DE10024572B4 - Spring damper system with double roll - Google Patents

Abstract

Combined spring-damper system for supporting wheel suspensions or axles on a vehicle body with a bellows arranged between a wheel-carrying or wheel-guiding connection and a connection on the vehicle body side,
- wherein the hose rolling bellows is an at least two-part double rolling bellows (11, 51),
- Wherein the upper and the lower end of the mounted Doppelrollbalgs (11, 51) are each secured to a rolling piston (22, 62),
- One of the rolling piston (22) on the chassis structure and the other rolling piston (62) is attached to the suspension or axle,
- Wherein the outer circumferential surface of the Doppelrollbalgs (11, 51) on an outer bell (12, 52) rests and
- The bellows space (5) is filled with a fluid (1) and communicates with a chassis or vehicle side mounted hydraulic accumulator (30).

Description

The The invention relates to a combined spring-damper system for supporting suspension or axles on a vehicle body with one between a wheel-bearing or bike-leading Connection and a vehicle body-side connection arranged Flexible member.

The DE 199 52 799 A1 discloses a suspension device, in particular for use in a front fork of a two-wheeled vehicle. The suspension device has two coaxially arranged spring elements, each with a rolling bellows and a rolling piston. The rolling piston of the two spring elements are rigidly connected together.

From the DE 297 02 927 U1 is a spring-damper system known, which consists of a displacer without bellows, a hydraulic accumulator and a hydraulic line connecting these parts. In the hydraulic line, a mechanical throttle valve is arranged. The displacer connects the vehicle wheel suspension to the vehicle body as known in a hydropneumatic suspension system. The system is filled with a hydraulic fluid. The latter is displaced during compression of a driving zeugrades through the throttle valve in a hydraulic accumulator. The flow resistance of the throttle valve generates a damping force, while the compression of the gas volume in the hydraulic accumulator causes a resilient force. In the displacer principle presented here, a displacer plunges into a displacer cylinder. Both parts move friction against each other in a guiding and sealing joint.

The Friction impaired the response time of the spring-damper system, so that When used in a vehicle no optimal rolling behavior the supported with this system Wheels results.

Of the The present invention is based on the problem, a combined Spring-damper system to develop one based on a flexible tube, low friction displacer Includes a slim design. The spring-damper system should consist of a few, uncomplicated and low-maintenance components exist and with low installation costs be installed in the vehicle.

The Problem is solved with the features of the main claim. To a bellows is used, as at least two-piece Double rolling bellows is formed. The upper and the lower end of the mounted Doppelrollbalgs is each at one on the vehicle body and the landing gear arranged rolling piston attached. The outer surface of the Doppelrollbalgs is located on an outer bell. The bellows room is filled with a fluid and communicates with a vehicle or vehicle-mounted Hydraulic accumulator.

The Type of displacement bellows, the type of connection to the chassis and the vehicle body and the fill of the bellows compartment with one over allow a gas biased fluid a slim displacer without mechanical, frictional longitudinal guide. A separate longitudinal guide is superfluous because the pressure in the displacement bellows the relatively moved strut parts on the two bellows meniscus centered and stabilized.

at loading or unloading of the displacer flows between the displacer and the hydraulic accumulator over a cross-sectional constriction in the form of a hydraulic line or a breakthrough a hydraulic fluid back and forth. The design the direction or breakthrough and the nature of the there arranged throttle point influenced by the size and shape of the opening cross-section the system damping. In this case, the throttle point can be formed either as a nozzle or aperture or at least one throttle check valve. When using throttle check valves is in the line or in breakthrough cross section per flow direction in each case at least arranged a valve.

The Gas cushion of the hydraulic accumulator is the main factor in system suspension.

By the use of a flexible hose in the form of a double roll the mechanical friction of the entire system is essentially on reduces the internal friction of the bellows and / or membrane material. This shows the spring-damper system over the total spring and damper rate range a nearly ideal response. Articulated connections of the Displacer at Vehicle body or omitted on the chassis. The two rolling pistons per spring damper system can directly - without an interposition of rubber-elastic elements - to vehicle body and be attached to the chassis. This lowers u.a. the component weight, the manufacturing costs, assembly costs and maintenance costs.

Further Details of the invention will become apparent from the dependent claims and the following description of a schematically illustrated embodiment:

1 : Spring damper system with a double-roll;

The only 1 shows a combined spring-damper system comprising a displacer ( 10 ei hydraulic accumulator ( 30 ) and arranged between these liquid-carrying working line ( 40 ) with an integrated throttle valve ( 47 ).

The displacer ( 10 ) consists inter alia of a multi-part outer bell ( 12 . 52 ), two rolling pistons ( 22 . 62 ) and a multi-part double-rolling bellows connecting the two parts ( 11 . 51 ). When rebounding and rebound, for example, the vehicle body and chassis mounted rolling piston move ( 22 . 62 ) towards or away from each other. Between the movable rolling piston ( 22 . 62 ) sits the double roll ( 11 . 51 ). The latter lies with the outer wall ( 19 . 59 ) on the outer bell ( 12 . 52 ) at. The double roll-up bellows ( 11 . 51 ) carries and centers the outer bell ( 12 . 52 ).

The outer bell ( 12 . 52 ) is a hollow body, the two frustoconical parts ( 12 . 52 ) and a coupling sleeve ( 15 ). The mutually mirror-symmetrical truncated cone-shaped parts ( 12 . 52 ) each have a flange in the area of their assembly joint ( 14 . 54 ). Both outer bells ( 12 . 52 ) are aligned coaxially with each other. The flanges ( 14 . 54 ) are not on top of each other. Between the outer bells ( 12 . 52 ) and the flanges ( 14 . 54 ), the connection sleeve (12) is clamped, which also has a flange ( 16 ) having. The coupling sleeve ( 15 ) has outside of its flange an outer contour, at least partially parallel to the flange-like inner contours of the outer bells ( 12 . 52 ) along.

Between the flange ( 14 ) and ( 54 ) are the upper and the lower part of the double roll ( 11 . 51 ) between the coupling sleeve ( 15 ) and the outer bells ( 12 . 52 ) by screwing, cf. Screws ( 21 ), gas tight clamped.

At least the inner contours of the outer bells ( 12 . 52 ) taper from the flange area to the open end. Ie in the area of the assembly joint, the outer bells ( 12 . 52 ) has a larger diameter than at its open ends. The conical contours of the outer bells ( 12 . 52 ), for example, each have a cone angle of 10 °. Of course, both outer bell parts do not have to have the same cone angle. Possibly. can also have at least one cone angle 0 degrees.

The upper rolling piston ( 22 ) is a hollow body with a cylindrical outer wall ( 23 ), for example, at its free, outer end the housing ( 34 ) of the hydraulic accumulator ( 30 ) wearing. Its cavity forms a working line ( 40 ), which communicate with the fluid space ( 35 ) of the hydraulic accumulator ( 30 ) communicates. In the exemplary embodiment is located at the upper end of the rolling piston ( 22 ) by way of example a threaded bolt ( 25 ) over which the spring-damper system on the vehicle body rigid or possibly resiliently secured by elastic intermediate elements.

The lower rolling piston ( 62 ) has here, with the exception of the working line and the hydraulic accumulator a comparable structure and, for example, the same outer diameter.

Between the rolling piston ( 22 . 62 ) is the Doppelrollbalg ( 11 . 51 ) attached. For this purpose, for example, the upper end of the open at the hose ends Doppelrollbalgteils ( 11 ) with the inner wall ( 20 ) on the lower end of the upper rolling piston ( 22 ) and with the help of a clamping ring ( 24 ) For example non-positively non-slip and sealing fixed. The lower end of Doppelrollbalgteils ( 51 ) is identical to the lower rolling piston ( 62 ) attached.

In the ready-to-install state of the spring-damper system are the rolling piston ( 22 . 62 ) so in the outer bells ( 12 . 52 ), that in the upper rolling piston ( 22 ) the upper end of the Doppelrollbalgteils ( 11 ) to form an upwardly oriented meniscus ( 18 ) is turned inside. The lower end of Doppelrollbalgteils ( 51 ) is to form a downwardly oriented meniscus ( 58 ) also turned inside out. As a result, each operational relative movement between the parts ( 22 ) and ( 62 ) the outer walls ( 19 . 59 ) of the bellows ( 11 . 51 ) on the outer walls ( 23 . 63 ) and the inner walls ( 13 . 53 ).

The menisci ( 18 . 58 ) move in the entire stroke range between the rolling piston ( 22 . 62 ) and the outer bell ( 12 . 52 ,). Due to the two-sided taper of the outer bell ( 12 . 52 ) increases with increasing deflection of the chassis, the effective piston area of Doppelrollbalges ( 11 . 51 ). This requires on the one hand a progressive spring characteristic and on the other hand causes a fast centering of Doppelrollbalgs ( 11 . 51 ) and the outer bell ( 12 . 52 ).

The small outer diameter of the outer bell ( 12 . 52 ) allows a slender strut construction and keeps the load on the bellows ( 11 ) in the meniscus area low.

The smallest inner diameter of the outer bell ( 12 . 52 ) Here, for example, is approximately equal to the usable total stroke of the shock absorber.

The lengths of the individual rolling bellows parts ( 11 ) respectively. ( 51 ) correspond, for example, to one to one and a half times the mean bellows diameter.

Possibly. can the outer bells ( 12 . 52 ) are widened in the region of the open ends, cf. 1 , Edge ( 27 ). In any case, there is one such broadening outside the meniscus range. It prevents in the case of larger spring angle deviations between the center line of the outer bell ( 12 . 52 ) and the center line of the respective rolling piston ( 22 . 62 ) a collision between the outer bell ( 12 . 52 ) and rolling piston ( 22 . 62 ).

Outside the bellows compartment ( 5 ) between the outer bell ( 12 . 52 ) and the rolling piston ( 22 . 62 ) are back rooms ( 7 . 8th ) with the help of antifouling bellows ( 28 . 29 ) are sealed against the ingress of dirt. At least one backroom ( 7 . 8th ) is connected via a vent hole, not shown, with the environment.

In the upper area of the rolling piston ( 22 ) is a possibly lockable supply line ( 17 ), who are assigned to the management ( 40 ) opens. Via the supply line ( 17 ) is - when used as an active spring-damper system or as a level control - the liquid displaced or removed. By the supply and removal of a certain amount of liquid additional forces can be realized in the desired manner. The addition or removal of these additional quantities changes the damper and spring forces in the overall system.

The hydraulic accumulator ( 30 ) is designed for example as a bubble or membrane memory. A through the bladder or membrane ( 31 ) divided gas cushion ( 32 ) forms the suspension of the spring damper system. At the transition from the management ( 40 ) to the housing ( 34 ) of the hydraulic accumulator ( 30 ) are two oppositely acting pressure stage valves in the form of spring plate valves. One valve each ( 47 ) opens in another flow direction. In this case, the throttle effect of the individual throttle check valve ( 47 ) If necessary, be made adjustable by means of a controllable or adjustable drive.

In some constructions, the length of the working line ( 40 ) shorten to a breakthrough, for example, when liquid-carrying components of the displacer protrude into the hydraulic accumulator or are surrounded by this. For example, the outer bell ( 12 . 52 ) be surrounded by an example annular housing. In such a case, the total annular space lying between this housing and the outer contour of the outer bell is divided by a tubular membrane into an inner and outer annular space. The outer annulus is filled with gas while the inner annulus is comparable to the fluid space (FIG. 35 ) out 1 , with the bellows space ( 5 ) communicates via at least one throttle valve.

The fluid used in the spring-damper system ( 1 ) is, for example, a solution of water and alcohol. For this solution, all alcohols are miscible at room temperature in any ratio with water. For example, a water-ethanol solution or a water-glycol solution is used. A common water-glycol solution, as it is also used as a frost-protected coolant in internal combustion engines, for example, has an ethylene glycol content of 33 to 50%. The fifty percent solution allows operation of the spring-damper system up to -35 ° C cold. This solution also does not attack the usual elastomer materials. Also, the rubber swell is in the order of magnitude of the swelling in pure water.

As an alternative to the previously described embodiment, a spring-damper system is conceivable in which the fluid used in the system ( 1 ) is a magnetorheological fluid. Will now be on the hydraulic working line ( 40 ), for example, a short annular portion enclosed by a current-excited magnetic coil, so does the excited magnetic coil in combination with the fluid ( 1 ) is a variable throttle point. With increasing energization of the coil, the flow rate increases by an increase in the apparent or dynamic viscosity in the working line ( 40 ), whereby, among other things, the damping behavior of the entire system can be changed specifically.

1

fluid, Water-glycol solution

5

bellows space

7.8

backcourt

10

displacement

11.51

flexible member, Doppelrollbalg

12.52

outer bell

13.53

interior walls

14.54

Flanges on outer bell ( 12 . 52 )

15

coupling sleeve

16

connecting flange

17

supply

18.58

menisci

19.59

Outer walls of ( 11 . 61 )

20.60

Inner walls of ( 11 . 61 ), Bellows wall

21

screw

22,62

roll-off

23.63

exterior walls

24.64

Retainers

25.65

threaded bolt

27

edge

28.29

Schmutzschutzbälge

30

hydraulic accumulator

31

membrane

32

gas cushion

34

casing

35

fluid space

40

working line

47

Throttle valves, Pressure stage valves

Claims (13)

Combined spring-damper system for supporting wheel suspensions or axles on a vehicle body with a hose roll bellows arranged between a wheel-carrying or wheel-guiding connection and a connection on the vehicle body, wherein the hose roll bellows is an at least two-part double roll bellows (US Pat. 11 . 51 ), wherein the upper and the lower end of the mounted double rolling bellows ( 11 . 51 ) each on a rolling piston ( 22 . 62 ), wherein the one rolling piston ( 22 ) on the chassis structure and the other rolling piston ( 62 ) is attached to the suspension or axle, - wherein the outer circumferential surface of the Doppelrollbalgs ( 11 . 51 ) on an outer bell ( 12 . 52 ) and - wherein the bellows space ( 5 ) with a fluid ( 1 ) and is fitted with a hydraulic accumulator mounted on the chassis or vehicle ( 30 ) communicates. Combined spring-damper system according to claim 1, characterized in that the double rolling bellows ( 11 . 51 ) is divided transversely to the stroke direction and is formed mirror-symmetrical to the division plane. Combined spring-damper system according to claim 1, characterized in that the double rolling bellows ( 11 . 51 ) is made in two parts, wherein the two Rollbalgteile ( 11 ) and ( 51 ) in the parting plane through a connecting sleeve ( 15 ) are interconnected. Combined spring-damper system according to claim 3, characterized in that the outer bell ( 12 . 52 ) on the connecting sleeve ( 15 ) is arranged. Combined spring-damper system according to claim 1, characterized in that the outer bell ( 12 . 52 ) is divided transversely to the stroke direction and is formed mirror-symmetrical to the division plane. Combined spring-damper system according to claim 5, characterized in that the two parts of the outer bell ( 12 . 52 ) are formed as a truncated cone coats whose largest diameter are in the region of the dividing plane. Combined spring-damper system according to claim 5, characterized in that the two parts of the outer bell ( 12 . 52 ) are each flange-shaped in the region of the division plane. Combined spring-damper system according to claim 7, characterized in that the connecting sleeve ( 15 ) a flange ( 16 ), which between the flanges ( 14 ) and ( 54 ) of the outer bells ( 12 . 52 ) is clamped. Combined spring-damper system according to claim 1, characterized in that the hydraulic accumulator ( 30 ) is a membrane or bladder storage. Combined spring-damper system according to claim 1, characterized in that in the fluid flow between the bellows space ( 5 ) and the hydraulic accumulator ( 30 ) at least one throttle point or at least two throttle check valves ( 47 ) are arranged. Combined spring-damper system according to claim 10, characterized in that the throttle check valve ( 47 ) is a compression valve. Combined spring-damper system according to claim 1, characterized in that the fluid ( 1 ) is a water-alcohol solution. Combined spring-damper system according to claim 1, characterized in that the bellows space ( 5 ) via a supply line ( 17 ) is in driving to realize an active spring-damper system with an external fluid supply in communication.