EP3224498A1 - Palier hydraulique et véhicule à moteur équipé d'un tel palier hydraulique - Google Patents

Palier hydraulique et véhicule à moteur équipé d'un tel palier hydraulique

Info

Publication number
EP3224498A1
EP3224498A1 EP15770899.1A EP15770899A EP3224498A1 EP 3224498 A1 EP3224498 A1 EP 3224498A1 EP 15770899 A EP15770899 A EP 15770899A EP 3224498 A1 EP3224498 A1 EP 3224498A1
Authority
EP
European Patent Office
Prior art keywords
bypass channel
hydraulic bearing
passage
valve
hydraulic
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.)
Withdrawn
Application number
EP15770899.1A
Other languages
German (de)
English (en)
Inventor
Meinert Holst
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.)
ContiTech Vibration Control GmbH
Original Assignee
ContiTech Vibration Control GmbH
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 ContiTech Vibration Control GmbH filed Critical ContiTech Vibration Control GmbH
Publication of EP3224498A1 publication Critical patent/EP3224498A1/fr
Withdrawn legal-status Critical Current

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
    • 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
    • F16F13/26—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 characterised by adjusting or regulating devices responsive to exterior conditions
    • F16F13/262—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 characterised by adjusting or regulating devices responsive to exterior conditions changing geometry of passages between working and equilibration chambers, e.g. cross-sectional area or length

Definitions

  • the invention relates to a hydraulic bearing for transmitting power in a longitudinal direction of the hydraulic bearing, comprising an elastic suspension spring, a working chamber at least partially enclosed by the suspension spring, which is filled with a hydraulic fluid, a compensation chamber, and a throttle channel formed between the working chamber and the compensation chamber for the exchange of Hydraulic fluid, a bypass channel formed between the working chamber and the compensation chamber for the exchange of hydraulic fluid, and a valve associated with the bypass valve with at least one blocking means for blocking or opening of the bypass channel.
  • the invention relates to a motor vehicle comprising a vehicle frame, an engine and a motor bearing designed as a hydraulic bearing, which produces a bearing connection between the engine and the vehicle frame.
  • Hydraulic bearings which are also referred to as hydraulic bearings, are known from the prior art. They serve for the elastic support of aggregates, in particular motor vehicle engines. With the help of such, z. B. located between an engine and a chassis of the motor vehicle hydraulic bearings should be prevented
  • Vibrations of the engine are transmitted to the chassis, since the vibrations are often perceived by a passenger of the motor vehicle as unpleasant noises.
  • such hydraulic bearings usually have a rubber element as a suspension spring, which is also referred to as a supporting body, in conjunction with a hydraulic damper.
  • the rubber element is often designed as a hollow cone.
  • the suspension spring can thus form a jacket wall of the working chamber.
  • an upper cover is usually provided, to which a connection element for fixing the motor is attached.
  • the connecting element is for example a threaded bolt which can be screwed to the engine.
  • the hydraulic damper usually comprises at least two chambers, namely the said working chamber and the compensation chamber.
  • the compensation chamber In the longitudinal direction of the hydraulic bearing, the compensation chamber is usually arranged below the working chamber.
  • a partition wall can be arranged between the compensation chamber and the working chamber.
  • Throttle channel provided for the exchange of hydraulic fluid.
  • Throttle channel therefore obtains a hydraulic coupling between the working chamber and the compensation chamber.
  • the throttle channel is at least partially formed by the partition wall.
  • the throttle channel may also be formed separately from the partition wall.
  • the compensation chamber are at least partially and the throttle channel filled with hydraulic fluid.
  • the hydraulic fluid used is preferably a mixture of oil and water or a fluid with glycol.
  • Compensation chamber flows.
  • the throttle channel a flow resistance.
  • the flow through the appropriately designed throttle channel therefore generates dissipation and thus damping work.
  • the compensation chamber is preferably also configured elastically. So it can at least one membrane-like deformable wall part, in particular a
  • Rolling membrane have, so that the inflowing into the compensation chamber part of the hydraulic fluid can be accommodated.
  • Such a hydraulic bearing is known for example from the document DE 693 00 371 T2.
  • Hydraulic fluid from the working chamber through the throttle channel in the
  • bypass channel parallel to the throttle channel.
  • the bypass channel therefore extends from the working chamber to the compensation chamber, so that the two chambers are also hydraulically coupled by means of the bypass channel.
  • the bypass channel typically has a larger central passage area.
  • the blocking means can be moved from a corresponding blocking position to an open position, or vice versa.
  • the valve can thus open, block or reduce the passage cross-sectional area of the valve.
  • the valve when it is said that the valve is opened, it means at the same time that the bypass passage is opened, and vice versa.
  • the valve is locked, because in this case is also meant that the bypass channel is locked, and vice versa.
  • the valve is applicable to the
  • hydraulic bearing is used as an engine mount, it has proven to be advantageous in practice if the valve is closed while driving and is open in standby mode. With the opening of the valve, another frequency section is created within which vibrations are damped particularly well. So can the
  • valve switchable throttling units that implement an activation or blocking by means of a solenoid.
  • a solenoid Longitudinal direction of the bypass channel - ie parallel to the flow direction of a
  • Hydraulic fluid column moves in the bypass channel, in particular on the
  • Working chamber acts. To close the valve, the membrane is pressed over the entire circumference onto a matching valve seat of the valve, which then prevents the flow of hydraulic fluid. It is also known that diaphragms of the valves are switched via a vacuum supply. However, this is very expensive and expensive. For this purpose, a considerable larger space is also required.
  • the invention is therefore based on the object to provide a hydraulic bearing, in which the disadvantages mentioned are prevented or reduced.
  • a hydraulic bearing of the type mentioned is to be improved in such a way that the valve is adjustable even with an increased pressure in the working chamber with the lowest possible force between an open position and a closed position.
  • the object is achieved by the invention
  • Hydraulic bearing for transmitting power in a longitudinal direction of the hydraulic bearing, comprising an elastic suspension spring, a working chamber at least partially enclosed by the suspension spring, which is filled with a hydraulic fluid, a compensation chamber, and formed between the working chamber and the compensation chamber throttle channel for the exchange of hydraulic fluid between the working chamber and the compensation chamber trained bypass channel for the exchange of hydraulic fluid, and a the
  • By-pass valve associated with at least one blocking means for blocking or opening the bypass channel, wherein the blocking means is mounted such that the blocking means for blocking or opening the bypass channel transversely to a passage direction of the
  • Bypass channels can be moved on the valve
  • the invention is based on the idea of keeping the forces necessary for moving the blocking means as small as possible, even at a high pressure in the working chamber and / or the bypass channel. If the hydraulic fluid in the bypass passage is under high pressure, the hydraulic fluid exerts a force corresponding to the pressure, directed in the passage direction of the bypass passage, on the locking means. However, the blocking means is movably mounted transversely to the passage direction of the bypass channel. Thus, the aforementioned force acting on the blocking means is absorbed by a corresponding bearing of the blocking means. If, for example, a bearing in the manner of a linear guide is provided for the blocking means, the aforementioned force is absorbed by the linear guide.
  • the blocking means In order to move the blocking means, at least substantially only the frictional force resulting from the storage is to be overcome. However, this frictional force is only a small fraction of the aforementioned force.
  • the blocking means can be moved with particularly small forces in order to block or open the bypass channel. Due to the low force requirement, the locking means can be moved quickly with a particularly low power, which allows a quick change between an open state and a locked state of the valve or bypass channel.
  • a can
  • the blocking means may have any form of blocking means for a valve known from the prior art.
  • the locking means is also referred to in the art as a closure member. It is preferably provided that the
  • Blocking means as a slide, in particular throttle slide, is formed.
  • the locking means can be pushed as a slide over a valve seat of the valve to close the valve or the bypass channel or the valve seat by a method of the slide again partially or completely release the valve or the
  • the blocking means has a blocking surface which is designed to block the bypass channel, wherein the blocking means is mounted such that the blocking means for blocking or opening the bypass channel in at least one
  • Extension direction of the blocking surface is movable. If the bypass channel is blocked by the blocking means, a pressure acts on the blocking surface of the blocking means by the hydraulic fluid from the bypass channel.
  • the blocking surface of the blocking means is thus the region of the blocking means to which the hydraulic fluid from the bypass channel strikes and prevents it from continuing to flow.
  • the blocking surface extends perpendicular to a passage direction of the bypass channel on the valve. The pressure of the
  • Hydraulic fluid caused forces therefore act perpendicular to the blocking surface. If the blocking means is now in the extension direction of the blocking surface method, as explained above, at least substantially only the frictional forces of a bearing for the blocking means to overcome.
  • a further preferred embodiment of the hydraulic bearing is characterized in that the hydraulic bearing has an actuator which is mechanically coupled to the locking means to move the locking means.
  • the actuator is in particular an electromagnetic linear actuator and preferably a reluctance linear actuator.
  • other actuators in particular other electrical actuators, can be used. As particularly useful actuators have been found, each comprising a stator and an armature.
  • the armature is movably mounted to the stator, so that the armature can be deflected relative to the stator in the longitudinal direction of the actuator.
  • the armature and the locking means may be mechanically interconnected and / or coupled. It can be provided that the armature is not directly connected to the locking means, but that, for example, a hinge mechanism and / or a plunger are provided, which are arranged between the armature and the locking means to movements and / or forces from the armature to the Transfer blocking agent. Such a hinge mechanism and / or plunger is then assigned to the actuator.
  • a further preferred embodiment of the hydraulic bearing is characterized in that the hydraulic bearing has a return spring which is mechanically coupled to the locking means to move the locking means in a predetermined position.
  • valve or the bypass channel is preferably closed or opened.
  • the bypass channel is closed by the return spring, provided that the aforementioned actuator does not actively move the blocking means.
  • Compensation chamber of an elastic body in particular a rolling diaphragm, may be formed.
  • a rolling diaphragm is preferably formed as an annular body.
  • the radially inner end of the rolling diaphragm can be mechanically, in particular by means of an auxiliary means, connected to the locking means, wherein the rolling diaphragm forms the return spring for the locking means.
  • the rolling diaphragm can therefore also be designed to move the locking means transversely to the passage direction of the
  • the rolling diaphragm in this case would have a dual function.
  • the rolling diaphragm serves as an elastic wall for the compensation chamber in order to allow hydraulic fluid to flow from the working chamber into the compensation chamber, the volume of the compensation chamber being dimensioned by elastic deformation of the rolling diaphragm against the volume of hydraulic fluid to be received.
  • the rolling diaphragm as explained above, serve as a return spring for the locking means.
  • a further preferred embodiment of the hydraulic bearing is characterized in that the valve has at least one passage window for the bypass channel, and each passage window of the or one of the locking means can be closed. Since the valve is designed to open or block the bypass channel, hydraulic fluid which flows through the bypass channel also flows through the at least one passage window. If the at least one passage window is closed by the at least one blocking means, this prevents a flow of hydraulic fluid through the bypass channel. With the closing of the at least one passage window, the bypass channel can thus be blocked. With the opening of the at least one passage window, the bypass channel open. Each passage window may therefore have a valve seat for an associated one
  • Blocking means to allow the opening or locking of the bypass channel.
  • a further preferred embodiment of the hydraulic bearing is characterized in that the passage direction of the bypass channel is aligned on the valve in the transverse direction of the hydraulic bearing. Therefore, no forces caused by the pressure of the hydraulic fluid occur in the longitudinal direction of the hydraulic bearing on the valve or on the blocking means.
  • Such a configuration has proven to be advantageous in practice to ensure a compact design of the hydraulic bearing. Because the hydraulic bearing is primarily used for power transmission of forces in the longitudinal direction. To the appropriate
  • valves may be provided, wherein on the valves opposite transverse forces arise, which in a
  • Transverse direction of the hydraulic bearing is aligned.
  • the bypass channel has a plurality of openings, which are each aligned in the transverse direction of the hydraulic bearing.
  • transverse direction is meant a direction transverse to the longitudinal direction of the
  • Passage window of the valve to be closed by means of the blocking means do not occur in the longitudinal direction of the hydraulic bearing caused by the pressure of the hydraulic fluid in the bypass passage forces.
  • the analogous advantages, as explained in the previous section, therefore apply are.
  • the arrangement of the valve at the outlet openings to the compensation chamber can ensure a particularly compact design of the hydraulic bearing. Because in this section, the at least one blocking means of the valve can be designed to be movable in a particularly simple manner via the openings or the passage windows.
  • a further preferred embodiment of the hydraulic bearing is characterized in that the bypass channel in the region of its one end portion which encloses in the compensation chamber has shell-side openings which form the passage window of the valve, wherein the front end of the end portion is closed.
  • the hydraulic fluid can not leave the bypass passage at the end portion facing the balance chamber in the axial direction of the bypass passage, but flows through the shell side openings in the radial direction.
  • Such a configuration has proved to be particularly advantageous in practice to ensure that the hydraulic fluid flows in the transverse direction through the passage window of the valve in the compensation chamber, if the valve or the bypass channel is opened.
  • the bypass channel extends in the longitudinal direction of the hydraulic bearing from the working chamber to the compensation chamber.
  • the cross section of the bypass channel in the region of the valve is larger, preferably significantly larger than the average cross section of the remaining bypass channel.
  • the passage windows have a small extent in the axial direction of the bypass channel, so that only a small stroke for the at least one blocking means for opening or closing the valve or the bypass channel necessary is. In other words, the bypass channel can be opened or closed particularly quickly.
  • Hydraulic bearing is movable. In other words, that or the locking means are stored in the longitudinal direction of the hydraulic bearing.
  • the blocking means may be provided a common actuator for the process. This reduces the complexity of the hydraulic bearing and also ensures a compact design. If one
  • Direction of the valve or the associated passage window is aligned in the transverse direction of the hydraulic bearing is or are, the aforementioned storage, to move the at least one blocking means for blocking or opening the bypass channel transversely to a passage direction of the bypass channel on the valve.
  • a further preferred embodiment of the hydraulic bearing is characterized in that the valve has a plurality of passage windows for the bypass channel, which are arranged next to each other at a distance from each other. The entire passage cross section of the valve is thus determined from the sum of the passage cross sections of the passage window.
  • a further preferred embodiment of the hydraulic bearing is characterized in that the valve has a plurality of locking means, wherein each passage window is associated with at least one locking means.
  • each transmission window is assigned a blocking means.
  • a blocking window is assigned a plurality of blocking means.
  • a further preferred embodiment of the hydraulic bearing is characterized in that a common blocking means is assigned to a plurality of passage windows.
  • Hydraulic bearing can serve as a throttle valve.
  • a further preferred embodiment of the hydraulic bearing is characterized in that webs are arranged between the passage windows, and the passage windows and the webs form a ring or a ring section.
  • the valve can be designed to be particularly compact.
  • the aforementioned ring or ring portion may form a portion of a preferably cylindrical jacket wall of the bypass channel.
  • Passage windows then form openings in the cylindrical jacket wall of the bypass channel. To allow hydraulic fluid to flow through the bypass passage, the hydraulic fluid passes through the apertures in the passageway
  • the blocking means for opening or closing the passage windows are preferably arranged on the jacket wall of the bypass channel, so that they are moved transversely to a passage direction of the bypass channel on the valve. If the bypass channel is aligned in the longitudinal direction of the hydraulic bearing, the blocking means in the longitudinal direction of the hydraulic bearing for opening or closing of the
  • Bypass channels be stored movable.
  • a further preferred embodiment of the hydraulic bearing is characterized in that the at least one blocking means is designed as a ring, a ring portion, a cup-shaped body or a crown-shaped body.
  • the blocking means for example as a ring or as a ring section, can then be moved in parallel over a plurality of passage windows of the valve in order to open, close or partially close them at the same time. It has proven to be particularly advantageous to arrange the passage windows next to one another to form a ring, wherein the passage window of the closed ring designed as a blocking means can be moved over this ring, so that the
  • Passage window can be opened, closed or partially closed with a single blocking means.
  • this blocking agent only one actuator is necessary.
  • a hydraulic bearing with such a configuration is particularly compact and easy to design.
  • the blocking means is designed as a crown-shaped body, the blocking means can be in the circumferential direction and / or in the axial direction method to open the passage window to close or partially close.
  • Corresponding to the recesses between the crown tips webs may be provided between the passage windows.
  • a further preferred embodiment of the hydraulic bearing is characterized in that a cross-sectional area of the bypass channel in the region of an end section adjoining the compensation chamber is greater than a mean cross-sectional area of the remaining region of the bypass channel.
  • the cross section of the bypass channel in the region of an end section adjoining the compensation chamber is greater than a mean cross-sectional area of the remaining region of the bypass channel.
  • Bypass channels in an adjoining the compensation chamber end portion This also reduces the flow velocity of the hydraulic fluid which flows through the bypass channel in said region.
  • the compensation channel is exposed to a lower hydraulic load, which increases the life of the hydraulic bearing.
  • a motor vehicle which comprises a vehicle frame, a motor and an engine mount which produces a bearing connection between the engine and the vehicle frame, wherein the engine mount is formed by a hydraulic bearing according to the invention.
  • Hydraulic bearing according to the invention are described, of course, also in Connection with the motor vehicle according to the invention and in each case vice versa, so that with respect to the disclosure of the individual aspects of the invention always reciprocal reference is or may be.
  • Fig. 1 is a schematic cross-sectional view of the hydraulic bearing.
  • FIG. 1 shows a hydraulic bearing 2 according to the invention.
  • the hydraulic bearing 2 comprises a designed as a rubber element support spring 36.
  • This suspension spring 36 is usually formed as a hollow body, wherein the upper side of the support spring 36 has a cover 38.
  • a connection element for attaching a motor is usually mounted on the cover 38.
  • the connection element is a threaded bolt or a bore which serves for screwing to the motor.
  • the partition wall 8 connects. Between the suspension spring 36, the cover 38 and the partition wall 8, the working chamber 4 is formed.
  • the working chamber 4 is with a
  • Hydraulic fluid filled This is preferably a mixture of oil and water.
  • the rolling diaphragm 25 In the longitudinal direction L below the partition wall 8 close the rolling diaphragm 25 and the hollow cylindrical base housing 40 at.
  • the rolling diaphragm 26 In the base housing 40, the rolling diaphragm 26 is inserted, which is made of elastic material. With its ring shape, the rolling diaphragm 26 forms a radially inner edge 28 and a radially outer edge 30. With the radially outer edge 30, the rolling diaphragm 26 between the
  • the rolling diaphragm 26 connects to a blocking means 18 of a valve 16 of the hydraulic bearing 2.
  • the rolling diaphragm 26 is annular on a flange 44 of the base housing 40.
  • the base housing 40 may be multi-part and / or fasteners for attachment to and / or transmission of forces to a vehicle body.
  • the trapped by the partition wall 8 and the rolling diaphragm 26 space forms the compensation chamber 6 of the hydraulic bearing 2.
  • the compensation chamber 6 is with
  • Hydraulic fluid filled which is preferably a mixture of oil and water. It can thus be seen from FIG. 1 that the dividing wall 8 is arranged between the working chamber 4 and the compensation chamber 6.
  • a throttle channel 10 formed between the working chamber 4 and the compensation chamber 6 is provided, which serves to exchange hydraulic fluid , As shown in Fig. 1, the throttle channel 10 is at least partially formed by the partition wall 8 or is enclosed in this.
  • the throttle channel 10 is at least partially annular, wherein the throttle channel 10 with an opening at one end of the ring to the
  • the throttle channel 10 has such a small Diameter and / or a long length on that dissipation or
  • the hydraulic bearing 2 has at least one control diaphragm 46, which is formed in fluid communication with the working chamber 4.
  • at least one control channel 48 is provided, which produces a hydraulic connection to the at least one control diaphragm 46.
  • the control diaphragm 46 in particular in the longitudinal direction L of the hydraulic bearing 2 can be deflected. In the case of higher-frequency vibrations, the control diaphragm 46 is excited by the hydraulic fluid to oscillations which are suitable for the high-frequency energy absorbed from outside
  • the control diaphragm 46 is, as previously presented, only to a limited extent for the isolation of vibrations that arise when idling a motor vehicle engine.
  • the throttle channel is used to attenuate low-frequency vibrations, wherein due to the length and / or diameter of the throttle channel 10 a limited frequency bandwidth is determined within the vibrations are effectively damped.
  • the hydraulic bearing 2 has the bypass channel 12.
  • the bypass channel 12 is hydraulically parallel to the
  • Throttle channel 10 is formed.
  • the bypass channel 12 extends at least in
  • the bypass channel 12 has a larger cross-section, as in the remaining part of the bypass channel 12. In other words, the cross-section widens
  • the compensation chamber 6 facing, frontal end 34 of the bypass channel 12 is closed. In this case, at least a part of the end portion 32 of a
  • Bypass channel 12 associated valve 16 may be formed.
  • the valve 16 may thus form an integral part of the bypass channel 12. If the valve 16 is open, can
  • valve 16 Hydraulic fluid flow between the working chamber 4 and the compensation chamber 6. If the valve 16 is closed, this also applies to the bypass channel 12. In other words, the bypass channel 12 can be locked or opened.
  • the valve 16 has a cylindrical blocking means 18.
  • the blocking means 18 in this case comprises a cylindrical ring section 52, whose one longitudinal axial end of a cover element 50
  • the locking means 18 is fixed to the radially inner edge 28 of the rolling diaphragm 26.
  • the area of the rolling diaphragm 26 between the radially inner edge 28 and the flange 44, on which the rolling diaphragm 46 flies, serves as the return spring 20 to the locking means 28 in the position to process, as shown in FIG.
  • This position of the locking means 18 is the blocking position of the locking means 18, with which the valve 16 and thus the bypass channel 12 is locked.
  • the cylindrical ring portion 52 of the locking means 18 closes the shell-side passage window 22 of the valve 16.
  • the passage window 22 are spaced apart from each other on a ring or a ring portion, arranged side by side. Between the passage windows 22 webs 42 are formed, which connect a shell-side wall of the valve 16 and the bypass channel 12 with the front end 34.
  • the blocking means 18 releases the openings 24 formed by the passage windows 22, so that hydraulic fluid can first flow from the working chamber 4 in the longitudinal direction L of the hydraulic bearing 2 through the bypass channel 12 until it meets the front end 34, at which a deflection in Transverse Q occurs, so that the hydraulic fluid then in the transverse direction Q through the openings 24 of
  • Passage window 22 flows into the compensation chamber 6.
  • the transverse direction Q means the at least one direction that is transverse to the longitudinal direction L of the hydraulic bearing.
  • the hydraulic fluid flows out of the bypass passage 12 in the radial direction.
  • the blocking means 18 has therefore been moved in the longitudinal direction L of the hydraulic bearing 2 in order to open the valve 16.
  • the blocking means 18 was thus moved transversely to a passage direction of the bypass channel 12 on the valve 16.
  • the valve 16, which is assigned to the bypass channel 12 a corresponding linear guide by means of a bearing.
  • This is preferably a sliding bearing between a radially inner side surface of the cylindrical annular portion 52 of the locking means 18 and a radially outer side wall of the passage window 22 of the valve 16 and a radially outer side wall of the end portion 32 of the bypass channel 12th
  • the blocking means 18 can be moved transversely to the passage direction of the bypass channel 12 on the valve 16 to open or block the bypass channel 12, the valve 16 can be opened or closed even at a high pressure in the working chamber 4.
  • Hydraulic fluid are caused in the bypass channel 12, are aligned transversely to the direction in which the locking means 18 movable.
  • Blocking means 18 are therefore only overcome by the frictional forces caused by the storage. This is enough for a small performance. Therefore, it is provided that the blocking means 18, at least supporting, by the rolling diaphragm 26 is movable into the blocking position. To open the valve 16 and the bypass channel 12, an actuator, not shown, may be provided, which is mechanically connected to the locking means 18 and this can be controlled in the longitudinal direction L of the hydraulic bearing 2.
  • the lid member 50 of the locking means 18 may have holes in the longitudinal direction L through which a fluid exchange between the compensation chamber 6 and a space formed between the lid member 50 and the front end 34 to enable. LIST OF REFERENCE NUMBERS

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

Abstract

L'invention concerne un palier hydraulique (2) pour le transfert de forces dans un sens longitudinal L du palier hydraulique (2), présentant un ressort de suspension élastique (36), une chambre de travail (4) au moins partiellement entourée par le ressort de suspension (36), qui est remplie d'un liquide hydraulique, une chambre de compensation (6), un canal d'étranglement réalisé entre la chambre de travail (4) et la chambre de compensation (6) pour l'échange du liquide hydraulique, un canal de dérivation (12) réalisé entre la chambre de travail (4) et la chambre de compensation (6) pour l'échange du liquide hydraulique et une soupape (16) associée au canal de dérivation (12) présentant au moins un moyen de blocage (18) pour bloquer ou ouvrir le canal de dérivation (12), le moyen de blocage (18) étant logé de manière telle que le moyen de blocage (18) peut être déplacé, en vue du blocage ou de l'ouverture du canal de dérivation (12), transversalement par rapport à une direction de passage du canal de dérivation (12) au niveau de la soupape (16). L'invention concerne également un véhicule comprenant un tel palier hydraulique (2).
EP15770899.1A 2014-11-27 2015-09-29 Palier hydraulique et véhicule à moteur équipé d'un tel palier hydraulique Withdrawn EP3224498A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014224244.4A DE102014224244A1 (de) 2014-11-27 2014-11-27 Hydrolager sowie Kraftfahrzeug mit einem derartigen Hydrolager
PCT/EP2015/072308 WO2016082987A1 (fr) 2014-11-27 2015-09-29 Palier hydraulique et véhicule à moteur équipé d'un tel palier hydraulique

Publications (1)

Publication Number Publication Date
EP3224498A1 true EP3224498A1 (fr) 2017-10-04

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP15770899.1A Withdrawn EP3224498A1 (fr) 2014-11-27 2015-09-29 Palier hydraulique et véhicule à moteur équipé d'un tel palier hydraulique

Country Status (4)

Country Link
EP (1) EP3224498A1 (fr)
CN (1) CN208845627U (fr)
DE (1) DE102014224244A1 (fr)
WO (1) WO2016082987A1 (fr)

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DE102016110703A1 (de) * 2016-06-10 2017-12-14 Vibracoustic Gmbh Hydrolager
DE102017103603B4 (de) 2017-02-22 2023-03-16 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Hydrolager zur Lagerung eines Aggregats eines Kraftfahrzeugs
DE102017007999A1 (de) 2017-08-24 2019-02-28 Sumitomo Riko Company Limited Schaltbares Hydrolager
DE102019003604B4 (de) * 2019-05-22 2022-03-31 Sumitomo Riko Company Limited Schaltbares Hydrolager
KR20210125645A (ko) 2020-04-08 2021-10-19 현대자동차주식회사 엔진 마운트

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DE102014224244A1 (de) 2016-06-02
CN208845627U (zh) 2019-05-10

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