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
  • F16F13/30—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 comprising means for varying fluid viscosity, e.g. of magnetic or electrorheological fluids
  • F16F13/305—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 comprising means for varying fluid viscosity, e.g. of magnetic or electrorheological fluids magnetorheological
• • 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
• • 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
  • F16F13/30—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 comprising means for varying fluid viscosity, e.g. of magnetic or electrorheological fluids

Definitions

• the present invention relates to a device and a method for controlling a bearing element for mounting an engine, in particular an internal combustion engine and / or a transmission, in a motor vehicle.
• a hydraulic bearing element that has a working chamber and a compensation chamber between which a magnetorheological fluid is reciprocal.
• a valve plate is provided between the working chamber and the compensation chamber, which can be "closed” (current / magnetic field on) or opened (current / magnetic field off) by means of an electrically controllable magnetic coil
• stiffness and damping can be achieved by deliberately closing and opening the valve plate the bearing movement are controlled.
• US 2006-0173592 also discloses the use of a sensor which measures fluid pressure in a hydraulic bearing element.
• the US 2006-0173592 further discloses a control system and method for controlling hydraulic, used for storage of an aggregate bearing elements, in which detects the state of motion of the bearing elements via in each case on the unit and a frame on which the unit is mounted by means of the bearing elements mounted acceleration sensors becomes.
• a control system and method for controlling hydraulic, used for storage of an aggregate bearing elements in which detects the state of motion of the bearing elements via in each case on the unit and a frame on which the unit is mounted by means of the bearing elements mounted acceleration sensors becomes.
• Such an arrangement has a complicated assembly, since separately from the bearing elements sensors must be attached and wired at distributed locations.
• between the occurrence of forces in the bearing elements to the registration of accelerations caused by these forces delays occur that hinder a rapid response of the system.
• An object of the present invention is to provide an improved method and an improved control device for controlling a bearing element for mounting an assembly, in particular an internal combustion engine and / or a transmission, in a motor vehicle, wherein the control of the bearing element by means of a simple and inexpensive arrangement should be done.
• the control device according to the invention for controlling a bearing element for mounting an assembly, in particular an internal combustion engine and / or a transmission, in a motor vehicle, according to claim 1 and the corresponding method according to claim 10 have the advantage that the control with particularly little delay to vibrations of the Aggregate reacts. Also, a particularly cost-effective, robust and easy to maintain assembly can be achieved, in which the sensor forms a unit with the bearing element, so that it takes up little space and eliminates the separate installation of a sensor and corresponding leads. Furthermore, no mechanical parts between the unit and the vehicle frame are required, thereby avoiding possible sound transmission paths.
• the idea underlying the present invention is to use for controlling the bearing element, a pressure sensor attached to the bearing element itself, which performs measurements of the pressure of the magnetorheological fluid in the working chamber of the bearing element, wherein in each case a rate of change of the pressure is obtained from two or more measurements ,
• a likewise predetermined control current is conducted through the coil of the bearing element, so that the flow of the fluid from the working chamber of the bearing element in the compensation chamber obstructed and the compression movement is opposed to a large resistance.
• the Rate of change is the rate of change below the predetermined threshold, so that the control current is not turned on.
• the control device comprises a parameter setting unit which dynamically sets the control current and / or the threshold value in each case according to a predetermined functional dependency on the detected measured values of the pressure.
• the control device preferably comprises a reference pressure unit, which records the pressure of the fluid in the working chamber and stores it as reference pressure, the predetermined functional dependence being a functional dependency on a difference between the cyclically detected measured values of the pressure and the reference pressure.
• control device comprises an operating situation setting device which dynamically defines one of a plurality of different operating situations of the motor vehicle, the parameter setting unit being designed to derive the functional dependence of the control current and / or the threshold value depending on the operating situation from a corresponding one Select a plurality of predetermined functional dependencies.
• Figure 1 is a simplified longitudinal cross-section of a magnetorheological
• FIG. 2 is a logic block diagram of a control device according to an embodiment of the present invention.
• FIG. 3 is a logic block diagram of a control apparatus according to another embodiment of the present invention.
• FIG. 4 is a flowchart of a method according to an embodiment of the present invention
• FIG. 5 is a diagram showing an exemplary time history of a pressure in a working chamber of a magnetorheological bearing element according to an embodiment of the present invention, in conjunction with an exemplary timing of a control current switched by a control device according to an embodiment of the present invention.
• Fig. 1 shows a simplified longitudinal cross section of a magnetorheological bearing element with a pressure sensor, as used according to an embodiment of the present invention for controlling the bearing element.
• the bearing element VLE has within a housing a working chamber 104 and a compensation chamber 102, between which a magnetorheological fluid is reciprocal. Between working chamber 104 and compensation chamber 102, a partition wall or plate 125 is provided, which has at its periphery, for example in three directions, gap-shaped openings 112 through which the transport of the fluid between the chambers 104, 102 takes place. Along the periphery of the partition, which is formed, for example, as a plate 125, windings of a coil 106, in which via an electrical connection 120, a control current can be initiated.
• a pressure sensor holder 116 connected to the working chamber 104 via a fluid-permeable channel is a pressure sensor holder 116, to which a pressure sensor 118 is mounted, which supplies via an electrical connection 122 to the pressure in the working chamber 104 corresponding measurement signal.
• the pressure sensor is mounted so that on the one hand, the magnetic field of the coil 106 does not affect the connection between the pressure sensor and the working chamber and on the other hand, the measurement signal can be removed near the place where the terminal 120 of the coil 106 is located.
• the working chamber 104 is further defined by an elastic outer wall 108, e.g. a rubber-metal component, limited to which a threaded rod 110 is attached.
• the compensation chamber 102 is bounded by a likewise elastic diaphragm 124, for example made of an elastomeric material.
• pressurization may be provided between the diaphragm 124 and the cover 126 of the bearing member VLE to assist fluid reflux from the balance chamber 102 into the working chamber 104 in the decompression phase.
• the bearing element is for example mounted so that the unit to be stored with the threaded rod 110 and the housing of the bearing element VLE is connected to a frame of the motor vehicle. If the unit exerts a pressure force on the bearing element VLE via the threaded rod 110, the fluid is pressed out of the working chamber 104 into the compensation chamber 102, where it forms the diaphragm 124 elastically stretches.
• stiffness and damping of the bearing element can be controlled by selectively varying the flow resistance in the gap-shaped openings 112.
• Fig. 2 is a logic block diagram of a control device RE according to an embodiment of the present invention.
• On the left is a schematic representation of a reduced representation of the bearing element VLE shown in FIG.
• the pressure sensor 118 is connected to a pressure detection unit 202 of the control device RE, to which it delivers a pressure measurement signal indicating the pressure prevailing in the working chamber of the bearing element.
• the coil 106 of the bearing element VLE is connected to a switching unit 208 which switches a control current through the coil.
• a calculation unit 204 is arranged in the signal flow between the pressure detection unit 202 and the switching unit 208. Furthermore, the pressure detection unit 202 communicates with a reference pressure unit 212 and a parameter setting unit 210, to which they, as well as the calculation unit 204, are measured values of the pressure in the working chamber of the Storage element VLE provides.
• the parameter setting unit 210 sets parameters according to which the switching unit 208 switches the control current through the coil.
• the pressure detection unit 202 performs dynamic measurements of the pressure in the working chamber of the bearing element VLE.
• the calculation unit 204 receives these measurements and also dynamically calculates with its help a rate of change of pressure, for example, by taking the difference of the measurements of two consecutive cyclic measurements and dividing by the duration of a cycle.
• the resulting signal which describes the rate of change as a function of time, is provided to the low pass 206, which passes only frequencies below a predetermined cutoff frequency.
• the resulting low-pass filtered signal is provided to the switching unit 208, which compares its amplitude to a predetermined threshold and outputs an in its power also turns on predetermined control current through the coil 106 whenever the amplitude of the low-pass filtered rate signal exceeds the threshold and turns it off whenever the amplitude falls below the threshold.
• the reference pressure unit 212 determines that the unit is at rest, with the control current through the coil 106 turned off, it determines, via the pressure detection unit 202, a reading of the pressure in the working chamber that is due to the open connection to the equalization chamber in the equalizing chamber, and stores the measured value as the reference pressure.
• the reference pressure unit 212 When running, i. When the unit is not at rest, the reference pressure unit 212 provides the stored reference pressure to the parameter setting unit 210.
• the parameter unit 210 simultaneously receives from the pressure detection unit the cyclically detected measured values of the pressure and also cyclically calculates a relative pressure by subtracting the reference pressure from the cyclically acquired measured values.
• the parameter setting unit 210 now cyclically sets the predetermined threshold value and / or the predetermined strength of the control current to be switched by the switching unit 208, which influences the current supplied by the switching unit 208 to the coil 106 as a parameter.
• tables may be stored which in each case assign a value of the threshold value and / or the control current to be set to a possible value of the relative pressure.
• FIG. 3 is a logical block diagram of a control apparatus according to another embodiment of the present invention.
• the structure of the control device RE already described with reference to FIG. 2 is assumed, which is shown here for the sake of clarity as an empty rectangle.
• the case shown in Fig. 2 has been generalized to that in the present embodiment, a plurality of bearing elements VLEl ... VLEn are controlled, including the elements of the control device RE shown in Fig. 2 are also provided in a corresponding plurality.
• reference numerals S1, S2, ..., Sn denote a plurality of sensors indicating operational situation-specific parameters of a motor vehicle, such as speed sensor, brake sensor, engine speed sensor, steering angle sensor, clutch sensor, vertical acceleration sensor, lateral acceleration sensor, wheel speed sensor, accelerator pedal sensor, etc.
• reference symbols ST1, ST2,..., STn designate control units which are in a respective operating situation-specific operating state, which i.a. of the signal values of the sensors Sl, S2, ..., Sn is determined.
• Both the sensors S1, S2, ..., Sn and the controllers ST1, ST2, ..., STn can be bidirectionally connected to a data bus CB, e.g. a CAN bus, communicate.
• a data bus CB e.g. a CAN bus
• Reference numeral SES denotes an operation Situations detection means having a plurality of operating Situations detection blocks El, E2, E3, E4 for detecting a corresponding plurality of different operational situations of the motor vehicle based on the operating situation of specific input signals of the sensors S 1 S2, ..., SN and the control devices STl, ST2, ..., STn, which are the operational situation
• Detection device SES can be supplied from the data bus CB, and for providing a corresponding respective operating situation output signal Bl, B2, B3, B4.
• Detection device SES four operational situation detection blocks El, E2, E3, E4, namely a first operating situation recognition block El for detecting at least one traction operating situation, a second operating situation recognition block E2 for recognizing at least one handling operating situation, a third operating situation recognition block E3 for detecting at least one driving comfort operating situation and a fourth operating situation recognition block E4 for detecting at least one sound initiation operating situation which can detect four different operating situations and a corresponding operating situation output signal Bl, B2, B3, B4 deliver.
• a first operating situation recognition block El for detecting at least one traction operating situation
• a second operating situation recognition block E2 for recognizing at least one handling operating situation
• a third operating situation recognition block E3 for detecting at least one driving comfort operating situation
• a fourth operating situation recognition block E4 for detecting at least one sound initiation operating situation which can detect four different operating situations and a corresponding operating situation output signal Bl, B2, B3, B4 deliver.
• a prioritizing device PR constantly receives the respective output signals Bl, B2, B3, B4 of the operational situation detection blocks El, E2, E3, E4 and determines a bearing position relevant operating situation according to a predetermined stored priority distribution and outputs a corresponding prioritized operational situation signal PB.
• reference numeral PF designates a parameter setting means for setting a setting parameter set EPSl ... EPSn for a respective bearing element VLE1 ... VLEn based on the output signal PB of the prioritizer PR.
• These setting parameter sets EPSI... EPSn are either stored in the parameter setting device PF or can be calculated therefrom according to predetermined algorithms.
• the cut-off frequency of the low-pass filter can be adjusted according to the operating situation, so that it is possible to vaporize oscillation frequencies which occur specifically in a specific operating situation.
• the reference pressure stored in the reference pressure unit can be modified, for example in order to take account of a changed situation of the unit in a specific operating situation.
• the operating tables can also be used to change the tables stored in the parameter setting unit, which predefine the assignment of a given relative pressure to values of the threshold value and / or the control current, eg by accessing different tables in different operating states.
• the parameter-setting device PF is also a mode signal MS for setting the setting parameter set EPSl ... EPSn in consideration of the
• Mode signal MS can be fed.
• the setting parameter sets EPS1... EPSn can additionally be varied depending on the current operating state, e.g. in
• the value of the threshold value and / or the value determined by the parameter setting unit from a table can be determined
• the control device RE comprises a control device which is designed to perform a control of the control current to be applied to the bearing elements VLE1 ... VLEn.
• the control device RE supplies a respective control current signal SSl ... SSn to and receives a respective actual control current signal ISl ... ISn from the bearing elements VLEl ... VLEn, in addition to the pressure measuring signal WSl supplied by the respective pressure sensors 31 ... 3n. .. WSn.
• a decision step 400 it is checked whether the unit is at rest, ie whether the vehicle is at a standstill or almost at a standstill. If so, in step 402 a pressure value p ⁇ is sensed and stored as the reference pressure, with the control current being set to zero in step 404 to allow for a free flow of magnetorheological fluid balance between the chambers. If the unit is not at rest, a pressure change over the period of a cycle is calculated in step 406 from the pressure reading p (n) detected in the current cycle and at least the pressure reading p (nl) detected in the previous cycle. This calculated value forms a time-dependent signal with corresponding values calculated in previous cycles, which is subjected to low-pass filtering in step 408. The cutoff frequency may depend on the current operating situation.
• a relative pressure is calculated from the pressure measurement value p detected in the current cycle by subtracting the reference pressure p ⁇ .
• This relative pressure is used in step 412, for example, to find a corresponding threshold in a table.
• the table may be selected from a plurality of tables in accordance with the currently established operating situation.
• step 414 it is determined whether the currently established operating situation specifies speed-dependent parameters. If so, in step 416 the threshold determined from the table is compensated according to the current amount of vehicle speed, e.g. based on a predetermined calculation rule.
• Step 418 determines if the pressure change calculated in step 406 and lowpass filtered in step 408 is greater than the threshold. If so, in step 420 the control current to be delivered to the bearing element is determined, e.g. from a given table.
• the table may be selected from a plurality of tables in accordance with the currently established operating situation.
• the control current can be e.g. be modified in certain operating situations with the driving speed or similar additional parameters.
• control current is set to a defined minimum value. This measure allows the free return of the Fluids from the compensation chamber 102 into the working chamber 104 when the pressure of the unit decreases to the bearing element during the remindschwingphase.
• the reflux can be supported with advantage by pressurizing the compensation chamber 102.
• FIG. 5 is a diagram showing an example timing of a pressure 504 in a working chamber of a magnetorheological bearing member according to an embodiment of the present invention, in conjunction with an example timing 506 of a control device according to FIG. 5
• the diagram has a time axis 500; the other axis is used to represent the pressure 504 and the control current 506 in arbitrary units. It can clearly be seen that the control current 504 is always turned on when the rate of change of the pressure, ie the slope of the curve 504 in FIG. 5, reaches a certain threshold value
• the control current remains off not only during the ring back phases but also when the oscillation is near the motion reversal points.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Vehicle Body Suspensions (AREA)
• Combined Devices Of Dampers And Springs (AREA)
• Support Of The Bearing (AREA)
• Vibration Prevention Devices (AREA)
• Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)

Priority Applications (3)

Applications Claiming Priority (2)

Publications (1)

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ID=39059369

Family Applications (1)

Country Status (5)

Cited By (2)

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Citations (4)

Family Cites Families (1)

• 2006
  • 2006-11-02 DE DE102006051605A patent/DE102006051605B4/de active Active
• 2007
  • 2007-10-29 KR KR1020097009927A patent/KR101378652B1/ko active IP Right Grant
  • 2007-10-29 WO PCT/EP2007/009362 patent/WO2008052726A1/de active Application Filing
  • 2007-10-29 JP JP2009535604A patent/JP4881441B2/ja not_active Expired - Fee Related
  • 2007-10-29 EP EP07819404A patent/EP2087255A1/de not_active Withdrawn

Patent Citations (4)

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