EP0529192A2 - Elastic supporting device for attaching a suction tube to an internal combustion engine - Google Patents

Elastic supporting device for attaching a suction tube to an internal combustion engine Download PDF

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Publication number
EP0529192A2
EP0529192A2 EP92105086A EP92105086A EP0529192A2 EP 0529192 A2 EP0529192 A2 EP 0529192A2 EP 92105086 A EP92105086 A EP 92105086A EP 92105086 A EP92105086 A EP 92105086A EP 0529192 A2 EP0529192 A2 EP 0529192A2
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EP
European Patent Office
Prior art keywords
fastening device
spring body
spring
holding element
plate spring
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.)
Granted
Application number
EP92105086A
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German (de)
French (fr)
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EP0529192B1 (en
EP0529192A3 (en
Inventor
Hans-Gerd Dr. Eckel
Armin Barth
Klaus Dr. Kurr
Karl-Heinrich Dr. Spies
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Carl Freudenberg KG
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Carl Freudenberg KG
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Publication date
Application filed by Carl Freudenberg KG filed Critical Carl Freudenberg KG
Publication of EP0529192A2 publication Critical patent/EP0529192A2/en
Publication of EP0529192A3 publication Critical patent/EP0529192A3/en
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Publication of EP0529192B1 publication Critical patent/EP0529192B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/10314—Materials for intake systems
    • F02M35/10321—Plastics; Composites; Rubbers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/10006—Air intakes; Induction systems characterised by the position of elements of the air intake system in direction of the air intake flow, i.e. between ambient air inlet and supply to the combustion chamber
    • F02M35/10078—Connections of intake systems to the engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/08—Thermoplastics

Definitions

  • the invention relates to an elastic fastening device for connecting an intake pipe to an internal combustion engine, consisting of an annular spring body made of rubber-elastic material and two holding elements arranged concentrically to the spring body for fixing it to the parts to be connected.
  • Such a fastening device is known from DE-PS 36 41 811. Then elastic bearing elements between the intake system and the cylinder head of an internal combustion engine are used, which cause vibration decoupling. However, it must be ensured that the fasteners are difficult to access, which makes quick and easy assembly of the intake system difficult.
  • the invention has for its object to provide an elastic fastening device of the generic type, which enables quick and easy assembly of an intake system to an internal combustion engine and ensures good, vibration-decoupled performance characteristics during a long period of use at all temperatures occurring in this area.
  • the spring body is delimited in the axial direction on both sides by support surfaces extending essentially transversely to its axis, the holding elements touch the support surfaces overlapping one another and the spring body is assigned at least one disc spring made of a non-creeping material in a series connection .
  • the advantage here is that the plate spring is particularly compact in the axial direction, which is of particular importance in view of the increasingly aerodynamically designed bodies and the particularly flat engine compartments associated therewith.
  • the entire fastening device has essentially constant usage properties due to the disc spring connected in series over a long period of use. Relaxation phenomena of the spring body made of rubber-elastic material are compensated for by using the disc spring.
  • the plate spring is preloaded in such a way that the spring rate is essentially zero after generation of the intended preload and has approximately a straight shape.
  • the plate spring consists of fiber-reinforced plastic or steel.
  • the plate spring has an S-shaped spring characteristic, the deformation which is present in the vibration-free state after the pretensioning of the fastening device lies in the region of the spring characteristic which runs essentially horizontally. The during the intended Use of excited, acoustically effective vibrations are almost completely isolated and decoupled. Lower-frequency vibrations with a larger amplitude are reliably damped by the spring body and the deflected disc spring.
  • suspension spring as a plate spring with an S-shaped characteristic in conjunction with its adjustment to the rubber spring ensures that the character obtained overall with the suspension system of the elastic fastening device remains unaffected by the ambient temperature and is essentially constant. This is of particular importance in the area of the cylinder head of an internal combustion engine, since very high temperatures can occur in these areas.
  • an S-shaped spring characteristic is a disc spring made of non-creeping material, for example made of fiber-reinforced plastic or steel.
  • An initially degressive course of the spring characteristic curve is followed by a clearly prominent area in which there are considerable deformation paths even when the load to be absorbed undergoes only a very slight change. Then there is again a steep rise in the spring characteristic curve, but with a reversed, i.e. progressive, course. Outside the clearly protruding area, greater forces are required to achieve a deformation of the spring.
  • the spring body made of rubber-elastic material reliably performs vibrations with a larger amplitude to dampen.
  • the ring-shaped spring body is not yet effective when acoustically effective vibrations of small amplitude are introduced.
  • the acoustically disturbing vibrations are isolated by the pre-tensioned disc spring.
  • low-frequency vibrations with larger vibration amplitudes are introduced, they are damped by both the spring body and the deflected disc spring. Both the damping of low-frequency vibrations and the isolation of acoustically effective, high-frequency vibrations over long periods of time, even at elevated ambient temperatures, is possible without any problems.
  • a pot-shaped axial projection of the second holding element can be penetrated substantially centrally in the first holding element, the first holding element being associated with the axial projection adjacent to it at a radial distance.
  • This radial distance is to be dimensioned such that vibrations which occur transversely to the axis of the fastening device can be isolated to a sufficient extent without even slight displacements of the two holding elements leading to contact and thus to stop noises.
  • the disk spring can be arranged to achieve particularly compact dimensions, in particular in the axial direction, on the one hand in the side of the first holding element facing away from the spring body and, on the other hand, on a support bearing which overlaps the two holding elements and the spring body in the axial direction.
  • both the two holding elements and the annular spring body made of rubber-elastic material are protected from contamination by the arrangement of the support bearing, which further improves the performance properties.
  • the support bearing can have at least one ventilation opening along its circumference in the axial region of the spring body, as a result of which the performance characteristics with regard to vibration damping and vibration isolation are further improved.
  • the first holding element can have a guide bead on the inside in the radial direction for positioning the plate spring and starting with the plate spring in the non-prestressed state in the guide bead Limit the V-shaped gap open in the radial direction to the outside. This configuration provides good mobility of the plate spring on both sides in the axial direction.
  • the spring body can be rounded to deflect from the outer and / or the inner peripheral surface into the support surfaces.
  • An angular beveling of the corners is also conceivable. This configuration requires a favorable load on the spring body even in the case of vibrations that occur transversely to its axis.
  • Tilting of the spring body between the two holding elements during the intended use is largely excluded.
  • the spring body can have a maximum extent in the radial direction which does not exceed that of the first holding element.
  • the spring body like the first holding element, is at a distance from the axial projection of the second holding element, so that the vibration insulation / vibration damping is not impeded in the case of vibrations introduced transversely to the axis.
  • FIG. 1 shows the elastic fastening device according to the invention in the non-prestressed state, while in FIG. 2 the elastic fastening device from FIG. 1 is shown in the prestressed state during its intended use.
  • FIGS. 1 and 2 An elastic fastening device for connecting an intake pipe 1 to an internal combustion engine 2 is shown in FIGS. 1 and 2.
  • the intake pipe 1 is indicated schematically and only the receiving element of the internal combustion engine 2 is shown.
  • the fastening device consists essentially of a rubber-elastic annular spring body 3 and two holding elements 4, 5 which are arranged concentrically to the spring body 3 and touch the support surfaces 7, 8 adjacent.
  • the support surfaces 7, 8 extend essentially transversely to the axis 6 of the fastening device, with the spring body 3 being assigned a plate spring 9 in a series connection.
  • the plate spring 9 consists of a metallic material.
  • the fastening device is shown in the non-prestressed state.
  • the second holding element touches in the axial direction the support bearing 10, which overlaps the two holding elements 4, 5 and the spring body 3 in the axial direction.
  • the spring body 3 is also largely unloaded between the two holding elements 4, 5.
  • a clamping screw 14 is provided, which is connected to the second holding element 5.
  • the clamping screw 14 passes through the cup-shaped axial projection 5.1 of the second holding element 5 centrally and is guided in a threaded piece which is arranged non-rotatably in this projection.
  • the support bearing 10 is fastened with a fastening screw 15 on a carrier of the internal combustion engine 2.
  • FIG. 2 shows the elastic fastening device shown in FIG. 1 in the prestressed state during the intended use.
  • the position of the second holding element 5, the spring body 3, the first holding element 4 and the plate spring 9 has changed relative to the internal combustion engine 2, the support bearing 10 and the intake pipe 1.
  • the pot-shaped axial projection 5.1 of the second holding element 5 lies in a recess in the intake pipe 1.
  • the mounting of the fastening device is particularly simple if the recess of the intake pipe 1 can be used as an end stop.
  • the spring rate of the plate spring 9 is essentially zero in the position shown here after generation of the intended preload.
  • This configuration in connection with an S-shaped spring rate of the plate spring 9 requires a very good isolation of high-frequency vibrations, without any signs of relaxation of the fastening device occurring over a long period of use.
  • the second holding element 5 is at a distance from the support bearing 10 in the axial direction, so that these two parts do not touch during the intended use of the elastic fastening device. This effectively prevents impact noises.
  • stop knobs made of rubber-elastic material on the facing surfaces of the support bearing 10 and the second holding element 5, so that the movements are limited in the event of extreme deflections and stop noises are nevertheless avoided.
  • the main advantage of the elastic fastening device according to the invention for connecting an intake pipe to an internal combustion engine is the simple, comparatively low-part design and the consistently good performance characteristics over a long service life.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Vibration Prevention Devices (AREA)
  • Springs (AREA)

Abstract

Elastische Befestigungsvorrichtung zur Verbindung eines Ansaugrohres (1) mit einer Verbrennungskraftmaschine (2), bestehend aus einem ringförmigen Federkörper (3) aus gummielastischem Werkstoff sowie zwei konzentrisch zu dem Federkörper (3) angeordneten Halteelementen (4, 5) zu seiner Festlegung an den zu verbindenden Teilen. Der Federkörper (3) ist in axialer Richtung beiderseits durch sich im wesentlichen quer zu seiner Achse (6) erstreckende Stützflächen (7, 8) begrenzt, wobei die Halteelemente (4, 5) die Stützflächen (7, 8) einander übergreifend berühren und wobei dem Federkörper (3) eine Tellerfeder (9) aus einem nichtkriechenden Werkstoff in einer Reihenschaltung zugeordnet ist. <IMAGE>Elastic fastening device for connecting an intake pipe (1) to an internal combustion engine (2), consisting of an annular spring body (3) made of rubber-elastic material and two holding elements (4, 5) arranged concentrically to the spring body (3) for fixing it to the ones to be connected Share. The spring body (3) is delimited on both sides in the axial direction by support surfaces (7, 8) which extend essentially transversely to its axis (6), the holding elements (4, 5) touching the support surfaces (7, 8) in an overlapping manner and wherein the spring body (3) is assigned a disc spring (9) made of a non-creeping material in a series connection. <IMAGE>

Description

Die Erfindung betrifft eine elastische Befestigungsvorrichtung zur Verbindung eines Ansaugrohres mit einer Verbrennungskraftmaschine, bestehend aus einem ringförmigen Federkörper aus gummielastischem Werkstoff sowie zwei konzentrisch zu dem Federkörper angeordneten Halteelementen zu seiner Festlegung an den zu verbindenden Teilen.The invention relates to an elastic fastening device for connecting an intake pipe to an internal combustion engine, consisting of an annular spring body made of rubber-elastic material and two holding elements arranged concentrically to the spring body for fixing it to the parts to be connected.

Eine derartige Befestigungsvorrichtung ist aus der DE-PS 36 41 811 bekannt. Danach gelangen elastische Lagerelemente zwischen der Ansauganlage und dem Zylinderkopf einer Verbrennungskraftmaschine zur Anwendung, die eine Schwingungsentkopplung bedingen. Dabei ist allerdings darauf zu achten, daß die Befestigungselemente schlecht zugänglich sind, was eine rasche und einfache Montage der Ansauganlage erschwert.Such a fastening device is known from DE-PS 36 41 811. Then elastic bearing elements between the intake system and the cylinder head of an internal combustion engine are used, which cause vibration decoupling. However, it must be ensured that the fasteners are difficult to access, which makes quick and easy assembly of the intake system difficult.

Der Erfindung liegt die Aufgabe zugrunde, eine elastische Befestigungsvorrichtung der gattungsgemäßen Art bereitzustellen, die eine schnelle und einfache Montage einer Ansauganlage an eine Brennkraftmaschine ermöglicht sowie gute, schwingungsentkoppelte Gebrauchseigenschaften während einer langen Gebrauchsdauer bei sämtlichen in diesem Bereich auftretenden Temperaturen gewährleistet.The invention has for its object to provide an elastic fastening device of the generic type, which enables quick and easy assembly of an intake system to an internal combustion engine and ensures good, vibration-decoupled performance characteristics during a long period of use at all temperatures occurring in this area.

Diese Aufgabe wird mit den kennzeichnenden Merkmalen von Patentanspruch 1 gelöst. Auf vorteilhafte Ausgestaltungen nehmen die Unteransprüche Bezug.This object is achieved with the characterizing features of patent claim 1. The subclaims refer to advantageous refinements.

Bei der erfindungsgemäßen elastischen Befestigungsvorrichtung zur Verbindung eines Ansaugrohres ist der Federkörper in axialer Richtung beiderseits durch sich im wesentlichen quer zu seiner Achse erstreckende Stützflächen begrenzt, die Halteelemente berühren die Stützflächen einander übergreifend und dem Federkörper ist zumindest eine Tellerfeder aus einem nichtkriechenden Werkstoff in einer Reihenschaltung zugeordnet. Hierbei ist von Vorteil, daß die Tellerfeder in axialer Richtung besonders kompakt baut, was im Hinblick auf die zunehmend aerodynamischer gestalteten Karosserien und damit verbundenen, besonders flachen Motorräumen von hervorzuhebender Bedeutung ist. Desweiteren ist von Vorteil, daß die gesamte Befestigungsvorrichtung durch die in Reihe geschaltete Tellerfeder während einer langen Gebrauchsdauer im wesentlichen konstante Gebrauchseigenschaften aufweist. Relaxationserscheinungen des Federkörpers aus gummielastischem Werkstoff werden durch die Verwendung der Tellerfeder kompensiert.In the elastic fastening device according to the invention for connecting an intake pipe, the spring body is delimited in the axial direction on both sides by support surfaces extending essentially transversely to its axis, the holding elements touch the support surfaces overlapping one another and the spring body is assigned at least one disc spring made of a non-creeping material in a series connection . The advantage here is that the plate spring is particularly compact in the axial direction, which is of particular importance in view of the increasingly aerodynamically designed bodies and the particularly flat engine compartments associated therewith. Furthermore, it is advantageous that the entire fastening device has essentially constant usage properties due to the disc spring connected in series over a long period of use. Relaxation phenomena of the spring body made of rubber-elastic material are compensated for by using the disc spring.

Im Rahmen dieser Erfindung ist es vorgesehen, daß die Tellerfeder derart vorgespannt ist, daß die Federrate nach der Erzeugung der bestimmungsgemäßen Vorspannung im wesentlichen Null ist und annähernd eine gradlinige Gestalt aufweist. Darüber hinaus ist vorgesehen, daß die Tellerfeder aus faserverstärktem Kunststoff oder Stahl besteht. Die Tellerfeder weist eine S-förmige Federkennlinie auf, wobei die im schwingungsfreien Zustand vorhandene Verformung nach dem Vorspannen der Befestigungsvorrichtung in dem Bereich der Federkennlinie liegt, der im wesentlichen horizontal verläuft. Die während der bestimmungsgemäßen Verwendung angeregten, akustisch wirksamen Schwingungen werden nahezu vollständig isoliert und abgekoppelt. Tieferfrequente Schwingungen mit größerer Amplitude erfahren durch den Federkörper und die ausgelenkte Tellerfeder eine zuverlässige Dämpfung. Durch die spezielle Ausbildung der Tragfeder als Tellerfeder mit S-förmiger Kennlinie in Verbindung mit ihrer Abstimmung auf die Gummifeder wird erreicht, daß der insgesamt mit dem Federungssystem der elastischen Befestigungsvorrichtung erhaltene Charakter unbeeinflußt durch die Umgebungstemperatur bleibt und im wesentlichen konstant ist. Dies ist gerade im Bereich des Zylinderkopfes einer Verbrennungskraftmaschine von hervorzuhebender Bedeutung, da in diesen Bereichen sehr hohe Temperaturen auftreten können.In the context of this invention, it is provided that the plate spring is preloaded in such a way that the spring rate is essentially zero after generation of the intended preload and has approximately a straight shape. In addition, it is provided that the plate spring consists of fiber-reinforced plastic or steel. The plate spring has an S-shaped spring characteristic, the deformation which is present in the vibration-free state after the pretensioning of the fastening device lies in the region of the spring characteristic which runs essentially horizontally. The during the intended Use of excited, acoustically effective vibrations are almost completely isolated and decoupled. Lower-frequency vibrations with a larger amplitude are reliably damped by the spring body and the deflected disc spring. The special design of the suspension spring as a plate spring with an S-shaped characteristic in conjunction with its adjustment to the rubber spring ensures that the character obtained overall with the suspension system of the elastic fastening device remains unaffected by the ambient temperature and is essentially constant. This is of particular importance in the area of the cylinder head of an internal combustion engine, since very high temperatures can occur in these areas.

Voraussetzung für eine S-förmig verlaufende Federkennlinie ist eine Tellerfeder aus nichtkriechendem Werkstoff, beispielsweise aus faserverstärktem Kunststoff oder aus Stahl. An einen anfänglich degressiven Verlauf der Federkennlinie schließt sich ein deutlich hervortretender Bereich an, in welchem sich erhebliche Verformungswege auch dann ergeben, wenn die aufzunehmende Belastung nur eine sehr geringe Veränderung erfährt. Anschließend erfolgt wiederum ein steiler Anstieg der Federkennlinie allerdings mit umgekehrtem, also progressivem Verlauf. Außerhalb des deutlich hervortretenden Bereiches sind größere Kräfte zur Erzielung einer Verformung der Feder erforderlich. Der Federkörper aus gummielastischem Werkstoff übernimmt bei der erfindungsgemäßen elastischen Befestigungsvorrichtung die Aufgabe, Schwingungen mit größerer Amplitude zuverlässig zu dämpfen. Bei Einleitung akustisch wirksamer Schwingungen kleiner Amplitude ist der ringförmige Federkörper noch nicht wirksam. Die akustisch störenden Schwingungen werden von der vorgespannten Tellerfeder isoliert. Bei Einleitung tieffrequenter Schwingungen mit größeren Schwingungsamplituden werden diese sowohl vom Federkörper als auch von der ausgelenkten Tellerfeder gedämpft. Sowohl die Dämpfung tieffrequenter Schwingungen als auch die Isolierung akustisch wirksamer, hochfrequenter Schwingungen über lange Zeiträume auch bei erhöhten Umgebungstemperaturen, ist problemlos möglich.The prerequisite for an S-shaped spring characteristic is a disc spring made of non-creeping material, for example made of fiber-reinforced plastic or steel. An initially degressive course of the spring characteristic curve is followed by a clearly prominent area in which there are considerable deformation paths even when the load to be absorbed undergoes only a very slight change. Then there is again a steep rise in the spring characteristic curve, but with a reversed, i.e. progressive, course. Outside the clearly protruding area, greater forces are required to achieve a deformation of the spring. In the elastic fastening device according to the invention, the spring body made of rubber-elastic material reliably performs vibrations with a larger amplitude to dampen. The ring-shaped spring body is not yet effective when acoustically effective vibrations of small amplitude are introduced. The acoustically disturbing vibrations are isolated by the pre-tensioned disc spring. When low-frequency vibrations with larger vibration amplitudes are introduced, they are damped by both the spring body and the deflected disc spring. Both the damping of low-frequency vibrations and the isolation of acoustically effective, high-frequency vibrations over long periods of time, even at elevated ambient temperatures, is possible without any problems.

Das erste Halteelement kann von einem topfförmigen Achsialvorsprung des zweiten Halteelementes im wesentlichen zentrisch durchdrungen sein wobei das erste Halteelement dem Achsialvorsprung mit radialem Abstand benachbart zugeordnet ist. Dieser radiale Abstand ist so zu bemessen, daß auch Schwingungen, die quer zur Achse der Befestigungsvorrichtung auftreten in ausreichendem Maße isoliert werden können ohne daß schon geringe Verschiebungen der beiden Halteelemente zu einer Berührung und damit zu Anschlaggeräuschen führen.A pot-shaped axial projection of the second holding element can be penetrated substantially centrally in the first holding element, the first holding element being associated with the axial projection adjacent to it at a radial distance. This radial distance is to be dimensioned such that vibrations which occur transversely to the axis of the fastening device can be isolated to a sufficient extent without even slight displacements of the two holding elements leading to contact and thus to stop noises.

Die Tellerfeder kann zur Erzielung besonders kompakter Abmessungen insbesondere in axialer Richtung einerseits in der von dem Federkörper abgewandten Seite des ersten Halteelementes angeordnet sein und andererseits auf einem die beiden Halteelemente und den Federkörper in axialer Richtung übergreifenden Traglager. Darüber hinaus ist von Vorteil, daß sowohl die beiden Halteelemente als auch der ringförmige Federkörper aus gummielastischem Werkstoff durch die Anordnung des Traglagers vor Verunreinigungen geschützt sind, was die Gebrauchseigenschaften weiter verbessert.The disk spring can be arranged to achieve particularly compact dimensions, in particular in the axial direction, on the one hand in the side of the first holding element facing away from the spring body and, on the other hand, on a support bearing which overlaps the two holding elements and the spring body in the axial direction. In addition, from Advantage that both the two holding elements and the annular spring body made of rubber-elastic material are protected from contamination by the arrangement of the support bearing, which further improves the performance properties.

Das Traglager kann entlang seines Umfanges im axialen Bereich des Federkörpers zumindest eine Entlüftungsöffnung aufweisen, wodurch die Gebrauchseigenschaften bezüglich der Schwingungsdämpfung und Schwingungsisolierung weiter verbessert werden.The support bearing can have at least one ventilation opening along its circumference in the axial region of the spring body, as a result of which the performance characteristics with regard to vibration damping and vibration isolation are further improved.

Zur guten Beweglichkeit der Tellerfeder, die unter der bestimmungsgemäßen Vorspannung eine im wesentlichen quer zu der Achse verlaufende Position einnimmt, kann das erste Halteelement in radialer Richtung innenliegend eine Führungssicke zur Positionierung der Tellerfeder aufweisen und mit der Tellerfeder im nicht vorgespannten Zustand in der Führungssicke beginnend einen in radialer Richtung nach außen geöffneten, V-förmigen Spalt begrenzen. Eine gute, in axialer Richtung beiderseitige Beweglichkeit der Tellerfeder ist durch diese Ausgestaltung gegeben.For good mobility of the plate spring, which assumes an essentially transverse position to the axis under the intended preload, the first holding element can have a guide bead on the inside in the radial direction for positioning the plate spring and starting with the plate spring in the non-prestressed state in the guide bead Limit the V-shaped gap open in the radial direction to the outside. This configuration provides good mobility of the plate spring on both sides in the axial direction.

Zur weiteren Verbesserung der Gebrauchsdauer kann der Federkörper von der Außen- und/oder der Innenumfangsfläche in die Stützflächen umlenkend abgerundet sein. Auch eine kantige Abschrägung der Ecken ist denkbar. Diese Ausgestaltung bedingt eine günstige Belastung des Federkörpers auch bei Schwingungen, die quer zu seiner Achse auftreten.To further improve the service life, the spring body can be rounded to deflect from the outer and / or the inner peripheral surface into the support surfaces. An angular beveling of the corners is also conceivable. This configuration requires a favorable load on the spring body even in the case of vibrations that occur transversely to its axis.

Ein Verkanten des Federkörpers zwischen den beiden Halteelementen während der bestimmungsgemäßen Verwendung wird dadurch weitgehend ausgeschlossen.Tilting of the spring body between the two holding elements during the intended use is largely excluded.

Desweiteren kann der Federkörper eine maximale Erstreckung in radialer Richtung aufweisen, die die des ersten Halteelementes nicht übersteigt. Durch diese Ausgestaltung weist der Federkörper ebenso, wie das erste Halteelement einen Abstand vom Axialvorsprung des zweiten Halteelementes auf so daß die Schwingungsisolierung/Schwingungsdämpfung bei quer zur Achse eingeleiteten Schwingungen nicht behindert wird.Furthermore, the spring body can have a maximum extent in the radial direction which does not exceed that of the first holding element. As a result of this configuration, the spring body, like the first holding element, is at a distance from the axial projection of the second holding element, so that the vibration insulation / vibration damping is not impeded in the case of vibrations introduced transversely to the axis.

Die Erfindung wird nachstehend anhand einer bevorzugten Ausführungsform unter Bezugnahme auf die beigefügten Zeichnungen weiter erläutert.The invention is explained below using a preferred embodiment with reference to the accompanying drawings.

In Figur 1 ist die erfindungsgemäße elastische Befestigungsvorrichtung im nicht vorgespannten Zustand dargestellt, während in Figur 2 die elastische Befestigungsvorrichtung aus Figur 1 im vorgespannten Zustand während ihrer bestimmungsgemäßen Verwendung gezeigt ist.FIG. 1 shows the elastic fastening device according to the invention in the non-prestressed state, while in FIG. 2 the elastic fastening device from FIG. 1 is shown in the prestressed state during its intended use.

In den Figuren 1 und 2 ist eine elastische Befestigungsvorrichtung zur Verbindung eines Ansaugrohres 1 mit einer Verbrennungskraftmaschine 2 gezeigt. Das Ansaugrohr 1 ist schematisch angedeutet und von der Verbrennungskraftmaschine 2 ist nur das Aufnahmeelement dargestellt. Die Befestigungsvorrichtung besteht im wesentlichen aus einem gummielastischen ringförmigen Federkörper 3 sowie zwei Halteelementen 4, 5 die konzentrisch zum Federkörper 3 angeordnet sind und dessen Stützflächen 7, 8 anliegend berühren. Die Stützflächen 7, 8 erstrecken sich im wesentlichen quer zu der Achse 6 der Befestigungsvorrichtung, wobei dem Federkörper 3 eine Tellerfeder 9 in einer Reihenschaltung zugeordnet ist. Im Hinblick auf gleichmäßig gute Gebrauchseigenschaften während einer langen Gebrauchsdauer besteht die Tellerfeder 9 aus einem metallischen Werkstoff.An elastic fastening device for connecting an intake pipe 1 to an internal combustion engine 2 is shown in FIGS. 1 and 2. The intake pipe 1 is indicated schematically and only the receiving element of the internal combustion engine 2 is shown. The fastening device consists essentially of a rubber-elastic annular spring body 3 and two holding elements 4, 5 which are arranged concentrically to the spring body 3 and touch the support surfaces 7, 8 adjacent. The support surfaces 7, 8 extend essentially transversely to the axis 6 of the fastening device, with the spring body 3 being assigned a plate spring 9 in a series connection. With regard to uniformly good usage properties over a long period of use, the plate spring 9 consists of a metallic material.

In Figur 1 ist die Befestigungsvorrichtung im nicht vorgespannten Zustand dargestellt. Das zweite Halteelement berührt in axialer Richtung das Traglager 10, das die beiden Halteelemente 4, 5 und den Federkörper 3 in axialer Richtung übergreift. Die Tellerfeder 9, die einerseits im Traglager 10 und andererseits auf dem ersten Halteelement 4 abgestützt ist, weist in diesem, unbelasteten Zustand eine tellerförmige Gestalt auf. Auch der Federkörper 3 ist weitgehend unbelastet zwischen den beiden Halteelementen 4, 5 angeordnet. Zum Verspannen des Befestigungselementes ist eine Spannschraube 14 vorgesehen, die mit dem zweiten Halteelement 5 verbunden ist. Nach einer bevorzugten Ausführungsform durchgreift die Spannschraube 14 den topfförmigen Axialvorsprung 5.1 des zweiten Halteelementes 5 zentrisch und ist in einem Gewindestück, das unverdrehbar in diesem Vorsprung angeordnet ist, geführt. Das Traglager 10 ist mit einer Befestigungsschraube 15 auf einem Träger der Verbrennungskraftmaschine 2 befestigt.In Figure 1, the fastening device is shown in the non-prestressed state. The second holding element touches in the axial direction the support bearing 10, which overlaps the two holding elements 4, 5 and the spring body 3 in the axial direction. The plate spring 9, which is supported on the one hand in the support bearing 10 and on the other hand on the first holding element 4, has a plate-like shape in this unloaded state. The spring body 3 is also largely unloaded between the two holding elements 4, 5. To tighten the fastening element, a clamping screw 14 is provided, which is connected to the second holding element 5. According to a preferred embodiment, the clamping screw 14 passes through the cup-shaped axial projection 5.1 of the second holding element 5 centrally and is guided in a threaded piece which is arranged non-rotatably in this projection. The support bearing 10 is fastened with a fastening screw 15 on a carrier of the internal combustion engine 2.

In Figur 2 ist die in Figur 1 dargestellte, elastische Befestigungsvorrichtung in vorgespanntem Zustand während der bestimmungsgemäßen Verwendung gezeigt. Durch das Anziehen der Spannschraube 14 hat sich die Position des zweiten Halteelementes 5, des Federkörpers 3, des ersten Halteelementes 4 sowie der Tellerfeder 9 relativ zur Verbrennungskraftmaschine 2, dem Traglager 10 sowie dem Ansaugrohr 1 verändert. Der topfförmige Achsialvorsprung 5.1 des zweiten Halteelementes 5 liegt in diesem Fall in einer Aussparung des Ansaugrohres 1 an. Die Montage der Befestigungsvorrichtung gestaltet sich dann besonders einfach, wenn die Ausnehmung des Ansaugrohres 1 als Endanschlag genutzt werden kann. Die Federrate der Tellerfeder 9 ist in der hier dargestellten Position nach Erzeugung der bestimmungsgemäßen Vorspannung im wesentlichen Null. Diese Ausgestaltung in Verbindung mit einer S-förmigen Federrate der Tellerfeder 9 bedingt eine sehr gute Isolierung hochfrequenter Schwingungen, ohne daß Relaxationserscheinungen der Befestigungsvorrichtung während einer langen Gebrauchsdauer auftreten würden. Das zweite Halteelement 5 weist in axialer Richtung einen Abstand vom Traglager 10 auf, so daß sich diese beiden Teile während der bestimmungsgemäßen Verwendung der elastischen Befestigungsvorrichtung nicht berühren. Anschlaggeräusche werden dadurch wirkungsvoll vermieden. Allerdings besteht nach einer anderen Ausgestaltung auch die Möglichkeit, auf den einander zugewandten Flächen von Traglager 10 und zweitem Halteelement 5 Anschlagnoppen aus gummielastischem Material vorzusehen, so daß bei Extremauslenkungen die Bewegungen begrenzt und Anschlaggeräusche trotzdem vermieden werden.FIG. 2 shows the elastic fastening device shown in FIG. 1 in the prestressed state during the intended use. By tightening the clamping screw 14, the position of the second holding element 5, the spring body 3, the first holding element 4 and the plate spring 9 has changed relative to the internal combustion engine 2, the support bearing 10 and the intake pipe 1. In this case, the pot-shaped axial projection 5.1 of the second holding element 5 lies in a recess in the intake pipe 1. The mounting of the fastening device is particularly simple if the recess of the intake pipe 1 can be used as an end stop. The spring rate of the plate spring 9 is essentially zero in the position shown here after generation of the intended preload. This configuration in connection with an S-shaped spring rate of the plate spring 9 requires a very good isolation of high-frequency vibrations, without any signs of relaxation of the fastening device occurring over a long period of use. The second holding element 5 is at a distance from the support bearing 10 in the axial direction, so that these two parts do not touch during the intended use of the elastic fastening device. This effectively prevents impact noises. However, according to another embodiment, there is also the possibility of providing stop knobs made of rubber-elastic material on the facing surfaces of the support bearing 10 and the second holding element 5, so that the movements are limited in the event of extreme deflections and stop noises are nevertheless avoided.

Auch in dem hier dargestellten Beispiel bleibt ein im wesentlichen V-förmiger Spalt zwischen dem ersten Halteelement 4 und der nahezu waagrecht angeordneten Tellerfeder 9 erhalten, so daß die Axialauslenkung der Befestigungsvorrichtung in beide Richtungen nicht behindert werden.In the example shown here, a substantially V-shaped gap between the first holding element 4 and the almost horizontally arranged disc spring 9 is retained, so that the axial deflection of the fastening device is not hindered in both directions.

Der wesentliche Vorteil der erfindungsgemäßen elastischen Befestigungsvorrichtung zur Verbindung eines Ansaugrohres mit einer Verbrennungskraftmaschine besteht in dem einfachen, vergleichsweise teilearmen Aufbau und in den gleichbleibend guten Gebrauchseigenschaften während einer langen Gebrauchsdauer.The main advantage of the elastic fastening device according to the invention for connecting an intake pipe to an internal combustion engine is the simple, comparatively low-part design and the consistently good performance characteristics over a long service life.

Claims (9)

Elastische Befestigungsvorrichtung zur Verbindung eines Ansaugrohres mit einer Verbrennungskraftmaschine, bestehend aus einem ringförmigen Federkörper aus gummielastischem Werkstoff sowie zwei konzentrisch zu dem Federkörper angeordneten Halteelementen zu seiner Festlegung an den zu verbindenden Teilen, dadurch gekennzeichnet, daß der Federkörper (3) in axialer Richtung beiderseits durch sich im wesentlichen quer zu seiner Achse (6) erstreckende Stützflächen (7, 8) begrenzt ist, daß die Halteelemente (4, 5) die Stützflächen (7, 8) einander übergreifend berühren und daß dem Federkörper (3) eine Tellerfeder (9) aus einem nichtkriechenden Werkstoff in einer Reihenschaltung zugeordnet ist.Elastic fastening device for connecting an intake pipe to an internal combustion engine, consisting of an annular spring body made of rubber-elastic material and two holding elements arranged concentrically to the spring body for fixing it to the parts to be connected, characterized in that the spring body (3) is axially on both sides by itself is limited essentially transverse to its axis (6) extending support surfaces (7, 8) that the holding elements (4, 5) touch the support surfaces (7, 8) overlapping each other and that the spring body (3) from a plate spring (9) is assigned to a non-creeping material in a series connection. Befestigungsvorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Tellerfeder (9) derart vorgespannt ist, daß ihre Federrate nach der Erzeugung der bestimmungsgemäßen Vospannung im wesentlichen Null ist.Fastening device according to claim 1, characterized in that the plate spring (9) is pretensioned in such a way that its spring rate is essentially zero after the intended tension has been generated. Befestigungsvorrichtung nach Anspruch 1 bis 2, dadurch gekennzeichnet, daß die Tellerfeder (9) aus faserverstärktem Kunststoff oder Stahl besteht.Fastening device according to claim 1 to 2, characterized in that the plate spring (9) consists of fiber-reinforced plastic or steel. Befestigungsvorrichtung nach Anspruch 1 bis 3, dadurch gekennzeichnet, daß das erste Halteelement (4) vom einem topfförmigen Axialvorsprung (5.1) des zweiten Halteelementes (5) im wesentlichen zentrisch durchdrungen wird und daß das erste Halteelement (4) dem Axialvorsprung (5.1) mit radialem Abstand benachbart zugeordnet ist.Fastening device according to claims 1 to 3, characterized in that the first holding element (4) is penetrated essentially centrally by a cup-shaped axial projection (5.1) of the second holding element (5) and in that the first holding element (4) is radial to the axial projection (5.1) Distance is assigned adjacent. Befestigungsvorrichtung nach Anspruch 1 bis 4, dadurch gekennzeichnet, daß die Tellerfeder (9) einerseits auf der von dem Federkörper (3) abgewandten Seite des ersten Halteelementes (4) angeordnet ist und andererseits in einem die beiden Halteelemente (4, 5) und den Federkörper (3) in axialer Richtung übergreifenden Traglager (10)Fastening device according to claims 1 to 4, characterized in that the plate spring (9) is arranged on the one hand on the side of the first holding element (4) facing away from the spring body (3) and on the other hand in one of the two holding elements (4, 5) and the spring body (3) support bearing (10) spanning in the axial direction Befestigungsvorrichtung nach Anspruch 5, dadurch gekennzeichnet, daß das Traglager (10) entlang seines Umfanges im axialen Bereich des Federkörpers (3) zumindestens eine Entlüftungsöffnung (13) aufweist.Fastening device according to claim 5, characterized in that the support bearing (10) has at least one ventilation opening (13) along its circumference in the axial region of the spring body (3). Befestigungsvorrichtung nach Anspruch 5 bis 6, dadurch gekennzeichnet, daß das erste Halteelement (4) in radialer Richtung innenliegend eine Führungssicke (11) zur Positionierung der Tellerfeder (9) aufweist und daß das erste Halteelement (4) mit der Tellerfeder (9) im nicht vorgespannten Zustand, in der Führungssicke (11) beginnend, einen in radialer Richtung nach außen geöffneten, V-förmigen Spalt (12) begrenzt.Fastening device according to claims 5 to 6, characterized in that the first holding element (4) has a guide bead (11) on the inside in the radial direction for positioning the plate spring (9) and that the first holding element (4) with the plate spring (9) does not preloaded state, starting in the guide bead (11), delimiting a V-shaped gap (12) which is open in the radial direction to the outside. Befestigungsvorrichtung nach Anspruch 1 bis 7, dadurch gekennzeichnet, daß der Federkörper (3) von der Außen- und/oder der Innenumfangsfläche in die Stützflächen (7, 8) umlenkend abgerundet ist.Fastening device according to claims 1 to 7, characterized in that the spring body (3) is rounded off in a deflecting manner from the outer and / or the inner peripheral surface into the support surfaces (7, 8). Befestigungsvorichtung nach Anspruch 1 bis 8, dadurch gekennzeichnet, daß der Federkörper (3) eine maximale Erstreckung in radialer Richtung aufweist, die die des ersten Halteelementes (4) nicht übersteigt.Fastening device according to claims 1 to 8, characterized in that the spring body (3) has a maximum extent in the radial direction which does not exceed that of the first holding element (4).
EP92105086A 1991-07-31 1992-03-25 Elastic supporting device for attaching a suction tube to an internal combustion engine Expired - Lifetime EP0529192B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4125249 1991-07-31
DE4125249A DE4125249C2 (en) 1991-07-31 1991-07-31 Elastic fastening device for connecting an intake pipe to an internal combustion engine

Publications (3)

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EP0529192A2 true EP0529192A2 (en) 1993-03-03
EP0529192A3 EP0529192A3 (en) 1993-05-05
EP0529192B1 EP0529192B1 (en) 1994-09-28

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EP92105086A Expired - Lifetime EP0529192B1 (en) 1991-07-31 1992-03-25 Elastic supporting device for attaching a suction tube to an internal combustion engine

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US (1) US5231957A (en)
EP (1) EP0529192B1 (en)
JP (1) JP2554226B2 (en)
DE (2) DE4125249C2 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110080914A (en) * 2018-01-25 2019-08-02 丰田自动车株式会社 The internal combustion engine of vehicle

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4413392C1 (en) * 1994-04-18 1995-06-08 Freudenberg Carl Fa Elastic attachment of supercharger to IC engine
DE4413393C1 (en) * 1994-04-18 1995-06-08 Freudenberg Carl Fa Elastic attachment of supercharger to engine
DE4436244C1 (en) * 1994-10-11 1996-02-08 Freudenberg Carl Fa Flexible support bearing for IC engine
DE19528047A1 (en) * 1995-07-31 1997-02-06 Bosch Gmbh Robert Internal combustion engine with an attached suction module or intake manifold and method for attaching an intake module or intake manifold to an internal combustion engine
DE102004007113B4 (en) * 2004-02-13 2007-06-28 Pierburg Gmbh Vibration decoupling system for an air intake duct system of an internal combustion engine
SE529284C2 (en) * 2005-11-14 2007-06-19 Johan Stenberg diaphragm Pump

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH448643A (en) * 1965-06-18 1967-12-15 Tech Fortschritt Mbh Ges Noise isolating pipe connection
EP0271811A1 (en) * 1986-12-18 1988-06-22 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Intake system for internal-combustion engines

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1343717A (en) * 1962-10-11 1963-11-22 Applic Ind Soc Et Car engine carburetor assembly
DE2317856A1 (en) * 1973-04-10 1974-11-28 Metzeler Gummitechnik BEARING BODY IN ELASTOMER METAL CONSTRUCTION
JPS54152883U (en) * 1978-04-14 1979-10-24
FR2505431B1 (en) * 1981-05-08 1986-05-02 Pineau Andre SHOCK ABSORBER AND / OR VIBRATION DEVICE BETWEEN A CARRIER ELEMENT AND A CARRIED ELEMENT
JPS5982567A (en) * 1982-11-02 1984-05-12 Honda Motor Co Ltd Suction system support construction for engine
DE3330817A1 (en) * 1983-08-26 1985-03-14 Holstein Und Kappert Gmbh, 4600 Dortmund DEVICE FOR READINESS REVIEW OF INSPECTION MACHINES
IL74976A (en) * 1985-04-21 1992-01-15 Popper Technologies Ltd Shock and vibration mount
JPS629041A (en) * 1985-07-05 1987-01-17 Toyota Motor Corp Vibration absorbing rubber device
KR900000143B1 (en) * 1985-10-04 1990-01-20 마쯔다 가부시기가이샤 Induction system for v-type internal combustion engine
DE3641811C1 (en) * 1986-12-06 1988-05-26 Porsche Ag Intake system for a preferably multi-cylinder internal combustion engine
US4776313A (en) * 1987-06-01 1988-10-11 Ford Motor Company Compact integrated engine induction air/fuel system
DE8716461U1 (en) * 1987-12-12 1988-02-18 Adam Opel AG, 6090 Rüsselsheim internal combustion engine
DE68917183T2 (en) * 1988-03-31 1995-03-09 Dunlop Ltd Elastic bearing.
JP2518930B2 (en) * 1989-07-24 1996-07-31 日産自動車株式会社 Internal combustion engine intake system
DE4116653A1 (en) * 1991-05-22 1992-11-26 Porsche Ag INTAKE SYSTEM FOR A MULTI-CYLINDER INTERNAL COMBUSTION ENGINE

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH448643A (en) * 1965-06-18 1967-12-15 Tech Fortschritt Mbh Ges Noise isolating pipe connection
EP0271811A1 (en) * 1986-12-18 1988-06-22 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Intake system for internal-combustion engines

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110080914A (en) * 2018-01-25 2019-08-02 丰田自动车株式会社 The internal combustion engine of vehicle
CN110080914B (en) * 2018-01-25 2021-01-26 丰田自动车株式会社 Internal combustion engine for vehicle

Also Published As

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JPH05231254A (en) 1993-09-07
DE4125249C2 (en) 1994-03-03
DE4125249A1 (en) 1993-02-04
DE59200563D1 (en) 1994-11-03
EP0529192B1 (en) 1994-09-28
US5231957A (en) 1993-08-03
JP2554226B2 (en) 1996-11-13
EP0529192A3 (en) 1993-05-05

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