JPH0262739B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to an adjustable damper, in particular for motor vehicles, comprising a cylinder containing a damping medium, which is sealed and arranged so as to be axially movable in the cylinder. a damping piston rod and a damping piston, which partitions the cylinder chamber into two working chamber halves and is provided with a fluid passage for producing a damping force, the effective cross section of which is a throttling mechanism. and an electromagnetic drive acting thereon, the electromagnetic drive having a magnetic circuit and a winding, the magnetic circuit and the winding controlling the fluid passage and its throttling mechanism. Concerning things of a type that are located very close to.

PRIOR ART Adjustable dampers for vehicles with an electromagnetically adjustable throttle mechanism are disclosed, for example, in West German patent no.
1084528 specification, patent application publication specification no.
3215614 and the specification of the same patent application publication number 3241984.

Problems to be Solved by the Invention In the dampers described in these specifications, a throttle plate rotatably supported on the buffer piston is provided as a throttle mechanism, and this throttle plate is provided on the piston body. It has a flow opening that more or less coincides with the fluid passageway, or the hole opens a flow opening that more or less forms a bypass for the fluid passageway of the piston. In this case, the adjustment of the throttle plate is carried out by means of an adjusting rod which is fixedly connected thereto and passes through the hollow piston rod over its entire length, the adjusting rod being connected to a suitably discharged piston rod. Various rotational adjustment positions are provided by an electromagnet attached to the free end of the piston rod within the head. Another known adjustable vehicle damper is disclosed in West German Patent Publication No.
In this damper, an electromagnetic winding is attached to the outer end of a hollow piston rod, and the piston rod is used as a mover within this winding. An adjusting rod is provided which passes through the entire length and is movable axially within the piston rod, with its inner end more or less adjusting the bypass opening located in the vicinity of the damping piston within the piston rod. Close. A common feature of these known controllable dampers is that, despite a very wide range of task settings, only coarse adjustments of the throttling mechanism can be made and it is therefore not possible to obtain different desired damping force characteristics. There is a particular thing. This is because the adjusting means of this damper have a very large mass and, moreover, the adjusting rod, which passes through the hollow piston rod over its entire length, creates a significant gap between the electromagnetic drive and the throttle mechanism. This is because it extends for a long time.

Furthermore, French Patent No. 109402,
According to the specifications No. 1095506 and No. 1130621, an electromagnetically controlled damper of this type is known. The drive device includes a winding in close proximity to the fluid passageway of the buffer piston and the throttle mechanism. In this case, the throttle mechanism is designed as a throttle piston which is mounted movably in the longitudinal direction of the piston rod against the action of a spring.
This throttle piston is adjusted in a predetermined throttle position and held in that position as a function of the current flowing in the winding, and this adjustment takes place independently of the different hydraulic pressures occurring in each of the working chamber halves. This is because this hydraulic pressure is compensated in each case by pressure-receiving surfaces of the same size on the throttle piston and is therefore not influenced by the position of the throttle piston. This results in a comparatively rough adjustment of the damping force and only an exponential damping force characteristic as a function of the piston speed, which is characteristic of throttle openings with a constant cross section.

Therefore, an object of the present invention is to provide a damping characteristic curve that extends almost linearly, can be arbitrarily and steplessly adjusted or controlled over a wide range, and that the damping force can be adjusted by individual movements of the damper. The object of the present invention is to provide an electromagnetically controlled damper as mentioned at the outset, which is extremely sensitive within a range of conditions and which also allows automatic adjustments to be made manually or, for example, by a computer. .

MEANS OF THE INVENTION SOLVING THE PROBLEM A first aspect of the invention that solves the above-mentioned problems is that the throttling mechanism produces a fluid loading surface that produces an adjustment force that is dependent on the fluid pressure difference between the two working chamber halves. and the electromagnetic drive device is configured to apply a controllable return force to the throttle mechanism that acts in the opposite direction to this adjustment force. The throttle mechanism is configured to be zero in a rest position of the throttle mechanism and increase as the hydraulic adjustment of the throttle mechanism increases, the throttle mechanism being rotatably supported in the percussion piston and having a flow opening. This flow opening is
Between this rotatable throttle mechanism and the metered piston body, at least one tube is connected to the one and the other working chamber halves, respectively, and is configured to be more or less matched to the fluid passage of the stationary piston body. Two flow-receiving openings are provided, in which the fluid load surfaces provided on the throttle mechanism and the piston body are located opposite to each other when viewed in the direction of rotational adjustment of the throttle mechanism. be.

Effects of the present invention According to the present invention, the electromagnetic drive device is configured such that its return force is zero at the rest position of the throttle mechanism and increases as the amount of hydraulic adjustment of the throttle mechanism increases. ing. In short, in the rest position of the throttle mechanism, the electromagnetic return force becomes zero or loses its effect, independent of the control current flowing in the winding. However, this return force increases as the throttle mechanism is deflected from the zero or rest position, and the increase in this return force is dependent on the current flowing in the winding. Therefore, not only the control of the damper but also its regulation can be carried out without complex control devices by regulating the direct current. In short, this damper has a predetermined damping characteristic curve without controlling the damping force and can be adjusted to different stiffnesses by varying the predetermined current. This damper can also be used as a normal damper without current supply and control.

According to the invention, there is further provided a throttle mechanism rotatably mounted in the damping piston and provided with a flow opening, the flow opening being adapted to more or less coincide with the fluid passage of the metered piston body. formed between the rotatable throttle mechanism and the stationary piston body, at least two at least two
A flow-receiving opening is provided in which, viewed in the direction of rotational adjustment of the throttle mechanism, fluid load surfaces on the throttle mechanism and on the piston body, respectively, are located opposite one another. In this case, the diaphragm mechanism can advantageously be designed as a ring-shaped armature with permanent magnets of alternating polarity,
This ring-shaped armature is rotatably supported in the piston body and surrounds a centrally arranged winding of the piston body with a plurality of radial pole shoes of an electromagnet forming an electromagnetic drive.

If the damper is provided with a valve plate that closes the fluid passage of the buffer piston as a throttling mechanism, especially a valve spring plate, the rod-shaped mover can be fixed to this valve plate or to a support plate provided on the back side of the valve plate. , this rod-shaped mover projects into the winding inserted into the receiving hole of the damping piston. The winding forms part of an electromagnet forming an electromagnetic drive. However, this configuration requires a relatively strong electromagnetic driving force.

In a second embodiment of the invention, an adjustable damper, in particular for a motor vehicle, comprises a cylinder containing a damping medium, a piston rod which is sealed and arranged to project into the cylinder and can be moved axially; It is equipped with a damping piston, which divides the cylinder chamber into two working chamber halves, and is provided with a fluid passage for producing a damping force, the effective cross section of which is located between the throttle valve body and its opening. It is adjustable by means of a controllable electromagnetic drive acting against the force, which drive comprises a magnetic circuit and a winding mounted on the damping piston, so that the throttle valve body performs both tasks. between the throttle valve body and an electromagnetic drive acting against its hydraulic regulation, in those types with a fluid load surface that produces a regulation dependent on the medium pressure difference between the chamber halves; is provided with a hydraulic compensator that strengthens the return force. and a load chamber which is connected to both working chamber halves via a separately extending fluid connection passage to the working chamber half located on the opposite side from the fluid passage. An auxiliary throttle valve, which can be controlled by an electromagnetic drive, is integrated in the guided connecting channel. With this configuration, even if the electromagnetic driving force or return force is extremely weak,
The valve plate can be controlled with high sensitivity. This is because the relatively strong hydraulic pressure that occurs on the side receiving the flow is significantly compensated for by the counterpressure of the oppositely hydraulically loaded support.

As an electromagnetic drive, often windings,
An electromagnet with a magnetic circuit and a movable armature is used. However, basically, in order to quickly and sensitively control the adjustment of the throttle mechanism, a moving coil placed on the auxiliary valve plate can be used as an electromagnetic drive device for controlling the auxiliary valve plate. This moving coil projects into a suitable annular gap of a permanent magnet in the piston.
The moving coil principle provides a very rapid control of the damping force and thus any desired type of damping diagram.

According to a further embodiment of the invention, a single throttle valve body with a load chamber and an electromagnetically loaded control valve is provided for damping compressive loads and damping tension loads; This allows them to be installed compactly within the damping piston. For this purpose, the throttle valve body has, on the load side facing the load chamber, in addition to the first load surface that closes off the fluid passage, a second load surface of approximately the same size. The second load surface is loaded by the hydraulic pressure in the working chamber half surrounding the valve body. In this case, a control restriction is integrated in the medium connection line leading from the load chamber to both working chamber halves, which control restriction is adjusted as a function of the pressure difference between the two working chamber halves. They are controlled in opposite directions by control valves, so that the load chamber is connected in a slightly constricted manner to the working chamber half with the lower hydraulic pressure and to the working chamber half with the higher hydraulic pressure. Connected in a severely restricted state. It is therefore important that the throttle valve body is provided with three different types of pressure receiving surfaces. two pressure-receiving surfaces located on one side of the throttle body and loaded by the different pressures in the two working chamber halves, and on the other side of the throttle body facing the load chamber. It is a pressure receiving surface. The latter pressure receiving surface has a size corresponding to the sum of the former two pressure receiving surfaces. As a result, in the rest position of the damper, all three chambers act oppositely on the throttle body with the same pressure, so that the throttle body stays in the closed position, completely closing off the fluid passage. It will be done. But when the piston carries out a movement, either in the tension or compression direction, the load chamber is connected with a slight constriction to the working chamber half conducting the low pressure, and at the same time is significantly constricted to the other working chamber half. The pressure in the load chamber is thereby reduced accordingly in any case, which results in an opening movement of the throttle valve always in the same direction. In short, the throttle valve is always opened in the same direction, regardless of the direction of piston movement.

A spring element is preferably provided between the throttle valve body and the control valve. Depending on the degree of opening of the throttle valve body, this spring element exerts a return force on the control valve, which acts in a direction opposite to the hydraulic adjustment force. This results in an effective damping force even if a current is relayed for any reason to the electromagnet loading the control valve, and thus provides an emergency operating characteristic of the damper under tensile as well as compressive loads. Furthermore, vibrations in the damping piston, especially in its control valve, are avoided.

The damping piston can advantageously be provided with a control valve and its control throttle as well as an insert with a fluid passage leading from the load chamber to both working chamber halves.
This insert has a ring-shaped load chamber on its outer periphery and a ring-shaped throttle valve that covers the load chamber like a hood. It is guided in an axially movable and sealed manner on the outer periphery of the insert on both sides, and furthermore has an annular shoulder which separates the annularly extending pressure surfaces on both sides from each other, by means of which the throttle valve body contacts an annularly extending closing lip on the piston body in the vicinity of the flow passage. In this way, an insert with important functional parts is created, which can be easily assembled into the damping piston body.

DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows a controllable damper, particularly for motor vehicles, which comprises a cylinder 1 partially filled with a buffer solution and a pressurized gas, into which the cylinder is guided through a packing 2. It has an axially movable piston rod 3 and a damping piston 4 fixed to the inner end of the piston rod 3.
This buffer piston 4 partitions a cylinder chamber filled with a buffer solution into two working chamber halves 5, 6. The working chamber half 6 is separated from the chamber 7, which is filled with pressurized gas, by a partition piston 8 which is guided tightly in the cylinder 1.

As shown in particular in FIG. 2, the damping piston 4 has a piston body consisting of two discs fixed to the end 3' of the piston rod 3, which disc 9 , 10 are provided with fluid passages 11. A diaphragm plate 12 is rotatably mounted between the two disks 9, 10, and has a through hole 12', which is connected to the disks 9, 10. Fluid passage 11 provided in 10
It is formed more or less in accordance with the The throttle plate 12 is fixedly connected via a driver pin 13 fixed thereto to an armature 15 which is rotatably mounted on the piston head 14 and which forms an electromagnetic drive. It forms the mover of the electromagnetic rotating magnet. The electromagnetic rotating magnet winding 16 is located within a piston head made of ferromagnetic material. Mover 1 similarly made of ferromagnetic material
5, like the piston head 14, is provided with a pole shoe, which generates a maximum magnetic force at positions facing each other. The supply of current to the winding 16 takes place through the piston rod 3, which is provided with a suitable hole 3'', from a regulating or control device located on the vehicle side.The spring 13' closes the throttle plate 12. Thus, even if the current is cut off for some reason, the damper always maintains a buffering force.

In order to obtain a relatively large control range and at the same time a relatively large sensitivity, the piston head 14
A permanent magnet 14' is inserted inside. The return force produced by this permanent magnet 14' produces a normal or moderate damping force in the absence of current supply. When a control current flows, this return force of the permanent magnet is increased or decreased, and thereby the damping force is also increased or decreased. In this case spring 13' is not used.

The aperture plate 12 has two crescent-shaped holes in addition to the through hole 12'.
It is provided with two recesses 12'', through which in each case two pins 17 are guided, which connect the two discs 9, 10 to one another. The pin 17 is provided with a collar-shaped cylindrical thick walled part 17' at its center, and this thick walled part 17' fits tightly on both sides within the crescent-shaped notch 12''. Each crescent-shaped notch 12'' is divided into two holes for passing the wires through. An opening 11' provided in the stationary discs 9, 10 ensures that one hole for passing the wires is located in the upper working chamber. One half 5 and the other hole are connected to the other working chamber half 6, so that the diaphragm plate 12
is rotated in one direction or the other depending on the direction of movement of the piston rod 3 by the respective hydraulic load on the side receiving the flow (referred to as the countercurrent side). Via the electromagnets 15, 16, a controllable restoring force acting against this rotation acts on the diaphragm plate 12, by means of which a predetermined damping characteristic can be obtained by appropriately controlling the current.

FIGS. 3 and 4 schematically illustrate the principle of the control described above. The damping piston shown in FIG. 3 is essentially the same as that shown in FIGS. 1 and 2. This damping piston has a throttle plate 12 which is rotatably arranged between the two stationary disks 9,10. The discs 9, 10 are provided with fluid passages 11 and openings 11'. A through hole 12' is provided in the throttle plate 12, which is arranged to more or less coincide with the fluid passage 11. Furthermore, the diaphragm plate 12 is provided with at least two holes (hereinafter referred to as counterflow holes 12) for receiving the flow.
This counterflow hole 12 is connected to one or the other working chamber half 5, 6 via an opening 11'. In the counterflow bore 12, viewed in the direction of rotation of the throttle plate 12, one fluid load surface A, A' is formed facing each other, which is provided on the throttle plate 12 and on the web 4' of the piston.

As can be seen in FIG. 4, for example when the damping piston is lowered, i.e. when the piston rod is retracted into the cylinder, this causes the counterflow hole 12 to
The hydraulic pressure generated in a is applied to the aperture plate 12 in the direction of arrow 18.
When the piston rod rotates and the piston rod moves to protrude from the cylinder, the resulting pressure increase in the counterflow chamber 12b causes the throttle plate 1 to
2 is rotated in the opposite direction. Electromagnet winding 1
By controlling the current flowing through 6, the rotational adjustment movement described above is correspondingly reversed, whereby the amount of rotational adjustment of the throttle plate 12 is finely adjusted, and thereby the piston groove The liquid flowing through and thus the damping force are controlled accordingly.

The adjustable damper shown in FIGS. 5 and 6 also
It has a rotationally adjustable throttle mechanism, which in this case is designed as a ring-shaped armature 21 with permanent magnets 20 having alternately different polarities, which ring-shaped armature 21 has a weight It is also directly three-dimensionally connected to a piston body 4 with a bottom cover 4 which is correspondingly hollow due to space constraints. The ring-shaped armature surrounds a winding 23 located centrally on the piston body with a plurality of radial pole shoes 22.
The winding 23 is connected via a switch 24 to one or the other of the two control current conductors 25, 26 alternately in an alternating rhythm in the direction of rotation of the ring-shaped armature 21. The two control current conductors 25, 26 are provided for damping of tensile and compressive loads. The two control current conductors 25, 26 lead through the piston rod 3 to an operating or control mechanism on the vehicle side. .

As can be seen from FIG. 6, in the inner wall of the piston body 4 surrounding the ring-shaped mover 21, an arc-shaped counterflow groove 27 forming both counterflow holes ′27′, 27″ is formed. Both counterflow holes 27', 2
7'' is connected to one or the other working chamber half 5, 6 via supply channels 28', 28''. Inside the counterflow groove 27 are protrusions 2 provided on the outer peripheral surface of the ring-shaped mover 21 that form fluid load surfaces A' on both sides.
1' is in close contact. Here too, the ring-shaped armature 21 is thereby adjusted more or less rotationally in one direction or the other depending on the direction of movement of the damping piston 4 and the hydraulic pressure difference that occurs. This rotational adjustment is counteracted by adjusting the strength of the current flowing through the electromagnet winding, whereby the damping behavior of the damping piston is influenced accordingly. The switch 24 is equipped with a fork 24', and inside this fork,
A driving pin 21″ fixed to the ring-shaped mover 21
has entered, and therefore the switch 24 is switched when the rotational direction of the ring-shaped movable element 21 changes. The winding 23 is thereby loaded with the control current desired in each case for damping tensile and compressive loads, so that, as already mentioned, an arbitrary damping force diagram is obtained. This is because the fluid channels 11, openings 11' and 4' are then more or less opened or constricted in the corresponding direction, as indicated by the double arrows. In this case too,
If the supply of current is cut off for some reason, the buffer piston 4 will not be locked, but rather the fluid will flow due to the hydraulic load on the throttle plate 12 or the ring-shaped movable element through the counterflow hole. The route is opened. In that case only the force of the permanent magnet controls the damping effect.

Instead of a ring-shaped armature 21 with a permanent magnet 20 as shown in FIGS. 5 and 6, an axially movable diaphragm mechanism can also be used. In that case, the fluid passages and counterflow holes are modified accordingly. The axially movable possibility of the throttle mechanism further simplifies the electromagnetic drive.

The controllable damper shown in FIGS. 7 and 8 is particularly simple in construction. In this case, the damping piston 4 is provided with two fluid ducts 31, 31' each for damping compressive or tensile loads. The two fluid ducts 31, 31' are each located at an angle of 90° with respect to one another and are connected by valve spring plates 32, 32', each of which is clamped in a pairwise central region to the end 3' of the piston rod. The valve spring plates 32, 32' are arranged on opposite end faces of the damping piston. Behind the substantially diamond-shaped valve spring plate 32, a supporting plate 33, 33' is provided, which supporting plate 33 or 33' is substantially H-shaped. This support plate 33,3
3' is fixed with a rod-shaped mover 34 arranged on both sides of the valve spring plates 32, 32', and this rod-shaped mover 34 protrudes into the winding 35 of the electromagnet, and the winding The wire 35 is inserted into a blind hole 36 of the buffer piston 4. This winding 35 is connected via the current supply line 3 to a regulating or control mechanism on the vehicle side. The rod-shaped mover 34 is attached to the bottom 3 of the blind hole 36.
6' and the buffer piston 4
is likewise made of ferromagnetic material and therefore produces a corresponding electromagnetic force effect in this case as well. When the piston rod 3 is retracted into the cylinder, the damping piston 4 moves downwards, and the hydraulic pressure created thereby in the fluid passage 31 causes the valve spring plate 32 as well as the support 33 to move upward. At least it will be lifted. This bending deformation is more or less reversed by adjusting the current flowing in the winding 35 and by adjusting the return force acting on the spring plates 32 and 33 via the bar armature 34, so that this bending deformation is more or less reversed. By means of the winding integrated directly into the damping piston 4, a damping diagram with arbitrary characteristics can be obtained. In this case, the electromagnetic return force is relatively large because it directly counteracts the high pressure due to the liquid load.

With the embodiment shown in FIG. 9, the control and regulation behavior for the damping properties is significantly more effective. According to this embodiment, the fluid passage is controlled by one or more valve spring plates 32 which are likewise clamped to the end 3' of the piston rod in the central region. In this case too, a hydraulic compensator is provided between the valve spring plate 32 and the electromagnetic drive which acts against its hydraulic adjustment, increasing the return force of this drive. There is. In this embodiment, this compensating device consists of a support 38 which engages on the rear side of the valve spring plate 32 and is loaded hydraulically against it, which support is mounted on the piston cover 39. The load chamber 40 is supported so as to be movable in the axial direction. This load chamber 40 is a fluid passage 4 provided in the piston cover 39.
1. Via the opening 32'' of the valve spring plate 32 and the fluid passage 42 of the piston body, the working chamber half 6 provided on the counter-current side with respect to the valve spring plate 32, in other words in this case the lower working chamber half 6, is constantly supplied. In this case, the support body 38, which is designed for example as a ball or a piston, has a slightly larger diameter than the fluid channel 31 located below it, so that during the downward movement of the damping piston 4, the valve spring The plate 32 does not bend because the pressure inside the load chamber 40
This is because it is equal to the countercurrent pressure within 1.

A relief passage 43 branches from the fluid passage 41, and this relief passage 43 is connected to the other half of the working chamber,
In this case, it leads to the upper working chamber half 5,
The opening is covered by an auxiliary valve plate 45 held on the outer peripheral surface of the piston cover 39 via, for example, a coupling pin 44. This auxiliary valve plate 45 forms the armature of an electromagnet, the winding 46 of which is suitably arranged in the piston cover 39. The supply wire 47 to the electromagnet is again guided outwards through the hollow piston rod 3. On the underside of the damping piston 4, as indicated by the dash-dotted line 48, there is a correspondingly designed hydraulic compensator with an angular offset of 90° upwards, which compensates for the compression load. Equipped with an electromagnetic drive for damping. The supply line 47' of this drive is likewise guided through the piston rod 3.

When the piston rod 3 protrudes from the cylinder, i.e. during the downward movement of the damping piston 4, a pressure is created in the load chamber 40 via the fluid channels 41, 42, which pressure is applied to the lower working chamber half 6 and the fluid Corresponds to the pressure in the passage 31. This hydraulic pressure is transmitted through the extremely small diameter relief passage 43 and the auxiliary valve plate 45.
, thereby causing the auxiliary valve plate 45 to be more or less lifted, thereby opening the relief passage 4
3 and thus the pressure in the load chamber 40 decreases, so that the valve spring plate 32 is lifted off the piston surface under the action of the hydraulic pressure in the fluid channel 31, thereby opening the fluid channel 31. An auxiliary valve plate 45 forming an armature by adjusting the control current flowing through the winding 46 of the electromagnet on the other side.
is pushed back into its closed position, exerting a more or less restoring force, and in this way the relief passage 43
The hydraulic pressure in the load chamber 40 and the load pressure on the support body (ball) 38 change through the
The hydraulic adjustment or bending force acting on the valve spring plate 32 via the fluid channel 31 is reversed, and a correspondingly controllable restoring force acts on the valve spring plate 32. This allows the damping force to be controlled very quickly. This results in damping force oscillations of significantly higher amplitude and frequency in the damping force piston displacement diagram, for example, within only one movement state, that is, when the piston rod protrudes from the cylinder. With such a damping piston and an electrical control device, therefore, a damping force diagram with arbitrary characteristics, in particular the maximum possible energy absorption, is obtained. It goes without saying that a similar result can be achieved with an electro-hydraulic compensator 48 arranged below the damper piston 4 during compressive loading of the damper.

The damping piston shown in FIGS. 10 and 11 has the same characteristics and mode of operation as the damping piston shown in FIG. 9, but is simpler in construction. In this case, the fluid passage 31', which is available alternately for compressive and tensile loads, is covered by tongues 50' of a valve spring ring plate 50, which valve spring ring shape 50 is connected to the piston body 4'' and the piston cover. 39'.A plurality of supply passages 51 are formed in the piston cover 39' and are uniformly distributed in an annular manner. A load chamber 40' is permanently connected to the lower working chamber half 6. In this annular load chamber 40', a support ring 53 with a packing 52 forming a support is displaceable in the axial direction. This bearing ring 53 is in contact with the rear side of the tongue 50' of the corresponding valve spring ring plate 50 and is located between the fluid passages 31 of the passage group for damping tension loads. A relief passage 43' branches off from the supply passage 51.
The relief channel 43' leads to the other working chamber half 5 and is closed off by an auxiliary valve plate 45' or by correspondingly arranged valve elements. Piston body 4'' and piston cover 3 made of ferromagnetic material
An electromagnet winding 46 is disposed between the coil 9' and the coil 9'. A ring 54 made of non-magnetic material is inserted into the annular recess provided in the piston bottom 39' below the auxiliary valve spring plate 45' or its valve member. This makes the magnetic flux at the auxiliary valve plate 45' fully effective, and by suitably adjusting the control current through the winding 46, the auxiliary valve plate 45'
5' is pressed into its closed position more or less by means of an electromagnet, so that the valve spring ring plate can be pressed via a correspondingly loaded support ring 53 in this case as well, similar to the embodiment shown in FIG. 50 tongue pieces 5
0' is controlled in a correspondingly sensitive manner, thereby again fine-tuning the damping force characteristic curve.

The damping piston shown in FIG. 12 is substantially similar in its structural characteristics to the damping piston shown in FIGS. 10 and 11, and like parts are designated with the same reference numerals. For example, 4'' is the piston body, 39' is the piston cover, 51 is the supply passage, 43' is the relief passage, 40' is the load chamber, and 53 is the sealed support ring 53.
shows. In this case, as an electromagnetic drive for the valve spring plate 45'' covering the relief passage 43',
There is a moving coil 55 mounted on the underside of the valve spring plate 45', which moving coil 55 is arranged in a gap 56 formed between the piston cover parts 39'', 39;
This gap is formed by a ring-shaped permanent magnet 57, a piston body 4'' made of ferromagnetic material, and piston cover parts 39'' and 39.
a piston body 4″ and a ring-shaped permanent magnet 57;
A sleeve 58 made of a non-magnetic material is arranged between the piston rod 3 and the piston rod 3 for magnetic shielding of the permanent magnet.

In this case too, by controlling the control current flowing through the moving coil, a correspondingly controlled return force acts on the auxiliary valve spring plate 45'', thereby opening the relief channel 43' to a greater or lesser extent. As a result, a correspondingly controlled counterpressure acts on the valve spring ring plate 50 via the support ring 53, so that also in this embodiment a flexible control and adjustment of the damping force characteristics can be carried out with great sensitivity. Can be done.

Instead of the support ring 53 shown in FIGS. 10, 11 and 12, another support member, such as a hose, a metal bellows or a diaphragm, can be used as a support for the valve spring ring plate 50, for example a hydraulically expandable member such as a hose, a metal bellows or a diaphragm. A removable support can be used. The advantage of such a support is that it is simple in construction and does not require any special sealing elements. This hydraulically expandable support is likewise connected to the supply channel 51 or to the relief channel 43'.

What is characteristic of all the embodiments described so far is that the throttling mechanism is subjected on the one hand to a force generated by a hydraulic pressure difference, and on the other hand to a force generated magnetically and electrically. It is under the influence of a controlled return force which acts counter to the opening of the throttle mechanism and is zero in the closed state or central rest position of the throttle mechanism. All the embodiments described so far are operated as continuously controlled and simply adjustable dampers, the damping force of which is adjusted or controlled only via adjustable resistances. Furthermore, according to the present invention, variations in damping characteristics caused by manufacturing errors, temperature differences, etc. are easily compensated for.

In all the embodiments described so far, in which only one electromagnetically controllable hydraulic compensator is provided for the load of the throttle mechanism, the second Two electrohydraulic compensation devices can be provided on the damping piston. In this way, the damping force characteristics are correspondingly controlled not only under compressive loads but also under tensile loads of the damper. This control can be carried out manually or automatically depending on various parameters that are indicators of the ride comfort and driving safety of the vehicle.

The damping piston shown in FIGS. 13, 14, 15, 16 and 17 has a single throttle valve with a load chamber for both working directions and an electromagnetically loadable control valve. 1 shows a buffer piston with a body. In this case too, the cylinder chamber filled with a buffer medium, in particular buffer oil, is divided into two working chamber halves A ₁ and A ₂ .
The buffer piston partitioned into the thread 104'
A damping piston body 104 is coupled to the piston rod via a damping piston body 104. This buffer piston body 104
In particular, as shown in the right half of FIG.
The flow passage narrows in a hopper-like manner towards the underside of the piston body and opens into a recess 104'' in the piston body. surrounded.

An insert 105 formed in the shape of a tap is fixed in the buffer piston body 104 by a fixing screw 106 passing through a hole in the buffer piston body 104 . The insert 105 is provided with a ring body 107 made of a permanent magnet.
is held by a pole show plate which is fixed to the lower end of the valve bush 109 which is connected to the insert 10.
insert 105 by means of a ring flange provided in the central notch of 5 and provided at its lower end.
is engaged in. The insert 105 is closed at its lower end by a closure cover 110. A further valve bushing 111 is inserted into this closing cover in its central hole.

Through valve bushes 109 and 111, control valve S
A valve needle 112 belonging to the valve needle 112 is axially passed through, which carries control pistons 113, 114 at both ends thereof, which control pistons can be moved into the bore extensions of the valve bushes 111, 109. is supported by. Both control pistons 113, 114 are respectively provided with an annular groove 113',
114' and a relief groove 11 extending in the axial direction.
3'', 114'', this relief groove serves for pressure compensation on both sides of the piston. The annular grooves 113' and 114' are connected to the valve bushes 111 and 10.
It cooperates with radial holes 111', 109' and 111'', 109'' provided in 9. The radial holes 111', 109' connect via the closing cover 110 and the connecting conduits 115, 116 provided in the insert 105 to the load chamber 104 which surrounds the insert 105 in an annular manner.
The radial hole 111'' is connected to the working chamber half _A2 , and the radial hole 109'' is connected to the notch 104〓
and is connected to the working chamber half _A1 via a connecting passage 104V. The annular passages 113', 114' provided in the control pistons 113, 114 are connected to the radial holes 111', 111' in the valve bushings, as shown in FIG.
11'' inwardly offset, the amount of offset corresponding to approximately half the diameter of the radial bore.

A winding support 120 is provided on the valve needle 112 between its two control pistons 113, 114, which winding support 120 is connected to the closing cover 110.
and the pole show plate 108
The pole shoe plate 108 and the permanent magnet 107 are surrounded by a wall 120' and an electromagnetic moving coil 122 provided thereon. A strong permanent magnetic field is generated between the permanent magnet 107 and the insert 105 and the pole shoe plate 108, each made of a ferromagnetic material, and within this permanent magnetic field, the moving coil 122 moves in one direction or the other depending on externally controlled energization. It is movable axially in the other direction so that an electromagnetic adjustment or return force can be applied via the winding support 120 to the valve needle 112 via its control pistons 113, 114. can. The actual adjustment of the valve needle 112 takes place by hydraulic means, depending on the pressure difference that occurs between the two working chamber halves A ₁ , A ₂ .

Around the insert 105, an annular throttle valve body 150, which covers the load chamber 140 in a hood-like manner, is arranged so as to be axially movable and guided in a sealed manner. This annular throttle valve body 150 is designed and arranged in such a way that it has a total of three hydraulically loaded active surfaces. The first active surface is designed as a surface F ₁ facing the load chamber 140 , which surface F ₁ is essentially loaded by the pressure of the load chamber 140 . On the opposite side, two annular surfaces F ₂ and F ₃ are arranged which extend annularly and concentrically with each other. The surface F ₂ is loaded by the hydraulic pressure in the working chamber half A ₂ directly surrounding the throttle body 105, and the surface F ₃ lies facing the flow channel 131 and is thereby It is constantly loaded by the pressure in chamber half _A1 . The area ratios of these three surfaces are designed such that surfaces F ₂ and F ₃ are approximately equal, and surface F ₁ corresponds to the sum of surfaces F ₂ and F ₃ .
Between the two faces F ₂ , F ₃ , the throttle body 150 is provided with an annular shoulder which separates these two faces from each other, by means of which the throttle body 150 in the rest position is located above the damping piston body 104 . It rests against the closing edge 104 and thereby closes the flow passage 131.

On the underside of the insert 105 or its closing cover 110 there are two leaf springs 160, 170 shown in FIGS. 15, 16 and 17.
The leaf spring 160 acts under tensile loading and has a cruciform shape. The leaf spring 160 is connected by its outer end 163 to the lower edge 15 of the throttle valve body 150.
Hole 1 for screw fixing so as to contact 0'
It is fixed to the closing cover 110 via a fixing bolt 162 passing through the cover 61 . The leaf spring 160 further includes a resilient inner tongue 164 formed by stamping, the inner end 1 of the tongue 164 being formed by stamping.
By means of 64', the tongue 164 is placed over the control piston 113 of the control valve S via the control piston 113. The inner end 164' of the tongue is attached to the control piston 113 in such a way that the opposite deflection of the outer end 163 is gradually increased by the throttle body 150 contacting the end during the opening movement of the throttle body 150. It is gradually applied more strongly. The leaf spring 170, which acts under compressive loading, has an approximately rectangular shape. This leaf spring 170 also has its outer end 1
71 rests on the lower edge of the throttle valve body 150 or on the end 163 of the leaf spring 160 and tightens the cross-shaped leaf spring 163 into a bridge shape. The leaf spring 170 is provided with a tongue 172, also formed by stamping, which at its inner end is connected to the entrainment flange 112 which is seated on the opposite outer end of the valve needle 112. ' is engaged from below.

As can be seen in particular from FIG. 4, when the piston rod protrudes from the cylinder, i.e. during the tensile loading of the damper, the valve needle 112 moves to the left due to the hydraulic load, thereby causing The conduit connection located between the control piston 114 and the working chamber half A ₁ is significantly constricted, and the fluid connection located between the control piston 113 and the working chamber half A ₂ is relatively wide open; As a result, the pressure inside the load chamber 140 decreases, and the surfaces F ₂ and F ₃ of the throttle valve body 150
is loaded with different pressures, which causes the throttle valve body 150 to move to the left and cause the annular shoulder 151 to move to the left.
and the closing edge 104 are more or less opened. At the same time, the throttle valve body 1
This movement of 50 causes the cruciform leaf spring 160
curves upward at its outer end 163;
As a result, the inner end 164' of the tongue 164 is pressed increasingly tightly against the control piston 113 of the valve needle 112, which results in a corresponding mechanical return force. In addition to this, by controlling the current flowing in the moving coil 122, an electromagnetic adjusting or restoring force can be applied to the valve needle 112. During compressive loading of the damper, when the piston rod plunges deeper into the damping cylinder, the valve needle 112 is adjusted to the right, so that the load chamber 140 is connected to the working chamber half A ₁ with less throttling effect. , is connected in a highly constricted manner to the working chamber half A ₂ , so that in this case too the throttle valve body 150 carries out an axial opening movement and closes the throttle gap between the annular shoulder 151 and the closing edge 104 . Open more or less.
In this case, a corresponding mechanical restoring force is applied to the entraining flange 11 via the leaf spring 170 and its tongue 172.
2' and thus on the valve needle 112, the force of which acts more or less counteracting the hydraulic adjustment force. In this case as well, by controlling the current flowing in the moving coil 122, the valve needle 11
2 is additionally loaded magnetically in one direction or the other, whereby the damping force is controlled or adjusted.

Effects of the Invention According to the invention, a stepless regulation that is extremely sensitive linearly related to the piston speed is achieved. This is because, while the throttle mechanism is moved by the hydraulic load pressure to more or less open the fluid duct into the corresponding open position or offset position, this movement is caused by a counter-acting return of the electromagnetic drive. This is because they are more or less stopped by force.

[Brief explanation of the drawing]

FIG. 1 is a vertical sectional view of the first embodiment of the present invention, and the second
The figure is an exploded perspective view of the first embodiment, Figure 3 is an explanatory diagram of the operation of the embodiment of Figure 1, Figure 4 is a principle diagram of Figure 3,
FIG. 5 is a vertical sectional view of the main part of the second embodiment of the present invention, FIG. 6 is a partially sectional top view of FIG. 5, and FIG. 7 is a vertical sectional view of the main part of the third embodiment of the invention. , FIG. 8 is a top view of FIG. 7, FIG. 9 is a vertical sectional view of the main part of the fourth embodiment of the present invention, and FIG. 10 is a partial longitudinal sectional view of the main part of the fifth embodiment of the invention. , Figure 11 is the 10th
12 is a partial vertical sectional view of the main part of the sixth embodiment of the present invention, and FIG. 13 is a combination of a top view and a bottom view of the seventh embodiment of the present invention, FIG. 14 is a sectional view taken along the - line in FIG. 13, FIG. 15 is a plan view of the spring member acting under a tensile load, FIG. 16 is a plan view of the spring member acting under a compressive load, and FIG. 17 is a plan view of the spring member acting under a compressive load. It is a side view of the same spring member. 1...Cylinder, 2...Packing, 3...Piston rod, 4...Buffer piston, 5, 6...Working chamber half, 7...Chamber, 8...Partition piston, 9, 10
...Disk, 11...Fluid passage, 12...Aperture plate,
13... Taking pin, 14... Piston head, 1
5...Mover, 16...Winding.

Claims (1)

Claims: 1. Adjustable damper, in particular for motor vehicles, comprising a cylinder containing a damping medium, a sealed piston rod extending into the cylinder and arranged for axial movement, and a damping piston. The damping piston divides the cylinder chamber into two working chamber halves, and is equipped with a fluid passage for producing a damping force, the effective cross section of which is the throttling mechanism and the electromagnet acting on it. a drive device, the electromagnetic drive device having a magnetic circuit and a winding, the magnetic circuit and the winding being located in close proximity to the fluid passageway and its throttling mechanism; In the type, the aperture mechanism 12 is
A control device comprising a fluid load surface A which produces an adjustment force dependent on the fluid pressure difference between the two working chamber halves 5, 6, and an electromagnetic drive acting counteracting this adjustment force. Mechanism 1 to reduce possible return force
The return force of the electromagnetic drives 14 to 16 is zero at the rest position of the throttle mechanism 12 and increases as the hydraulic adjustment of the throttle mechanism 12 increases. a throttle mechanism rotatably supported within the damping piston and having a flow aperture;
This flow opening is formed in such a way that it is more or less matched to the fluid passage of the stationary piston bodies 9, 10 and is located between the rotatable throttle mechanism 12 and the stationary piston bodies 9, 10 on the one hand and at least two flow-receiving openings 12a, 12b connected to the other working chamber half 5, 6, respectively;
is provided, and within this opening, an aperture mechanism 1 is provided.
2, the aperture mechanism 12
and a fluid load surface A provided on the piston bodies 9 and 10,
An adjustable damper characterized in that A′ are located opposite each other. 2. Piston head 1 of a rotating electromagnet, in which the throttle mechanism 12 is designed in the form of a plate and forms an electromagnetic drive via a driver pin 13 or the like.
4. A damper according to claim 1, wherein the damper is fixedly connected to a movable element (15) rotatably supported in the damper (15). 3. In addition to the flow opening 12', the diaphragm plate 12 is provided with flow-receiving openings 12a, 12b arranged on both sides of the stationary piston body web 4', which openings extend in the direction of rotational adjustment of the diaphragm plate. 3. A damper according to claim 2, wherein the damper has a fluid loading surface A extending at right angles thereto. 4. The throttle mechanism is designed as a ring-shaped armature 21 with permanent magnets 20 of alternatingly different polarities, which ring-shaped armature is rotatably mounted in the piston body 4'', and a plurality of radial pole shoes 22 surrounding a centrally located winding 23 of the piston body;
2. A damper according to claim 1, wherein the winding forms a winding of an electromagnet forming an electromagnetic drive. 5. The piston body 4'' is provided with a switch 24 to be operated by the ring-shaped mover 21, which switches the tensile load and the compressive load with the alternating rhythm of the rotational direction of the ring-shaped mover 21. The damper according to claim 4, wherein the winding 23 is connected to one and the other of the two control current supply conductors 25 and 26 for damping.6 On the inner wall of the piston body surrounding the ring-shaped movable element 21, Openings 27', 2 receiving both said flows
An arc-shaped groove 27 for receiving the flow is formed, and the ring-shaped movable element 2 is inserted into this groove.
6. The damper according to claim 5, wherein the projections 21' provided on the outer circumference of the damper 1 and forming the fluid load surfaces A' on both sides are sealed and protrude. 7 Adjustable damper, in particular for motor vehicles, comprising a cylinder 1 containing a damping medium, a piston rod 3 sealed and arranged so as to be axially movable projecting into this cylinder, and a damping piston 4, 104. This buffer piston divides the cylinder chamber into two
two working chamber halves 5, 6; fluid passages 31, 3 which are partitioned into A1 and A2 and which generate a buffering force;
1', 131, and its effective cross section is
It is adjustable by means of the throttle valve body 32, 50, 150 and a controllable electromagnetic drive acting against its opening force, which drives the magnetic circuit attached to the damping piston 4, 104. winding 46,
55, 122, and throttle valve bodies 32, 5.
0,150 is for both working chamber halves 5, 6 or A
1 and A2, which are equipped with fluid load surfaces F ₁ , F _{2 ;} A hydraulic compensation device is provided between the electromagnetic drive device 46, 55, 122, which acts against the throttle valve body 32, 50, 122, and which strengthens the return force. 150, the load chamber 40 is arranged on the side opposite to the fluid passages 31, 31', 131 and acts hydraulically in the opposite direction on the throttle valve body.
The load chamber 40 is connected to the two working chamber halves 5, 6 or A ₁ , A ₂ via separately extending fluid connection channels 41, 43 or 51, 43' or 115, 116. , fluid passage 31,
Connecting passage 43, 4 guided to the working chamber half 5 or A ₂ located on the side opposite to 31', 1311
3', 115, an electromagnetic drive device 46, 5
5,122 controllable auxiliary throttle valve 45,
45', 45'', 113. 8. The throttle valve body is formed as a valve spring plate 32, on the rear side of which a support body 38 engages. , this support is movably mounted in the load chamber 40 , and the auxiliary throttle valve is connected to the associated connecting channel 4 .
3, 43' is designed as a hydraulically elastic auxiliary valve plate 45, which is engaged by an electromagnetic drive 46 with an adjustable return force. Claim No. 7
Damper described in section. 9 The support 38, its load chamber 40, its liquid connection passages 41, 43 and the auxiliary valve plate 45 are connected to the valve plate 32.
The cover 3 of the buffer piston 4 is mounted on the back of the
9. The damper according to claim 8, wherein the damper is mounted on or in the damper. 10 As an electromagnetic drive, an electromagnetic winding 46 inserted into the piston cover 39 made of ferromagnetic material serves, the armature of which is
The damper according to claim 9, wherein the damper is formed by an auxiliary valve plate 45 covering a fluid connection passage 43 forming a relief passage. 11 As an electromagnetic drive for controlling the auxiliary valve plate 45'', a moving coil 55 attached to the auxiliary valve plate 45'' serves, which moves the annular gap of the permanent magnet 57 on the piston 4. 10. The damper according to claim 9, wherein the damper is inserted within the damper. 12. Claim 8, in which the hydraulically loaded support is designed as a ball or a piston.
The damper according to any one of items 1 to 11. 13 Support ring 5 in which the hydraulically loaded support is arranged in a cylindrically designed load chamber 40
3, the supporting rings 50' being spaced from each other on the outer periphery of the valve plate 50 and covering the associated fluid channel 31;
A damper according to one of claims 8 to 11, each of which engages an opening of a fluid channel 31' belonging to another damping direction, which is located freely between them. . 14 On the load side of the throttle valve body 150, which is located opposite to the load chamber 140, in addition to the first load surface F3 that covers the fluid passage 131, there is a second load surface _F3 of approximately the same size.
It has a load surface F ₂ of , and this load surface is the valve body 1
Both fluid connection passages 115, 116 which are loaded by the fluid pressure in the working chamber half A ₂ surrounding 50 and which lead from the load chamber 140 to both working chamber halves A ₁ , A ₂ Control throttles 113, 114 are inserted therein, which control throttles are controlled by a control valve S that is regulated as a function of the pressure difference between the two working chamber halves _A1 , _A2 ; The control throttle thereby connects the load chamber 140 with a small amount of restriction to the working chamber half with the lower fluid pressure in each case and to the working chamber half with the higher fluid pressure in each case. The damper according to any one of claims 7 to 13, which is connected with a significant amount of constriction. 15 Between the throttle valve body 150 and the control valve S, a mechanical return force is applied to the control valve, which acts inversely to the respective hydraulic adjustment force depending on the opening degree of the throttle valve body 150. 15. The damper according to claim 14, wherein return spring members 160, 170 are provided. 16 Fluid connection channel 1 through which the damping piston leads from the control valve S and its control throttles 113, 114 and from the load chamber half 140 to both working chamber halves A ₁ , A ₂
15, 116;
This insert supports around its periphery an annularly formed load chamber 140 and an annular throttle valve body 150 that covers this in a hood-like manner.
0 and has an annular shoulder 151 which is axially movable and closely slidably guided around the insert on both sides of the insert and which separates its two annularly extending load surfaces F ₂ , F ₃ from each other. , with its annular shoulder touching an annularly extending closing lip 104 located in the piston body in the vicinity of a fluid passage 131 opening into the piston body. damper. 17 The control valve S is supported for axial movement within the insert 105 and has a valve needle 11 passing through the insert.
2, the valve needle is equipped with control pistons 113, 114 at both ends, between which the valve needle 112 is provided with a winding support 120, the winding support of which An electromagnetic moving coil 122 is arranged on the periphery 120', which moving coil surrounds one permanent magnet 107 provided in the insert 105. The damper according to any one of the items. 18. Both control pistons 113, 114 each have one axially extending relief hole 113'',
114'' and a circumferentially extending annular passageway 113', 11
4' and is movably supported in valve bushes 109, 111 provided on both sides of the insert 105, with radially extending holes 109', 109'', 111', 111'' in the valve bushes. are provided, the holes being provided in the insert 105 and connecting passages 115, 116 leading to the load chamber 140;
Each annular passage 1 communicating with each working chamber half A ₁ , A ₂ and provided in the control piston 113 , 114
13', 114' are the radial holes 10 provided in the valve bushes 109, 111 surrounding the annular passage.
18. The damper of claim 17, wherein the damper is offset toward the interior of the insert by approximately half its diameter with respect to 9', 111'. 19 A return spring is arranged on the side of the insert 105, which is closed by the closing cover 110, opposite the piston body 104 and the leaf springs 160,1
70, the outer end of this leaf spring rests on the throttle valve body ring 150, and of the two leaf springs 160, 170, the leaf spring 160 that acts during a tensile load has a cruciform shape. and is provided with an inner tongue (164) shaped in the opposite direction in relation to its outer end 163, the inner end 164' of the control valve S The leaf spring 170 which is in contact with the opposite control piston 113 and which acts under compressive load is of substantially square design and has its outer end 17
Inner tongue 1 springing in the opposite direction in relation to 2
72, the inner end of the tongue engages a driving flange 112' located at the opposite outer end of the valve needle 112. Any one of the items up to
Damper described in section. 20 A cross-shaped leaf spring 160 is screwed onto the closing cover 110 of the insert 105, the screwing point 161 being outside the elastic tongue 164 and close to its inside end 164'. 20. A damper as claimed in claim 19, located in the leaf spring region.