Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
  • F16F9/06—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid
  • F16F9/064—Units characterised by the location or shape of the expansion chamber
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
  • F16F9/06—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid
  • F16F9/08—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid where gas is in a chamber with a flexible wall
  • F16F9/096—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid where gas is in a chamber with a flexible wall comprising a hydropneumatic accumulator of the membrane type provided on the upper or the lower end of a damper or separately from or laterally on the damper
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
  • F16F9/32—Details
  • F16F9/54—Arrangements for attachment

Definitions

• the invention relates to a support bearing of a vibration-damping element according to the preamble of patent claim 1.
• hydropneumatic spring-damper arrangements can completely fulfill the tasks of conventional spring-damper systems, the installation space requirements being somewhat less expensive than with conventional spring-damper systems. It is also advantageous with these hydropneumatic spring-damper arrangements that they offer a very simple possibility for realizing active damping of body or wheel movements in a vehicle by supplying or removing hydraulic fluid from the working space of the hydraulic cylinder ,
• the object of the invention is to provide a support bearing of a vibration-damping element, in particular a hydro-pneumatic spring-damper system, which increases the driving comfort of a vehicle.
• the invention makes it possible to create simply constructed active suspensions, which are based in particular on hydropneumatic systems, with a high level of comfort, since a central problem of hydropneumatic systems essentially eliminates or at least greatly reduces the disruptive influences of friction in the hydraulic cylinder can be.
• the support bearing according to the invention When used as a head bearing, disruptive properties of the actual power transmission component can be prevented or weakened.
• FIG. 5 is a schematic diagram of a preferred hydropneumatic spring damper system with a first preferred support bearing
• FIG. 6 is a schematic diagram of a preferred hydropneumatic spring damper system with a second preferred support bearing
• FIGS. 7 and 8 10 is a schematic diagram of a preferred embodiment of a support bearing
• FIG. 11 is a schematic diagram of a further preferred embodiment of a support bearing with tension and compression stops
• Fig. 12 is a schematic diagram of a further preferred embodiment of a support bearing with a longitudinal guide.
• a hydropneumatic spring-damper system has, as an overall vibration-damping element, a hydraulic cylinder 1 with a piston 6 that moves up and down inside the hydraulic cylinder 1.
• the spring action and the carrying of an operating load is carried out by a gas spring accumulator 2, which is connected to the hydraulic cylinder 1 via an overflow line 4, through which a hydraulic medium can be exchanged between the hydraulic cylinder 1 and the gas spring accumulator 2.
• the damping is implemented by a throttle orifice 5 in the overflow line 4 between the hydraulic cylinder 1 and gas spring accumulator 2.
• a support bearing 3 with a spring stiffness C L is arranged on the body side.
• FIG. 4 The principle of the solution according to the invention is outlined in FIG. 4. Only one support bearing 7 is shown as a detail, the further arrangement, not shown, largely corresponds to the system shown in FIG. 1.
• a spring-damper system is provided as the vibration-damping element.
• the support bearing 7 has defined hydraulic, elastic and possibly damping properties and is hydraulically coupled to a hydraulic cylinder 1, not shown in the figure.
• the body of the support bearing 7 preferably has defined stiffness properties.
• a hydraulic active surface A L is arranged between the support bearing 7 and the hydraulic cylinder 1.
• the support bearing 7 has a housing 10 with a spring stiffness C L.
• the housing 10 is preferably completely filled with a hydraulic medium.
• a pressure p prevails within the housing 10. Since the support bearing 7 is in hydraulic connection with the working space of the hollow cylinder 1, p is also the pressure of the working space.
• the hydraulic coupling of the support bearing 7 and the hydraulic cylinder 1 means that the actual tasks of the support bearing 7, carrying the load and length compensation, can be separated.
• the existing hydraulic medium is used to carry the load. With a given hydraulic effective area it can be ensured that the support bearing . 7 fulfills its supporting function for every required and usual load.
• the length compensation, ie a longitudinal flexibility of the support bearing 7 can now be realized by rubber or steel spring elements. Since there is no base load, the voting bandwidth is hardly restricted by design restrictions.
• the spring stiffness of a support bearing according to the invention can therefore be significantly lower than that of a conventional support bearing 7 according to FIG. 1.
• the active surface A L between the hydraulic cylinder 1 and the support bearing 7 is preferably substantially constant when the hydraulic cylinder 1 and / or the support bearing 7 is deflected. This allows a significant improvement in comfort to be achieved. But even if the hydraulic effective area varies, at least an improvement over the known systems can be seen.
• a substantially constant, ie surface-neutral, hydraulic effective area A L is favorable in order to provide sufficient deflection path for “smoothing” the friction in the hydraulic cylinder 1. For example, if the support bearing 7 is deflected by ⁇ X during deflection, this is counteracted by the spring stiffness C L and a hydraulic counterforce on the hydraulic active surface A L on the support bearing 7 by a bearing force K against the deflection ⁇ X:
• the hydraulic medium can escape from the hydraulic cylinder 1 into a gas spring accumulator 2 (not shown).
• the support bearing 7 is preferably arranged hydraulically parallel to the gas spring accumulator 2.
• the support bearing 7 is designed as an ellipsoid body. The arrangement otherwise largely corresponds to the schematic diagram in FIG. 1.
• the support bearing 7 is arranged on the hydraulic cylinder 1 axially in the direction of the longitudinal extent thereof.
• the support bearing 7 forms a head bearing of a hydropneumatic spring Damper. It is possible to actively operate such an arrangement and to use a hydraulic pump, not shown, which pumps additional hydraulic medium into the arrangement or discharges it therefrom.
• FIG. 6 shows a second preferred arrangement according to the invention.
• a bellows is used as a support bearing 7.
• This arrangement has the particular advantage that the hydraulic effective area A L remains surface-neutral under movements of the piston 6 or deflection and rebound movements.
• An elastomer can be used as the material for the housing.
• Another cheap and particularly corrosion-resistant alternative is a metal bellows.
• FIGS. 7 and 8 clearly show the improvements compared to FIGS. 2 and 3 for a conventional system according to FIG. 1.
• 8 shows the associated spring-damper force change (dF_Zyl [N]) in comparison to the spring component (dF_elast). It can be seen that practically no jumps in force are observed when the piston 6 is reversed.
• the change in force according to FIG. 7 is constant with a reversal of movement with a smooth transition into a counter movement.
• FIG. 9 shows the deflections Xz of the hydraulic cylinder 1, ⁇ X of the support bearing 7 and the deflection Xe belonging to the previous FIGS. 7 and 8.
• the support bearing 7 hydraulically coupled to the hydraulic cylinder 1 according to the invention takes over a large part of the deflections in this operating case.
• the transitions to the actual hydraulic cylinder deflections Xz take place harmoniously and smoothly. Uncertainties regarding the amount of frictional forces hardly play a role, fluctuations in frictional force would only shift the times of the cylinder inserts somewhat, but would not disturb the constant transitions when the movement is reversed.
• the support bearing 7 shows a further preferred embodiment of a support bearing 7 according to the invention.
• the support bearing 7 can have a housing 10 which is formed at least in regions from an elastomer.
• the housing 10 can preferably be attached directly to the hydraulic cylinder 1 and to a force absorption 9.
• a clamping ring 11 can be provided, with which the housing 10 is fixed directly to the housing of the hydraulic cylinder 1.
• a corresponding fixation 12 for example a clamping ring, can be provided, by means of which the housing 10 is fastened to the force absorption 9.
• a perforated diaphragm 8 can be provided for the hydraulic cylinder 1. The opening of the pinhole 8 gives the hydraulic effective area A L.
• the force absorption 9 is with a bearing point 13 on e.g. tied a vehicle body.
• the housing 10 particularly preferably consists of a rubber cylinder, which forms the actual bearing element.
• the rubber itself causes longitudinal flexibility in the direction h of the support bearing 7.
• Favorable compressive strength and sufficient radial rigidity in the direction b can be brought about by tangential or at least almost tangential reinforcing fibers in or on the rubber cylinder.
• the rubber cylinder itself can also perform transverse guidance tasks of the support bearing 7. If higher transverse forces are transmitted or greater demands are placed on the precision of the transverse guide, appropriate longitudinal guides can be introduced.
• FIG. 11 A favorable embodiment of the support bearing 7 is shown in FIG. 11.
• the arrangement essentially corresponds to that in FIG. 10.
• a rod 14 is provided in the housing 10, which is oriented axially to the hydraulic cylinder and which can protrude into the hydraulic cylinder.
• a pressure stop 15 and / or a Z ⁇ ganschlag 15 can be attached to the rod 14. The maximum compression and / or expansion of the support bearing 7 can thus be limited or set.
• FIG. 12 Another favorable embodiment of the support bearing 7 is shown in FIG. 12.
• a longitudinal guide 18 is attached to the rod 14 and limits or prevents transverse deflection of the support bearing 7.
• the longitudinal guide 17 can be a cylinder which concentrically surrounds the rod.
• the cylinder widens on the underside towards the perforated diaphragm 8 and preferably has a ring 18 there.
• Overflow openings are expediently provided in the perforated diaphragm 8, the cross sections of which overall form a hydraulic effective area A L.
• the ring 18 can also be arranged on the side of the support bearing 14 which faces the force absorption 9.
• other configurations of a support bearing hydraulically coupled to a hydraulic cylinder 1 are also conceivable.
• the invention is characterized in that the support bearing 7 according to the invention is hydraulically freed from the high static loads to be borne. This enables a "soft" construction and e.g. an elastomer insert.
• the support bearing 7 forms a head bearing of a hydraulic cylinder 1. It is particularly expedient to design an overall stiffness of the support bearing 7 such that when the spring deflection or rebound occurs, the change in force over an available deflection in the support bearing 7 is greater than the frictional force, in particular the static frictional force, of the piston 6 in the hydraulic cylinder 1. that the piston 6 can travel out of a frictional clamping again before the support bearing 7 reaches its deflection limits.
• the necessary stiffness can be achieved either solely by elastic material properties of the support bearing 7 or the housing 10 or additionally or alternatively by changing the area of the hydraulic effective area A L via the spring deflection. Both work in a comparable way, provided the overall stiffness was designed according to the above condition.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Fluid-Damping Devices (AREA)
• Vehicle Body Suspensions (AREA)

Applications Claiming Priority (3)

Publications (1)

Family

ID=32403971

Family Applications (1)

Country Status (5)

Families Citing this family (8)

Family Cites Families (24)

• 2002
  • 2002-12-19 DE DE10259532A patent/DE10259532A1/de not_active Withdrawn
• 2003
  • 2003-11-12 JP JP2004561161A patent/JP2006510859A/ja not_active Abandoned
  • 2003-11-12 WO PCT/EP2003/012615 patent/WO2004057208A1/de active Application Filing
  • 2003-11-12 EP EP03779893A patent/EP1573224A1/de not_active Withdrawn
• 2005
  • 2005-06-17 US US11/155,931 patent/US20050284716A1/en not_active Abandoned

Non-Patent Citations (1)

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