of its seat on the flow disk 27 with respect to the force of the spring 14. This point can be shifted towards higher values by screwing the valve pin 26 in deeper, by prestressing the spring 14 more.
- the effect of the setting of the valve 4 is indicated in Fig. 10.
- valve 4 1 shown in FIG. 2b differs from that according to FIG. 2a in that the cylindrical section 20 has a smaller diameter than the bore in the flow disc 27 '. This creates an annular gap between the cylindrical part 20 of the valve cone 13 and the opening in the flow disc 27 'in the stationary state of the damper. A type of bypass valve is thus formed which determines the course of the damping force in the region of low deflection speeds.
- valve 4 1 ' which again consists of a valve pin 26 *' with a valve cone 13 '' thereon,
- the spring 14 ′′ and spring seat 15 ′′ exist can be completely removed from the valve holder 18.
- the valve pin 26 '* is screwed with its thread 29 •' into a screw-in holder 19, which in turn is screwed into the valve holder 18 via a thread 19 '.
- a shut-off device 33 is provided which is the space in which the valve 4' can separate 'is from übri ⁇ gen interior of the system.
- bypass valve 5 is provided (hydraulically) parallel to the valve 4. This is drawn in detail in FIG. 3.
- This bypass valve 5 has an externally adjustable valve needle 34, which is held in the damper spar 9 via a thread 31.
- the valve needle 34 has a conical front end which more or less exposes a bore 35 depending on the screwing depth.
- valve 6 fitted in the second telescopic shock absorber l 1 is shown in more detail in FIG. 4.
- This comprises a valve needle 36, which is attached via a thread 32 in a valve holder 18 * and has a cone 37 which projects into a bore 38.
- the bore 38 is more or less closed by the cone 37.
- the throughflow and thus the damping force curve are set in the region of high deflection speeds by means of the valve 6 (see FIG. 10).
- Valves 4, 5 and 6 are advantageously designed as prefabricated valve cartridges in order to enable rational series production by being pressed in or screwed in (see FIG. 2 c) in corresponding receiving bores of the respective damper cylinder or valve holder. Depending on the damper type and intended use, 4, 5 and 6 can be used for each valve
- Valve cartridges with different flow characteristics are used.
- the valve cartridges 4, 5 and 6 are designed in such a way that they cannot be mixed up during assembly, e.g. due to different diameters, each valve identifies its type and performance class through distinctive labeling (e.g. color markings).
- valves 4, 5 and 6 are designed as exchangeable valve inserts (see FIG. 2c) in order to make it possible to extend the setting ranges beyond the setting range of the currently installed valves by means of valves of other performance classes.
- the valve 4 is used to adjust the basic hardness, the throttle valve 5 lying parallel to it to adjust the response behavior.
- a shock introduced by a bump in the road causes the damper spar 9 to deflect at an initial speed V A.
- the damper oil flows up through the bore 10.
- the spring-loaded valve cone 13 in the valve 4 opens up an additional cross section, this cross section being controllable via a precisely defined cone shape depending on the deflection.
- the valve 4 is preferably interchangeable such that a plurality of valve cones 13 with different cone shapes and springs 14 of different hardness can be used.
- the valve cone 13 and the spring 14 should be easy to replace without dismantling the strut.
- the bias of the spring 14 can be easily adjusted from the outside.
- the cone 13 rests on the flow disc 27 in the idle state, so that the oil flow only flows after the spring preload, which can be set by turning the valve pin 26 (which is axially displaced by the thread 29), is overcome .
- the spring pretension which occurs when the cone 13 emerges from the flow disc 27 is influenced by turning the valve pin 26 'or 26''.
- the bypass valve 5 enables an effective cross section to be released in addition to the valve 4 'or 4' 'or also to the valve 4. It is thus possible to set the response behavior of the valve 4.
- the effective bypass cross section of valve 5 is also easily adjustable from the outside.
- the valve 6, which is shown in FIG. 4, is used to set the rapid deflection behavior and differs from the valve 5 in spite of similarities in principle with regard to FIG.
- valve 5 forms an independent functional unit with the valve 4.
- Valve 6 acts in addition to the combined functional unit of valve 5 and valve 4.
- Valve 6 throttles the oil flow at high deflection speeds with a cross-section that is fixed in operation, but continuously variable.
- the adjustable valve 17 is provided, in which a sleeve 24, which is biased by a spring 25 against the piston plate 23, is displaced relative to the control needle 16 by the flow forces of the oil when it is pulled.
- the control needle 16 is held by a thread 30 and provided at its lower end with a conical section 21 and an overlying cylindrical section 20.
- the diameter of the cylindrical section 20 is denoted by d2 in FIG. 5, the diameter at the slender end of the cone 21 is denoted by d3.
- the inside diameter of the sleeve 24 is denoted by dl in FIG. 5.
- the length of the cone is indicated by h, while the immersion depth of the conical section in the interior of the sleeve 24 is designated by t.
- the flow is determined with a constant inner diameter of the sleeve 24 by the diameter of the control needle 16, by its screw-in depth t and by the cone shape.
- the depth of the control needle 16 with respect to the sleeve 24 can be changed from the outside by turning (and thus by adjusting the thread 30) without opening the shock absorber.
- the depth of adjustment of the control needle 16 in connection with the shape of the conical section 21 determines the oil flow when rebounding.
- a corresponding family of characteristic curves is given in FIG. 6.
- the control needle 16 is preferably replaced without removing the telescopic shock absorber 1 by opening a closure cap 22 provided there.
- the control needle 16 inserted is unscrewed without influencing the oil filling, and another (preferably color-coded) control needle 16 with one another shape of the conical portion 21 is screwed in.
- the changeable effective parameters are on the rebound stage side the diameter d2 of the control needle, the setting depth t in relation to the sleeve 24 and the cone shape. These parameters influence the characteristic curves on the rebound side, as indicated in FIG. 6.
- the vibration damper according to the invention shown here can be supplied and assembled as a unit in known combinations with a resilient element, such as a coil spring or an air cushion (see FIG. 7).
- the usual form of use will be the single-rod damper with valves 4, 5, 6 and 17.
- simplified versions can be useful, for example those which are only equipped with valves 4, 5 and 17.
- the shock absorber at the upper end is designed such that the control needle 16 can still be replaced or at least adjusted in a controlled manner after the shock absorber has been installed.
- valves 4, 5, 6 and 17 On the front wheel of high-performance motorcycles, the two bars with damping / suspension are usually equipped symmetrically with valves 4, 5, 6 and 17. In order to reduce costs as well as to reduce mass, an asymmetrical arrangement of the valves can be useful, as shown in FIG. 1. One can also equip a shock absorber with valves 4, 5 and 17, the others with valves 6 and 17. The desired effect then only results from the coordinated interaction of all elements. In fact, tests with sufficiently rigid wheel axles and axle suspension prove that such an asymmetrical system works properly.
- valves 4, 5 and 17 are metrically distributed on the spring legs of the front wheel of a motorcycle.
- valves 4, 5, 6 and 17 are, for example, by means of transmission elements known per se, e.g. adjustable from the dashboard of a motor vehicle. It is also advantageous if the setting status of the valves can be read numerically.
- Scales are useful for angles of rotation below 360 °. In the case of larger angles of rotation, scaling of the setting depth is preferred.
- FIG. 7 shows the principle of a gas pressure shock absorber known per se, in which a gas cushion 20 is provided.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
- Axle Suspensions And Sidecars For Cycles (AREA)
- Vehicle Body Suspensions (AREA)
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19914137176 DE4137176C2 (de) | 1991-11-12 | 1991-11-12 | Kennlinienvariables Stoß- und Schwingungsdämpfersystem |
DE4137176 | 1991-11-12 | ||
PCT/EP1992/002601 WO1993010371A1 (de) | 1991-11-12 | 1992-11-12 | Schwingungsdämpfer |
Publications (1)
Publication Number | Publication Date |
---|---|
EP0611422A1 true EP0611422A1 (de) | 1994-08-24 |
Family
ID=6444617
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP92923357A Withdrawn EP0611422A1 (de) | 1991-11-12 | 1992-11-12 | Schwingungsdämpfer |
EP92119390A Withdrawn EP0542282A1 (de) | 1991-11-12 | 1992-11-12 | Schwingungsdämpfer |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP92119390A Withdrawn EP0542282A1 (de) | 1991-11-12 | 1992-11-12 | Schwingungsdämpfer |
Country Status (4)
Country | Link |
---|---|
EP (2) | EP0611422A1 (de) |
JP (1) | JPH07501130A (de) |
DE (1) | DE4137176C2 (de) |
WO (1) | WO1993010371A1 (de) |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4429562C2 (de) * | 1994-08-19 | 1998-03-19 | Stefan Maier | Hydraulischer Schwingungsdämpfer für das gefederte Vorderrad eines Fahrrads |
WO1996015004A1 (en) * | 1994-11-14 | 1996-05-23 | Nai Neway, Inc. | Trailer suspension and locking column therefor |
DE4440581A1 (de) * | 1994-11-14 | 1996-05-30 | Industrieanlagen Betriebsges | Schwingungsdämpferventil für definierte Kennlinien |
EP0715091B1 (de) * | 1994-12-03 | 2002-07-10 | ZF Sachs AG | Schwingungsdämpfer mit einstellbarer Dämpfkraft |
DE19542293B4 (de) * | 1994-12-03 | 2006-08-31 | Zf Sachs Race Engineering Gmbh | Schwingungsdämpfer mit einstellbarer Dämpfkraft |
DE19501490A1 (de) * | 1995-01-19 | 1996-07-25 | Hunger Walter Dr Ing E H | Hydropneumatisches Federbein, insbesondere für eine Gabel eines Fahrrades |
DE19547910C1 (de) * | 1995-12-21 | 1997-01-16 | Bilstein August Gmbh Co Kg | Vorrichtung zur Beeinflussung von Kennlinien eines Schwingungsdämpfers |
FR2751713B1 (fr) | 1996-07-24 | 1998-09-18 | Donerre Amortisseur Soc | Systeme amortisseur a huile |
DE19701272A1 (de) * | 1997-01-16 | 1998-07-23 | Bayerische Motoren Werke Ag | Federbein zur Federung des Vorderrades eines Motorrades |
DE19853854A1 (de) * | 1998-11-23 | 2000-05-25 | Anton Pfeifer | Bodenventil für 2-Rohrdämpfer |
DE10315088A1 (de) * | 2003-04-02 | 2004-10-14 | Gustav Magenwirth Gmbh & Co. Kg | Dämpfungssystem |
DE102008013359A1 (de) * | 2008-03-10 | 2009-09-17 | Gustav Magenwirth Gmbh & Co. Kg | Dämpfereinheit |
DE102011002014B4 (de) * | 2011-04-13 | 2016-12-15 | Ktm Ag | Einrichtung und Verfahren zur Führung eines Rades eines Fahrzeugs |
FR3009539B1 (fr) * | 2013-08-06 | 2015-09-04 | Decathlon Sa | Dispositif de suspension telescopique muni d'un systeme de reperage de precontrainte |
CN104455175A (zh) * | 2014-12-05 | 2015-03-25 | 重庆市亮影工贸有限公司 | 后减震器复原阻力调节机构 |
DE102018110490A1 (de) * | 2018-05-02 | 2019-11-07 | Dt Swiss Ag | Stoßdämpfer für ein Fahrrad |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB565630A (en) * | 1943-01-08 | 1944-11-20 | Ribbesford Company Ltd | Improvements in or relating to liquid damped shock absorbers |
GB792868A (en) * | 1955-01-28 | 1958-04-02 | Armstrong Patents Co Ltd | Improvements in or relating to hydraulic shock absorbers |
DE1268990B (de) * | 1957-07-12 | 1968-05-22 | Boge Gmbh | Kolben fuer doppeltwirkende hydraulische Schwingungsdaempfer, insbesondere fuer Kraftfahrzeuge |
DE1967943U (de) * | 1965-12-22 | 1967-09-07 | Hoesch Ag | Mit einem kraftbegrenzungsventil versehener daempferkolben. |
DE2113948A1 (de) * | 1970-03-25 | 1971-10-14 | Grinnell Corp | Hydraulischer Stossdaempfer |
GB1354385A (en) * | 1971-11-16 | 1974-06-05 | Armstrong Patents Co Ltd | Telescopic hydraulic shock absorbers |
GB1447229A (en) * | 1972-10-26 | 1976-08-25 | Itt | Shock absorber |
JPS57107450A (en) * | 1980-12-24 | 1982-07-03 | Kayaba Ind Co Ltd | Damping force adjuster in hydraulic damper |
DE3214599A1 (de) * | 1982-04-20 | 1983-10-20 | Anton Ing.(grad.) 8492 Furth Pfeifer | Teleskop-federbein |
DE3503318C2 (de) * | 1985-01-31 | 1987-01-29 | ACE Stoßdämpfer GmbH, 4018 Langenfeld | Hydraulische Vorrichtung für automatische oder halbautomatische Feuerwaffen zur Rückstoßdämpfung |
DE3544474A1 (de) * | 1985-12-16 | 1987-06-19 | Anton Ing Grad Pfeifer | Fahrzeugstossdaempfer |
-
1991
- 1991-11-12 DE DE19914137176 patent/DE4137176C2/de not_active Expired - Fee Related
-
1992
- 1992-11-12 JP JP5508964A patent/JPH07501130A/ja active Pending
- 1992-11-12 EP EP92923357A patent/EP0611422A1/de not_active Withdrawn
- 1992-11-12 WO PCT/EP1992/002601 patent/WO1993010371A1/de not_active Application Discontinuation
- 1992-11-12 EP EP92119390A patent/EP0542282A1/de not_active Withdrawn
Non-Patent Citations (1)
Title |
---|
See references of WO9310371A1 * |
Also Published As
Publication number | Publication date |
---|---|
JPH07501130A (ja) | 1995-02-02 |
WO1993010371A1 (de) | 1993-05-27 |
DE4137176C2 (de) | 1993-10-28 |
EP0542282A1 (de) | 1993-05-19 |
DE4137176A1 (de) | 1993-05-13 |
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