WO2004097250A1 - Systemes d'amortisseurs pour automobiles - Google Patents

Systemes d'amortisseurs pour automobiles Download PDF

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Publication number
WO2004097250A1
WO2004097250A1 PCT/EP2004/004037 EP2004004037W WO2004097250A1 WO 2004097250 A1 WO2004097250 A1 WO 2004097250A1 EP 2004004037 W EP2004004037 W EP 2004004037W WO 2004097250 A1 WO2004097250 A1 WO 2004097250A1
Authority
WO
WIPO (PCT)
Prior art keywords
spring
diameter
shock absorber
height
spring element
Prior art date
Application number
PCT/EP2004/004037
Other languages
German (de)
English (en)
Inventor
Klaus Sobolewski
Jan Wucherpfennig
Frank Thye-Moormann
Original Assignee
Basf Aktiengesellschaft
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 Basf Aktiengesellschaft filed Critical Basf Aktiengesellschaft
Priority to DE112004000404T priority Critical patent/DE112004000404D2/de
Publication of WO2004097250A1 publication Critical patent/WO2004097250A1/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
    • F16F1/00—Springs
    • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
    • F16F1/373—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers characterised by having a particular shape
    • F16F1/3732—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers characterised by having a particular shape having an annular or the like shape, e.g. grommet-type resilient mountings
    • 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
    • F16F9/58—Stroke limiting stops, e.g. arranged on the piston rod outside the cylinder
    • F16F9/585—Stroke limiting stops, e.g. arranged on the piston rod outside the cylinder within the cylinder, in contact with working fluid

Definitions

  • the invention relates to automobile shock absorber systems containing piston rod (i) and on the piston rod (i) at least one additional spring (ii) which is located between a damper cap (v) located on the piston rod (i) and a base (vi), preferably a support pot, in particular as an additional spring (ii) of one of the spring elements according to the invention, which are described below.
  • the invention relates to spring elements based on a hollow cylindrical
  • Damping element (x) preferably on the basis of rubber or cellular polyisocyanate polyaddition products, particularly preferably on the basis of cellular polyurethane elastomers, which may optionally contain polyurea structures, particularly preferably on the basis of cellular polyurethane elastomers, preferably with a density according to DIN 53420 from 200 to 1100, preferably 300 to 800 kg / m 3 , preferably with a tensile strength according to DIN 53571 of> 2, preferably 2 to 8 N / mm 2 , an elongation according to DIN 53571 of> 300, preferably 300 to 700% and one Tear resistance according to DIN 53515 of ⁇ 8, preferably 8 to 25 N / mm, with a height (ix) between 70 mm and 80 mm, preferably 72 mm to 76 mm, particularly preferably 74 mm, an outer diameter (iii) between 60 mm and 70 mm, preferably 62 mm to 68 mm, particularly preferably 63
  • Suspension elements made from polyurethane elastomers are used in automobiles, for example, within the chassis and are generally known. They are used in particular in motor vehicles as vibration-damping spring elements.
  • the spring elements take on an end stop function and influence the force-displacement identification of the wheel by forming or reinforcing a progressive characteristic of the vehicle suspension.
  • the pitching effects of the vehicle can be reduced and the roll support is strengthened.
  • the starting stiffness is optimized in particular by the geometric design, this has a significant influence on the suspension comfort of the vehicle.
  • the targeted design of the geometry results in almost constant component properties over the service life shadow. This function increases driving comfort and ensures maximum driving safety.
  • the additional springs are usually positioned on the piston rod of a shock absorber and mounted between the head bearing element, for example with an attached support tube, and the damper cap.
  • the additional spring can be fixed by undersizing an inner construction section on the piston rod or preferably by oversizing the largest outside diameter. It is often problematic with regard to this installation that the geometry of the mounting pot and the damper cap can lead to high loads on the additional spring in the automobile chassis, in which destruction of the additional spring can possibly not be ruled out.
  • the object of the present invention was therefore to develop an automobile shock absorber system in which even large forces can be permanently absorbed under difficult installation conditions.
  • the ratio of the diameter (iii) of the additional spring (ii) at the base (vi) to the diameter (vii) of the damper cap (v) was at least 1.2: 1, preferably 1.3: 1 to 15: 1, particularly preferably 1.4: 1 to 4: 1.
  • the outer diameter (iii) preferably represents the outer diameter which the additional spring (ii) has at the point where the additional spring touches the edge (viii) of the support pot.
  • the outer diameter (iii) is particularly preferably the maximum outer diameter of the additional spring (ii).
  • FIG. 1 An exemplary, preferred automotive shock absorber system according to the invention is shown in detail in FIG. 1.
  • the advantages of the automobile shock absorber system according to the invention are that, due to the novel geometry, the axial forces can be transmitted very well, but radial forces, which can lead to the destruction of the additional springs, are minimized.
  • the piston rod can be generally known piston rods, for example of a gas pressure shock absorber.
  • the damper cap (v) is usually located below the additional spring as the end of the damper tube and usually takes on the task of transmitting the wheel forces to the additional spring via the damper tube.
  • the base (vi) can be, for example, a support pot that prevents the integrated additional spring from stretching transversely.
  • the support pot can take on the task of supporting parts of the air spring, here the roll-off bellows, against excessive kinking during assembly.
  • the support pot is preferably fixed to the head bearing, which dampens the vibrations of the piston rod.
  • the base can be made of generally known materials, for example aluminum, steel and / or iron.
  • the base (vi) is particularly preferably a support pot, between the edge (viii) of which the additional spring (ii) is pressed.
  • the edge (viii) preferably encloses the additional spring (ii) almost completely, ie almost completely in its axial extension on the piston rod, preferably more than 90% of the height of the additional spring (ii), particularly preferably 95% to 100% of the additional spring (ii) towards the piston rod.
  • the additional spring is preferably in contact with the inside of the edge (viii) through an edge (xiv), which preferably has a height (xix) between 5 mm and 30 mm, particularly preferably 6 mm and 20 mm, in particular 8 to 15 mm. of the support pot.
  • the edge (xiv) preferably has an outer diameter which is at least 1 mm, particularly preferably 2 to 3 mm larger than the inner diameter of the edge (viii), ie the additional spring is radially pressed into the support pot.
  • This geometry according to the invention has the effect that the transverse expansion of the start-up area is blocked under load and thus a higher block dimension is achieved and damage to the spring material by swelling out from under the damper cap is prevented.
  • the additional spring (ii) can be based, for example, on rubber or cellular polyisocyanate polyadducts, particularly preferably on cellular polyurethane elastomers, which may optionally contain polyurea structures, particularly preferably on cellular polyurethane elastomers, preferably with a density according to DIN 53 420 of 200 to 1100, preferably 300 to 800 kg / m 3 , preferably with a tensile strength according to DIN 53571 of> 2, preferably 2 to 8 N / mm 2 , an elongation according to DIN 53571 of ⁇ 300, preferably 300 to 700% and a tear resistance according to DIN 53515 of> 8, preferably 8 to 25 N / mm.
  • rubber or cellular polyisocyanate polyadducts particularly preferably on cellular polyurethane elastomers, which may optionally contain polyurea structures, particularly preferably on cellular polyurethane elastomers, preferably with a density according to DIN 53 420 of
  • the hollow cylindrical additional spring (ii) is based on cellular polyisocyanate polyaddition products, particularly preferably on cellular polyurethane elastomers, in particular based on cellular polyurethane elastomers with a density according to DIN 53 420 of 200 to 1100 kg / m 3 , with a tensile strength according to DIN 53571 from
  • the spring element preferably comprises a hollow, preferably ring-shaped support disk (xv) which surrounds the damping element (x) in a depression (xvi) running around the outer surface of the damping element (x).
  • the circumferential depression (xvi) is preferably at a height (xviii) between 40 mm and 50 mm, particularly preferably 42 mm to 48 mm, in particular 45 mm.
  • the outer diameter (xxii) of the damping element (x) in the circumferential recess (xvi) is preferably 26 mm to 39 mm, particularly preferably 31 mm to 36 mm, in particular 33.5 mm.
  • the support disk (xv) which preferably has a height (xx) between 15 mm and 25 mm, particularly preferably 17 mm to 21 mm, in particular 19 mm and an inner diameter (xxi) between 25 mm and 40 mm, particularly preferably 30 mm up to 35 mm, in particular 32 mm, can be based on generally known materials, for example hard plastics, for example polyamide, polyoxymethylene, thermoplastic polyurethane, or metals, for example aluminum, steel, copper, iron, which can optionally be coated with an elastic material ,
  • the diameter (xxii) of the damping element (x) in the depression (xvi) is particularly preferably 1 mm to 2 mm larger than the inner diameter (xxi) of the support disk (xv).
  • the inner diameter (xvii) of the support disk (xv) is thus preferably smaller than the diameter of the damping element (x) in the recess (xvi) without the support disk (xv), ie the damping element (x), ie the additional spring (ii ) or the spring element is pressed through the support disc (xv).
  • the surface of the support disk (xv), in particular the surface facing the damping element (x), is preferably rough.
  • the angle ⁇ of the support disk (xv) is preferably between 0 ° and 45 °, preferably between 0 ° and 10 °.
  • the support disk (xv) preferably has an edge (xxv) which comprises the damping element (x) outside the circumferential recess (xvi).
  • FIGS. 2 and 3 An exemplary, preferred spring element according to the invention is shown in detail in FIGS. 2 and 3, the support disk (xv) being additionally shown in FIG.
  • An exemplary support disc (xv) is shown in detail in FIG. 4.
  • the length dimensions are given in [mm].
  • the spring elements according to the invention i.e. the damping elements (x) or the additional springs (ii) according to the invention are preferably based on elastomers based on polyisocyanate polyaddition products, for example polyurethanes and / or polyureas, for example polyurethane elastomers, which may optionally contain urea structures.
  • the elastomers are preferably microcellular elastomers based on polyisocyanate polyadducts, preferably with cells with a diameter of 0.01 mm to 0.5 mm, particularly preferably 0.01 to 0.15 mm.
  • the elastomers particularly preferably have the physical properties shown at the beginning.
  • Elastomers based on polyisocyanate polyaddition products and their preparation are generally known and can be described in many different ways, for example in EP-A 62 835, EP-A 36 994, EP-A 250 969, DE-A 195 48770 and DE-A 195 48,771th
  • the preparation is usually carried out by reacting isocyanates with compounds which are reactive toward isocyanates.
  • the elastomers based on cellular polyisocyanate polyadducts are usually produced in a form in which the reactive starting components are reacted with one another.
  • generally customary shapes are considered as shapes, for example metal shapes which, because of their shape, ensure the three-dimensional shape of the spring element according to the invention.
  • the polyisocyanate polyaddition products can be prepared by generally known processes, for example by using the following starting materials in a one- or two-stage process:
  • auxiliaries and / or additives for example polysiloxanes and / or fatty acid sulfonates.
  • the surface temperature of the mold inner wall is usually 40 to 95 ° C, preferably 50 to 90 ° C.
  • the production of the molded parts is preferably carried out at an NCO / OH ratio of 0.85 to 1.20, the heated starting components being mixed and placed in a heated, preferably tight-closing mold in an amount corresponding to the desired molded part density.
  • the molded parts are hardened after 5 to 60 minutes and can therefore be removed from the mold.
  • the amount of the reaction mixture introduced into the mold is usually such that the moldings obtained have the density already shown.
  • the starting components are usually introduced into the mold at a temperature of 15 to 120 ° C., preferably 30 to 110 ° C.
  • the degrees of compaction for the production of the shaped bodies are between 1, 1 and 8, preferably between 2 and 6.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Springs (AREA)

Abstract

L'invention concerne un système d'amortisseur pour automobile comprenant une tige de piston (i), sur laquelle est monté un ressort supplémentaire (ii), qui est disposé entre un capuchon d'amortisseur (v) placé sur la tige de piston (i) et une base (vi), le rapport entre le diamètre (iii) du ressort supplémentaire (ii) à la base (vi) et le diamètre (vii) du capuchon d'amortisseur (v) étant d'au moins 1,2: 1.
PCT/EP2004/004037 2003-04-29 2004-04-16 Systemes d'amortisseurs pour automobiles WO2004097250A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112004000404T DE112004000404D2 (de) 2003-04-29 2004-04-16 Automobilstoßdämpfersysteme

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2003119463 DE10319463A1 (de) 2003-04-29 2003-04-29 Automobilstoßdämpfersysteme
DE10319463.0 2003-04-29

Publications (1)

Publication Number Publication Date
WO2004097250A1 true WO2004097250A1 (fr) 2004-11-11

Family

ID=33305065

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2004/004037 WO2004097250A1 (fr) 2003-04-29 2004-04-16 Systemes d'amortisseurs pour automobiles

Country Status (2)

Country Link
DE (2) DE10319463A1 (fr)
WO (1) WO2004097250A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017202620A1 (fr) * 2016-05-27 2017-11-30 Basf Se Élément ressort pour un amortisseur de véhicule, amortisseur de véhicule et véhicule équipé de celui-ci
US10031422B2 (en) 2012-10-26 2018-07-24 Asml Netherlands B.V. Lithographic apparatus

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009022063A1 (de) * 2009-05-20 2010-11-25 Zf Friedrichshafen Ag Schwingungsdämpfer mit einer Elastomeranschlagfeder

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03117736A (ja) * 1989-09-28 1991-05-20 Kinugawa Rubber Ind Co Ltd 自動車用バウンドバンパ
JPH06137357A (ja) * 1992-10-30 1994-05-17 Bridgestone Corp バンパーバウンドとダストカバーとの組立構造
JPH11210806A (ja) * 1998-01-23 1999-08-03 Nippon Mektron Ltd バンプストッパ
DE20108487U1 (de) * 2001-05-18 2001-09-06 Basf Ag Federelement
JP2001271864A (ja) * 2000-03-24 2001-10-05 Tokai Rubber Ind Ltd バウンドストッパ
DE20109932U1 (de) * 2001-06-19 2001-10-18 Basf Ag Federelement
DE20204328U1 (de) * 2002-03-19 2002-06-06 Basf Ag Zusatzfeder
DE20213259U1 (de) * 2002-08-26 2002-11-21 Basf Ag Federkonstruktion
DE10124924A1 (de) * 2001-05-21 2002-11-28 Basf Ag Federelement

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03117736A (ja) * 1989-09-28 1991-05-20 Kinugawa Rubber Ind Co Ltd 自動車用バウンドバンパ
JPH06137357A (ja) * 1992-10-30 1994-05-17 Bridgestone Corp バンパーバウンドとダストカバーとの組立構造
JPH11210806A (ja) * 1998-01-23 1999-08-03 Nippon Mektron Ltd バンプストッパ
JP2001271864A (ja) * 2000-03-24 2001-10-05 Tokai Rubber Ind Ltd バウンドストッパ
DE20108487U1 (de) * 2001-05-18 2001-09-06 Basf Ag Federelement
DE10124924A1 (de) * 2001-05-21 2002-11-28 Basf Ag Federelement
DE20109932U1 (de) * 2001-06-19 2001-10-18 Basf Ag Federelement
DE20204328U1 (de) * 2002-03-19 2002-06-06 Basf Ag Zusatzfeder
DE20213259U1 (de) * 2002-08-26 2002-11-21 Basf Ag Federkonstruktion

Non-Patent Citations (4)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 015, no. 314 (M - 1145) 12 August 1991 (1991-08-12) *
PATENT ABSTRACTS OF JAPAN vol. 018, no. 446 (M - 1659) 19 August 1994 (1994-08-19) *
PATENT ABSTRACTS OF JAPAN vol. 1999, no. 13 30 November 1999 (1999-11-30) *
PATENT ABSTRACTS OF JAPAN vol. 2002, no. 02 2 April 2002 (2002-04-02) *

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10031422B2 (en) 2012-10-26 2018-07-24 Asml Netherlands B.V. Lithographic apparatus
WO2017202620A1 (fr) * 2016-05-27 2017-11-30 Basf Se Élément ressort pour un amortisseur de véhicule, amortisseur de véhicule et véhicule équipé de celui-ci
CN109154347A (zh) * 2016-05-27 2019-01-04 巴斯夫欧洲公司 用于车辆减震器的弹簧元件、车辆减震器以及具有车辆减震器的车辆
US10920843B2 (en) 2016-05-27 2021-02-16 Basf Se Spring element for a vehicle shock absorber, and vehicle shock absorber and vehicle having same
CN109154347B (zh) * 2016-05-27 2021-10-22 巴斯夫欧洲公司 用于车辆减震器的弹簧元件、车辆减震器以及具有车辆减震器的车辆

Also Published As

Publication number Publication date
DE112004000404D2 (de) 2006-02-23
DE10319463A1 (de) 2004-11-18

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