DE19718678A1 - Hydraulically damped elastic mounting - Google Patents

Abstract

The elastic mounting has elastomer blocks between the mounting ends and two hydraulic chambers (7,10) linked by a flow restriction. The link also includes a disc with shaped fluid ducts which rotates in a space between the two chambers. The rotation of the disc varies the damping. The disc can be braked by an electromagnetic control. The flow of fluid rotates the disc which is braked by the solenoid thereby taking energy out of the damping movements. The flow can also be controlled by a variable flow system e.g. using magneto rheologic control.

Description

The invention relates to a hydraulically damping unit bearing, in particular especially for the drive unit of a motor vehicle, and on a method to control or regulate such an aggregate storage.

DE 40 21 039 C2 discloses a hydraulically damping unit bearing, with an upper working chamber and a lower compensation chamber mer. The working chamber is enclosed by a suspension spring that supports the weight of the drive unit. The two chambers are covered by a wall a ring channel separated from each other. The hydraulic system can be operated via the ring channel Overflow liquid from the working chamber into the compensation chamber if the aggregate bearing is loaded. Conversely, when the Unit bearing a backflow of the hydraulic fluid. This will make hydraulic damping of the Ag in addition to the internal friction of the suspension spring gregatelagers reached. In particular, the ring channel can be designed that an oscillation of the liquid column forms in the ring channel, which is targeted to a certain low-frequency vibration of the drive unit (Internal frequency) is matched. In this area of maximum damping the liquid column moving back and forth in the ring channel acts as an absorber. Hereby lane-excited vertical vibrations of the drive unit in its own frequency (so-called stucker vibrations) can be counteracted.  

A disadvantage of the known unit bearing is that the hydraulic damping cannot be changed.

The object of the invention is to provide a fundamentally different embodiment of a hy To show drastically damping aggregate bearings, in which the hydraulic Damping effect and thus the absorber effect can be changed. In particular, it should also be possible to actively build up warehouse forces.

This object is solved by the features of claim 1. Claims 12 to 16 describe methods for influencing the hydraulic damping an assembly bearing according to the invention.

Claim 1 describes an aggregate bearing with a new operating principle: the Passage between the two chambers not only allows replacement of the Hydraulic fluid, but also drives a preferably disc-shaped rotor by a force component in the circumference with the flowing fluid direction acts on the rotor. So flows when the aggregate bearing is compressed Liquid from the working chamber into the compensation chamber, causing the rotor to move in Rotation is offset. This acceleration of the rotor is taken from the Ag gregatelager initiated movement energy. With a subsequent discharge of the aggregate bearing, the liquid flows as a result of the developing bottom pressure in the working chamber back into this. This will entge the rotor driven opposite direction and in turn dampens the movement of itself on the drive unit supporting the drive unit. Thus the energy is out the vertical vibration of the drive unit is converted into rotational energy.

The development of the invention according to claim 2 results in a decision advantage, since the hydraulic damping effect of the unit bearing is active can be influenced. By increasing or decreasing the rotation speed of the rotor can ver the damping behavior of the aggregate bearing be changed, especially in the range of the natural frequency of the drive aggregates is an advantage.  

The rotor is preferably acted on electromagnetically (claim 3) slow down or drive. By a stationary (generator principle) or a rotating magnetic field (electric motor principle) it is possible to d. H. to act on the rotor without external intervention in the unit bearing. Here this results in a simple and trouble-free construction of the unit gers. In addition, the electromagnetic principle is characterized by a high one Regulation or control speed off. The damping behavior and the resonance range of the engine mount acting as a damper dynamically to each because of the conditions.

The rotor can also use an alternating magnetic field that is rotating metallic rotor eddy currents are generated, braked. The eddy current principle (claim 4) is characterized by low construction costs, because on Rotor no additional measures are required. Actively driving the Rotors are not possible here.

Claim 5 describes an aggregate bearing with a reason compared to claim 2 additional different way of changing the hydraulic damping. By changing the cross section of the passage, the liquid can exchange between the two chambers of the unit storage can be regulated. Ins in particular, it is possible to open or close the passage completely. This can be done by all suitable devices, such as shooting over, flaps, chokes, etc. done.

The development according to claim 6 specifies a preferred type of control that works without contact and therefore does not require any intervention in the unit storage.

The opening and closing of the passage can also be controlled by centrifugal force, for example, to automatically limit the rotor speed, by closing the passage increasingly with increasing speed.

The magnetorheological device according to claim 7 also works touchless. A magnetorheological fluid (e.g. "Nanorheological fluid" from BASF) is used. By creating one  Magnetic field in the passage turns the fluid from the liquid to the solid phase transferred and thus the passage closed. It is particularly advantageous that the This "valve" works without moving parts and is therefore completely wear-free. Of the Blocking section in the passage is preferably designed so that the magnetic field is focused on a small area, so that even with less introduced magnetic energy a blocking effect by solidifying the magneto rheological fluid occurs.

Through differently inclined passages (claim 8) can be different Direction of rotation of the rotor can be achieved. In addition, Einrich are preferred provided for closing the individual passages as required.

The passage is, for example, a simple through hole in the rotor forms. According to claim 9, a tube can alternatively be used in the rotor has a corresponding inclination in the circumferential direction. This is particularly so an advantage in such rotors, whose radially inner area has thin walls is carried out with a mass concentration on the outer circumference for generation a corresponding moment of inertia. A pipe is placed over the pipe correspondingly long inclined surface is provided, on which the liquid flow we can.

Through the development of the invention according to claim 10, the delivery rate of the rotor increased significantly. The blades (or other conveyors) are especially with smooth-surface disc-shaped rotors with simple diameters aisle holes (without pipes inserted) are an advantage.

According to claim 11, a device for damping is in the unit bearing higher-frequency vibrations integrated. Such facilities are in themselves known. They are between the two liquid-filled chambers of the Aggre gate bearings arranged and consist, for example, of two perforated plates Discs with a membrane in between that separate the chambers seals. The membrane, which is spaced from the perforated plates, can also be used Excitation by higher-frequency vibrations of this vibration excitation fol gene, while the passage in the rotor with a vibration excitation above  Natural frequency of the damper device according to the invention for the storage liquid locks. Thus, e.g. B. the motor-excited vibrations (due to the gas and Inertial forces of the internal combustion engine) against the body of the vehicle be dampened.

The device according to claim 11 can be integrated in the rotor or radially outside half of the rotor to be fixed.

In the event of a change in the load on the aggregate bearing, as described above the rotor starts rotating. This results in a damping or til effect. The core of the method according to claim 12 is now underlying the idea of influencing this damping or eradication behavior, by the rotor being additionally driven or counter to the rotation of the rotor is braked. This can change the characteristics of the aggregate bearing will. In particular, a corresponding braking of the rotor can additional energy reduction achieved in the compression phase of the assembly bearing will.

According to claim 13, it is particularly effective to have the rotor in the correct phase to slow down. As a result, a maximum energy reduction in the order points of the oscillating movement of the drive unit reached without an abrupt introduction of force into the camp, which is a transfer of Kör impact sound into the body. By the inventive method ren becomes exactly at the times of the oscillation, at which the speed speed curve of the drive unit has a zero crossing, the rotor maxi times slowed down, so that he then by the movement of the drive unit must be accelerated again to the maximum. By using the highly dynamic electromagnetic principle for deceleration (or acceleration) of the rotor is an in-phase energy extraction (or energy on delivery) possible within a narrow time window.

The described method can not only be used to influence dynamic Use vibration processes. Even slowly changing loads ("static or quasi-static load cases"), such as the torque ment support of the drive unit in the event of a load change or the flee  Force-related support of the drive unit when cornering the power vehicle can be influenced according to claim 14. By active driving of the rotor, for example, the balance chamber is additionally hydrau Liquids pumped into the working chamber, which stiffens the Aggregate bearing results, with the consequence of a lower flexibility under the Drive unit load. This can change the position of the drive gregates in a load change or under the influence of centrifugal force.

According to claim 15, the damping of the aggregate bearing by a change tion of the passage cross-section is affected. Of course, the changes tion of the passage cross section can also be combined with a controller or Regulation of the speed of rotation of the rotor.

By mutually opening and closing the passages accordingly According to claim 16 can be achieved that the rotor not only during the Compression stroke, but also while relieving the load on the assembly bearing is driven with the same direction of rotation. It is particularly advantageous that due to the constant direction of rotation of the rotor (without braking in the Reversal points of the initiated swinging motion) the rotor always without Pha energy shift can absorb energy. Although with a direction of rotation the rotor's energy absorption capacity is correspondingly higher, however exact control is required for this, since the braking process leads to Reversal of direction of rotation can result in a phase shift, with the consequence of a Impairment of the absorber effect.

Due to the acceleration in the same direction in both load directions The rotor always rotates at a relatively high speed and thus stores kineti energy, which can be called up subsequently if required. A possible one The application for this is, for example, a desired hardening of the Ag gregatelager with a load change of the drive unit, the z. B. by public NEN or closing the correspondingly inclined passage can be achieved can, whereby the hydraulic fluid is pumped selectively.  

By means of the method according to claim 16, therefore, can be actively on the aggregate bearing be acted on without additional means (e.g. electromagnetic means) for Influencing the rotational speed of the rotor are required.

The combination with an eddy current brake is particularly suitable (Compare claim 4), since the rotor thereby additional with little effort can be braked.

The opening and closing of the passages in question in such a way that the Rotor regardless of the direction of the Be acting on the unit bearing load is accelerated with the same direction of rotation, play automatically by check valves in the passages.

Possible embodiments of the invention are shown in the drawing and explained in more detail below. It shows:

Fig. 1 shows an inventive assembly bearing in partial cross-section,

Fig. 2 shows the rotor of an assembly bearing according to the invention in plan view,

Fig. 3 shows a section along the section line III-III in Fig. 2 and

Fig. 4 shows another embodiment of a rotor in one of the Fig. 2 speaking representation.

Fig. 1 shows an assembly bearing 1 , which receives an unillustrated drive unit of a motor vehicle via an upper threaded bolt 2 . On the underside, the unit bearing 1 is supported on the body of the vehicle, for example on a side member, by means of a threaded bolt 3 . The bolt 2 is arranged on a suspension spring 4 made of an elastomer material. The lower threaded bolt 3 is supported by a base part 5 and a housing part 6 relative to the suspension spring 4 .

The interior of the unit bearing 1 is divided into a working chamber 7 and an equalizing chamber 10 , both of which are filled with a hydraulic fluid 8 . An intermediate element in the form of a disc-shaped rotor 9 separating the two chambers 7 and 10 from each other, wherein the working chamber is enclosed by the upper side of the suspension spring 4. 7 The compensation chamber 10 is sealed by means of a bellows 11 .

The rotor 9 is rotatably supported by a low-friction roller bearing 12 about the vertical axis 13 of the unit bearing 1 and has four passage openings 14 (see also FIG. 2) through which an exchange of the hydraulic fluid 8 between the two chambers 7 and 10 can take place . The rolling bearing 12 is arranged in a housing 19 which is the outside radially with the housing part 6 is the. The housing 19 is permeable to the hydraulic fluid 8 in the direction of the vertical axis 13 of the assembly bearing 1 (wide-meshed lattice structure or the like) and also optimizes the seal in the region of the circumferential gap 15 along the outer circumference of the rotor 9 .

The unit bearing 1 is surrounded at the level of the rotor 9 by a ring-shaped electromagnetic assembly 16 . The electromagnet arrangement 16 is designed as a separate component and interacts with the rotor 9 without contact. The outer edge region of the rotor 9, in turn, is designed as a permanent magnet, with several successive sections of different polarity. The electromagnet 16 is connected to a control or regulating device 17 . The control or regulating device 17 is in turn fed with various input signals 18 , which originate, for example, from sensors that record acceleration values of the vehicle, the drive unit, etc.

In FIGS. 2 and 3, the rotor is shown in detail. 9 The rotor 9 is constructed symmetrically, the passage openings 14 being offset from one another by 90 °. The openings 14 are inclined in the circumferential direction of the rotor 9 with respect to the vertical axis 13 of the unit bearing 1 , as can be seen in particular from FIG. 3 (angle of inclination γ). In addition, the passage channels 14 can be completely or partially closed via rotary or longitudinal slides 20 or 21 . The actuation of the slide 20 , 21 is preferably carried out electromagnetically and against the force of return springs 22 , the actuation and return forces being so determined that a correct function of the control of the passage cross section is given even under the influence of centrifugal force of the rotating rotor 9 .

The diameter of the passages 14 is dimensioned such that the rotor 9 is not driven to a significant degree in the event of slow load changes (low-frequency vibrations). Even with higher-frequency vibrations (in the acoustic range), the rotor 9 reacts too sluggishly, whereas in the range of the natural frequency of the drive unit a maximum damping of the unit gate vibrations is achieved.

The mode of operation of the unit bearing 1 is explained in more detail below:
At a load F in the direction of the vertical axis 13 , the suspension spring 4 is pressed together, so that the volume of the working chamber 7 is reduced. Hereby occurs hydraulic fluid 8 from the working chamber 7 into the compensating chamber 10 via, wherein due to the inclination of the passages 14, the flowing through Hy draulikflüssigkeit 8 to the rotor 9 to rotate (rotation indicated by arrow 26). Conversely, when the assembly bearing 1 (arrow E) is relieved, hydraulic fluid 8 is sucked upward out of the compensation chamber 10 via the passages 14 , as a result of which the rotor 9 is driven in the opposite direction (arrow 27 ).

The rotary movement of the rotor 9 can be supported or hindered by appropriate control or regulation of the electromagnet 16 in order to influence the damping behavior of the unit bearing 1 . Furthermore, the damping behavior can also be changed by adjusting the valves 20 , 21 on the passages 14 .

Also, the rotor 9 can be driven actively in the event of slowly changing loads on the unit bearing 1 , for example in order to pump hydraulic fluid 8 from the compensating chamber 10 into the working chamber 7 and thereby cause the bearing 1 to harden. To increase the delivery rate of the rotor 9 , blade-shaped devices 25 are provided on its underside. The blades 25 can also be designed such that they can be changed in position (between a rest position and an active position).

A further exemplary embodiment of a rotor 30 is shown in FIG. 4. The rotor 30 is composed of a thin-walled central region 31 and an outer ring 32 with a correspondingly large material thickness. The passages are formed by pipe sections 33 inserted into the central region 31 .

Claims (16)

1. Hydraulically damping unit bearing, with two liquid-filled chambers, which are separated from each other by an intermediate element which has at least one passage that allows liquid exchange between the two chambers, characterized in that the intermediate element as the vertical axis ( 13 ) of the unit bearing ( 1 ) rotatable rotor ( 9 ) is formed, with at least one passage ( 14 ), the center line (M) - based on the vertical axis ( 13 ) of the unit bearing ( 1 ) - in the circumferential direction of the rotor ( 9 ) is inclined (Angle of inclination γ). 2. Unit bearing according to claim 1, characterized in that means ( 16 ) for driving or braking the rotor ( 9 ) are provided. 3. Unit bearing according to claim 2, characterized in that the means ( 16 ) generate a changeable magnetic field which interacts with a magnetic device on the rotor ( 9 ). 4. unit bearing according to claim 2, characterized in that the means generate a changeable magnetic field by which the rotor is braked according to the eddy current principle can. 5. Unit bearing according to one of the preceding claims, characterized in that a device for changing the cross section of the passage ( 14 ) is provided. 6. aggregate bearing according to claim 5, characterized in that the device can be actuated magnetically. 7. unit bearing according to claim 5, characterized in that the device acts magnetorheologically. 8. Unit bearing according to one of the preceding claims, characterized in that at least a second passage with - based on the first passage ( 14 ) - opposite direction inclination in the circumferential direction of the rotor ( 9 ) is provided. 9. Unit bearing according to one of the preceding claims, characterized in that the passage ( 14 ) is formed by a tubular element ( 33 ) which is inserted into the rotor ( 30 ). 10. Unit bearing according to one of the preceding claims, characterized in that in the area of at least one end portion of the passage ( 14 ) a blade-shaped device ( 25 ) is provided. 11. Unit bearing according to one of the preceding claims, characterized in that a device for damping higher frequencies ter vibrations is provided.   12. A method for controlling or regulating a hydraulically damping ag gregatelager according to one of the preceding claims, characterized in that the rotor ( 9 ), which is due to a change in loading of the aggregate bearing ( 1 ) about the vertical axis ( 14 ) of the aggre gate bearing ( 1st ) rotates, decelerates or accelerates. 13. The method according to claim 12, characterized in that the angular velocity of the rotor ( 9 ) in each case in the region of the reversal points of the oscillatory movement is maximally reduced in the case of an oscillating load acting on the aggregate bearing ( 1 ). 14. A method for controlling or regulating a hydraulically damping Ag gregatelager according to one of the preceding claims, characterized in that with a quasi-static load on the Ag gregatelager ( 1 ) the rotor ( 9 ) is driven to the liquid ( 8 ) between the two Chambers ( 7 or 10 ) of the unit bearing ( 1 ) umzupum pen. 15. A method for controlling or regulating a hydraulically damping unit gregatelager according to one of the preceding claims, characterized in that the cross section of the passage ( 9 ) is changed. 16. A method for controlling or regulating a hydraulically damping ag gregatelager according to one of the preceding claims, with at least one second passage, with - based on the first passage - against sensible inclination in the circumferential direction of the rotor, characterized in that when loading and unloading the Unit bearing ( 1 ) alternately opens or closes the passages in such a way that the rotor ( 9 ) is driven in the same direction in both loading directions of the unit bearing ( 1 ) by the liquid exchange between the two chambers ( 7 and 10 ).