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
  • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
  • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
  • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
  • F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
  • F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
  • F16F13/16—Units of the bushing type, i.e. loaded predominantly radially specially adapted for receiving axial loads
• • 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
  • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
  • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
  • F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
  • F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
  • F16F13/1427—Units of the bushing type, i.e. loaded predominantly radially characterised by features of flexible walls of equilibration chambers; decoupling or self-tuning means

Definitions

• the invention relates to an axially damping, hydraulic elastomer bearing according to the Oberbe handle of claim 1.
• Hydraulically damping elastomer bearings are also referred to as hydraulic bearings and are used as chassis bearings, such as subframe bearings, in motor vehicles in order to dampen and / or eliminate vibrations that occur.
• Axial damping hydraulic bearings comprise axially spaced fluid chambers which are separated from one another by membranes and / or elastomer bodies and connected to one another in a fluid-conducting manner via a damping channel.
• one of the two fluid chambers is at least partially compressed or the other is enlarged at least partially.
• the fluid located therein flows via the damping channel from one fluid chamber into the other fluid chamber. In this way, a damping and / or damping effect is achieved, this particularly affecting vibrations with large amplitudes and low frequencies.
• the present invention is concerned with an axially damping hydraulic Elastomerla ger that can be used in the chassis area and in particular for mounting a rear subframe, the rear subframe being assigned to the rear axle and designed to accommodate at least one electric motor or other units such as a rear axle transmission can be.
• a bearing can also be used as a subframe bearing and serves to support and dampen the forces and vibrations acting on a subframe.
• the bearing can be used in a receiving eye formed in the subframe or screwed to a flange.
• the radial installation space of the axially damping bearing is limited by the diameter of the Aufnah meauges or the flange.
• a large part of the bearing with its fluid chambers can be accommodated in this radially limited installation space.
• a bearing can also be used to mount other vehicle structures that require axial damping, for example to mount a vehicle body on a ladder frame, to mount an internal combustion engine on a connection structure or to mount a swinging battery.
• the bearing can still cover relevant distances in the Z-direction even in a highly loaded condition so that a sufficient liquid volume is displaced and a pumping effect and the associated damping can occur.
• This must be taken into account when limiting the Z-travel by means of suitable end stops, since after the Z-stops have been inserted, damping can hardly be observed.
• the coordination of the working frequency is also dependent on the basic rigidity of the bearing. For this reason, the most linear possible profile of the Z stiffness over the Z path is often required for an operating frequency that is as constant as possible. If the Z-stops finally come into play, there is a considerable increase in rigidity and thus naturally also a shift in the working frequency of the hydraulic bearing.
• bearings should often have great resilience in the X direction (vehicle longitudinal direction or direction of travel) in order, for example, to enable comfortable rolling over the obstacle when crossing edges.
• X direction vehicle longitudinal direction or direction of travel
• two axially spaced fluid chambers within the bearing must be separated from one another in such a way that, in the event of an additional dynamic axial vibration excitation in all operating states, fluid from one ner axial fluid chamber can be pumped into the other fluid chamber.
• Axi aldämpfende Flydrolager often have an elastomeric separating membrane between the two fluid chambers to ensure the necessary flexibility.
• Such a separating membrane must on the one hand withstand the large deflections or paths in the X, Y (transverse vehicle direction), and / or Z direction, but at the same time be rigid so that a sufficient pumping effect can be achieved between the axially arranged chambers and ultimately large Differences in pressure between the fluid chambers, as they can occur with shock loads, withstand life. This represents a conflict of requirements that is difficult to solve, but which could be solved for this task with a membrane geometry according to EP 3589861 A1.
• This disclosure suggests a functional separation between, on the one hand, a Z-load-bearing, inflation-resistant first elastomer body (axial bearing) which, together with the membrane, generates a high pressure in one fluid chamber (working chamber) when deflected in the Z direction, or a high differential pressure to the axially spaced other Fluid chamber (compensation chamber) causes, and on the other hand a second elastomer body (radial bearing), which is largely responsible for setting or spreading the X / Y stiffness, but is not itself part of the hydraulic system.
• the invention is based on the object of creating an axially damping, hydraulic elastomer bearing which is less complex and less expensive while having at least the same functionality and has a smaller number of components.
• an axially damping hydraulic elastomer bearing through which a central longitudinal axis protrudes, comprising a core which extends along the central longitudinal axis and for receiving a fastening element a through Current through opening provides an outer tube, which is arranged on the circumference of the core, an elastomer body which is arranged between the core and the outer tube, a first membrane which delimits a first fluid chamber from an axially spaced second fluid chamber, the fluid chambers with a Fluid are filled, and a damping channel which connects the fluid chambers to one another in a fluid-conducting manner.
• a second membrane delimits at least the first fluid chamber at least in sections in the axial direction, each of the two membranes comprising a section with a thicker cross section and a section with a thinner cross section.
• the cross-sectionally thicker sections can be arranged facing one another.
• the first membrane can be supported on the inner circumference side, that is to say radially on the inside, on the core or an inner sleeve and / or on the outer circumference, that is to say radially on the outside, on the outer tube or on an outer sleeve.
• the second membrane can also be supported on the inner circumference, that is to say radially on the inside, on the core or a cover or ring element and / or on the outer circumference, that is on the radial outside, on the outer tube or an outer sleeve.
• the two membranes include the first fluid chamber, which can be designed as a working chamber.
• the two membranes can be designed to achieve a requirement-specific pumping action.
• Each of the two membranes can comprise an expandable section and an expandable soft section, the expandable section being formed by the section with a thicker section and the expandable section being formed by the section with a thinner section.
• Rigid sections are used to generate a sufficient pumping effect. It is conceivable that the expansion-resistant sections are from the mutually facing sections.
• Conceivable design aspects can be the arrangement, the shape, the cross-sectional thickness and / or the choice of material of the membranes. In this way, too, a good pumping effect can be achieved with a simple and inexpensive design.
• the section with a thinner section and the section with a thicker section lie in a cross-sectional plane in which the central longitudinal axis also lies and / or can be exposed to a fluid or can be arranged to delimit a fluid chamber.
• the elastomer body forms a main support cushion and is the only support cushion in the space between the core and the outer tube.
• the main support cushion is characterized by the fact that it bears the primary load and / or at least in some areas has a positive connection overlap height of the elastomer body.
• the connection overlap height of the elastomer body is that distance, preferably axially, in which two connection sections of the elastomer body overlap in the longitudinal direction.
• the invention can provide the functional integration of the axial bearing and the radial bearing in a single component, namely the main support cushion.
• the main support cushion can be arranged between the core and the outer tube in such a way that it is able to seal off one of the hydraulic chambers axially on the outside.
• the elastomer body both forms the main support cushion and also includes a membrane section. This can be designed monolithically with the elastomer body and / or as an elastomer membrane.
• the elastomer bearing according to the invention can be designed in such a way that the elastomer body delimits at least one of the fluid chambers at least in sections in the axial direction, preferably delimits the second fluid chamber configured as a compensation chamber.
• the elastomer body as the main support cushion can therefore be arranged between the core and the outer tube in such a way that it forms an axial limit for this at least one fluid chamber. It can be arranged both radially on the inside on the core and on the radially outside on the outer tube.
• the second membrane delimits the first fluid chamber, which is designed as a working chamber.
• the first membrane as an intermediate membrane, can separate the first fluid chamber, which is designed as a working chamber, from the second fluid chamber, which is designed as a compensation chamber.
• a fluid chamber can thus be delimited by two membranes and a fluid chamber by a membrane and the elastomer body.
• the working chamber can be structurally complex to seal the working chamber, at least in sections, with an elastomer membrane or a membrane section as a supplement to the main support cushion, since the elastomer body, which can comprise the main support cushion and the elastomer membrane or the membrane section, has to endure all of the deflections of the bearing in its entirety.
• the elastomeric membrane or the membrane section is to be designed to be relatively long in order to minimize the elongations that occur and to distribute them evenly.
• Such a long membrane however, has too little inflation rigidity to generate a high differential pressure with respect to the equalization chamber and thus a high pumping capacity.
• the fluid chamber which is usually designed as a compensation chamber, becomes the pressurized working chamber and the primary pumping work takes over for the hydraulic damping.
• This chamber can be delimited in the axial direction by two membranes, which can be manufactured and assembled separately. Since both components can be mounted separately on the core, they can be preloaded in the assembly position in such a way that the load on the bearing in the K 0 position counteracts this preload, the K 0 position being understood as the construction position. Since the position of a vehicle changes continuously during operation, the K 0 position is specified as the reference point, i.e.
• the two membranes can be made of an elastomeric material or elastomeric membranes.
• At least one membrane or the intermediate membrane has a very low expandability with respect to differential pressures between the adjoining fluid chambers, since a sufficient pumping effect is only achieved with a low expandability.
• the intermediate membrane also advantageously has a region which has a high level of flexural flexibility in the axial direction, so that it can follow large axial relative movements of its radially inner and radially outer connection structure in the axial direction without being greatly stretched.
• the membrane advantageously has an area that is primarily sheared when there is a radial relative movement from a radially inner to the radially outer connection structure, so that hardly any tensile or compressive strains occur in the membrane even with radial loads. This leads to the fact that such a membrane is exposed to extremely low expansions with a typically occurring superposition of high axial and radial paths with simultaneously high differential pressures between the chambers and thus has a long service life.
• the first and second diaphragms can additionally be protected from excessively high pressures in a pressure differential direction, since they can at least indirectly be supported on their connection structure, for example on the core, on the inwardly or outwardly facing side.
• high tensile loads can arise on the radially inner connecting section of the membranes.
• At least one of the two membranes preferably both membranes in each case, has a first leg, a second leg and a base connecting the two legs, with an average thickness of one of the legs is at least twice as thick as that of the other leg.
• the section with a thicker cross section can be formed by the limb that is at least twice as thick and the section with thinner section can be formed by the other limb.
• average thickness is understood to mean the average value of the thickness of a leg over its entire length, that is, from the base to its free end. If there is a radial relative movement between the inner and outer connection structure of the bearing, both legs are primarily subjected to thrust.
• the thinner leg Since the mean thickness of one leg is at least twice as large as the other leg, the thinner leg is more flexible than the thicker leg. Therefore, the thinner leg primarily contributes to compliance in the radial direction, while the thicker leg is relatively soft in the radial direction. This results in a functional separation between the thicker and thinner legs for the radial flexibility.
• an intermediate membrane is insensitive to inflation due to high differential pressures between the two fluid chambers filled with fluid. In most operating states, this leads to a high degree of Blähstei strength of the membrane, which results in a large pump volume and thus in an improved damping effect. In addition, this configuration ensures that the membrane is very stiff at differential pressures between the fluid chambers.
• the base is advantageously U-shaped or L-shaped in cross-section with a uniform thickness, the legs protruding from the U-shaped or L-shaped base.
• the cross-section of the limb which is at least twice as thick on average, of at least one of the membranes, starting from the base, widens steadily or un steadily.
• the leg which is at least twice as thick on average, can, for example, increase in cross section starting from the base in a funnel-shaped or exponential-shaped manner.
• the leg which is at least twice as thick, is very rigid when compared to the other leg of the membrane, but at the same time it has a harmonious bending line in the case of large translational deflections, which leads to low tensile stress and thus a long service life of a first or second intermediate membrane Membrane leads.
• the leg Due to the decreasing thickness of the leg towards the base of the leg and advantageously additionally supported by a bulging of the leg, the leg, which is at least twice as thick, is flexible in the axial direction.
• the leg which is at least twice as thick and tapers towards the base, which preferably has a bulge, primarily contributes to the compliance in the axial direction, while the thinner leg does not have to have any noteworthy axial compliance. This achieves a functional separation between the thicker and thinner legs for the axial compliance.
• the leg which is at least twice as thick on average, can have a cross-sectional arched course according to a further development.
• the limb which is at least twice as thick on average, can also be slightly protruding in the direction in which the limb extends when a pressure is applied Fluid chamber, for example the working chamber, would bend further.
• This curvature has the advantage that the thick limb is not compressed or stretched during axial displacement, but rather the limb can bend.
• the thin leg can be largely cylindrical / tubular and have a linear cross-section, so that it can yield in the axial direction primarily only by upsetting or pulling.
• the elastomer bearing is designed in such a way that the leg, twice as thick on average, of a membrane, preferably the first membrane or the intermediate membrane, is at a pressure difference at which the fluid chamber formed as a working chamber has a higher pressure than that as the compensation chamber has formed fluid chamber, bends in the direction of the core, preferably the base connecting the two legs rests against an inside element.
• the membrane is particularly rigid, so that a high pump output and, associated with it, a high level of damping can be achieved.
• the elastomer bearing can be designed in such a way that the leg of a membrane, on average twice as thick, is in front of the second membrane, at a pressure difference at which the fluid chamber formed as a working chamber has a higher pressure than the has fluid chamber designed as a compensation chamber, bends in the direction of the outer tube, preferably the base connecting the two legs rests against an element on the outer circumference.
• the membrane is particularly rigid, so that a high pump output and, associated with it, a high level of damping can be achieved.
• the leg which is twice as thick on average, has a first length and the other leg has a second length, the first length being greater than or equal to the second length.
• the longer leg can advantageously ensure a high degree of mobility in translational directions through a high degree of flexibility in the axial direction.
• a greater length can lead to a low inflation rigidity and thus a low pumping capacity.
• This can be compensated for by a suitably greater thickness of the longer leg.
• a membrane geometry is realized that is characterized by a long service life, but at the same time also allows a good pumping effect in the axial direction.
• the first length of one leg is at least twice as large as the second length of the other leg.
• the upper surface and the lower surface of the membrane can each have a profile that is as uniform as possible, so that the membrane has no larger or no thickness jumps at all.
• the length of each Leg is determined by the distance in the Z direction between the lower reversal point of the base and the highest connection section in the X direction of the respective leg or by the distance in the Z direction between the highest reversal point of the base and the lower connection section in the X direction respective leg defined. Since the thinner leg is advantageously at most half as long as the thicker leg, it is relatively stiff and bulky. In this way, a membrane geometry is realized which has a particularly good pumping action in the axial direction.
• the mathematical derivation of the function describing the upper surface is equal to zero at the reversal point of the base.
• the mathematical derivation of the functions describing the lower geometry of the legs the mathematical derivation of which at its highest point either also becomes zero, alternatively ends in a stiff connection area or can have a discontinuity.
• the leg at least twice as thick on average forms the radially outer leg and / or in a membrane, preferably in the second membrane, the leg at least twice as thick on average the radially inner leg.
• the thick legs of two membranes can also face each other.
• the on average at least twice as thick limb of a membrane, preferably the first membrane, and the on average at least twice as thick limb of another membrane, preferably the second membrane can face one another in the longitudinal axial direction and / or be arranged opposite one another with respect to a fluid chamber.
• the two legs can thus turn vorei n one another even with a correspondingly curved or angled course.
• the fluid chamber which is usually designed as a compensation chamber, becomes the pressurized working chamber and the primary pumping work takes over for the hydraulic damping.
• the working chamber can therefore be delimited axially by two membranes.
• the first and second diaphragms can be protected from excessively high pressures in a pressure differential direction in that their base is at least indirectly supported on the connection structures associated with the thin legs, for example the core and / or the first outer sleeve.
• Such a support also leads to an increase in the inflation rigidity, which further promotes the pumping effect.
• the membrane can consequently be arranged in such a way that it is now protected against high pressures in the former compensation chamber, since in the embodiment proposed according to the invention this generates the higher pressures compared to the chamber delimited by the main support cushion.
• a second membrane can be used as the closing membrane of the working chamber, but wel che has the wide membrane base or the leg at least twice as thick on the core side and the other leg on the outer circumference side. The two membranes are thus arranged in opposite directions to one another or opposite one another.
• the diaphragms described tolerate large movements in the X / Y / Z direction due to their geometry, they protect themselves from damage in the event of a high pressure difference in the critical direction.
• the two membranes thus have a two-stage expansion stiffness. With small deflections or amplitudes, they cause the fluid to be pumped. In the case of larger deflections or amplitudes, on the other hand, the membrane can rest against the core or the outer sleeve or the outer tube, preferably with its thick limb, and thereby become very rigid. In this state, the membrane can absorb greater hydraulic forces and therefore make a significant contribution to the load-bearing capacity.
• connection widths of the legs of the two diaphragms which are at least twice as thick, overlap at least in sections in the radial direction.
• the overlap is preferably in the Z direction or in the longitudinal direction, so that the connection widths overlap at least in sections in the radial direction.
• a connection width is the maximum thickness of the thick leg that it has in its connection area, this connection width being dimensioned in the X or Y direction.
• the overlapping sections of both connection widths therefore have an overlap width. The greater this coverage width, the greater the pumping effect.
• a tangent of a central area in the at least twice as thick leg of at least one membrane can, at least in sections, enclose an angle with the central longitudinal axis in the range from 0 ° to 90 °, preferably in the range from 10 ° to 50 °.
• the tangents of the central central surface of the first membrane or intermediate membrane can predominantly enclose angles in the range from 10 ° to 30 °.
• the tangents of the central central surface of the second membrane or closing membrane can predominantly include angles in the range from 25 ° to 35 °.
• the central central surfaces can have a curved or straight course or a predominantly curved or predominantly straight course or a combination thereof. The smaller the included angle, the greater the axial support effect.
• the central middle surface is at the same distance from both surfaces of the leg.
• connection structures on which the two membranes are arranged can overlap at least in sections in the radial direction.
• the connection structures can each have a flange section which runs in the space between the core and the outer sleeve or outer tube and / or protrudes into this.
• the connection structures can be, for example, a second outer sleeve for the first membrane and a ring element for the second membrane.
• the connection structures can be rigid structures and thus enable a change in volume of the chambers. The greater the radial overlap of these connection structures, the greater the pumping effect.
• connection structures do not overlap, but rather protrude without overlap into the gap between the core and the outer sleeve or outer tube, for example by up to 25% of the gap width, preferably by up to 50% of the gap width, with also different Lich wide extensions into the space are conceivable.
• one connection structure can have an extension of 24% and the other connection structure an extension of 76%.
• the elastomer body and the first membrane or the elastomer body, the first membrane and the second membrane can be separate elements in the elastomer bearing.
• the elastomer bearing can only have two or three elastomer parts in total or in the space between the core and the outer tube, which, compared to bearings with more than three separately manufactured elastomer elements, leads to a considerable reduction in complexity and costs due to reduced manufacturing and assembly costs.
• the separate elements can be arranged at least partially one above the other and spaced apart in the longitudinal direction of the elastomer bearing. This results in two axially spaced apart fluid chambers.
• At least one membrane in the elastomer bearing can be designed to be largely rotationally symmetrical. It is also conceivable that at least one of the legs is designed to be largely rotationally symmetrical, preferably the base and the legs protruding therefrom are designed to be largely rotationally symmetrical. The center of the rotational symmetry can form the central longitudinal axis. Even if there may be slight asymmetries, for example due to X-stops or filling holes, it is still advantageous to make the geometry of the membrane itself as uniform as possible in the circumferential direction in order to avoid unfavorable stress distributions under load. Additionally or alternatively, the elastomer body can be designed to be rotationally symmetrical. Additionally or alternatively, the elastomer bearing can be designed to be rotationally symmetrical.
• the outer tube of the elastomer bearing can either be part of an assembly comprising the elastomer body. This is shown in the figures.
• the outer tube can be installed as a separate component.
• a multi-part design of the outer tube is then advantageous, for example a two-part structure - a metal sleeve could be used, for example, into which 3 internal assemblies (first membrane, second membrane, elastomer body) are mounted, which results in advantageous press-out forces over the service life and no relaxation occurs.
• the outer tube can be part of a first outer sleeve or a second outer sleeve.
• the first membrane and the second membrane are arranged overlapping at least in sections in the longitudinal direction. This leads to a compact design.
• a connection overlap height of the elastomer body in the longitudinal direction of the elastomer bearing can correspond at least in sections to between 0.2 and 0.6 times, preferably between 0.3 and 0.5 times the height of the elastomer bearing.
• the connection sections can be formed from opposite sides with respect to the elastomer body.
• the elastomer body in the case of the elastomer bearing, can be designed at least in sections as a wedge bearing in the longitudinal direction.
• the connection sections are at least partially, preferably completely, tilted with respect to the central longitudinal axis. The tilt can vary along the circumferential direction. Preferably, angles lying diametrically with respect to the central longitudinal axis are identical.
• the two connection sections can be tilted at the same angle, but also at different angles.
• the elastomer body can have at least one connection section in the longitudinal direction that is not tilted with respect to the central longitudinal axis.
• a connection overlap height of the elastomer body in the longitudinal direction can be at most zero, at least in sections.
• the binding overlap height of the elastomer body is understood as the distance in which two connection sections of the elastomer body overlap in the longitudinal direction.
• the lower the overlap of the connection overlap height of the elastomer body in the second direction the lower the radial rigidity in this direction and the greater the spread of the identifier.
• a binding overlap height of the elastomer body varies in the longitudinal direction along the circumferential direction around the central longitudinal axis, preferably those diametrically opposite the central longitudinal axis are identical.
• the connection overlap height of the elastomer body is the distance in which two connection sections of the elastomer body overlap in the longitudinal direction.
• the elastomer body of the elastomer bearing can be designed in such a way that in an assembled state it has at least twice as high static rigidity in the unloaded state in the vehicle transverse direction as in the vehicle longitudinal direction.
• a hydraulically damping elastomer bearing according to this disclosure as an axially damping bearing in a vehicle, preferably an electric vehicle, preferably as a bearing operatively connected to a rear subframe for receiving at least one electric motor.
• FIG. 1 shows a plan view of an elastomer bearing according to the invention and
• FIG. 2 shows a sectional view along the line II-II according to FIG. 1.
• the reference document uses different reference symbols, elements with the same name, unless technically excluded, are to be considered to be identical or have the same effect as the elements of this application.
• a three-dimensional, right-angled, Cartesian coordinate system should be used for orientation.
• the X-axis and the Y-axis each define a transverse axis and the Z-axis corresponds to the longitudinal axis of the bearing.
• the X direction is understood to mean the direction in which a motor vehicle moves along the X axis (longitudinal direction of the vehicle).
• the Y direction is understood to mean a direction transverse to the direction of travel (transverse direction of the vehicle) and the Z direction is the direction in the fleas of the motor vehicle, i.e. the direction opposite to the weight force (vertical direction of the vehicle), which represents the axial direction of the bearing in the assembled state.
• the Z-direction arrow runs downwards, since the elastomer bearing is shown upside down with regard to its assembly position.
• FIG. 2 shows the elastomer bearing with a section arranged at 90 ° along the line II-II.
• a hydraulically damping elastomer bearing in particular a hydraulic damping subframe bearing, is shown, which is used to support a subframe, not shown, of a motor vehicle. Flierzu the camp 2 is used in a not shown on receiving eye of the frame.
• a central longitudinal axis A extends through the elastomer bearing 2 along the longitudinal direction L of the elastomer bearing 2. With respect to the central longitudinal axis A, a radial direction R and a circumferential direction U are plotted.
• the bearing 2 has a core 4 and an outer tube 6 surrounding the core 4 with the formation of a distance.
• the core 4 is formed in one piece and is cylindrical and has a through opening 28 through which a fastening element for fastening the bearing 2 to the vehicle body can be passed.
• the through opening 28 enables a structure arranged on one axial side of the bearing to be screwed to a structure arranged on the other side, passing through the bearing.
• the bearing 2 is inserted into a receiving eye of a subframe, in particular pressed.
• the core 4 and the outer tube 6 can be made of metal or plastic.
• An elastomer body 8, a first membrane 10 and a second membrane 12 are arranged between the core 4 and the outer tube 6, so that only three elastomer elements are provided in the space.
• the elastomer body 8 partially forms a main support pad 78 and serves both as an axial bearing 30 and as a radial bearing 32. In the circumferential direction U, the main support pad 78 alternates at a 90 ° angle with a membrane section 76, which is shown in the right half of FIG you can see.
• the elastomer body 8 encloses with the first membrane 10, which here serves as an intermediate membrane, a second fluid chamber 16 which functions as a compensation chamber.
• Both fluid chambers 14, 16 are filled with a fluid and connected to one another in a liquid-conducting manner via a damping channel 18.
• the elastomer body 8, the first membrane 10 and the second membrane 12 overlap at least in sections in the longitudinal direction L.
• the elastomer body 8 is approximately hollow cone-shaped at least in sections and integrally connected to the core 4 and the outer tube 6 via inner and outer connection sections 52, 54, preferably vulcanized.
• the core 4 runs conically in the area of the connection section 52 in the left half of FIG. 2 and has a radial extension 74 in the area of the connection section 52 in the right half of FIG. 2, with the aid of which the pumping surface of the second fluid chamber 16 can be adjusted .
• the first membrane 10 is connected on the inside to an inner sleeve 42 and on the outside to a second outer sleeve 46, preferably vulcanized on.
• the second membrane 12 is connected on the inside to a ring element 40 and on the outside to a first outer sleeve 44, preferably anvulka nized.
• the inner sleeve 42 is pushed onto the core 4, in particular pressed on.
• the Au chemistryhülsen 44, 46 are pushed into the outer tube 6, in particular pressed.
• the ring element 40 can serve as a stop plate and is supported axially on the core 4 and can be pressed with this. These connections can be press fits.
• a filling device 56 for filling the fluid chambers 14, 16 is formed in the ring element 40.
• the second outer sleeve 46 forms the damping channel 48 with a ring element 58.
• the radial stops 37 are formed on the second outer sleeve 46 two radial stops 37, which limit the relative movement of the core 4 to the outer tube 6 in the vehicle longitudinal direction X.
• the radial stops are opposite one another with respect to the central longitudinal axis A and are arranged in the X-plane.
• the radial stops 37 thus have a radial effective direction and can each be arranged on an axially extending section of the second outer sleeve 46.
• the radial stops 37 can each be configured monolithically with the first membrane 10 and / or arranged in a fluid chamber 14, 16.
• the radial stops 37 can be arranged in the elastomer bearing 2 in such a way that they are arranged in an axial central area between the two axially outer elastomer elements.
• the Ra dial stops 37 are arranged centrally between the one end axially outer second membrane 12 and the other end axially outer elastomer body 8.
• the ring element 40 protrudes at least in sections into an interspace between the core 4 and the outer tube 6, a flange section of the ring element 40 running there.
• This flange section which extends from the core 4 in the direction of the outer tube 6, carries the second membrane 12.
• the ring element 40 extends in the radial direction R over half the distance from the outer tube 6.
• the second outer sleeve 46 has a flange section which carries the first membrane 10. Starting from the outer tube 6, this flange section extends in the direction of the core 4 and in the radial direction R over half the distance from the core 4.
• the flange sections of the ring element 40 and the second outer sleeve 46 thus overlap at least in sections in the radial direction R.
• the outer tube 6 has a collar section 34 which carries a first stop 36 on the end face.
• the first outer sleeve 44 carries a second stop 38 on the end face.
• the stops 36, 38 can restrict a relative movement from the core 4 to the outer tube 6 in the axial direction.
• the first stop 36 can be designed monolithically with the elastomer body 8.
• the second stop 38 can be formed monolithically with the second membrane 12.
• the elastomer body 8 is in the longitudinal direction L at least partially leads out as a wedge bearing - both its radially inner connection sections 52 and its radially outer connection sections 54 are at least partially relative to the central longitudinal axis A tilts ver. These tilts run in the left and right halves of FIG. 2 in the direction of the central longitudinal axis A.
• the elastomer bearing 2 has a flea HL in its longitudinal direction L.
• the elastomer body 8 has a connection overlap height FIA in the longitudinal direction L. It can be seen that the Connection overlap height HA of the elastomer body 8 in the longitudinal direction L corresponds at least in sections to between 0.2 times and 0.6 times the height HL of the bearing 2.
• the connection overlap height HA of the elastomer body 8 varies along the circumferential direction U around the central longitudinal axis A, here offset by 90 °, so that the connection overlap height HA lying diametrically with respect to the central longitudinal axis A are identical. In the left half of Fig.
• connection overlap height HA has a first value, since here an overlap of the two connection sections 52, 54 of the elastomer body 8 in the longitudinal direction L is given.
• the two connection sections 52, 54 are axially spaced from one another in the longitudinal direction L, so that the connection overlap height HA theoretically assumes a negative value here - there is no overlap, since the connection overlap height HA on the right-hand side is at most zero in sections amounts to.
• Both membranes 10, 12 each have a first leg 20, a second leg 22 and a base 24 connecting the two legs 20, 22 to one another.
• the second leg 22 is cylindrical or tubular in a short segment and has a connecting portion 48 in the form of a thickening 50 at each end.
• the thickening 50 is integrally bonded to an outside of the inner sleeve 42, in particular by vulcanization.
• the thickening 50 is connected to an inner side of the outer sleeve 44 with a material fit, in particular vulcanized on.
• An average thickness of the first leg 20 is at least twice as thick as the average thickness of the other leg 22 in the tubular segment.
• the cross section of the leg 20, which is at least twice as thick on average expands steadily according to the shape or the course of an exponential function starting from the base 50.
• the leg 20 which is at least twice as thick on average forms the radially outer leg and in the second membrane 12 the leg 20 which is at least twice as thick on average forms the radially inner leg.
• the on average at least twice as thick leg 20 of the first membrane 10 and the on average at least twice as thick leg 20 of the second membrane 12 extend towards each other in the longitudinal axial direction.
• Each membrane 10, 12 has a central surface 70.
• a tangent of the central area 70 can, at least in sections, enclose an angle in the range from 0 ° to 90 ° with the central longitudinal axis A.
• Each thick leg 20 has a radially aligned connection width 26 at its connection section 68, via which it is connected to a connection structure (ring element 40, second outer sleeve 46).
• connection width 26 is that length which the leg 20 has in the radial direction R over its entire extent. This also includes the area of the membrane 10, 12 which is not engaged from behind by a connection structure in the longitudinal direction L, in the event that the thickness or extent of the corresponding membrane 10, 12 in this area has sufficient stability to absorb axial forces.
• the section of the membrane 10 not supported in the longitudinal direction L (FIG. 2, right half of the figure) extends so far in the longitudinal direction L that this section cannot evade even with high axial forces and therefore absorbs them.
• each of the two thick legs 20 each has a connection width 26.
• connection widths 26 of the two at least twice as thick legs 20 of the two membranes 10, 12 overlap at least in sections in the radial direction R and thus form an overlap width 72.
• the two thick legs 20 of the two membranes 10, 12 and the two connection structures are now at least largely brought into axial alignment.
• the functionality of the elastomer bearing 2 will be discussed with reference to the two halves of the figure in FIG. In the left half of the figure, the section in the Y direction is shown.
• the elastomer body 8 oriented in the Y direction extends over a large Z distance or it has a large FIA value.
• the elastomer body 8 which is oriented in the X direction, is primarily loaded with thrust when it is deflected in the X direction.
• the main support cushion 78 is therefore softer in the X direction in relation to the Y rigidity.
• the additional Radialan strikes 37 are therefore provided in the X direction.
• the elastomer body 8 In an assembled state in the transverse direction of the vehicle Y, the elastomer body 8 thus has at least twice as high a static rigidity in the unloaded state as in the longitudinal direction of the vehicle X.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Combined Devices Of Dampers And Springs (AREA)

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• 2020
  • 2020-05-19 DE DE102020113527.0A patent/DE102020113527A1/de active Pending
• 2021
  • 2021-03-25 CN CN202180033903.8A patent/CN115552143A/zh active Pending
  • 2021-03-25 WO PCT/EP2021/057794 patent/WO2021233598A1/de active Application Filing

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