WO2015185274A1 - Système de soupapes d'amortissement fonction de la fréquence - Google Patents

Système de soupapes d'amortissement fonction de la fréquence Download PDF

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Publication number
WO2015185274A1
WO2015185274A1 PCT/EP2015/059012 EP2015059012W WO2015185274A1 WO 2015185274 A1 WO2015185274 A1 WO 2015185274A1 EP 2015059012 W EP2015059012 W EP 2015059012W WO 2015185274 A1 WO2015185274 A1 WO 2015185274A1
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WO
WIPO (PCT)
Prior art keywords
control
piston
pot
damping
spring element
Prior art date
Application number
PCT/EP2015/059012
Other languages
German (de)
English (en)
Inventor
Helmut Baalmann
Oswald Lichtlein
Eberhard Simon
Original Assignee
Zf Friedrichshafen Ag
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 Zf Friedrichshafen Ag filed Critical Zf Friedrichshafen Ag
Publication of WO2015185274A1 publication Critical patent/WO2015185274A1/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
    • F16F9/504—Inertia, i.e. acceleration,-sensitive means

Definitions

  • the invention relates to a Dämpfventilan extract with a frequency-dependent Dämpfkraftkennline, according to claim 1.
  • the object of a vibration damper in a motor vehicle is to dampen the vibrations excited by the uneven road surface.
  • a compromise must always be found between driving safety and driving comfort.
  • a vibration damper, the Dämpfventilan Aunt is tuned hard and has a high Dämpfkraftkennline is optimal for a high driving safety. If a high level of comfort is to be met, then the damping valve arrangement should be as soft as possible. In a vibration damper with a conventional, not electronically adjustable by means of an actuator damping valve arrangement, this compromise can be found only with great difficulty.
  • Dämpfventilan strips with a frequency-dependent Dämpfkraftkennline are known from the prior art, which are equipped with an additional electronic and / or mechanical control and switch on or off depending on a compression and / or rebound frequency of the vibration damper an additional Dämpfventilanaku
  • Solutions which have a control arrangement mounted on the piston rod, coaxial to the damping piston, comprising a control pot, and an axially displaceable control piston arranged in the control pot.
  • the control piston axially delimits an enclosed in the control pot control chamber which is connected via an inlet connection with the Dämpfventilan eleven.
  • a spring element is arranged, which introduces a spring force in the control piston on the one hand and in the damping valve on the other hand axially. If the control room is filled with damping medium, then pushes the spool in the direction of the damping valve and increases over the spring element, the contact pressure of the valve discs of the damping valve, which increases the damping force.
  • All known Dämpfventilanssenen are characterized by a high complexity, among other things, since they require a high tuning accuracy. In particular, it is difficult in these vibration dampers, the soft and the hard Dämpfkraftkennline, and the balance of power between the spring force of the spring element and the force with which the damping medium in the control chamber shifts the control piston, without adjusting additional control.
  • the object of this invention is to provide a simple and inexpensive Dämpfventilan extract which has a frequency-dependent Dämpfkraftkennline and allows easy adjustment of the Dämpfkraftkennline.
  • control arrangement has an adjusting device for adjusting the pretensioning of the spring element.
  • the adjusting device has at least one recess formed in the bottom of the pot, as well as an adjusting element arranged in the recess, which protrudes into the control chamber and defines the bias of the spring element via the control piston.
  • a bore may be provided into which a pin is inserted as an adjusting element which pushes the control piston in the direction of the spring element and thus increases the bias of the spring element.
  • the pin Upon reaching a defined preload, the pin can be caulked in the bottom of the pot or attached in some other way.
  • a threaded hole as a recess and a screw can be provided as an adjustment.
  • the pot bottom and / or the control piston may be designed such that a radial extension surface of the end of the control piston facing the bottom of the pot and / or the surface of the pot bottom facing the control chamber is an imaginary one, including a defined angle , is aligned with respect to the longitudinal axis of the Dämpfventilan extract perpendicular surface.
  • the adjusting device comprises at least one executed on the control piston and extending in the direction of the pot bottom survey, which engages in at least one executed on the bottom of the pot recess. If several depressions with different depths are present, then the adjustment of the pretensioning of the spring element can take place by choosing the depression of suitable depth. Alternatively, the survey may be performed on the bottom of the pot and the recess on the control piston.
  • the adjusting device can have at least one spacer element arranged between the spring element and the control piston or between the spring element and the damping piston.
  • the damping force characteristic can be adjusted by means of the number or the thickness of the spacer elements used.
  • the adjusting device may have at least one additional spring arranged between the spring element and the control piston or between the spring element and the damping piston, as indicated in a further advantageous exemplary embodiment.
  • the adjusting device has an adjusting sleeve, which surrounds the control pot in the circumferential direction and is fixedly connected to the control pot, wherein the shim is axially supported with its outer edge region on the, facing the damping piston end portion of the adjusting.
  • the control pot may have at least one fastening recess running on the pot wall, wherein the adjusting sleeve may be connected to the control pot by means of a partial plastic deformation in the direction of the fastening recess.
  • Fig. 1 is a sectional view of an embodiment of a
  • Fig. 2 is a sectional view of an alternative embodiment
  • FIG. 3a shows a sectional view of a further alternative embodiment of a Dämpfventilan extract with an adjusting device according to claim 1;
  • Fig. 3b shows a representation of an adjusting device according to FIG. 3a) in the neck
  • FIG. 4 is a sectional view of a further alternative embodiment of a Dämpfventilanix with an adjusting device according to claim 1.
  • FIG. 5 is a sectional view of a further alternative embodiment of a Dämpfventilanix with an adjusting device according to claim 1.
  • FIG. 6 is a sectional view of another alternative embodiment of a Dämpfventilanix with an adjusting device according to claim 1.
  • Fig. 1 shows a piston rod 3, which has a so-called piston rod pin 32.
  • the piston rod pin 32 is a reduced diameter portion of the piston rod 3.
  • the entire damping valve assembly 1 is threaded on the piston rod pin 32 and is between a portion of the piston rod 3 adjacent the piston rod pin 32 which has a larger diameter than the piston pin pin 32 , and a fastening means 33, which is shown in FIG. 1 as a piston rod nut, axially braced.
  • the damping valve arrangement 1 comprises a damping piston 4, which is arranged within a cylinder 2 filled with a damping fluid and fixed axially on a piston rod 3.
  • the damping piston 4 is equipped with a piston seal 34, which radially seals them relative to the cylinder 2.
  • the fixed to the piston rod 3 damper piston 4 is disposed axially displaceable within the cylinder 2 together with the piston rod 3 and divides the cylinder interior in a first piston rod side working space 7 and a second, facing away from the piston rod
  • the damper piston 4 is each with a check valve 35; 36 equipped in each flow direction of the damper fluid.
  • the check valves 35; 36 each comprise at least one flow channel 6 designed in the damping piston 4, which is covered with at least one valve disk 5.
  • the flow channels 6 can be covered by a plurality of valve disks 5 stacked one above the other - so-called valve disk packs.
  • the number, size and design of the individual valve disks 5 in a valve disk package influence the contact pressure, as well as the Dämpfkraftkennline, and the damping behavior of a vibration damper.
  • Control pot 10 has a cylindrical pot wall 1 1 and a disc-shaped, on a side facing away from the damping piston 4 end of the control pot 10 cup bottom 12.
  • control piston 13 arranged in the control pot 10 control piston 13 bounded on the check valve 35 side facing axially enclosed in the control chamber 10 control chamber 14 so that an axial displacement of the control piston 13 within the control pot 10, the volume of the control chamber 14 defined changes.
  • the damping valve arrangement further has an inlet connection 37, which connects the first working space 7 with the control space 14.
  • this comprises one executed on the piston rod 3 Bypass 39, at least one the bypass 39 with the first working space 7 connecting flow recess 40, and at least one the bypass 39 with the control chamber 14 connecting throttle 41st
  • damping valve arrangement 1 has a drain connection 38, which connects the control chamber 14 with the second working space 8.
  • the throttle 41 can be realized in many ways, such as by drilling or embossing. Also conceivable are more complex valves as an inflow resistance to the control chamber 14, such as a pressure relief valve, which allows an inflow into the control chamber 14 only above an adjustable pressure. These embodiments are not shown in the figures, but are still within the meaning of the present invention feasible.
  • a tubular guide bush 42 is arranged between the damping piston 4 and the pot bottom 12 of the control arrangement 9 in order to realize a tensioning chain of the damping valve arrangement 1.
  • the control piston 13 surrounds the guide bush 42 radially and slides axially on the outer surface of the guide bush 42, during a change in volume of the control chamber fourteenth
  • a spring element 17 is arranged in the form of a plate spring. This is supported axially on the one hand on the control piston 13 and on the other hand on the valve disc of the check valve.
  • the spring element 17 thus acts on the valve disc 5 axially in the direction of the flow channel 6 and the control piston 13 in the direction of the pot bottom 12 with a defined spring force.
  • the control piston 13 has a stop 43, which limits the axial movement of the control piston 13 in the direction of the pot bottom 12. In the position of the control piston 13 shown in FIG. 1, the biasing force of the spring element 17 is the lowest, so that a low defined damping force level is achieved.
  • the control piston 13 is radially inside and outside in comparison to the smallest cross section of the inlet connection 37 approximately close. However, it may be a defined leak between the control piston 13 and the pot wall 1 1 of the control pot 10 and / or an outflow throttle in the control piston 13 and / or executed in the control pot 10, which affects the drain connection 38.
  • the surface of the control piston 13 facing the control chamber 14 is larger than a surface of the valve disk 5 delimited by the flow channel 6. This means that when the piston rod 3 moves out of the cylinder 2 it is acted upon by the increasing pressure of the damping medium - that is to say pressure-loaded axial surface of the control piston 13 is greater than the pressurized axial surface of the zugsten check valve 35th
  • the damping medium is throttled through the smallest cross-sectional area of the opening into the control chamber 14 inlet connection 37 conveyed into the control chamber 14.
  • the control piston 13 is displaced, thereby tensioning the spring element 17, which is axially supported on the valve disk 5 of the check valve 6, whereby the damping force of the check valve 35 is increased.
  • the control chamber 14 is not or only slightly filled, so that the spring element 17 is not further biased and the damping force remains at a defined low level.
  • the integral of pressure difference of Dämpffluid réelle on the valve disc 5 to Dämpffluid réelle in the control chamber 14 over time, despite the throttle resistance of the feed connection 37 is large enough to supply the control chamber 14 as much Dämpffluid in that the control piston 13 biases the spring element 17 until the control piston 13 strikes a stop disk 44 arranged between the guide bush 42 and the valve disks 5 of the check valve 35.
  • the stop disc 44 limits the axial movement of the control piston 13 in the direction of the damping piston 4, and defines the maximum bias of the spring element 17 and thus also the highest damping force characteristic. After reversing the piston rod movement, the damping fluid pressure drops again.
  • the spring element 17 prestressed by the control piston 13 forces the damping fluid back via the control piston 13, predominantly via the inlet connection 37, into the piston rod-side working space 7.
  • control arrangement 1 has a setting device 18 for adjusting the prestressing of the spring element 17.
  • FIG. 1 shows, for example, that the adjusting device 18 has at least one recess 19 made in the bottom of the pot 12, as well as an adjusting element 20 arranged in the recess 19.
  • the adjusting element 20 may be designed as a screw or as a pin which projects into the control chamber 14, is supported on the control piston 13 and defines the bias of the spring element 17 via the control piston 13.
  • the adjusting device 18 according to FIG. 2 may be designed such that it has a radial extension surface 21 of the end portion 15 of the control piston 13 facing the bottom of the pot 12 and / or the surface 16 of the cup bottom 12 facing the control chamber 14, which includes a defined one Angle ⁇ to an imaginary, with respect to the longitudinal axis L of the damper valve assembly 1 perpendicular surface 22 is aligned.
  • the adjusting device 18 may alternatively comprise at least one elevation 23 extending on the control piston 13 and extending in the direction of the pot bottom 12 or running on the bottom of the pot 12 and extending in the direction of the control piston 13, which in at least one the pot bottom 12 or on the control piston 13 running recess 24 engages.
  • FIG 4 shows an alternative embodiment of the adjusting device 18, which has at least one spacer element 25 arranged between the spring element 17 and the control piston 13 or between the spring element 17 and the damping piston 4.
  • the control arrangement 9 shown in FIG. 5 comprises an adjusting device 18, which has a rigid adjusting washer 26 which is disposed between the control ben 13 and the spring element 17 is arranged. Furthermore, the adjusting device 18 has an adjusting sleeve 27 which surrounds the control pot 10 in the circumferential direction and is fixedly connected to the control pot 10. In this case, the shim 26 is supported with its outer edge region 28 on the, to the damping piston 4 facing end portion 29 of the adjusting sleeve 27 axially.
  • the control pot 10 may have at least one fastening recess 30 made on the pot wall 11. This can for example also be designed as a circumferential groove.
  • the Ein-Stellhülse 27 can be connected by means of a partial plastic deformation in the direction of the piston rod 3 in the region of the mounting recess 30 with the control pot 10.
  • this can have at least one additional spring 31 arranged between the spring element 17 and the control piston 13 or between the spring element 17 and the damping piston 4, with a softer spring force characteristic than the spring element 17.

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

Abstract

L'invention concerne un ensemble de soupapes d'amortissement 1 pour amortisseur de vibrations, comprenant un piston amortisseur 4 pourvu au moins d'une soupape anti-retour 35, et un dispositif de commande 9 pourvu d'un piston de commande 13 et d'un élément ressort 17 disposé entre la soupape anti-retour 35 et le piston de commande 13. L'invention est caractérisée en ce que le dispositif de commande 9 présente un dispositif de régulation 18 destiné à la régulation de la précontrainte de l'élément ressort 17.
PCT/EP2015/059012 2014-06-05 2015-04-27 Système de soupapes d'amortissement fonction de la fréquence WO2015185274A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014210702.4A DE102014210702A1 (de) 2014-06-05 2014-06-05 Frequenzabhängige Dämpfventilanordnung
DE102014210702.4 2014-06-05

Publications (1)

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WO2015185274A1 true WO2015185274A1 (fr) 2015-12-10

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE1023716B1 (nl) * 2016-01-03 2017-06-26 Shi Yan Frequentie afhankelijke schokdemper
WO2017202647A1 (fr) * 2016-05-23 2017-11-30 Thyssenkrupp Bilstein Gmbh Amortisseur de vibrations sélectif en fréquence pour des véhicules à moteur comprenant une soupape de commande de dérivation
WO2017202646A1 (fr) * 2016-05-23 2017-11-30 Thyssenkrupp Bilstein Gmbh Amortisseur de vibrations sélectif en fréquence pour des véhicules à moteur comprenant une soupape de commande de dérivation
WO2017220252A1 (fr) * 2016-06-20 2017-12-28 Zf Friedrichshafen Ag Ensemble soupape de fond sélectif en fréquence
WO2018046195A1 (fr) * 2016-09-08 2018-03-15 Zf Friedrichshafen Ag Ensemble soupape d'amortissement dépendant de la fréquence et amortisseur de vibrations
EP3933227A4 (fr) * 2020-04-26 2022-05-11 Ningbo Kasico Shock Absorber Manufacture Co., Ltd. Amortisseur hydraulique à force autovariable

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Publication number Priority date Publication date Assignee Title
DE102016200935B4 (de) * 2016-01-22 2018-11-22 Thyssenkrupp Ag Schwingungsdämpfer mit frequenzabhängig arbeitender Ventilanordnung

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FR2576996A1 (fr) * 1985-01-31 1986-08-08 Daimler Benz Ag Amortisseur d'oscillations pour vehicules
US20120160624A1 (en) * 2010-12-28 2012-06-28 Yohei Katayama Shock absorber
EP2511563A1 (fr) * 2009-12-11 2012-10-17 Kayaba Industry Co., Ltd. Dispositif amortisseur de chocs

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DE4441047C1 (de) 1994-11-18 1996-01-18 Bilstein August Gmbh Co Kg Proportionalventil
US7958981B2 (en) 2005-06-06 2011-06-14 Kayaba Industry Co., Ltd. Shock absorber

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Publication number Priority date Publication date Assignee Title
FR2576996A1 (fr) * 1985-01-31 1986-08-08 Daimler Benz Ag Amortisseur d'oscillations pour vehicules
EP2511563A1 (fr) * 2009-12-11 2012-10-17 Kayaba Industry Co., Ltd. Dispositif amortisseur de chocs
US20120160624A1 (en) * 2010-12-28 2012-06-28 Yohei Katayama Shock absorber

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108713111A (zh) * 2016-01-03 2018-10-26 闫石 对频率依赖阀的改进
WO2017112980A1 (fr) * 2016-01-03 2017-07-06 Shi Yan Ensemble piston coulissant variant avec la fréquence
WO2017112981A1 (fr) * 2016-01-03 2017-07-06 Shi Yan Perfectionnement apporté à des soupapes variant avec la fréquence
BE1023907B1 (nl) * 2016-01-03 2017-09-11 Shi Yan Frequentie afhankelijke schokdemper
BE1023716B1 (nl) * 2016-01-03 2017-06-26 Shi Yan Frequentie afhankelijke schokdemper
US10907699B2 (en) 2016-01-03 2021-02-02 Plush Ride Gmbh Sliding frequency dependent piston assembly
WO2017202647A1 (fr) * 2016-05-23 2017-11-30 Thyssenkrupp Bilstein Gmbh Amortisseur de vibrations sélectif en fréquence pour des véhicules à moteur comprenant une soupape de commande de dérivation
CN109154353A (zh) * 2016-05-23 2019-01-04 蒂森克虏伯比尔斯坦有限公司 用于机动车辆的、具有旁通控制阀的频率选择性减震器
CN109154352A (zh) * 2016-05-23 2019-01-04 蒂森克虏伯比尔斯坦有限公司 用于机动车辆的、具有旁通控制阀的频率选择性减震器
CN109154353B (zh) * 2016-05-23 2020-11-24 蒂森克虏伯比尔斯坦有限公司 用于机动车辆的、具有旁通控制阀的频率选择性减震器
CN109154352B (zh) * 2016-05-23 2020-12-04 蒂森克虏伯比尔斯坦有限公司 用于机动车辆的、具有旁通控制阀的频率选择性减震器
US10883560B2 (en) 2016-05-23 2021-01-05 Thyssenkrupp Bilstein Gmbh Frequency-selective vibration damper for motor vehicles having a bypass control valve
WO2017202646A1 (fr) * 2016-05-23 2017-11-30 Thyssenkrupp Bilstein Gmbh Amortisseur de vibrations sélectif en fréquence pour des véhicules à moteur comprenant une soupape de commande de dérivation
US11002333B2 (en) 2016-05-23 2021-05-11 Thyssenkrupp Bilstein Gmbh Frequency-selective vibration damper for motor vehicles with a bypass control valve
WO2017220252A1 (fr) * 2016-06-20 2017-12-28 Zf Friedrichshafen Ag Ensemble soupape de fond sélectif en fréquence
WO2018046195A1 (fr) * 2016-09-08 2018-03-15 Zf Friedrichshafen Ag Ensemble soupape d'amortissement dépendant de la fréquence et amortisseur de vibrations
CN109690123A (zh) * 2016-09-08 2019-04-26 Zf腓特烈斯哈芬股份公司 与频率相关的减振阀组件以及减振器
EP3933227A4 (fr) * 2020-04-26 2022-05-11 Ningbo Kasico Shock Absorber Manufacture Co., Ltd. Amortisseur hydraulique à force autovariable

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