DE4137692C1 - Hydraulically damping support mounting with outer and inner portions - has wall part sealing bead between two chambers filled with damping medium. - Google Patents

Hydraulically damping support mounting with outer and inner portions - has wall part sealing bead between two chambers filled with damping medium.

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Publication number
DE4137692C1
DE4137692C1 DE19914137692 DE4137692A DE4137692C1 DE 4137692 C1 DE4137692 C1 DE 4137692C1 DE 19914137692 DE19914137692 DE 19914137692 DE 4137692 A DE4137692 A DE 4137692A DE 4137692 C1 DE4137692 C1 DE 4137692C1
Authority
DE
Germany
Prior art keywords
bearing
sealing bead
recess
chambers
wall part
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.)
Expired - Fee Related
Application number
DE19914137692
Other languages
German (de)
Inventor
Hubert Dipl.-Ing. 7076 Waldstetten De Bruehl
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BRUEHL, HUBERT, DIPL.-ING., 73550 WALDSTETTEN, DE
Original Assignee
Mercedes Benz AG
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Filing date
Publication date
Application filed by Mercedes Benz AG filed Critical Mercedes Benz AG
Priority to DE19914137692 priority Critical patent/DE4137692C1/en
Application granted granted Critical
Publication of DE4137692C1 publication Critical patent/DE4137692C1/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
    • F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
    • F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
    • F16F13/1481—Units of the bushing type, i.e. loaded predominantly radially characterised by features of plastic springs, e.g. presence of cavities or stiffeners; characterised by features of flexible walls of equilibration chambers, i.e. membranes
    • 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
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
    • F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
    • F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
    • F16F13/1463—Units of the bushing type, i.e. loaded predominantly radially characterised by features of passages between working chambers
    • 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
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
    • F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
    • F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
    • F16F13/1463—Units of the bushing type, i.e. loaded predominantly radially characterised by features of passages between working chambers
    • F16F13/1472—Valve elements to cope with over-pressure, e.g. lips
    • 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
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
    • F16F13/20—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper characterised by comprising also a pneumatic spring
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
    • B60G2204/41—Elastic mounts, e.g. bushings
    • B60G2204/4104—Bushings having modified rigidity in particular directions
    • B60G2204/41042—Bushings having modified rigidity in particular directions by using internal cam surfaces
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
    • B60G2204/42—Joints with cam surfaces
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
    • B60G2204/45—Stops limiting travel

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Combined Devices Of Dampers And Springs (AREA)

Abstract

An overflow channel connects the two chambers, and in the area of both chambers, integrated in the cover, an intermediate pipe having window-type recesses extends in the mounting peripheral direction. In the pipe is arranged a stop formed as a sealing bead and built on an elastomer wall part of the overflow channel, which opens dependent upon the chamber hydraulic pressure. The wall part with the sealing bead (38) limits a recess filled with gas in a bed-type deepened formation (44) of the intermediate pipe cover section (30'). The same wall part (40) is stressed in the closure direction by a spring element integrated in the elastomer body. (14). USE/ADVANTAGE - For engine and machinery port support,with the bead closing force independent of support deflections in reproducible manner.

Description

Die Erfindung betrifft ein hydraulisch dämpfendes Lager mit den Merkmalen des Oberbegriffes des Patentanspruches 1.The invention relates to a hydraulically damping bearing with the Features of the preamble of claim 1.

Ein Lager dieser Art ist aus der DE 38 10 309 A1 bereits be­ kannt. Auch bei dieser bekannten Lösung ist zwischen den Kam­ mern ein Überströmkanal vorgesehen, der in Abhängigkeit von Druckunterschieden in den Kammern öffnet, um bei Schwingungen mit großen Amplituden zu große Druckunterschiede, und mit die­ sen korrespondierende Lagerverhärtungen zu vermeiden. Der Über­ strömkanal ist hierzu durch ein Sperrglied in Form eines Dicht­ wulstes gesteuert.A bearing of this type is already be DE 38 10 309 A1 knows. Even with this known solution is between the Kam An overflow channel is provided, which is a function of Differences in pressure in the chambers opens to vibrations with large amplitudes too large pressure differences, and with the to avoid corresponding bearing hardening. The About Flow channel is for this purpose by a locking member in the form of a seal bead controlled.

Liegt dabei, wie in einer ersten Ausführungsform vorgeschlagen, der Überströmkanal zwischen Elastomerkörper und äußerem Lager­ teil, so liegt die als Sperrglied verwendete Dichtlippe unter radialer Vorspannung am Innenumfang des äußeren Lagerteils an. Bei entsprechenden Druckdifferenzen wird die Dichtlippe in Er­ streckungsrichtung des Überströmkanales ausgelenkt. Ihre Rück­ kehr in die ursprüngliche Sperrlage ist aufgrund der radialen Vorspannung nicht eindeutig reproduzierbar, zumal auch radiale Auslenkungen des Lagers senkrecht zum Überströmkanal den Grad der Vorspannung beeinflussen.As suggested in a first embodiment, the overflow channel between the elastomer body and the outer bearing part, so is the sealing lip used as a locking member below radial preload on the inner circumference of the outer bearing part. With corresponding pressure differences, the sealing lip becomes Er direction of extension of the overflow channel deflected. Your return return to the original blocking position is due to the radial Preload not clearly reproducible, especially radial Deflections of the bearing perpendicular to the overflow channel the degree affect the preload.

Erstreckt sich der Überströmkanal, wie in einer weiteren Aus­ führungsform vorgeschlagen, tangential zum inneren Lagerteil quer durch den Elastomerkörper, so ergeben Radialauslenkungen des Lagers senkrecht zum Überströmkanal Unterschiede in der Vorspannung mit der Folge entsprechender Schwankungen der Schließkraft des als Dichtlippe verwendeten Sperrgliedes.Extends the overflow channel, as in another Aus leadership proposed, tangential to the inner bearing part across the elastomer body, so there are radial deflections  of the bearing perpendicular to the overflow channel Preload with the consequence of corresponding fluctuations in the Closing force of the locking member used as a sealing lip.

Bei einer weiteren bekannten Konstruktion (US-PS 48 83 260) sind die einander gegenüberliegenden Kammern durch Teile eines Elastomerkörpers gebildet, die gegenüber dem Lagerinnenteil die Kammern verbindende Drosselkanäle begrenzen. In dem Elastomer­ körper sind parallel zu den Drosselkanälen verlaufende, mit der Atmosphäre verbundene Ausnehmungen vorgesehen, so daß die dem Lagerinnenteil gegenüberliegenden Drosselkanalwandungen gegen Atmosphärendruck radial verformbar sind. Der Drosselweg ist dadurch druckabhängig und zusätzlich auch in Abhängigkeit von der belastungsabhängigen Lage der Lagerteile zueinander quer­ schnittsveränderlich.In another known construction (US-PS 48 83 260) are the opposite chambers by parts of one Elastomeric body formed, the opposite of the bearing inner part Limit throttle channels connecting chambers. In the elastomer bodies are parallel to the throttle channels, with the Recesses associated atmosphere provided so that the Opposing throttle channel walls against the inner bearing part Atmospheric pressure are radially deformable. The throttle path is therefore dependent on pressure and also dependent on the load-dependent position of the bearing parts transverse to each other changeable.

Der Erfindung liegt die Aufgabe zugrunde, ein Lager der ein­ gangs genannten Art dahingehend weiterzubilden, daß die Schließkraft des als Sperrglied verwendeten Dichtwulstes von Lagerauslenkungen im wesentlichen unabhängig und reproduzier­ bar festlegbar ist.The invention has for its object a bearing gangs mentioned in such a way that the Closing force of the sealing bead used as a locking member of Bearing deflections are essentially independent and reproducible can be fixed in cash.

Dies wird durch die kennzeichnenden Merkmale des Anspruches 1 erreicht, da über einen vorgegebenen Gasdruck das Ansprechver­ halten des Sperrgliedes entsprechend gesteuert werden kann und damit lageunabhängig ist.This is due to the characterizing features of claim 1 reached because the response ver keep the locking member can be controlled accordingly and so it is independent of position.

Weitere Merkmale der Erfindung ergeben sich aus den Unteran­ sprüchen.Further features of the invention result from the Unteran sayings.

In der Zeichnung ist ein Ausführungsbeispiel eines erfindungs­ gemäßen Lagers dargestellt. Es zeigen:In the drawing is an embodiment of an Invention according to the camp. Show it:

Fig. 1 einen Längsschnitt des Lagers, entlang der Linie I-I der Fig. 2 gesehen,Seen a longitudinal sectional view of the bearing taken along the line II of Fig. 2 Fig. 1,

Fig. 2 einen Querschnitt des Lagers, entlang der Linie II-II der Fig. 1 gesehen und um 90° gedreht, wo­ bei sich das Sperrglied des Überströmkanals in seiner Schließstellung befindet, Fig. 2 seen a cross-section of the bearing, taken along the line II-II of Fig. 1 and rotated through 90 °, where the locking member of the transfer passage is at in its closed position,

Fig. 3 einen Längsschnitt des Lagers, entlang der Linie III-III der Fig. 2 gesehen, Fig. 3 seen a longitudinal sectional view of the bearing taken along the line III-III of Fig. 2,

Fig. 4 einen Ausschnitt der Fig. 2, wobei das Sperrglied des Überströmkanals in eine Offenstellung zu­ rückgedrückt ist, Fig. 4 shows a detail of Fig. 2, wherein the locking member of the overflow channel is pressed back into an open position to,

Fig. 5 und 6 jeweils einen Ausschnitt des Lagers ähnlich Fig. 4, zur Veranschaulichung von Konstruktions­ varianten,, Variants Fig. 5 and 6 each show a section of the bearing similar to FIG. 4 for illustration of construction,

Fig. 7 einen Schnitt entlang der Linie VII-VII der Fig. 6 und Fig. 7 is a section along the line VII-VII of Fig. 6 and

Fig. 8 einen Teillängsschnitt durch ein Lager ähnlich Fig. 3 zur Veranschaulichung einer Konstrukti­ onsvariante des im Gummikörper vorgesehenen Kanals zur Beaufschlagung des Dichtwulstes. Fig. 8 is a partial longitudinal section through a bearing similar to FIG. 3 to illustrate a construction variant of the provided in the rubber body channel to act on the sealing bead.

Das gezeigte Lager weist einen äußeren, hohlzylindrischen La­ gerteil 10 und einen inneren, hülsenförmigen Lagerteil 12 auf, der mit seinen Endstücken vorzugsweise über die Stirnenden des äußeren Lagerteils 10 übersteht.The bearing shown has an outer, hollow cylindrical La gerteil 10 and an inner, sleeve-shaped bearing part 12 , which preferably protrudes with its end pieces over the front ends of the outer bearing part 10 .

Zwischen beide Lagerteile 10 und 12 ist ein Gummikörper 14 einvulkanisiert. In diesen sind, einander diametral gegenüber­ liegend, vorzugsweise von dessen Außenumfang her, zwei Vertie­ fungen eingeformt, die zusammen mit dem sie überdeckenden, äu­ ßeren Lagerteil 10 nach außen abgeschlossene Kammern 16 und 18 bilden.A rubber body 14 is vulcanized between the two bearing parts 10 and 12 . In these, diametrically opposite one another, preferably from its outer circumference, two recesses are formed which, together with the outer bearing part 10 covering them, form closed chambers 16 and 18 to the outside.

Wie Fig. 1 zeigt, sind die jeweils einer Lagerstirnseite zuge­ kehrten Kammerwände 20 und 22 vorzugsweise rollbalgartig bzw. teilringförmig nach außen ausgewölbt ausgebildet.As shown in FIG. 1, the chamber walls 20 and 22 each facing a bearing end face are preferably bulged outward in the manner of a bellows or a partial ring.

Die sich zwischen diesen Kammerwänden 20 und 22 befindenden Mantelabschnitte 12′, 12′′ des inneren Lagerteils 12 sind in Richtung auf die jeweils benachbarte Kammer 16 bzw. 18 gewölbt, wodurch auch die mit diesen Mantelabschnitten 12′, 12′′ verbun­ denen Kammerböden 24 bzw. 26 in das Kammerinnere eingewölbt sind. Diese bilden hierbei zugleich auf dem inneren Lagerteil 12 sitzende, am äußeren Lagerteil 10 anschlagbare Anschlagpuf­ fer, die in der die Kammern 16 und 18 enthaltenden Querebene a-a die möglichen Radialwege zwischen beiden Lagerteilen 10 und 12 begrenzen.The located between these chamber walls 20 and 22 jacket sections 12 ', 12 ''of the inner bearing part 12 are curved in the direction of the respective adjacent chamber 16 and 18 , whereby also with these jacket sections 12 ', 12 '' verbun which chamber floors 24th or 26 are arched into the interior of the chamber. These form at the same time on the inner bearing part 12 seated on the outer bearing part 10 abutment buffer fer, which limit the possible radial paths between the two bearing parts 10 and 12 in the transverse plane aa containing the chambers 16 and 18 .

Beide Kammern 16 und 18 sind über einen Drosselkanal 28 mitein­ ander verbunden, der, zur Erzielung einer entsprechend großen Kanallänge, zwischen dem äußeren Lagerteil 10 und einem in den Gummikörper 14 koaxial einvulkanisierten Zwischenrohr 30, gemäß Fig. 2, senkrecht zur Zeichenebene beispielsweise mäanderförmig verläuft. Die einzelnen Kanalabschnitte sind mit 28′ bezeichnet. Im Bereich der beiden Kammern 16 und 18 ist das Zwischenrohr 30 mit fensterartigen Ausnehmungen 32 und 34 aus­ gestattet.Both chambers 16 and 18 are connected to each other via a throttle channel 28 , which, in order to achieve a correspondingly large channel length, runs between the outer bearing part 10 and an intermediate tube 30 vulcanized coaxially into the rubber body 14 , according to FIG. 2, perpendicular to the plane of the drawing, for example in a meandering manner . The individual channel sections are designated 28 '. In the area of the two chambers 16 and 18 , the intermediate tube 30 with window-like recesses 32 and 34 is permitted.

Wie aus Fig. 2 zu ersehen ist, bildet der Gummikörper 14 zwi­ schen beiden Kammern 16 und 18 sich zwischen innerem Lagerteil 12 und Zwischenrohr 30 bzw. zwischen letzterem und äußerem La­ gerteil 10 erstreckende Verbindungsstege 14′ und 14′′.As can be seen from Fig. 2, the rubber body 14 forms between the two chambers 16 and 18 between the inner bearing part 12 and intermediate tube 30 or between the latter and outer La gerteil 10 extending connecting webs 14 'and 14 ''.

Die im vorstehenden Umfang beschriebene Lagerkonstruktion er­ möglicht durch die nach außen gewölbte Gestaltung ihrer lager­ stirnseitigen Kammerwände 20 und 22 eine entsprechend große Axialnachgiebigkeit, indem sich diese Kammerwände 20 und 22 bei entsprechenden Relativverlagerung beider Lagerteile 10 und 12 zueinander rollbalgartig verhalten und somit Rückstellkräfte lediglich durch die dabei auf Schub beanspruchten Verbindungs­ stege 14′, 14′′ des Gummikörpers 14 aufgebracht werden.The bearing construction described in the above scope enables it by the outwardly curved design of its bearing end chamber walls 20 and 22 a correspondingly large axial compliance by these chamber walls 20 and 22 with a corresponding relative displacement of the two bearing parts 10 and 12 behave like a bellows and thus restoring forces only by thereby stressed connecting webs 14 ', 14 ''of the rubber body 14 are applied.

Zugleich ermöglicht die Ausbildung der Kammerwände 20 und 22 eine verhältnismäßig große kardanische Lagerbeweglichkeit in der die Kammern 16 und 18 enthaltenden Lager-Quermittenebene über einen Winkelbereich α (siehe Fig. 1). At the same time, the design of the chamber walls 20 and 22 enables a relatively large cardanic bearing mobility in the transverse transverse plane of the bearing containing the chambers 16 and 18 over an angular range α (see FIG. 1).

Wie aus den Fig. 2 und 7 zu ersehen ist, sind beide Kammern 16 und 18 noch über einen verhältnismäßig breiten Überströmkanal 36 miteinander verbindbar, der sich, dem Drosselkanal 28 dia­ metral gegenüberliegend, zwischen dem äußeren Lagerteil 10 und einem Mantelabschnitt 30′ des Zwischenrohres 30 in Lagerum­ fangsrichtung erstreckt.As can be seen from FIGS. 2 and 7, both chambers 16 and 18 can still be connected to one another via a relatively wide overflow channel 36 , which is diametrically opposed to the throttle channel 28 , between the outer bearing part 10 and a jacket section 30 'of the intermediate tube 30 extends in the circumferential direction.

Innerhalb des Überströmkanals 36 ist ein quer zu dessen Längs­ erstreckung bewegliches Sperrglied, in Form eines den Überströmkanal 36 verschließenden, leistenartigen Dichtwulstes 38 angeordnet, der vorzugsweise teilkreisförmigen Querschnitt hat.Arranged within the overflow channel 36 is a locking member which is movable transversely to its longitudinal extension, in the form of a strip-like sealing bead 38 which closes the overflow channel 36 and which preferably has a part-circular cross section.

Dieser Dichtwulst 38 ist an einen vorzugsweise radial nach au­ ßen gewölbten Wandteil 40 einer in den Gummikörper 14 einge­ formten Ausnehmung angeformt und wird unter entsprechender Vorspannung in seiner Schließstellung gehalten. Die Ausnehmung bildet im vorliegenden Fall beispielsweise einen im Querschnitt flach-ovalen Kanal 42, der den Gummikörper 14 bzw. dessen Ver­ bindungssteg 14′′ zwischen äußerem Lagerteil und Zwischenrohr 30 in Lagerachsrichtung durchsetzt. Alternativ könnte die Ausnehmung aber auch eine gasgefüllte Kammer bilden.This sealing bead 38 is integrally formed on a preferably radially outwardly curved wall part 40 of a recess formed in the rubber body 14 and is held in its closed position under appropriate pretension. The recess forms in the present case, for example, a cross-sectionally flat-oval channel 42 which passes through the rubber body 14 or its connecting web 14 '' between the outer bearing part and the intermediate tube 30 in the direction of the bearing axis. Alternatively, the recess could also form a gas-filled chamber.

Eine solche Kammer kann geschlossen ausgebildet sein. Eine vor­ teilhafte Weiterbildung kann dabei, gemäß Fig. 8, darin beste­ hen, der mit 48 bezeichneten Kammer über eine in den Gummikör­ per 14 dichtend eingepreßte oder ggfs. eingeklebte Leitung 50 ein Druckmedium vorzugsweise Druckluft, zuzuführen. Dies kann vorteilhaft in Abhängigkeit mindestens eines Betriebsparameters eines Fahrzeuges selbsttätig erfolgen, so daß die Vorspannung des Dichtwulstes 38 entsprechenden Fahrzuständen oder Geschwin­ digkeitsbereichen angepaßt wird. Such a chamber can be closed. 8, in this case, according to FIG. 8, the best is to supply a pressure medium, preferably compressed air, to the chamber denoted by 48 via a line 50, which is press-fit or possibly glued into the rubber body by 14 . This can advantageously take place automatically as a function of at least one operating parameter of a vehicle, so that the prestressing of the sealing bead 38 is adapted to corresponding driving conditions or speed ranges.

Wie die Fig. 2 und 4 zeigen, überspannt der den Dichtwulst 38 tragende Wandteil 40 eine in den Mantelabschnitt 30′ des Zwi­ schenrohres 30 eingeformte, bettartige Vertiefung 44, die den Kanal 42 aufnimmt.As shown in FIGS. 2 and 4, the sealing bead 38 spans the supporting wall portion 40 a in the skirt portion 30 'of the interim rule tube 30 formed therein, bed-like recess 44 that receives the channel 42.

Die Anordnung des mit einem als Ventilglied arbeitenden Dicht­ wulst 38 ausgestatteten Überströmkanals 36 stellt sicher, daß sich bei Schwingungen mit großer Amplitude, bzw. bei Über­ schreiten des Innendruckes einer der beiden Kammern 16 oder 18 über einen bestimmten Schwellenwert, eine unzulässig große dy­ namische Lagerverhärtung aufgrund eines entsprechend vergrö­ ßerten Flüssigkeitsaustausches zwischen den Kammern 16 und 18 nicht einstellen wird.The arrangement of the overflow channel 36 equipped with a sealing bead 38 working as a valve member ensures that in the case of vibrations with a large amplitude or when the internal pressure of one of the two chambers 16 or 18 exceeds a certain threshold value, an impermissibly large dynamic hardening of the bearing will not adjust due to a correspondingly enlarged liquid exchange between the chambers 16 and 18 .

Des weiteren bewirkt ein sich durch Lagererwärmung erhöhender Kammerdruck ein selbsttätiges Öffnen des Überströmkanals 36 zwecks eines Druckausgleichs, woraus wiederum eine entspre­ chende Verminderung der Lagertemperatur resultiert.Furthermore, a chamber pressure which increases due to bearing heating causes the overflow channel 36 to open automatically for the purpose of pressure equalization, which in turn results in a corresponding reduction in the bearing temperature.

Die bettartige Vertiefung 44 des Zwischenrohr-Mantelabschnittes 30′ stützt dabei den den Dichtwulst 38 tragenden, den weiteren Kanal 42 begrenzenden, membranartigen Wandteil 40 seitlich derart ab, daß dieser bei einem wirksam werdenden, den Dicht­ wulst 38 in Öffnungsrichtung zurückdrückenden Kammerdruck ver­ stärkt vorgespannt wird.The bed-like recess 44 of the intermediate tubular jacket portion 30 'is supported thereby to the sealing bead bearing 38, the further channel 42 delimiting, membrane-like wall section 40 laterally in such a way from that this is biased ver strengthens at a becomes effective, the sealing bead 38 back pressing in the direction of opening chamber pressure .

Wie Fig. 5 zeigt, lassen sich dabei unterschiedliche Öffnungs­ drücke der Kammern 16 und 18 einfach und vorteilhaft durch entsprechende, außermittige Anordnung des Dichtwulstes 38 zur bettartigen Vertiefung 44 erreichen.As Fig. 5 shows, there can be different opening pressures of the chambers 16 and 18 simply and advantageously by corresponding eccentric arrangement reach the sealing bead 38 to the bed-like recess 44.

Die Vorspannung des Dichtwulstes 38 zu dessen selbsttätiger Rückstellung in die Schließlage läßt sich, wie die Fig. 6 und 7 zeigen, vorteilhaft verstärken durch ein in den Wandteil 40 einvulkanisiertes, beispielsweise durch eine Blattfeder gebil­ detes Federelement 46. Alternativ hierzu könnte dasselbe auch auf die rückseitige Fläche des membranartigen Wandteils 40 wirken, wozu es in den Kanal 42 einzusetzen oder an die rückseitige Wandteilfläche anzuvulkanisieren wäre.The bias of the sealing bead 38 for its automatic return to the closed position can, as shown in FIGS. 6 and 7, advantageously be strengthened by a vulcanized into the wall part 40 , for example by a leaf spring formed spring element 46 . Alternatively, the same could also act on the rear surface of the membrane-like wall part 40 , for which purpose it would have to be inserted into the channel 42 or vulcanized onto the rear wall part surface.

Claims (7)

1. Hydraulisch dämpfendes Lager, mit einem äußeren Lagerteil, einem inneren Lagerteil, einem zwischen beiden angeordneten Elastomerkörper, mit mindestens zwei im Elastomerkörper ausge­ bildeten, in bezug auf eine Quermittenebene einander gegen­ überliegenden Kammern, die über wenigstens einen Drosselkanal miteinander verbunden und mit einem Dämpfungsmittel gefüllt sind, mit einem die Kammern miteinander verbindenden Über­ strömkanal, der sich zwischen dem äußeren Lagerteil und einem Mantelabschnitt eines in den Elastomerkörper integrierten und im Bereich beider Kammern in dessen Mantel eingeformte, fen­ sterartige Ausnehmungen aufweisenden Zwischenrohres in Lager­ umfangsrichtung erstreckt und in welchem ein in Abhängigkeit vom hydraulischen Druck der beaufschlagten Kammer öffnendes, als Dichtwulst ausgebildetes Sperrglied angeordnet ist, das an einen elastomeren Wandteil des Überströmkanales angeformt ist, dadurch gekennzeichnet, daß der den Dichtwulst (38) tragende Wandteil eine in einer bettartigen Vertiefung (44) des Zwischenrohr-Mantelabschnittes (30′) liegende, gasgefüllte Ausnehmung begrenzt.1. Hydraulically damping bearing, with an outer bearing part, an inner bearing part, an elastomer body arranged between the two, with at least two formed in the elastomer body, with respect to one another in a transverse center plane, opposite chambers which are connected to one another via at least one throttle channel and with a damping means are filled, with a connecting the chambers with each other via flow channel, which extends between the outer bearing part and a jacket section of an integrated in the elastomer body and molded in the region of both chambers in its jacket fen fen-like recesses intermediate tube in the bearing circumferential direction and in which a Dependent on the hydraulic pressure of the chamber being acted upon, a blocking member designed as a sealing bead is arranged, which is molded onto an elastomeric wall part of the overflow channel, characterized in that the Wa carrying the sealing bead ( 38 ) a gas-filled recess lying in a bed-like recess ( 44 ) of the intermediate tube jacket section ( 30 ') is delimited. 2. Lager nach Anspruch 1, dadurch gekennzeichnet, daß der den Dichtwulst (38) tragende Wandteil (40) mittels ei­ nes in den Elastomerkörper (14) integrierten Federelementes (46) in Schließrichtung vorgespannt ist. 2. Bearing according to claim 1, characterized in that the sealing bead ( 38 ) carrying wall part ( 40 ) by means of egg nes in the elastomer body ( 14 ) integrated spring element ( 46 ) is biased in the closing direction. 3. Lager nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Ausnehmung eine in den Elastomerkörper (14) eingeform­ te, geschlossene gasgefüllte Kammer ist.3. Bearing according to claim 1 or 2, characterized in that the recess is a molded in the elastomer body ( 14 ) te, closed gas-filled chamber. 4. Lager nach Anspruch 3, dadurch gekennzeichnet, daß die Kammer (48) mit einer Druckquelle verbindbar ist.4. Bearing according to claim 3, characterized in that the chamber ( 48 ) can be connected to a pressure source. 5. Lager nach Anspruch 4, dadurch gekennzeichnet, daß der Kammerdruck parameterabhängig veränderbar ist.5. Bearing according to claim 4, characterized, that the chamber pressure can be changed depending on the parameters. 6. Lager nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Ausnehmung ein den Elastomerkörper (14) in Lagerachs­ richtung durchsetzender Kanal (42) ist.6. Bearing according to claim 1 or 2, characterized in that the recess is an elastomer body ( 14 ) in the bearing axis direction penetrating channel ( 42 ). 7. Lager nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Dichtwulst (38) mit Bezug auf die gasgefüllte Ausneh­ mung bzw. die bettartige Vertiefung (44) außermittig angeordnet ist.7. Bearing according to one of the preceding claims, characterized in that the sealing bead ( 38 ) with respect to the gas-filled recess or the bed-like recess ( 44 ) is arranged off-center.
DE19914137692 1991-11-15 1991-11-15 Hydraulically damping support mounting with outer and inner portions - has wall part sealing bead between two chambers filled with damping medium. Expired - Fee Related DE4137692C1 (en)

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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0645556A1 (en) * 1993-09-23 1995-03-29 Lemfoerder Metallwaren Ag. Rubber support bushing in a motor vehicle
FR2713731A1 (en) * 1993-12-09 1995-06-16 Hutchinson Anti=vibration hydraulic damper mount
FR2762654A1 (en) * 1997-04-28 1998-10-30 Hutchinson ANTI-VIBRATION DEVICE
WO1999054638A1 (en) * 1998-04-20 1999-10-28 Lord Corporation Mount and bonded component therefor with shape factor reducing notches
EP1046833A2 (en) * 1999-04-22 2000-10-25 Volkswagen Aktiengesellschaft Hydraulic support
FR2835898A1 (en) * 2002-02-12 2003-08-15 Michelin Avs HYDROELASTIC ARTICULATION WITH VARIABLE SECTION PRESSURE CHANNEL
DE10213627A1 (en) * 2002-03-27 2003-10-23 Zf Boge Gmbh Rubber bearing comprises tubular inner and outer sections, between which chambers filled with damping fluid are enclosed, chambers being connected by channels, at least one of which can be opened and closed
DE19526069B4 (en) * 1994-07-19 2006-01-26 Avon Vibration Management Systems Ltd., Chippenham Hydraulically damped storage facility
EP1770303A1 (en) * 2005-09-30 2007-04-04 Carl Freudenberg KG Elastomeric mounting with hydraulic damping
US7540478B2 (en) 2001-10-16 2009-06-02 Woco Avs Sas Hydroelastic ball joint
FR2926863A1 (en) * 2008-01-29 2009-07-31 Michelin Soc Tech Cylindrical hydro-elastic articulation for force transmission structure of motor vehicle, has channel extending in one of three free spaces disjointing from other two spaces and occupying radial distance between cage and external sleeve
FR2943393A1 (en) * 2009-03-18 2010-09-24 Porsche Ag HYDRAULIC BEARING
DE102013105326A1 (en) * 2013-05-23 2014-11-27 Trelleborgvibracoustic Gmbh Hydraulic bush
WO2018015064A1 (en) * 2016-07-19 2018-01-25 Vibracoustic Gmbh Hydraulically damping bearing

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3514268A1 (en) * 1985-04-19 1986-10-23 Metzeler Kautschuk GmbH, 8000 München PRELVETABLE AND HYDRAULIC DAMPED BEARING ELEMENT
EP0234966A1 (en) * 1986-01-22 1987-09-02 Automobiles Peugeot Hydro-elastic bushing
DE8714241U1 (en) * 1987-10-26 1987-12-10 Fa. Carl Freudenberg, 6940 Weinheim Sleeve rubber spring
US4790520A (en) * 1985-11-25 1988-12-13 Nissan Motor Co., Ltd. Vibration insulating device with flexible diaphragm between radially outer gas chamber and radially inner liquid chamber
DE3735698A1 (en) * 1987-10-22 1989-05-03 Freudenberg Carl Fa SLEEVE RUBBER SPRING
DE3805761A1 (en) * 1988-02-24 1989-09-07 Daimler Benz Ag HYDRAULIC DAMPING RUBBER BEARING
DE3810309A1 (en) * 1988-03-26 1989-10-12 Boge Ag HYDRAULIC DAMPING RUBBER BEARING
US4883260A (en) * 1987-09-16 1989-11-28 Tokai Rubber Industries, Ltd. Elastic bushing having fluid chamber filled with highly viscous fluid
EP0392909A1 (en) * 1989-04-10 1990-10-17 Caoutchouc Manufacture Et Plastiques Hydraulically damped elastic bushing with a radial elasticity and decoupling of the rigidity

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3514268A1 (en) * 1985-04-19 1986-10-23 Metzeler Kautschuk GmbH, 8000 München PRELVETABLE AND HYDRAULIC DAMPED BEARING ELEMENT
US4790520A (en) * 1985-11-25 1988-12-13 Nissan Motor Co., Ltd. Vibration insulating device with flexible diaphragm between radially outer gas chamber and radially inner liquid chamber
EP0234966A1 (en) * 1986-01-22 1987-09-02 Automobiles Peugeot Hydro-elastic bushing
US4883260A (en) * 1987-09-16 1989-11-28 Tokai Rubber Industries, Ltd. Elastic bushing having fluid chamber filled with highly viscous fluid
DE3735698A1 (en) * 1987-10-22 1989-05-03 Freudenberg Carl Fa SLEEVE RUBBER SPRING
DE8714241U1 (en) * 1987-10-26 1987-12-10 Fa. Carl Freudenberg, 6940 Weinheim Sleeve rubber spring
DE3805761A1 (en) * 1988-02-24 1989-09-07 Daimler Benz Ag HYDRAULIC DAMPING RUBBER BEARING
DE3810309A1 (en) * 1988-03-26 1989-10-12 Boge Ag HYDRAULIC DAMPING RUBBER BEARING
EP0392909A1 (en) * 1989-04-10 1990-10-17 Caoutchouc Manufacture Et Plastiques Hydraulically damped elastic bushing with a radial elasticity and decoupling of the rigidity

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0645556A1 (en) * 1993-09-23 1995-03-29 Lemfoerder Metallwaren Ag. Rubber support bushing in a motor vehicle
FR2713731A1 (en) * 1993-12-09 1995-06-16 Hutchinson Anti=vibration hydraulic damper mount
DE19526069B4 (en) * 1994-07-19 2006-01-26 Avon Vibration Management Systems Ltd., Chippenham Hydraulically damped storage facility
FR2762654A1 (en) * 1997-04-28 1998-10-30 Hutchinson ANTI-VIBRATION DEVICE
EP0875692A1 (en) * 1997-04-28 1998-11-04 Hutchinson Damping device
WO1999054638A1 (en) * 1998-04-20 1999-10-28 Lord Corporation Mount and bonded component therefor with shape factor reducing notches
US6105944A (en) * 1998-04-20 2000-08-22 Lord Corporation Mount and bonded component therefor with shape factor reducing notches
EP1046833A2 (en) * 1999-04-22 2000-10-25 Volkswagen Aktiengesellschaft Hydraulic support
DE19918350A1 (en) * 1999-04-22 2000-10-26 Volkswagen Ag Hydro bearing
EP1046833A3 (en) * 1999-04-22 2001-05-16 Volkswagen Aktiengesellschaft Hydraulic support
US7540478B2 (en) 2001-10-16 2009-06-02 Woco Avs Sas Hydroelastic ball joint
WO2003069184A3 (en) * 2002-02-12 2004-04-15 Michelin Avs Hydroelastic joint with a suppression channel having a variable cross section
WO2003069184A2 (en) * 2002-02-12 2003-08-21 Woco Avs Sas Hydroelastic joint with a suppression channel having a variable cross section
FR2835898A1 (en) * 2002-02-12 2003-08-15 Michelin Avs HYDROELASTIC ARTICULATION WITH VARIABLE SECTION PRESSURE CHANNEL
DE10213627A1 (en) * 2002-03-27 2003-10-23 Zf Boge Gmbh Rubber bearing comprises tubular inner and outer sections, between which chambers filled with damping fluid are enclosed, chambers being connected by channels, at least one of which can be opened and closed
DE10213627B4 (en) * 2002-03-27 2012-04-05 Zf Boge Elastmetall Gmbh Hydraulically damping rubber mount
EP1770303A1 (en) * 2005-09-30 2007-04-04 Carl Freudenberg KG Elastomeric mounting with hydraulic damping
FR2926863A1 (en) * 2008-01-29 2009-07-31 Michelin Soc Tech Cylindrical hydro-elastic articulation for force transmission structure of motor vehicle, has channel extending in one of three free spaces disjointing from other two spaces and occupying radial distance between cage and external sleeve
FR2943393A1 (en) * 2009-03-18 2010-09-24 Porsche Ag HYDRAULIC BEARING
DE102013105326A1 (en) * 2013-05-23 2014-11-27 Trelleborgvibracoustic Gmbh Hydraulic bush
DE102013105326B4 (en) * 2013-05-23 2015-11-12 Trelleborgvibracoustic Gmbh Hydraulic bush
WO2018015064A1 (en) * 2016-07-19 2018-01-25 Vibracoustic Gmbh Hydraulically damping bearing
CN109477542A (en) * 2016-07-19 2019-03-15 威巴克公司 Hydraulic damping bearing
DE102016113309B4 (en) * 2016-07-19 2020-07-23 Vibracoustic Gmbh Hydraulically damping bearing

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