DE102011120305B4 - Anti-vibration bearing for a motor vehicle - Google Patents

Abstract

Vibration-damping bearing (10) for a motor vehicle, comprising - an elastomer body (12); - at least one chamber (14), which is introduced into the elastomer body (12) and is filled with a magnetorheological fluid (16), and - means (18) for producing a Magnetic field in the chamber (14), characterized in that a damper mass (20) which can be deflected in the main damping direction (s) of the bearing (10) is arranged in the at least one chamber (14) and that the means (18) for generating the magnetic field are arranged in this way are arranged so that when the magnetic field is generated, the magnetic field lines are oriented orthogonally to the main damping direction (s).

Description

The invention relates to a vibration-damping bearing for a motor vehicle, according to the type specified in the preamble of claim 1.

A generic bearing for a motor vehicle, which has a chamber filled with a magnetorheological fluid, hereinafter also referred to as MRF, and means for generating a magnetic field is shown in FIG EP 1 249 637 A1 disclosed. According to the teaching of EP 1 249 637 A1 It is provided that the MRF is excited to oscillate by means of an oscillating magnetic field in order to use the generated oscillating force effect to combat or suppress vibrations.

The invention has for its object to develop a vibration-damping bearing for a motor vehicle according to the type specified in the preamble of claim 1 such that vibration damping in a large frequency range is made possible.

This object is achieved by the characterizing features of claim 1 in conjunction with its preamble features.

The DE 197 11 689 A1 discloses an aggregate bearing, in particular for a motor vehicle, with at least one spring element and with fastening elements for connection to the parts to be stored. The bearing is characterized in that the spring element has a fluid chamber that is filled with a magnetorheological fluid, that at least one electromagnet is arranged outside and / or inside the fluid chamber in such a way that an increase in a magnetic field acting on the fluid of the electromagnet in question the viscosity of the fluid occurs from a liquid to a solid state, which leads to an increase in the spring rate of the aggregate bearing.

The subclaims form advantageous developments of the invention.

In a known manner, the vibration-damping bearing for a motor vehicle comprises an elastomer body having a chamber, the chamber being filled with a magnetorheological fluid (MRF). In addition, the bearing has means for generating a magnetic field in the chamber.

According to the invention, a damper mass which can be deflected in the main damping direction of the bearing is arranged in the at least one chamber, and the means for generating the magnetic field are arranged such that the magnetic field lines are oriented orthogonally to the main damping direction when the magnetic field is generated.

The design according to the invention now provides a bearing with an actively adjustable vibration damper in a simple manner: With the aid of a closed control loop, the damping characteristic can be changed by a corresponding change in the magnetic field and the associated change in the viscosity of the MRF in the chamber be adjusted to the underlying excitation vibration. Vibrations of different frequencies can thus advantageously be damped by the adjustability of the natural frequency that has now been implemented.

In the simplest case, the damper mass is plate-shaped and has several through openings. The absorber mass is arranged in the chamber in such a way that the passage openings are aligned in the direction of the main damping direction.

To tune the ideally damped frequency range, it can be advantageous to design the absorber mass differently in order to achieve the necessary absorber mass.

In order to ensure that the absorber mass is centered after a deflection of the bearing, the absorber mass is supported on the chamber walls by means of two spring assemblies when viewed in the main damping direction. The spring assemblies are to be designed so that they influence the absorber behavior as little as possible.

The means for generating the magnetic field are preferably designed as a coil concentrically surrounding the chamber. This can e.g. be vulcanized into the elastomer body. This on the one hand ensures a compact design and on the other hand enables simple control / regulation of the magnetic field.

According to a particularly advantageous embodiment of the invention, viewed in the main damping direction, two chambers are arranged in series. This advantageously enables improved vibration damping, since a larger tiger mass is available.

In this case, the two chambers are preferably fluidly communicating with one another via a throttle channel. In an advantageous manner, additional damping is now achieved when the bearing is deflected due to the fluid exchange taking place between the chambers.

Further advantages, features and possible uses of the present invention result from the following description in connection with the exemplary embodiments shown in the drawing.

In the description, in the claims and in the drawing, the terms and associated reference symbols used in the list of reference symbols given below are used.

• 1 eine erste Ausführungsform eines erfindungsgemäßen schwingungsdämpfenden Lagers, und
• 2 eine zweite Ausführungsform eines erfindungsgemäßen schwingungsdämpfenden Lagers.

In the drawing means:

• 1 a first embodiment of a vibration-damping bearing according to the invention, and
• 2nd a second embodiment of a vibration-damping bearing according to the invention.

1 shows a total with the reference number 10th designated vibration damping bearing for a motor vehicle. The main damping direction of the bearing is designated by the reference symbol s.

The anti-vibration bearing 10th has an elastomer body 12th on, inside a chamber 14 is trained.

The chamber 14 is with a magnetorheological fluid 16 - hereinafter abbreviated as MRF - filled and from a coil 18th concentrically enclosed so that by means of the coil 18th a magnetic field inside the chamber 14 can be generated, the magnetic field lines of which are oriented perpendicular to the main damping direction s.

How 1 is still in the chamber 14 an absorber mass 20 arranged such that it can swing in the main damping direction s. The absorber mass 20 is as a plate-shaped, several passage openings 22 having formed component.

The passage openings 22 are aligned in the direction of the main damping direction s, so that when the damper mass vibrates 20 through the openings 22 flowing MRF the vibration of the absorber mass 20 dampens.

In addition, the absorber mass 20 by means of two spring assemblies 24th held to after a deflection of the bearing 10th a centering of the absorber mass 20 to guarantee.

For active vibration damping, the excitation vibration of a component, e.g., not shown here for reasons of clarity, an attachment of a motor vehicle measured. For the sake of completeness, it should be pointed out that a separate sensor system can be dispensed with, e.g. further sensors in the motor vehicle already enable an estimation of the excitation vibration.

The natural frequency of the vibration system can be set with the aid of a control loop, which is likewise not shown here for reasons of clarity. This is done by changing the viscosity of the MRF accordingly, i.e. the strength of the magnetic field. The flow resistance, like a spring, exerts a counterforce to the relative movement of the absorber mass. The higher this resistance, the higher the natural frequency of the damper system and thus the maximum damped frequency.

At the in 2nd depicted camp 10th are between an inner sleeve 26 and an outer shell 28 viewed in the main damping direction s in the elastomer body 12th two chambers arranged in a row 14 arranged. The structure and the function correspond to what has already been explained above, so that in order to avoid repetition, reference is made to the above. By providing two chambers 14 and the resulting two absorber masses 22 an overall larger total amount of mass is advantageously made available.

Reference list

10th

Anti-vibration bearing

12th

Elastomer body

14

chamber

16

Magnetorheological Fluid (MRF)

18th

Kitchen sink

20

Absorber mass

22

Openings

24th

Spring pack

26

Inner sleeve

28

Outer sleeve

S

Main damping direction

Claims (6)

Vibration-damping bearing (10) for a motor vehicle, comprising - an elastomer body (12); - At least one chamber (14) introduced into the elastomer body (12) and filled with a magnetorheological fluid (16), and - Means (18) for generating a magnetic field in the chamber (14), characterized in that in the at least one chamber (14) a deflectable in the main damping direction (s) of the bearing (10) Absorber mass (20) is arranged and that the means (18) for generating the magnetic field are arranged such that when the magnetic field is generated, the magnetic field lines are oriented orthogonally to the main damping direction (s). Anti-vibration bearing after Claim 1 , characterized in that the damper mass (20) is plate-shaped, having a plurality of passage openings (22). Anti-vibration bearing after Claim 1 or 2nd , characterized in that the damper mass (20) is supported against the chamber walls by means of two spring assemblies (24) in the main damping direction (s). Vibration-damping bearing according to one of the preceding claims, characterized in that the means for generating the magnetic field are designed as a coil (18) concentrically surrounding the chamber (14). Vibration-damping bearing according to one of the preceding claims, characterized in that viewed in the main vibration direction (s) two chambers (14) are arranged in series. Anti-vibration bearing after Claim 5 , characterized in that the two chambers (14) are fluidly communicated with one another via a throttle channel.

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