WO2018202386A1 - Clapet d'amortissement pour amortisseur de vibrations - Google Patents

Clapet d'amortissement pour amortisseur de vibrations Download PDF

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Publication number
WO2018202386A1
WO2018202386A1 PCT/EP2018/059085 EP2018059085W WO2018202386A1 WO 2018202386 A1 WO2018202386 A1 WO 2018202386A1 EP 2018059085 W EP2018059085 W EP 2018059085W WO 2018202386 A1 WO2018202386 A1 WO 2018202386A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve seat
seat surface
valve
clamping surface
damping
Prior art date
Application number
PCT/EP2018/059085
Other languages
German (de)
English (en)
Inventor
Steffen Heyn
Michael Hegmann
Peter Wirth
Gerald Fenn
Wilhelm-Heinrich Broocks
Anton Krawczyk
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 WO2018202386A1 publication Critical patent/WO2018202386A1/fr

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
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
    • F16F9/3485—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by features of supporting elements intended to guide or limit the movement of the annular discs

Definitions

  • the invention relates to a damping valve for a vibration damper according to the preamble of patent claim 1.
  • a fundamental peculiarity of a damping valve with a soft damping force characteristic is the tendency to bumps that are audible especially in modern vehicles inside the vehicle.
  • a damping valve which has a central clamping surface for at least one valve disc and at least one bearing surface for this valve disc. Due to the level position of the bearing surface to the clamping surface, the opening and thus the noise behavior of the damping valve can be influenced.
  • the object of the present invention is to provide a damping valve that is as free as possible from Polter binen even with a soft damping force characteristic.
  • the height profile has, starting from the clamping surface at least on a peripheral region of the clamping surface a negative slope to the valve seat surface.
  • valve disc When the valve disc is pressed onto the clamping surface in the mounted state of the damping valve, for example in the context of a tensioning chain of a piston rod pin or a valve rivet in the case of a bottom valve, then the damping valve body is slightly axially compressed in the region of the clamping surface. The compression is on the order of a few ⁇ meters.
  • the valve disc is located due to the residual stress, by a valve disc package or a valve spring also on the valve seat surface. Due to the height profile, the valve disc rolls on the valve seat surface. The roll-off function is generated by the negative slope. This prevents that the valve disc is hollow, ie a minimal gap between the valve disc and the valve seat surface occurs.
  • the positive effect of a targeted Abhubiolo the valve disc of the valve seat surface occurs because the bias of the valve disc is defined over the circumference different. In the area of the lowest preload, the valve disc first lifts off the valve seat surface.
  • the clamping surface may have a negative slope in the direction of the valve seat surface.
  • the valve seat surface may define an at least partially extending groove radially, so that a first valve seat surface is radially closer to the clamping surface than a second valve seat, wherein between the first valve seat surface and the second valve seat surface there is a difference in height, of a negative slope will be described starting from the first valve seat surface.
  • This design is used when one wants to achieve a particularly large pressurized surface on the valve disc, which is greater than an exit area of a passage within the Dämpfventil stressess. Due to the radial distance of the two valve seat surfaces could result in a hollow location within the valve seat surfaces, which in turn is prevented by the negative slope.
  • the first valve seat surface has a greater negative slope than the clamping surface in order to achieve a curved valve disk plane.
  • the second valve seat surface has a greater negative slope than the first valve seat surface
  • a bridging plane between the clamping surface and the first valve seat surface has a greater negative slope than the clamping surface.
  • valve seat surface in relation to the clamping surface is simply made with a slight height excess and then partially reworked, z. B. ground. Then inevitably sets a positive increase, which causes the valve disc in an angular range has a higher bias voltage than in an adjacent angular range. Due to the different bias sets in the angular range with the lower bias the Abhubiolo the valve disc of the valve seat surface.
  • Fig. 1 sectional view through a damping valve
  • FIG. 2 shows a top view of the damping valve body according to FIG. 1.
  • FIG. 3 is a sectional view of the Dämpfventil stresses of FIG .. 1
  • FIG. 4 shows a further plan view of the damping valve body according to FIG. 1
  • FIG. 1 shows an example of a damping valve 1 for a vibration damper of any type.
  • the invention could also be embodied on a bottom valve or an adjustable damping valve.
  • the damping valve 1 is designed on a piston rod 3, of which only one piston rod pin 5 is shown.
  • a damping valve body 7 of the damping valve 1 has two separate groups of passage channels 9; 1 1, which extend substantially parallel to the central axis of the damping valve 1.
  • the central axis of the damping valve 1 is congruent with the longitudinal axis of the piston rod 3 and the piston rod pin 5.
  • the two groups of passage channels 9; 1 1 are flowed through in the opposite direction of a damping medium during operation of the damping valve.
  • the damping medium passes through inlet openings 13; 15 in the passageways 9; 1 1, the outlet openings 17; 19 of at least one valve disc 21; 23 are covered. 1, a valve disc arrangement is shown by way of example. Many variations are conceivable.
  • the complete damping valve 1 is fixed to the piston rod 3.
  • the damper valve body has a central opening 27 for receiving the piston rod pin 5.
  • An outer edge 33 of the clamping surface 31 z delimits a circumferential groove 35, which is closed radially on the outside by a closed meander-shaped valve seat surface 37 which is formed by a raised web 39 (FIG. 3).
  • five passage channels 9a - 9c are arranged, exit the outlet openings 17 in the groove 35.
  • the passage channels 9a - 9c are all located on a common pitch circle diameter and have a rectangular basic shape.
  • Each outlet opening 17 of this group of passage channels 9a - 9 c has a plurality of funnel-shaped transitions 41 a - 41 c, which form the flow surface between the passage channels 9 a - 9 c and the channel bottom. At least one of the funnel-shaped transitions 41 a of each outlet opening is directed radially outward.
  • the distance A1 of the valve seat surface 37 to the central axis in the region of an outlet opening 9a is different from the distance A2 of a valve seat surface or a valve seat surface region of a second outlet opening 9b executed to the central axis. It applies A1>A2> A3.
  • the funnel angle of the transitions 41 varies slightly, since the passage channels 9a, 9b, 9c are arranged on a pitch circle.
  • the passage channel 9 has at least one funnel-shaped transition 41 b; 41 c in the circumferential direction of the trough.
  • the damping valve body 7 has five passageways 9a; 9b; 9c and thus has an odd number of passage channels.
  • the distances A2; A2; A3 of the valve seat surface 37 with respect to an axis of symmetry 43 between the passage channel 9a and the center axis of the Dämpfventil stressess 7 are executed in mirror image.
  • the passage channels 1 1 are arranged for the other flow direction. These passageways 1 1 are designed as a slot, as shown in FIG. 2 can be seen, showing the inlet opening 15 of the passage channels 1 1.
  • FIGS. 4 and 6 it is clear that the outlet openings 19 of the passage channels have a greater width radially outward than radially inward and thus have a cloverleaf-like shape.
  • the outlet openings 19 are framed by raised valve seat surfaces 45 which are mounted on a second cover page 47, in the further pressure side, are connected to an annular clamping surface 31 d.
  • the valve seat surfaces 45 have in the region of the inlet openings 13 for the passage channels 9 of the opposite flow direction to a substantially parallel sealing edge. Furthermore, radially extending portions of the valve seat surface 45 define an inflow funnel 49 for the passageways 9.
  • FIG. 7 describes a cross section through the damping valve 1 using the example of FIGS. 4 and 6 with the inner clamping surface 31 and the radially positioned valve seat surface 45. Between these surfaces run the passage channels 9 which are enclosed by the valve seat surface 45.
  • a horizontal reference plane 51 is located, the z. B. can be formed from the top side 47 of the Dämpfventil stressess 7, from which the clamping surface 31 and the valve seat surface 45 extend axially.
  • the clamping surface 31 and the valve seat surface 45 thus form a height profile on the damping valve body 7.
  • the height profile starting from the clamping surface 31 at least on a peripheral region of the clamping surface 31 on a negative to the valve seat surface slope with the angle ⁇ . If one were to place the at least one valve disc 23 on the clamping surface 31 and not distort, then at least between the said peripheral region and the underside of the valve disc 23, a small air gap 53 before. The air gap would be very small in the order of between 0.001 and 0.005 mm.
  • the clamping surface 31 extends at right angles to the main axis, ie the central axis of the piston rod 3.
  • the clamping surface 31 in the direction of the valve seat surface 45 has a negative slope.
  • valve seat surface 45 is over-inflated compared to the right-hand half cut, ie, there is a positive gradient Consequently, there is then in this area a significant greater bias of the valve disc 23, since the valve disc 23 is more shielded during assembly of the piston nut 25 on the deeper clamping surface 31.
  • the valve disk 23 will therefore lift off first from the valve seat surface 45 in the right half and then only in the region of the left half section. Simplified here are all valve seat 45 executed in a plane plan, which is inclined to the reference plane 51.
  • Figure 8 represents the simplest variant, as z. B. in Figures 2 and 5 can be applied.
  • the valve seat surface 37 radially delimits the at least sectionally extending groove 35 so that a first valve seat surface 37i extends radially closer to the clamping surface 31 than a second valve seat surface 37a, wherein between the first valve seat surface 37i and the second valve seat surface 37a there is a height difference, that of a negative slope starting from the first valve seat surface 37i will be described.
  • the negative slope, starting from the clamping surface 31 is constant over the first valve seat surface 37i to the second valve seat surface 37a.
  • This embodiment represents a limit of the invention. Even with this construction, it is ensured that in the valve disc 21 in the mounted state, d. H. under tension there are no air gaps.
  • FIG. 9 shows a modification in which the pitch, starting from the clamping surface 31, is constant radially outward relative to a cutting plane, but can vary over the circumference.
  • the negative slope in the right half section is greater than in the left half section, i. ⁇ 1> ⁇ 2.
  • a larger bias voltage within the valve disc 21 is established than in the right half section.
  • FIG. 10 is intended to illustrate an optimized height profile, in which the first valve seat surface 37 i has a greater negative gradient than the clamping surface 31.
  • the second valve seat surface 37a in turn has a greater negative slope than the first valve seat surface 37i.
  • a bridging plane 55 between the clamping surface 31 and the first valve seat surface 37 i has a greater negative slope than the clamping surface 31.
  • the first valve seat surface 37i has a larger negative
  • the tangents at the said planes form a curve corresponding to a higher-order mathematical function.
  • the height profile over the entire circumference of the Dämpfventil stressess is constant.
  • the envelope, represented by the valve disk 21 for the height profile remains constant.
  • the envelope or the height profile is tilted, so that in turn the negative pitch between the clamping surface 31 and the valve seat surfaces 37i, 37a is designed differently over the circumference of the clamping surface. But also the slope within the clamping surface 31 is variable over the circumference.
  • FIG. 12 shows an alternative solution in which, starting from the clamping surface 31 to the valve seat surface 45, a positive gradient ⁇ 1; ⁇ 2 is present, which is dimensioned differently across the circumference.
  • the plane of the valve seat surface 45 and the plane of the clamping surface 31 are inclined to each other.
  • the valve seat surface 45 has a negative slope ⁇ 3 radially outward.
  • the valve disc 23 has between the clamping surface 31 and the valve seat surface radially outward a positive slope ⁇ 1, ie the valve seat surface 45 is dimensioned raised to the clamping surface 31.
  • the height profile, starting from the clamping surface 31, also extends with a positive pitch ⁇ 2 which is greater than in the right half section, ie the left area of the valve seat surface 45 is raised in relation to the clamping surface 31 and the valve seat surface 45 in the right half section.

Landscapes

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

Abstract

L'invention concerne un clapet d'amortissement pour un amortisseur de vibrations. Le clapet comporte un corps pourvu d'au moins une surface de serrage et d'au moins une surface de siège de clapet pour au moins un disque de clapet reposant sur ces surfaces. La surface de serrage et la surface de siège de soupape, en raison de leur position en hauteur, forment un profil de hauteur par rapport à un plan de référence du corps de clapet d'amortissement, le profil de hauteur présentant à partir de la surface de serrage, au moins sur une zone périphérique de la surface de serrage, une pente négative par rapport à la surface de siège de soupape.
PCT/EP2018/059085 2017-05-05 2018-04-10 Clapet d'amortissement pour amortisseur de vibrations WO2018202386A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017207605.4 2017-05-05
DE102017207605.4A DE102017207605A1 (de) 2017-05-05 2017-05-05 Dämpfventil für einen Schwingungsdämpfer

Publications (1)

Publication Number Publication Date
WO2018202386A1 true WO2018202386A1 (fr) 2018-11-08

Family

ID=62025802

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2018/059085 WO2018202386A1 (fr) 2017-05-05 2018-04-10 Clapet d'amortissement pour amortisseur de vibrations

Country Status (2)

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DE (1) DE102017207605A1 (fr)
WO (1) WO2018202386A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018220122A1 (de) * 2018-11-23 2020-05-28 Zf Friedrichshafen Ag Dämpferkolben für einen Kraftfahrzeugschwingungsdämpfer
EP4127506A1 (fr) * 2020-03-27 2023-02-08 DRiV Automotive Inc. Ensemble amortisseur
DE102020209804A1 (de) 2020-08-04 2022-02-10 Zf Friedrichshafen Ag Dämpfventil für einen Schwingungsdämpfer

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3445684A1 (de) 1984-12-14 1986-06-19 Fichtel & Sachs Ag, 8720 Schweinfurt Schwingungsdaempfer fuer fahrzeuge
EP0336692A2 (fr) * 1988-04-04 1989-10-11 Atsugi Unisia Corporation Amortisseur de chocs
EP0717191A2 (fr) * 1994-11-15 1996-06-19 Sanden Corporation Dispositif de clapet de refoulement d'un appareil à déplacement de fluide
KR19980054296U (ko) * 1996-12-31 1998-10-07 오상수 쇽업소버의 피스톤장치
DE19735249C1 (de) 1997-08-14 1999-03-04 Mannesmann Sachs Ag Verfahren zur Herstellung eines Kolbens
US20130048451A1 (en) * 2011-08-31 2013-02-28 Mikio Yamashita Shock absorber
DE102012020747A1 (de) * 2012-03-27 2013-10-02 Showa Corporation Dämpfungskraftgenerator für hydraulischen Stossdämpfer
US20140150897A1 (en) * 2012-11-30 2014-06-05 Hitachi Automotive Systems, Ltd. Shock absorber

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2727407C2 (de) * 1977-06-18 1982-05-27 Boge Gmbh, 5208 Eitorf Ventileinrichtung, insbesondere für Teleskopschwingungsdämpfer von Kraftfahrzeugen
DE19615587C2 (de) * 1996-04-19 1999-04-01 Mannesmann Sachs Ag Schwingungsdämpfer mit richtungsabhängigem Voröffnungsquerschnitt
JP6027451B2 (ja) * 2013-01-25 2016-11-16 Ｋｙｂ株式会社 緩衝装置
DE102014223086A1 (de) * 2014-11-12 2016-05-12 Zf Friedrichshafen Ag Dämpfventil für einen Schwingungsdämpfer
JP6487804B2 (ja) * 2015-08-07 2019-03-20 Ｋｙｂ株式会社 緩衝器のバルブ構造
DE102016210789B4 (de) * 2016-06-16 2020-08-06 Zf Friedrichshafen Ag Dämpfventil für einen Schwingungsdämpfer

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3445684A1 (de) 1984-12-14 1986-06-19 Fichtel & Sachs Ag, 8720 Schweinfurt Schwingungsdaempfer fuer fahrzeuge
EP0336692A2 (fr) * 1988-04-04 1989-10-11 Atsugi Unisia Corporation Amortisseur de chocs
EP0717191A2 (fr) * 1994-11-15 1996-06-19 Sanden Corporation Dispositif de clapet de refoulement d'un appareil à déplacement de fluide
KR19980054296U (ko) * 1996-12-31 1998-10-07 오상수 쇽업소버의 피스톤장치
DE19735249C1 (de) 1997-08-14 1999-03-04 Mannesmann Sachs Ag Verfahren zur Herstellung eines Kolbens
US20130048451A1 (en) * 2011-08-31 2013-02-28 Mikio Yamashita Shock absorber
DE102012020747A1 (de) * 2012-03-27 2013-10-02 Showa Corporation Dämpfungskraftgenerator für hydraulischen Stossdämpfer
US20140150897A1 (en) * 2012-11-30 2014-06-05 Hitachi Automotive Systems, Ltd. Shock absorber

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