Door component comprising a controllable damping system

Abstract

A method for damping a movement of a door system of a vehicle that is equipped with a damping system having an adjustable and controllable damping action. A movement of the door system between a closed position and an open position is damped in a controlled manner. A measurement of the change in speed of the speed of movement of the door system is calculated and if the change in speed exceeds a predefined limit value, a set, gentle damping action is changed over to a greater damping action.

Claims

1. A method of damping a movement of a door device having a damper device with an adjustable and controllable damping action, the method which comprises: damping a movement of the door device by controlling a degree of damping at least partially between a closed position and an open position; determining a measure of a rate of change of a movement speed of the door device; and when the rate of change exceeds a predetermined threshold value, switching from a currently set, relatively low degree of damping to a relatively high degree of damping.

2. The method according to claim 1, which comprises setting the degree of damping to a substantially maximum value if the rate of change, being a deceleration, overshoots the predetermined threshold value.

3. The method according to claim 1, which comprises determining a measure for a position and/or an angular position of the door device.

4. The method according to claim 3, which comprises increasing the degree of damping when the door device approaches a predetermined angular position.

5. The method according to claim 4, which comprises increasing the degree of damping when the door device approaches the closed position.

6. The method according to claim 3, which comprises increasing the degree of damping to thereby decrease a rotational speed of the door device to a predefined closing speed.

7. The method according to claim 1, which comprises evaluating closing speeds during closing processes with an integrated learning function to thereby adapt the predefined closing speed to enable a reliable closing of the door device.

8. The method according to claim 1, which comprises increasing the degree of damping when the door device approaches a maximum open position.

9. The method according to claim 1, which comprises increasing the degree of damping only if a rotational speed of the door device overshoots a predefined rotational speed.

10. The method according to claim 1, which comprises increasing the degree of damping if an obstruction is identified in a movement path of the door device and a collision with the obstruction is imminent.

11. The method according to claim 1, which comprises controlling the damper device to cause a rotational speed of the door device to adopt a profile such that a quiet closure of the door device is achieved and/or that a particular opening angle is attained without abrupt changes in speed.

12. The method according to claim 1, configured for controlling a closing and opening of a vehicle door.

13. A door component, comprising: two connector units movably disposed relative to one another, said connector units including a first connector unit connectable to a supporting structure and a second connector unit connectable to a movable door device; at least one controllable damper device and a control device connected to said at least one controllable damper device and configured to dampen, under control by said control device, a movement of the door device at least partially between a closed position and an open position; a sensor device connected to said control device for detecting a position of a pivotable said door device; said control device being configured to determine a characteristic value for a rate of change of a speed of the door device using sensor data from said sensor device, and to switch said damper device from a relatively low degree of damping to a relatively high degree of damping if a rate of change of the speed of the door device exceeds a predefined threshold value.

14. The door component according to claim 13, wherein said damper device is a magnetorheological damper device, and wherein the degree of damping is adjustable by subjecting a magnetorheological fluid to a variable magnetic field.

15. The door component according to claim 13, wherein a time duration for switching from the relatively low degree of damping to the relatively high degree of damping is less than 50 ms.

16. The door component according to claim 13, wherein the degree of damping is set to a maximum value if the rate of change, being a deceleration of a movement of the door device, overshoots the predetermined threshold value.

17. The door component according to claim 13, wherein the degree of damping is deactivated, or is reduced to a low value, when the speed of the door device or a rotational speed of the door device has decreased to zero.

18. The door component according to claim 14, wherein the damper device is formed with at least one flow channel through which the magnetorheological fluid can flow, wherein said flow channel can be subjected to the variable magnetic field to thereby adjust a flow resistance in said flow channel, and wherein a resultant degree of damping of said damper device is set to a more intense value by way of a relatively intense magnetic field in said flow channel and to a relatively weak value by way of a relatively weak magnetic field.

19. The door component according to claim 13 configured for a door of a vehicle.

Description

(1) Further advantages and features of the present invention will emerge from the description of the exemplary embodiments, which will be discussed below with reference to the appended figures.

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWING

(2) FIG. 1 shows a schematic plan view of a vehicle with a door component according to the invention;

(3) FIG. 2 shows a schematic exploded illustration of the door component as per FIG. 1;

(4) FIG. 3 shows an enlarged cross section of the door component as per FIG. 1;

(5) FIG. 4 shows another embodiment of a door component according to the invention;

(6) FIG. 5 shows a further embodiment of a door component according to the invention;

(7) FIG. 6 shows a yet further embodiment of a door component according to the invention;

(8) FIG. 7 shows a schematic cross section through a damping valve of a door component according to the invention; and

(9) FIG. 8 shows a diagram with the speed and the deceleration of a door during a closing process.

DESCRIPTION OF THE INVENTION

(10) FIG. 1 shows a schematic plan view of a motor vehicle 100 stopped at the edge of a road, in which motor-vehicle there are provided in this case two door devices 53 designed as doors, which are both open. The doors are situated in each case approximately in an angular position 13. The doors are each part of a door component 50, which in this case comprises the doors 53. It is equally possible for a door 53 to be attached to the door component 50. The door component 50 comprises, in any case, connector units 51 and 52 for connection to the supporting structure 101 of the vehicle 100 and to the door 53, for the purposes of holding the door pivotably on the supporting structure 101. Here, the door may be composed of multiple units, which are in each case pivotable and which are articulatedly connected to one another. The door may be held so as to be pivotable about one or two or more pivot axes. Hatching is used to show a door 53 in the closed position 2, in which the door in this case terminates flush with the vehicle.

(11) With the invention, it is possible to achieve that, in the event of an intense deceleration of the door 53, a greater or maximum damping action is set practically immediately in order to as far as possible prevent or at least reduce or minimize damage. If the pivotable door 53 of the motor vehicle 100 is slammed closed and thus moved rapidly in the closing direction, and if for example a leg or a hand or some other object is situated in the path of the closing movement, thenwithout the use of further sensorsthe door 53 firstly strikes the leg or the hand or an object and, in the process, is unexpectedly braked. This means that, for example in the case of a relatively high rotational speed of the door, an unexpected and unexpectedly large change in the rotational speed occurs. Here, this means that the rate of change of the movement speed of the door device, or in this case specifically the rate of change of the rotational speed, exceeds a predetermined threshold value.

(12) With the invention, in the event of such a process being detected, a maximum damping action is immediately set such that damage can be very substantially prevented.

(13) If, during the opening of the door 53, the latter strikes with the outer panel against an obstruction, the rotational speed of the door is immediately considerably reduced. Since the panels can however generally deform in a resiliently elastic manner over a certain range, it is thus often possible for damage to the door 53 to be prevented entirely in the case of an immediate reaction and maximization of the damping action.

(14) The method may also be performed with the door components described below.

(15) FIG. 2 shows, in an enlarged illustration, an exploded illustration of the door component 50, wherein the door component 50 comprises a damper device 1 which has a damper which operates on a magnetorheological basis.

(16) The door component 50 in FIG. 2 has connector units 51 and 52 for connection to the supporting structure 101 and to the door 53, in order a defined and controlled pivoting of the door during the movement from the open position illustrated in FIG. 1 into the closed position 2 also indicated in FIG. 1.

(17) The damper device 1 comprises a cylinder unit 31, in which the piston 38 of the piston unit 30 divides the cylinder volume 32 into a first chamber 33 and a second chamber 34 in a variable manner.

(18) A compensation volume 36 of a compensation chamber serves for the compensation of the piston rod 43 plunging into the cylinder unit 31.

(19) FIG. 3 shows an enlarged cross-sectional illustration of a part of the door component 50 from FIG. 2.

(20) On the assembled damper device 1 that is illustrated in section here, it is possible to see the piston unit 30 with the piston 38 in which the magnet device 9 with the electrical coil 10 is arranged. The piston 38 divides the cylinder volume 32 of the cylinder unit 31 into a first chamber 33 and a second chamber 34. The damping valve is arranged outside the piston unit 31. The magnet device 9 with the electrical coil 10 is arranged on the damping valve.

(21) Furthermore, in the cylinder unit 31, the compensation device with the compensation chamber 37 and the compensation volume 36 is illustrated. The compensation chamber 37 is separated from the second chamber 34 by a separating piston, which slides in a variable manner within the cylinder unit 31. It is also possible for the compensation chamber to be located on the other side, wherein sealing is then necessary with respect to the piston rod extending through and with respect to the first chamber 33. The compensation chamber 37 is situated on the low-pressure side of the one-way circuit. Valves 47 and 48 for the filling of the first and second chambers 33, 34 and of the compensation chamber 37 are provided. The compensation chamber 37 is filled with a gaseous medium at a low pressure, such that the plunging-in volume of the piston rod 43 can be compensated.

(22) To the piston rod 43 there is attached a sensor device 12, by means of which an absolute position of the damper device 1 can be detected here. By interrogation of the sensor device, the position of the two connector units 51 and 52 with respect to one another can be detected, such that, by means of the sensor device, the angular position of the door 53 is also directly detected.

(23) The connector cables for the electrical coil in the piston 38 and the sensor device 12 are in this case guided through the piston rod 43 to the outside.

(24) FIG. 4 shows a variant in which a continuous piston rod or 2 piston rods 43, 44 are provided. The interior of the cylinder unit 31 is divided further by the piston 38 into 2 chambers 33 and 34. Here, the two piston rods 43 and 44 are guided to the outside at the respective ends, such that there is no need for a plunging-in of the volume of a piston rod to be compensated. To be able to compensate a volume expansion as a result of temperature differences, a compensation device 39 is provided here, which is designed for example as a hollow rubber ring or the like, and which thus provides corresponding volume compensation by way of a volume expansion or decrease in volume as a result of temperature differences. Such a compensation device may be arranged in the chamber 33 or in the chamber 34. Compensation devices in both chambers 33 and 34 are possible.

(25) In all embodiments, the piston 38 is also designed as a damping valve 5, and has one or 2 or more flow channels 7 which connect the first chamber 33 to the second chamber 34. The chambers 33 and 34 are filled with a magnetorheological fluid 6. The damping is in this case achieved by virtue of a magnet device 9 or at least one magnet device 9, which comprises magnetically hard material and in this case also an electrical coil, being arranged on the damping valve 5.

(26) By means of a short electrical pulse at the coil 10, a magnetic pulse is triggered, which leads to a permanent magnetization of the magnet device 9, such that, subsequently, the flow resistance through the flow channel 7 increases in a manner corresponding to the intensity of the acting magnetic field 8.

(27) By means of corresponding remagnetization of the magnet devices 9, it is thus possible to set any desired damping of the door movement of the door 53. It is furthermore possible, in addition to a permanently acting magnetic field, to use the coil 10 to dynamically model the magnetic field 8 of the magnet devices 9. By means of a magnetic field oriented in the same direction, the damping can be intensified, and by means of a correspondingly oppositely oriented magnetic field, the damping can be attenuated or even reduced to zero.

(28) In this exemplary embodiment, the connector cable 42 or the connector cables 42 are guided to the outside through the piston rod 44. The piston rod 44 is displaceably received in a tube 46. Here, at the end of the piston rod 44, the connector cable 41 is guided out of the piston rod and is guided to the outside through a slot 42 in the tube 46.

(29) By way of example for all exemplary embodiments, a control device 4, by means of which the damping valve 5, the damper device 1 and/or the door component 50 as a whole can be controlled, is shown in FIG. 4. The control device 4 may also be part of the vehicle 100 or of some other apparatus.

(30) FIG. 5 shows another variant in which 2 magnet devices 9 or at least 2 electrical coils 10 and 11 are provided. The magnetic coils 10 and 11 of the magnet devices 9 are in turn arranged in the piston 38 of the piston unit 30 within the cylinder unit 31. In this case, too, the piston separates 2 chambers 33 and 34 of the cylinder volume 32. First and second piston rods 43 and 44 may be provided or only one piston rod is guided out on one side. In such a case, a compensation chamber 37 having a compensation volume 36 is again required.

(31) Here, an electrical coil 10, 11 is used for generating a magnetic pulse and for the permanent magnetization of the magnet device 9. The respective other electrical coil 11, 10 can be used for the modulation of the presently acting magnetic field.

(32) FIG. 6 shows another schematically illustrated variant of a damper device 1 of a door component 50 with connector units 51 and 52. The damper device 1 has a magnetorheological fluid 6 as working fluid. A piston unit 30 with a piston 38 separates a first chamber 33 from the second chamber 34. At least one flow channel 7 leads through the piston. The one-way valve 15 opens for the flow of the magnetorheological fluid from the second chamber 34 into the first chamber 33. From there, the working fluid is conducted through the return channel 35 to the in this case external damping valve 5, which is assigned a magnet device 9 and an electrical coil 10, in order to set the desired damping. The damping valve 5 is in turn connected in terms of flow to the second chamber 34 via a second one-way valve 16.

(33) Both during the plunging of the piston rod 43 into the cylinder unit 31 and during the deployment of the piston rod 43 out of the cylinder unit 31, the working fluid 6 flows in the same direction along the indicated arrows. Depending on whether the piston rod is plunged in or deployed out, magnetorheological fluid is fed to the compensation chamber 37 or magnetorheological fluid is removed from the compensation chamber 37. In the compensation chamber 37, there is provided a compensation volume 36, which is filled with a gas.

(34) One or more sensor devices 12 may be provided in order to detect a relative position of the two connector units 51 and 52 with respect to one another, in order to derive an angular position of the door 53 therefrom. In all embodiments, it is however also possible for other angle sensors to be provided, for example at the rotary joint, such that an angular position is directly output.

(35) In this case, too, an electrical coil 10 is used for the generation of a magnetic pulse and for the permanent magnetization of the magnet device 9. The same or another electrical coil may be used for the modulation of the presently acting magnetic field.

(36) FIG. 7 shows a schematic cross section through the cylinder unit 31 and the piston 38 arranged therein. It is possible to see clearly the flow channels 7 of the damping valve 5, which are in this case each divided further into 2 sub-channels by means of a partition. Also shown is a magnetic field line of the magnetic field 8. The magnetic field passes approximately perpendicularly through the flow channels 7 of the damping valve. The electrical coil 10 serves for the generation of a variable magnetic field, and in particular also for outputting a magnetic pulse in order to magnetize the magnet device 9 as desired.

(37) It is correspondingly also possible, as illustrated in section in FIG. 7, for an external damping valve for the door component, for example, to be designed as per FIG. 6. All of the parts shown are then preferably immovable relative to one another. The flow channels 7 of the damping valve 5 may each be divided into two sub-channels by means of a partition. In this case, too, the magnetic field again passes approximately perpendicularly through the flow channels 7 of the damping valve 5. The electrical coil 10 serves for generating a variable magnetic field and may in particular also be used for outputting a magnetic pulse in order to permanently magnetize the magnet device 9 as desired.

(38) FIG. 8 shows an exemplary diagram of the mode of operation during an opening process of a door. Normalized values for speed and deceleration are plotted versus the angle. The illustration shows the profiles of an uncontrolled speed 81 and the associated uncontrolled deceleration 84, and the profiles of the controlled speed 82 and the associated controlled deceleration 85, versus an opening angle.

(39) Also plotted is a threshold value 80 for a threshold acceleration or a threshold deceleration. The threshold value 80 is predefined, but can be set and changed. If an actual deceleration exceeds the threshold value 80, then an acute hazard situation is identified, and hazard damping is triggered. This means in this case that the door movement is thereafter damped with a maximum damping action.

(40) Here, at an angle of close to 44, the door strikes a previously unidentified or unknown obstruction, which subsequently brakes the door movement. The present deceleration of the door thereupon exceeds the predefined threshold value 80 at an angle of close to 45.

(41) A certain length of time passes before a reliable value for the present deceleration is determined. In the intervening time, the door has moved further and reaches an angle of slightly greater than 45.

(42) As a result of the exceedance of the threshold value 80, it can be identified that it is not a normal and interference-free opening process that is being performed here. If no countermeasures were implemented here, the speed profile 81 and the acceleration profile 84 versus the angle would arise, and the door would come to a standstill for the first time at an opening angle of, for example, close to 50. Permanent damage to the door (or to a neighbouring vehicle) or the like could already occur as a result.

(43) By contrast, with the invention, as soon as possible or directly after the exceedance of the threshold value, the door is braked by means of the damper device, and in particular braked as intensely as possible. The door is braked because it is assumed that the door has struck or is striking an obstruction. Here, in general, the outer panel of the door initially bends elastically, such that additional braking of the door can possibly entirely prevent lasting damage to the door or to other objects.

(44) If the door strikes a person, the person may be injured. Therefore, braking of the door is very much expedient and necessary in such situations.

(45) As a result of the impact against the obstruction, the deceleration has abruptly increased, and increases further. Without further measures, the uncontrolled profile of the deceleration 84 would arise. Since the door is however braked to the maximum extent after the exceedance of the threshold value 80, the controlled profile of the deceleration 85 and the controlled speed profile 82 arise.

(46) The door is braked with considerably greater intensity, and in this example comes to a standstill at an angle of close to 46.

(47) The hazard damping has brought the door (without near-field detection!) to a standstill earlier by an angular value 87 of approximately 4. The angular value 87 is a direct measure for the absorbed energy and thus also reduction of the hazard. The stated numerical values are to be understood merely as examples and are merely initial values from tests. The values that can actually be achieved are dependent on numerous factors.

(48) The control may be performed entirely by means of the position sensor or the angle sensor of the damper device 1. Other values need not be incorporated though may be used.

(49) The invention can likewise be used highly advantageously during the closing of the door. For this purpose, it is merely necessary to imagine the diagram from FIG. 8 as having been horizontally mirrored. If, during the closing process, the door strikes for example a body part of a user, the deceleration of the door immediately increases intensely. The door is subsequently damped to the maximum extent and thus comes to a standstill considerably earlier, such that bruising of body parts or damage to objects can be reduced or prevented.

(50) It is also possible and preferred for the door to be brought to a standstill at a particular small opening angle during every closing process, for example at 2.5 or at 3, in order to prevent trapping of fingers.

(51) The invention is also used for bringing the door smoothly to a standstill in targeted fashion at certain settable or selectable points or positions. For this purpose, the door movement is correspondingly damped in an adapted manner before the desired position is reached.

(52) If surroundings sensors or a near-field detection facility is active, or if an obstruction 86 is known, the door movement is controlled such that the door comes to a standstill for example at the angular distance 88 before the obstruction, and is fixed there.

LIST OF REFERENCE DESIGNATIONS

(53) 1 Damper device 2 Closed position 3 Open position 4 Control device 5 Damping valve 6 MRF 7 Flow channel 8 Magnetic field 9 Magnet device 10 Electrical coil 11 Electrical coil 12 Sensor device 13 Angular position 14 Predetermined angular position 15 First one-way valve 16 Second one-way valve 18 Magnetic pulse 19 Time period 20 Rate of change 21 Delay 22 Rotational speed 23 Limit value of 20 24 Relatively low damping 25 Relatively high damping 26 Maximum damping 27 Damping 28 Closing speed 29 Second compensation channel 30 Piston unit 31 Cylinder unit 32 Cylinder volume 33 First chamber 34 Second chamber 35 Return channel 36 Compensation volume 37 Compensation chamber 38 Piston 39 Compensation device 10 Electrical connector unit 41 Connection cable 42 Slot 43 First piston rod 44 Second piston rod 45 Diameter of 43 46 Tube 50 Door component 51 Connector unit 52 Connector unit 53 Door 54 Angular position 60 Obstruction 80 Threshold value 81 Speed 82 Controlled speed 84 Deceleration 85 Controlled deceleration 86 Obstruction 87 Angular value 88 Distance 100 Vehicle 101 Supporting structure