WO2000014428A1 - Amortisseur de chocs et de vibrations, notamment pour suspendre des circuits d'echappement d'automobiles - Google Patents

Amortisseur de chocs et de vibrations, notamment pour suspendre des circuits d'echappement d'automobiles Download PDF

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Publication number
WO2000014428A1
WO2000014428A1 PCT/EP1999/005655 EP9905655W WO0014428A1 WO 2000014428 A1 WO2000014428 A1 WO 2000014428A1 EP 9905655 W EP9905655 W EP 9905655W WO 0014428 A1 WO0014428 A1 WO 0014428A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
shock
housing
vibration damper
damper according
Prior art date
Application number
PCT/EP1999/005655
Other languages
German (de)
English (en)
Inventor
Harald Jahnel
Reino Eskelinen
Original Assignee
Feodor Burgmann Dichtungswerke Gmbh & Co.
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 Feodor Burgmann Dichtungswerke Gmbh & Co. filed Critical Feodor Burgmann Dichtungswerke Gmbh & Co.
Publication of WO2000014428A1 publication Critical patent/WO2000014428A1/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
    • F16F9/3207—Constructional features
    • 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
    • F16F6/00—Magnetic springs; Fluid magnetic springs, i.e. magnetic spring combined with a fluid
    • 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
    • F16F2230/00—Purpose; Design features
    • F16F2230/0052—Physically guiding or influencing

Definitions

  • the invention relates to a shock and vibration damper, as can be used in particular for the suspension of exhaust systems of motor vehicles.
  • DE 33 46 609 A describes a suspension element for the exhaust system of a vehicle, which has an articulated connection with the exhaust system and comprises interlocking elastic rings which enclose a transmission body between them, which is designed as a low-mass elastic damping member.
  • the object of the invention is to propose such a suspension element in the form of a shock and vibration damper, the functioning of which hardly changes over a very long period of use and at the same time also independently of the different temperatures occurring and the influence of the radiant heat is.
  • a shock and vibration damper with a housing which forms an interior in which a piston is slidably received along a displacement axis, which is attached to a piston rod led out of the housing and in the direction of its displacement axis on its opposite side of the piston rod
  • a shock and vibration damper with a housing which forms an interior in which a piston is slidably received along a displacement axis, which is attached to a piston rod led out of the housing and in the direction of its displacement axis on its opposite side of the piston rod
  • This shock and vibration damper represents a suspension element in which the piston is held in a central position in the sense of a contactless magnetic levitation, the magnetic forces acting on the piston and determining its position over a virtually unlimited period of time, ensuring constant functioning
  • suspension element which moreover is virtually unaffected by the different temperatures occurring during operation of such suspensions and is therefore always unchanged.
  • the suspension element according to the invention has an astonishing and hitherto unknown constancy in its mode of operation, which, as far as can be seen, is not even approximated by any previously known suspension element.
  • the suspension element according to the invention has a remarkably simple structure, is inexpensive and can be produced quickly and easily, requires little space and can be installed quickly on site.
  • end faces of the piston consist of permanent magnets. This makes it possible to create a virtually maintenance-free suspension element with predetermined functional characteristics, which after its installation maintains the desired function without any problems over a very long time.
  • the magnets of the magnet arrangements are electromagnets which are connected in a suitable manner to an electronic control device.
  • the effort for such a shock and vibration damper according to the invention is greater than in the case of the use of permanent magnets, but gives the possibility that one via the electronic control
  • each housing end wall and the corresponding end face of the piston can consist of a single magnet over their entire surface, in which case, very particularly preferably, the piston itself is made from a single magnet.
  • each magnet arrangement consists of a plurality of individual magnets, which are arranged either concentrically to the displacement axis or evenly distributed around the displacement axis, in which case the individual magnets are preferably of completely identical design.
  • a particularly simple embodiment of the shock and vibration damper according to the invention consists in that the interior of the housing is cylindrical, in which case the entire housing preferably forms a cylindrical body in which the
  • Piston is slidably received. This configuration is not only particularly simple to manufacture, it also offers the possibility of a particularly compact and small construction of the simplest form.
  • Control devices are connected electromagnets, the electronic control device is preferably designed so that it can be used to change the frequency and / or strength of the current for acting on the electromagnets, with a different setting of frequency and / or strength of the current for the individual magnet arrangements preferably also being carried out can be.
  • Another preferred embodiment of the invention also consists in that the chamber formed between each end face of the piston and the associated housing end wall is provided with a pressurized gas filling, which, especially when using permanent magnets for the magnet arrangements, further influences the
  • Damping behavior can be achieved with a deflection of the piston.
  • piston is provided with axial through bores, which run between its two end faces, and the chambers between the two end faces of the piston and the facing one
  • Housing end surface and these through holes filled with a suitable liquid are. This also allows an additional influence on the damping during the deflection of the piston, in particular when using permanent magnets.
  • a device that prevents (even small) rotation of the piston about its displacement axis. It is thereby achieved that the opposing magnetic field arrangements are always kept in an unchanged angular assignment to one another, which is advantageous with regard to the constant functional characteristics of the shock and vibration damper according to the invention.
  • the device which prevents the piston from rotating about its displacement axis is designed in such a way that it has a bolt which runs through the interior of the housing parallel to the displacement direction of the piston and which passes through an associated axial through-opening of the piston to form a
  • the shock and vibration damper according to the invention with the piston rod is e.g. at a suspension point on the exhaust system and with its housing e.g. at the
  • the design of the shock and vibration damper according to the invention i.e. the design of the repulsive magnetic forces acting between the piston on the one hand and the two housing end walls on the other hand takes place via a suitable choice of the magnetic field strength, the effective area of the magnets of each magnet arrangement and the spacing of the repelling magnets in the different arrangements.
  • B is the magnetic flux density
  • A is the effective area of the magnets of the magnet arrangement in question, which is penetrated perpendicularly by the magnetic flux ⁇
  • ⁇ 0 is the magnetic field constant
  • shock and vibration damper according to the invention is particularly suitable for use in the suspension of exhaust systems on motor vehicles, application in many other technical fields is equally possible in which the use of vibration and shock absorbers is common or useful, e.g. as a suspension element of engines, such as vehicle engines, and / or drums
  • Washing machines or as a shock-absorbing suspension element in milling machines, as a shock absorber in the vehicle industry, as a suspension element for bicycle saddles, etc.
  • FIG. 1 shows a cross section through a shock and vibration damper according to the invention with a cylindrical housing and permanent magnet corresponding to section l-l in Fig. 2.
  • Figure 2 is a section along ll-ll in Fig. 1.
  • Fig. 3 is a sectional view through a piston with a magnet arrangement modified to Fig. 1, and
  • Fig. 4 is a sectional view corresponding to FIG. 1 through a shock and vibration damper according to the invention, in which electromagnets are used.
  • 1 shows a shock and vibration damper, which is provided as a suspension element for the suspension of an exhaust system of a motor vehicle on the vehicle underbody.
  • the shock and vibration damper comprises a cylindrical housing 1, which is provided at its axial ends with an inwardly directed annular collar 2 or 3 and forms an interior 4 in its interior, in which a piston 5 in one of the axial direction of the housing 1 corresponding displacement direction is slidably attached.
  • the housing 1 made of aluminum tube with a wall thickness of 1.5 mm has an outer diameter of 40 mm and one
  • the piston 5 is fastened to a piston rod 6, which is guided through an axial end wall 7 of the housing 1 in the center and at its other end with an eyelet 8
  • the end wall 7 is covered radially in its edge region by the annular collar 3 present there.
  • a further end wall 9 is attached in the same way, which in turn is covered in its radially outer end region by the radially inwardly jumping ring collar 2.
  • This end wall 9 is also fastened in a suitable manner to the side walls of the housing 1 or to the collar 2.
  • each end wall 7 and 9 of the housing 1 is held firmly within the housing in its position between the respectively assigned ring point 2 or 3 and a ring bead 21 rolled in from the outside of the housing 1.
  • the piston 5 is provided both on its side facing the end wall 7 and on the opposite side facing the end wall 9 each with a plurality of individual magnets 12 and 12 'arranged uniformly distributed around the piston center axis in the outer edge region of the piston 5 along its circumference which form a magnet arrangement on each of the two axial end faces of the piston 5.
  • a magnet arrangement consisting of a plurality of magnets 13 and 13' is also attached to the sides of the end walls 7 and 9 facing the piston 5, the size of the individual magnets 13 being the same as the arrangement of the magnets 12 on the facing end face of the piston 5 and the magnets 13 'are of similar size and arrangement to the magnets 12' on the facing end face of the piston 5.
  • all magnets 12, 12 ', 13 and 13' are chosen identical in size and shape to each other and also their arrangement along the respective support surface (end walls 7 and 9 and the two axial end faces of the piston 5) is also chosen to be completely the same, so that the sectional view shown in FIG. 2 and the section II-II from FIG. 1 basically also reflects the basic design of all other magnet arrangements within the housing 1 .
  • the magnet arrangement on the end wall 9 consists of ten individual magnets 13 of the same size and area, which are designed as round magnets with a diameter of 8 mm and a thickness of 4 mm, and are evenly attached in the edge region of the piston 5 are and their centers on a common
  • Pitch circle R with a diameter of 28 mm, the center of which lies with the center the circular area of the piston 5 coincides, that is, lies on the axial longitudinal axis of the piston 5.
  • Magnets are used as magnets, which are known under the trade name Recoma 28 and are each attached to the associated holding surface of the end walls 7 or 9 or the piston 5 by means of a silicone adhesive.
  • the mutually facing magnet arrangements 12 and 13 or 12 'and 13' are designed so that the magnets used face each other with the same poles, so that the magnets 12 and 13 as well as the magnets 12 'and 13' are repelled from each other.
  • piston 5 In the otherwise unloaded state, piston 5 assumes a central position which, in the case of magnets 12, 12 ', 13 and 13' of the same size and the same arrangement, corresponds to the axial geometric central position in the interior 4.
  • the piston rod 6 is at one end on its piston side
  • the piston 5 also has, in the area between the central bore 15 and the position of the magnets 12 and 12 ', a further, smaller bore 17 (see FIG. 2), which serves as a through bore for a guide pin 18 (see FIG. 1), which protrudes axially and parallel to the direction of displacement of the piston 5 and through the two end walls 7 and 9 through the interior 4 of the housing 1, is provided with a threaded section 19 at its end regions and there by means of a nut 20 against the adjacent one
  • FIG. 2 The magnet arrangement shown in FIG. 2 is of course only one example from a large variety of different magnet shapes and magnet arrangements, the number of ten rounds used per magnet arrangement being shown in the exemplary embodiment shown
  • Permanent magnets could easily be replaced by a larger or smaller number of larger or smaller round magnets (or differently shaped magnets).
  • the total size of the area of the magnets used ie the effective area A of the magnets of the magnet arrangement in question
  • FIG. 3 illustrates another embodiment of the piston 5 with a different magnet arrangement.
  • axial through bores are provided in the piston 5 in accordance with the desired size and arrangement of the magnets, into which individual magnets 12 "are inserted.
  • the axial thickness of the piston 5 corresponds exactly to the thickness of the magnets 12" used, see above that the two end faces of the magnets 12 "each lie within one of the two axial end faces of the piston 5.
  • the magnets can be fastened in different ways within the through bores, although it is preferred to glue them in with suitable silicone adhesives. Instead of two magnet arrangements on each of the In this solution, only one magnet arrangement is let into the piston 5 on both axial piston end sides, which at the same time as the magnets 13 and 13 'on the two facing sides of the end walls 7 and 9 of the
  • Housing 1 interacts.
  • the housing-fixed guide pin 19 is used so that the piston 5 is always guided in the same angular orientation during a displacement movement and rotation of the piston 5 about its central axis, not even by a small angular deflection, is prevented. This always ensures a completely exact assignment of the individual magnet arrangements to one another, so that the geometric conditions and thus the magnetic characteristics that occur always remain the same as was desired in the design of the entire device, the magnets and their arrangement, even with a displacement movement.
  • FIG. 4 shows such a case in principle:
  • a single electronic control device 25 is preferably used for the control of all electromagnets, but is equipped in such a way that it can control the individual magnet arrangements independently of one another in any desired or predetermined manner.
  • the electronic control device 25 can preferably be designed such that, depending on the request and the application or need, different control programs can be switched on which, depending on different requirement profiles, bring about corresponding magnetic characteristics of the overall device (for example adjustability of the current strength or the frequency).
  • Piston 5 and the control device 25 is to be carried out, is not shown in the figure in detail, but only purely schematically with lines 30, since these are simple techniques familiar to any person skilled in the art.
  • a chamber 26 or 27 is formed between the latter and the associated end wall 7 or 9 of the housing 1 in the interior 4, which chamber is filled with air in normal use.
  • a compressed air or compressed gas filling is also introduced into the chambers 26 and 27 to change the damping properties.
  • a suitable seal between the piston rod 6 and the end wall 7 of the housing 1, through which the piston rod 6 passes, a pressure-tight seal must be created, which allows a relative displacement of the piston rod 6 without the risk of escaping Compressed gas filling exists.
  • the sliding fit of the piston 5 on the inner walls of the housing 1 must also be carried out with tolerances such that a good displacement of the piston is possible, a gas exchange between the two chambers
  • piston 5 Yet another embodiment of the piston 5 is that the entire piston 5 is in turn made in one piece from a magnet, so that the additional attachment and attachment of magnet arrangements to it is no longer necessary. If the two chambers 26, 27 between the piston 5 and the two end walls 7, 9 of the housing 1 are filled with air or another gas filling, it can be seen that in practical use the high-frequency vibrations of small amplitude occurring in vehicle exhaust systems with the interposition of such Gas fillings are almost not transferred from the piston 5 to the housing 1 (or vice versa).
  • the permanent magnets that can be used are those based on the material samarium-cobalt, which can withstand heating up to 350 ° C before noticeable changes in the magnetic properties occur.
  • shock and vibration damper also not shown in the figures, is that the piston 5 runs in an interior space 4 which is filled with a liquid, i.e. that the chambers 26 and 27 are filled with liquid on both sides of the piston 5 and axial through bores are provided in the piston 5 at suitable locations between the magnet arrangements, through which at one
  • the liquid from one chamber, into which the piston 5 is moved can pass into the other chamber.
  • the number, shape and cross section of the through holes can again ensure a very special damper characteristic beyond the damping achieved by the magnetic forces of the magnet arrangements.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

L'invention concerne un amortisseur de chocs et de vibrations tel qu'on peut notamment en utiliser pour suspendre des circuits d'échappement sur des automobiles. Il est prévu un boîtier (1) formant un espace intérieur (4) dans lequel est monté un piston (5), de manière à se déplacer le long d'un axe de déplacement. Le piston (5) est fixé sur une tige (6) sortie hors du boîtier et présente dans le sens de son axe de déplacement, sur sa face opposée à la tige (6), une surface terminale avant, ainsi qu'une surface terminale arrière, sur son autre face. Vu dans le sens de déplacement du piston (5), l'espace intérieur (4) du boîtier (1) est délimité dans chaque cas par une paroi (7; 9) du boîtier. Sur chaque paroi (7; 9) du boîtier et sur chaque surface terminale du piston (5), il est prévu un système magnétique (12; 12'; 13;13'). Les systèmes magnétiques d'une paroi (7; 9) du boîtier qui se font dans chaque cas mutuellement face et une surface terminale du piston (5) ont la même polarité sur leurs faces qui se font mutuellement face.
PCT/EP1999/005655 1998-09-03 1999-08-04 Amortisseur de chocs et de vibrations, notamment pour suspendre des circuits d'echappement d'automobiles WO2000014428A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19840244.9 1998-09-03
DE1998140244 DE19840244A1 (de) 1998-09-03 1998-09-03 Stoß- und Schwingungsdämpfer, insbesondere zur Aufhängung von Abgasanlagen von Kraftfahrzeugen

Publications (1)

Publication Number Publication Date
WO2000014428A1 true WO2000014428A1 (fr) 2000-03-16

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Application Number Title Priority Date Filing Date
PCT/EP1999/005655 WO2000014428A1 (fr) 1998-09-03 1999-08-04 Amortisseur de chocs et de vibrations, notamment pour suspendre des circuits d'echappement d'automobiles

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Country Link
DE (1) DE19840244A1 (fr)
WO (1) WO2000014428A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10035687C2 (de) * 2000-07-20 2002-05-29 Hoerauf & Kohler Verwaltungs K Bewegungsdämpfer
DE20120797U1 (de) 2001-12-21 2002-04-18 Giehle, Andreas, 14476 Leest Magnetisches Dämpfungssystem
US20040012168A1 (en) * 2002-07-19 2004-01-22 Martinrea International Inc. Suspension system with magnetic resiliency
DE102006027636B4 (de) * 2006-06-13 2014-03-27 Gilbert Doko Magnetischer Schwingungsdämpfer
GB0617290D0 (en) * 2006-09-01 2006-10-11 Univ Reading Suspension unit
CN101878176B (zh) * 2007-11-30 2014-02-05 奥蒂斯电梯公司 被动磁升降机车厢稳定器
CN103185098B (zh) * 2011-12-31 2017-02-08 上海汽车集团股份有限公司 电磁弹簧减振器
EP3118479B1 (fr) * 2015-07-15 2018-08-22 Safran Landing Systems UK Limited Amortisseur de chocs pour train d'atterrisage d'aeronef
WO2017068601A1 (fr) * 2015-10-20 2017-04-27 Goduguchinta Vijaykumar Vaideeshwar Système de suspension magnétique pour automobiles
DE102016113992A1 (de) * 2016-07-28 2018-02-01 Röhm Gmbh Spann-Löseeinheit

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE188359C (fr) *
DE3137746A1 (de) 1981-09-23 1983-06-09 Volkswagenwerk Ag, 3180 Wolfsburg "abgasanlage fuer die brennkraftmaschine eines fahrzeugs"
DE3306180A1 (de) * 1983-02-23 1984-08-30 Gerhard 4040 Neuss Strahl Magnetring-stossdaempfer
DE3346609A1 (de) 1983-12-23 1985-07-18 Adam Opel AG, 6090 Rüsselsheim Aufhaengeelement fuer die abgasanlage einer brennkraftmaschine eines kraftfahrzeuges
JPS643338A (en) * 1987-06-26 1989-01-09 Bridgestone Corp Shock absorber
RU1835003C (ru) * 1991-03-25 1993-08-15 С.К.Кеворков и С,Г. Бадал н, Магнитна пружина
US5285995A (en) * 1992-05-14 1994-02-15 Aura Systems, Inc. Optical table active leveling and vibration cancellation system
JPH08131480A (ja) * 1994-11-08 1996-05-28 Delta Kogyo Co Ltd 防振用の磁気ダンパおよび磁気ダンパを用いた車載防振ベッド
DE29715711U1 (de) * 1997-09-02 1997-11-06 NSM Magnettechnik GmbH, 59399 Olfen Dämpfungsanschlag an der Stapelstation für Scheibenelemente, insbesondere Blechzuschnitte u.dgl.

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE188359C (fr) *
DE3137746A1 (de) 1981-09-23 1983-06-09 Volkswagenwerk Ag, 3180 Wolfsburg "abgasanlage fuer die brennkraftmaschine eines fahrzeugs"
DE3306180A1 (de) * 1983-02-23 1984-08-30 Gerhard 4040 Neuss Strahl Magnetring-stossdaempfer
DE3346609A1 (de) 1983-12-23 1985-07-18 Adam Opel AG, 6090 Rüsselsheim Aufhaengeelement fuer die abgasanlage einer brennkraftmaschine eines kraftfahrzeuges
JPS643338A (en) * 1987-06-26 1989-01-09 Bridgestone Corp Shock absorber
RU1835003C (ru) * 1991-03-25 1993-08-15 С.К.Кеворков и С,Г. Бадал н, Магнитна пружина
US5285995A (en) * 1992-05-14 1994-02-15 Aura Systems, Inc. Optical table active leveling and vibration cancellation system
JPH08131480A (ja) * 1994-11-08 1996-05-28 Delta Kogyo Co Ltd 防振用の磁気ダンパおよび磁気ダンパを用いた車載防振ベッド
DE29715711U1 (de) * 1997-09-02 1997-11-06 NSM Magnettechnik GmbH, 59399 Olfen Dämpfungsanschlag an der Stapelstation für Scheibenelemente, insbesondere Blechzuschnitte u.dgl.

Non-Patent Citations (2)

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Title
PATENT ABSTRACTS OF JAPAN vol. 013, no. 170 (M - 817) 21 April 1989 (1989-04-21) *
PATENT ABSTRACTS OF JAPAN vol. 1996, no. 09 30 September 1996 (1996-09-30) *

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