DE102014005602A1 - Storage of a damper and / or strut on a vehicle - Google Patents

Abstract

The invention relates to a bearing (12) of a damper and / or suspension strut (10) on a vehicle (110), with at least one spring element (30) accommodated in a housing (20). By means of the spring element (30) at least one damper and / or spring component (40) of the damper and / or strut (10) on the housing (20) can be supported. By means of a compression device (50), the at least one spring element (30) with a biasing force (36) can be acted upon. The compression device (50) has an adjustable compression chamber (52), which via a fluid channel (42) of the damper and / or spring component (40) with a relative movement between the damper and / or spring component (40) and the housing ( 20) of movable fluid can be filled.

Description

The invention relates to a mounting of a damper and / or strut on a vehicle according to the preamble of patent claim 1.

Such storage is already out of the DE 10 2007 026 471 B4 to be known as known. The local bearing is designed as a strut support bearing for a strut and has at least one piston guided in a housing, by means of which a prestressable working spring under the action of an external energy source biased and thus the rigidity of the bearing can be varied. In other words, by means of the external energy source, which is designed, for example, as a hydraulic system, pneumatic system or electromagnet, a requirement-specific adjustment of the preload of the bearing can take place as a function of a particular driving situation. Thus, on the one hand by this bias the desire of the driver, for example, particularly sporty or, alternatively, particularly comfortable driving sequence be performed and, accordingly, a greater or smaller rigidity of the local shock absorber using the external energy source can be brought about. However, the local warehouse is designed particularly complex, which is associated with increased production costs.

Object of the present invention is to provide a storage of the type mentioned, by means of which the damper and / or strut in a particularly simple and cost-effective manner prestressed and thereby the stiffness of the damper and / or shock absorber is adjustable.

This object is achieved by a storage with the features of claim 1. Advantageous embodiments with expedient developments of the invention are specified in the other claims.

In order to provide a storage of the type mentioned, in which the bias and rigidity of the damper and / or shock absorber is adjustable in a particularly simple and cost-effective manner, it is inventively provided that a compression device is provided with an adjustable compression chamber, which be filled via a fluid passage of the damper and / or spring component with a movable under relative movement between the damper and / or spring component and the housing fluid while the at least one spring element with a biasing force can be acted upon.

This storage corresponds to a damper head bearing means of which forces of the damper and / or strut can be introduced into the vehicle. These forces include, for example, forces acting on a wheel of the vehicle as a result of bumps or, for example, pitching or rolling movements of the vehicle body relative to the ground. The spring element may be formed, for example, as a head bearing rubber pad, by means of which the damper and / or spring component is decoupled at least partially during rebound or compression, ie accordingly in the tensile or compressive direction of the structure of the vehicle. Under this partial decoupling is to be understood that the damper and / or spring component is not rigidly connected by means of storage on the structure of the vehicle, but instead takes place under the intermediary of the prestressable spring element, a force introduction into the structure. This force is introduced under elastic deformation of the spring element, wherein at least a part of the forces (for example due to uneven floors) are transmitted to the structure under elastic deformation of the spring element. When compression by a certain travel in conjunction with a certain, the compression inducing force a certain compression work is done (the compression work is the product of force and compression travel), which work in other words at least partially in a deformation work of the spring element (for example Head bearing rubber pad) flows in and thereby at least partially converted into heat. The compression spring is supported by the housing on the structure of the vehicle.

The compression device has a compression chamber, which is adjustable in volume. An increase in the volume of the compression chamber takes place when a fluid (for example hydraulic oil) flows into the compression device or the compression chamber and accordingly causes an expansion of the compression chamber. When the fluid flows out, in turn, the volume of the compression chamber is reduced. By adjusting the compression chamber, the spring element is now pretensioned or relaxed depending on whether the volume of the compression chamber is increased or decreased. Unlike in the prior art, the compression chamber or the compression device via the fluid channel of the damper and / or strut or the damper and / or spring component can be filled with the fluid and accordingly the biasing force on the at least one spring element exercisable. The filling of the compression device with the fluid, as well as the outflow of the fluid from the compression device is carried out under the relative movement between the damper and / or spring component and the housing and accordingly during compression or rebound of the damper and / or strut. Accordingly, the fluid within the damper and / or spring component is moved, wherein, for example, the fluid contained in a cylinder of the damper and / or strut displaced due to the movement of a piston of the damper and / or strut, and thereby passed into the compression chamber becomes. In other words, therefore, the compression chamber in response to the piston movement in the cylinder with the fluid acted upon, here - in contrast to known from the prior art embodiments - no external fluid supply or energy supply, for example by means of an external hydraulic system or pneumatic system is necessary. The energy for moving the fluid is thus caused by the relative movement between the piston and the cylinder and the concomitant displacement of the fluid contained in the cylinder.

There is thus a stress-dependent automatic adjustment of the stiffness of the bearing (damper head bearing) of the damper and / or strut relative to the structure of the vehicle, ie to the body of the vehicle. At low damper load of the damper and / or strut, the bias and thus the rigidity of the bearing is low for better vibration damping and high at high damper stress to maintain the strongest possible wheel-carriageway contact.

Further advantages, features and details of the invention will become apparent from the following description of a preferred embodiment, and with reference to the drawings.

These show in:

1 a schematic sectional view of a damper strut, which has at its storage a by means of a compression means acted upon by a biasing force spring element;

2 a schematic sectional view of the damper strut, which in the present case can be actively damped by means of an electrically operated actuator;

3 a further sectional view of the damper strut, which is supported in the present case via a housing on a vehicle;

4 a further sectional view of the damper leg whose spring element is prestressed by means of two compression means; and in

5 a further sectional view of the damper strut whose spring element by means of the two compression means can be prestressed, wherein the damper strut is actively damped by means of the actuator.

1 shows a schematic sectional view of a damper and / or shock absorber, which hereinafter referred to as damper leg 10 referred to as. The shock absorber leg 10 serves to dampen pulses or forces which, for example, as a result of bumps or pitching or rolling movements of a wheel of a vehicle shown here simplified 110 be directed in its construction. To introduce forces or pulses or damped energy is the shock absorber leg 10 about a storage 12 with the vehicle 110 connected. Warehousing 12 is presently designed as a damper head mounting. Warehousing 12 has in the present embodiment a in a housing 20 of the shock absorber leg 10 recorded spring element 30 , as well as another spring element 32 on. The spring element 30 and the further spring element 32 are presently designed as a headstock rubber pad and are used to decouple a damper and / or spring component of the damper strut 10 wherein the damper and / or spring component hereinafter referred to as damper component 40 referred to as. The spring element 30 as well as the further spring element 32 are present in each case on different sides of a with the housing 20 connected head bearing housing 22 of the shock absorber leg 10 arranged. The head bearing housing 22 of the housing 20 is body-tight with the vehicle 110 connected. When rebounding the damper leg 10 becomes the further spring element 32 compressed and accordingly elastically deformed. In contrast, when rebounding the spring element 30 relieved. During compression of the shock absorber leg 10 becomes the spring element 30 in the arrow direction of a clarified by an arrow biasing force 36 between the head bearing housing 22 and a compression device 50 compressed, whereas the other spring element 32 is relieved. To achieve the most comfortable damping effect, includes the shock absorber leg 10 in this case, in addition to the damper component designed as a piston rod 40 also a piston 48 which is on a piston area 46 the damper component 40 is arranged. The piston area 46 corresponds to an end of the damper component in the present embodiment 40 , ie the piston rod, on which the piston 48 is fixed. The piston 48 is in a cylinder 60 of the shock absorber leg 10 guided. The cylinder 60 includes a damping fluid, which is presently designed as hydraulic oil. The fluid is located in a working space 62 of the cylinder 60 , this working space 62 through the piston 48 in a first subspace 64 and in a second subspace 66 is divided. The cylinder 60 is with a wheel not shown here of the vehicle 110 coupled and is due to the wheel under Compression of the subspace 64 contained hydraulic oil when rebounding in the opposite direction of the arrow of the biasing force 36 and under compression of the second subspace 66 contained hydraulic oil during compression in the arrow direction of the biasing force 36 emotional.

The compression device 50 serves in the present embodiment to the spring element 30 with the preload force 36 to act on. The compression device 50 has an adjustable compression chamber 52 on, which via a fluid channel 42 the damper component 40 with the under the relative movement (compression and rebound of the shock absorber leg 10 ) movable fluid (hydraulic oil) can be filled. During the relative movement (compression and rebounding) the cylinder becomes 60 and thereby due to the transmission of power in the first compartment 64 or the second subspace 66 contained fluid on the piston 48 also the damper component 40 moved relative to the housing. The fluid channel 42 extends in the 1 shown embodiment axially along and within the damper component 40 , ie along the piston rod, and flows on the one hand into the compression chamber 52 the compression device 50 and, on the other hand, under the intermediary of each present in the piston 48 arranged throttle check valves 70 in the first subspace 64 or in the second subspace 66 , This according to the drawing level in 1 left throttle check valve 70 allows an inflow of the in the first subspace 64 contained hydraulic oil under particularly low flow resistance, provided the first compartment 64 (when rebounding, ie during the movement of the cylinder 60 opposite to the arrow direction of the preload force 36 ) is compressed. In the opposite direction of movement of the cylinder 60 however, the hydraulic oil flows under heavy throttling of a throttle of the left throttle check valve 70 in the first subspace 64 one.

Conversely, it behaves when looking at the right throttle check valve 70 , That in the second subspace 66 contained hydraulic oil flows during compression, ie during the movement of the cylinder 60 via the right throttle check valve 70 along the arrow direction of the biasing force 36 and due to the consequent compression of the second subspace 66 contained fluid (hydraulic oil) under particularly low flow resistance through the fluid channel 42 in the compression chamber 52 , When rebound, however, the inflow of the fluid is in the second subspace 66 by means of a throttle of the right throttle check valve 70 throttled.

The compression device 50 has a relative to the housing 20 axially displaceable first compression element 54 on, by means of which a second compression element 56 the compression device 50 which is at one end 44 the damper component 40 connected to this, relative to the housing 20 guided is movable. In the first compression element 54 it is an axially displaceable compression cylinder, by means of which in this case the spring element 30 compressed and thus can be stiffened, provided the compression chamber 52 filled with the fluid and thereby the first compression element 54 and the second compression element 56 under magnification of the first compression element 54 and the second compression element 56 formed compression chamber 52 be moved apart.

As already described, by means of the two throttle check valves 70 the fluid during compression of the first subspace 64 (Rebound) or when compressing the second subspace 66 (Compression) under particularly low resistance via the fluid channel 42 in the compression chamber 52 inflow, whereby the first compression element 54 and the second compression element 56 under enlargement of the compression chamber 52 be moved apart, and thereby the biasing force 36 on the spring element 30 is exercised. For heavy use of the shock absorber leg 10 So, for example, when driving fast over several bumps or cobblestones, there is a particularly high-frequency compression of the first subspace 64 or the second subspace 66 , whereby a part of the fluid (hydraulic oil) escapes particularly quickly from the working space 62 over the fluid channel 42 in the compression chamber 52 the compression device 50 flows. Accordingly, at high frequency stress on the damper leg 10 the spring element 30 especially strong due to the prestressing force 36 compressed and thus the overall stiffness of the shock absorber leg 10 elevated. When driving slowly, or at low-frequency load (for example, when driving slowly over isolated bumps) that is in the work area 62 contained compressed fluid in a particularly small extent, whereby the compression device 50 a particularly low preload force 36 on the spring element 30 exerts and accordingly the stiffness of the damper leg 10 is reduced.

The ratio between that in the compression device 50 Inflowing to the outflowing fluid depends on the one hand on load factors such as the vehicle weight (or the wheel load), the vehicle speed and the vibration excitation, and accordingly on the type of stress on the damper leg 10 from. On the other hand, this ratio is also, for example, by the throttling effect of the throttles compared to the flow rate of the fluid through the freewheeling area ( against the direction of return) of the two throttle check valves 70 affected. Thus, there is a superposition of the influences of constructive properties of the fluid-carrying components (such as the throttle check valves 70 , the fluid channel 42 and for example the compression device 50 ) with the load factors of the shock absorber leg 10 ,

Both the bias of the spring element 30 , as well as the relaxation of the spring element 30 takes place in contrast to known from the prior art embodiments without external power supply and is thus in a particularly small space and particularly inexpensive to implement simple and with considerable weight savings. To improve the spring action, the cylinder is 60 additionally by means of a bellows 14 under the mediation of the housing 20 on the vehicle 110 supported, with the bellows 14 as a rolling bellows, bellows (in the present embodiment each filled with air) or alternatively could be designed as a spring. As in 1 is recognizable, is the first subspace 64 or the second subspace 66 via respective additional throttle check valves 80 with a hydraulic accumulator 100 connected. In the present embodiment, the hydraulic accumulator 100 as indicated by a corresponding hydraulic symbol, a gas tensioning device. By means of additional throttle check valves 80 is a particularly unhindered inflow of hydraulic oil from the hydraulic accumulator 100 in the first subspace 64 or the second subspace 66 allows, whereas an outflow from the first compartment 64 and the second subspace 66 throttled takes place.

While in 1 the damping of a passive air spring strut (shock absorber leg 10 ) is shown, clarifies 2 in a further schematic sectional view of an alternative embodiment in which an active damping of the air spring strut (damper strut 10 ) he follows. In both cases, however, the hydraulic power source of the hydraulically pre-compressible and thus adjustable in its stiffness head bearing (by bias of the spring element 30 ) the strut 10 Even the worse the road conditions, so the higher frequency the wheel movement or the higher the jounce or rebound of the wheel and thus the cylinder 60 , The greater in the embodiments shown, the compression of the head bearing, or the spring element 30 , whereby the spring element 30 and make the headset stiffer.

As already with reference to 1 shown form the first compression element 54 and the second compression element 56 also in the 2 embodiment shown, the adjustable compression chamber 52 , by the filling with the fluid, the biasing force 36 on the spring element 30 is adjustable. Again, the damper component 40 (the piston rod) the piston 48 on which in the workroom 62 of the cylinder 60 of the shock absorber leg 10 guided is movable. As already with reference to 1 shown is also the fluid channel 42 of in 2 shown embodiment, mediation of the two throttle check valves 70 with the workspace 62 of the cylinder 60 fluidly coupled.

In contrast to 1 shows 2 However, an embodiment in which the damper leg 10 under pressure of the cylinder 60 with the fluid by means of an electrically operated actuator 90 under the mediation of the two additional throttle check valves 80 is actively damped. For this purpose, the electrically operated actuator 90 For example, be designed as a fluid pump, which can be controlled by means of a proximity sensor not shown here, or controlled. The proximity sensor could, for example, as an optical sensor of the vehicle 110 be formed, by means of which located in the direction of travel bumps can be detected even before driving over these bumps and depending on a selective filling of the first subspace 64 or the second subspace 66 can be done, thereby actively, for example, lifting the wheel of the vehicle 110 when driving over the bumps is enabled. This active lifting of the wheel by filling the first subspace 64 or the active lowering of the wheel by filling the second subspace 66 leads to a particularly comfortable driving experience, as uneven ground, such as bumps or potholes, can be effectively compensated active particularly effective.

The following embodiments already contain reference to FIG 1 respectively 2 shown features, which is why in the following only the differences should be discussed.

3 shows a sectional view of an installation position of the damper strut 10 on the vehicle 110 , 3 shows the damper component 40 (the piston rod) with the already based on 1 and 2 shown central pressure oil guide, so the fluid channel 42 through which the hydraulic oil enters the compression chamber 52 the compression device 50 can flow in. The second compression element 56 is present as a holder of the head stock compression device, so the compression device 50 , trained and piston rod-fixed, so at the end 44 the damper component 40 (Piston rod) fixed. As in 3 recognizable, is the second compression element 56 axially within the first compression element 54 . which is designed as an axially displaceable compression cylinder, displaceable. The first compression element 54 is present in a head storage cup 24 of the shock absorber leg 10 created, with the head stock cup 24 as well as the first compression element 54 axially on the end area 44 the damper component 40 is displaceable. The head bearing cup 24 encloses in the present embodiment designed as a head bearing rubber pad (for piston rod decoupling in tension and compression) trained spring element 30 at least in certain areas. By filling the compression chamber 52 becomes the spring element 30 between the body-mounted head bearing housing 22 of the housing 20 and the head stock cup 24 clamped and thereby elastically deformed, or under application of the biasing force 36 biased. By means of the further spring element 32 In particular, a damping occurs during rebound of the damper leg 10 , wherein the damper component 40 under the intermediary of the further spring element 32 on the body-mounted head bearing housing 22 is supported. A cathedral camp 26 storage 12 (Damper head bearing) serves to limit the axial displacement of the damper component 40 ,

4 shows in a schematic sectional view of another embodiment of the passive damper leg 10 which in the present case, a bias of the spring element 30 without the use of an external source of energy (for example hydraulic system). In the present case are several fluid channels 42 provided by means of which mediate the throttle check valves 70 or the additional throttle check valves 80 the fluid from the workspace 62 or from the hydraulic accumulator 100 in the present two compression devices 50 can be directed. Im in 4 embodiment shown are both compression devices 50 body test, whereby by filling with hydraulic oil, the spring element 30 can be particularly biased, since the spring element 30 between the two compression devices 50 is trapped in the Hydraulikölbeaufschlagung. 4 Thus shows an embodiment with two head bearing compression devices and external oil supply by means of the respective fluid channels 42 , which in contrast to the in 1 and 2 shown embodiments not within the damper component 40 are arranged. 5 shows that already by means of 4 illustrated embodiment with the difference that by means of the electrically operated actuator 90 an active damping of the shock absorber leg 10 (Air strut) can be done.

LIST OF REFERENCE NUMBERS

10

damper strut

12

storage

14

bellows

20

casing

22

Head bearing housing

24

Head bearing mount frame

26

Domlager

30

spring element

32

another spring element

36

preload force

40

damper component

42

fluid channel

44

end

46

piston area

48

piston

50

compression device

52

compression chamber

54

first compression element

56

second compression element

60

cylinder

62

working space

64

first subspace

66

second subspace

70

Speed Controller

80

Additional speed controller

90

actuator

100

hydraulic accumulator

110

vehicle

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102007026471 B4 [0002]

Claims (8)

Storage ( 12 ) of a damper and / or strut ( 10 ) on a vehicle ( 110 ), with at least one in a housing ( 20 ) received spring element ( 30 ), by means of which at least one damper and / or spring component ( 40 ) of the damper and / or strut ( 10 ) on the housing ( 20 ) is supportable, characterized in that a compression device ( 50 ) with an adjustable compression chamber ( 52 ) is provided, which via a fluid channel ( 42 ) of the damper and / or spring component ( 40 ) with a relative movement between the damper and / or spring component ( 40 ) and the housing ( 20 ) movable fluid and thereby the at least one spring element ( 30 ) with a biasing force ( 36 ) can be acted upon. Storage ( 12 ) according to claim 1, characterized in that the compression device ( 50 ) relative to the housing ( 20 ) axially displaceable first compression element ( 54 ), by means of which a second compression element ( 56 ) of the compression device ( 50 ), which at one end region ( 44 ) of the damper and / or spring component ( 40 ) is connected to this, relative to the housing ( 20 ) is guided guided. Storage ( 12 ) according to claim 2, characterized in that the first compression element ( 54 ) and the second compression element ( 56 ) the adjustable compression chamber ( 52 ), by the filling with the fluid, the biasing force ( 36 ) on the at least one spring element ( 30 ) is adjustable. Storage ( 12 ) according to one of the preceding claims, characterized in that the damper and / or spring component ( 40 ) a piston ( 48 ), which in a work space ( 62 ) of a cylinder ( 60 ) of the damper and / or strut ( 10 ) is guided guided. Storage ( 12 ) according to claim 4, characterized in that the fluid channel ( 42 ) by switching at least one throttle check valve ( 70 ) with the working space ( 62 ) of the cylinder ( 60 ) is fluidically coupled. Storage ( 12 ) according to one of the preceding claims, characterized in that the damper and / or strut ( 10 ) under the action of the cylinder ( 60 ) with the fluid by means of at least one electrically operated actuator ( 90 ) by mediation of at least one auxiliary throttle check valve ( 80 ) is actively damped. Storage ( 12 ) according to one of the preceding claims, characterized in that the damper and / or spring component ( 40 ) is designed as a piston rod. Storage ( 12 ) according to one of the preceding claims, characterized in that the fluid is designed as hydraulic oil.

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