Hydroelastic bearing

Abstract

Hydroelastic bearing (1) comprising a spring functional component (2) and an outer sleeve (3) coupled to the spring functional component (2), wherein the spring functional component (2) comprises an internal mounting connection (4) and at least two working chambers (7) filled with a damping fluid and connected via at least one damping channel (10), such that when the internal mounting connection (4) is deflected relative to the outer sleeve (3) the damping fluid flows at least partially from one working chamber (7) to the other via the damping channel (10), wherein the working chambers (7) are further connected via at least one decoupling channel (19), wherein a decoupling element (18) is arranged in a flow path of the decoupling channel (19), and wherein the decoupling channel (19) and the decoupling element (18) are at least partially arranged in a decoupling recess (13) provided for this purpose in the outer sleeve (3), wherein the bearing (1) further comprises a decoupling insert (12) which is at least partially inserted into the decoupling recess (13), wherein the decoupling channel (19) is formed in the decoupling insert (12), and wherein the decoupling element (18) is arranged in the decoupling insert (12), wherein the decoupling insert (12) comprises two insert parts (14), and the decoupling element (18) is arranged between the two insert parts (14).

Description

[0001] The invention relates to a hydroelastic bearing, particularly for use in a motor vehicle. The hydroelastic bearing can be used, for example, to support an axle carrier or a wheel guide, particularly a wishbone. The hydroelastic bearing can also be used as a bearing for assemblies and for supporting the oscillating mass of a vibration damper.

[0002] The hydroelastic mount is generally used when a relative movement of a vibration-loaded component, such as a motor vehicle component, to the body needs to be permitted and damped. Due to the use of elastomer material, the hydroelastic mount provides restoring spring forces as well as actively generated damping forces through dissipation losses in the mount.

[0003] Generally, the hydroelastic bearing comprises a spring functional component and an outer sleeve coupled to the spring functional component. The spring functional component has an internal mounting connection via which the bearing is to be mounted to a component subject to vibration loading, such as the body of a motor vehicle. The outer sleeve is usually attached to the motor vehicle part, which is to be connected to the motor vehicle body. The spring functional component is mounted in the outer sleeve and connected to the outer sleeve via an external mounting connection of the spring functional component. A reverse connection of the spring functional component to the motor vehicle body and the motor vehicle component can also be considered. A spring body of the spring functional component couples the mounting connections to one another to allow relative mobility between the mounting connections or between the internal mounting connection and the outer sleeve.The spring body at least partially defines two working chambers for accommodating a damping fluid. The working chambers can communicate fluidically with each other via a damping channel to allow fluid exchange between the working chambers during a defined relative deflection of the inner mounting connection and the outer sleeve, resulting in volume changes in the working chambers. This allows for dissipation losses due to the flow between the working chambers.

[0004] The damping properties can be determined by adjusting the flow resonance of the damping channel and the working chambers. However, with conventional hydroelastic mounts, despite such adjustment of the damping properties, it can happen that the hydroelastic mount exhibits high dynamic stiffness in a certain excitation frequency range and at certain excitation amplitudes due to the flow resonances in the damping channel. This can be particularly the case with medium-high excitation frequencies and, at the same time, low amplitudes. Medium-high excitation frequencies can be excitation frequencies in a range between approximately 20 Hz and approximately 300 Hz, which is particularly important for road noise generation. Low amplitudes refer to amplitudes that typically occur in this medium-high frequency range of a roadway.

[0005] To prevent dynamic stiffening of the hydroelastic mount at low amplitudes, decouplers can be incorporated into the hydroelastic mount. Typically, the decoupler is located in an additional decoupling channel, which also connects the working chambers and is typically larger in diameter and smaller in length than the damping channel. The decoupler is flexible or movable and is located within the decoupling channel. The decoupler ensures that the damping fluid can flow into and out of the decoupling channel at low excitation amplitudes, thereby decoupled from the working chambers at low excitation amplitudes and preventing dynamic stiffening due to flow resonances in the damping channel.At high excitation amplitudes, however, the decoupler closes the decoupling channel so that the damping fluid flows through the damping channel.

[0006] However, to date, no decoupling device has been developed that allows a satisfactory adjustment of the dynamic properties of the hydroelastic bearing.

[0007] FR 2 831 631 A1 discloses a hydraulic mount for damping vibrations of engines in vehicles, the mount comprising a fluid-filled working chamber, a fluid-filled, easily deformable compensation chamber and a decoupling valve located between the working chamber and a fluid-filled channel communicating with the compensation chamber.

[0008] EP 1 701 057 A1 discloses a hydroelastic mount for vehicle engines comprising a working chamber and a fluid-filled expansion chamber, the working chamber and the expansion chamber being connected by a connecting channel. The working and expansion chambers have elastically deformable walls.

[0009] Another hydroelastic bearing is also described in the document EP 0 304 349 A1.

[0010] It is therefore an object of the present invention to provide a hydroelastic bearing which allows an improved adjustment of the dynamic properties.

[0011] This object is achieved by the features of the independent claims. Preferred embodiments emerge from the dependent claims.

[0012] According to the present invention, a hydroelastic bearing is provided, comprising a spring functional component and an outer sleeve coupled to the spring functional component, wherein the spring functional component comprises an inner mounting connection and at least two working chambers filled with a damping fluid and connected via at least one damping channel, so that upon deflection of the inner mounting connection relative to the outer sleeve, the damping fluid flows at least partially from one working chamber to the other via the damping channel, wherein the working chambers are further connected via at least one decoupling channel, wherein a decoupling element is arranged in a flow path of the decoupling channel, and wherein the decoupling channel and the decoupling element are at least partially arranged in a decoupling recess provided for this purpose in the outer sleeve.

[0013] Advantageously, arranging the decoupling channel and the decoupling element in the decoupling recess of the outer sleeve enables an improvement in the adjustability of the dynamic properties of the hydroelastic bearing. In particular, additional installation space is provided for the decoupling channel and the decoupling element outside the spring function component, thus creating considerable flexibility for the configuration of the decoupling channel and the decoupling element without influencing or impairing the function of the spring function component. Furthermore, the additional installation space allows for a more favorable design of the flow path of the decoupling channel.

[0014] The dynamic properties of the hydroelastic bearing can be adjusted via the configuration of the decoupling channel and / or the decoupling element. The decoupling channel and the decoupling element can be configured such that at low excitation amplitudes, the damping fluid flows predominantly into and out of the decoupling channel, thereby preventing dynamic stiffening at these excitation amplitudes. Conversely, the decoupling channel and the decoupling element can be configured such that at high excitation amplitudes, the decoupling element essentially closes the decoupling channel, so that at these high excitation amplitudes, the damping fluid flows exclusively or at least predominantly through the damping channel.

[0015] The decoupling channel can generally be larger in diameter and smaller in length than the damping channel. The decoupling channel extends between the two working chambers and connects them, but the decoupling element is arranged in the flow path of the decoupling channel. The decoupling element is arranged in such a way that it separates or divides the decoupling channel into one side, which is connected to one working chamber, and another side, which is connected to the other working chamber. The decoupling element can be fixedly, i.e., immovably, clamped in place; in this case, fluid exchange between the two working chambers via the decoupling channel does not occur, and the inflow and outflow of the damping fluid into and from the decoupling channel is enabled solely by the elastic compliance of the decoupling element.The decoupling element can also be arranged loosely, i.e., movably, in a decoupling receptacle, whereby inflow and outflow of the damping fluid into and out of the decoupling channel is then enabled by a displacement of the decoupling element, in particular a back-and-forth movement of the decoupling element in the decoupling receptacle, in addition to a possible elastic compliance of the decoupling element. With a movable arrangement of the decoupling element, a certain fluid exchange can also take place between the two working chambers via the decoupling channel, flowing around the decoupling element. Such fluid exchange essentially only occurs at low excitation amplitudes, since at high excitation amplitudes the decoupling channel is closed by the pressed-on decoupling element.

[0016] The dynamic properties of the hydroelastic bearing can be adjusted, for example, by changing the length, cross-section, and / or cross-sectional shape of the decoupling channel, by changing the elastic compliance of the decoupling element, the shape and / or mass and / or arrangement of the decoupling element, and / or by changing the play of the decoupling element in the decoupling receptacle. By providing the decoupling recess in the outer sleeve, these parameters can be changed and adjusted over a wide range and without constraints due to the available space.

[0017] The decoupling recess is provided in the outer sleeve in addition to the recess for receiving the spring functional component. The recess for receiving the spring functional component can be substantially cylindrical, and the spring functional component can correspondingly also be substantially cylindrical. Due to the additional decoupling recess, the spring functional component can be substantially symmetrical, in particular with regard to the design of the spring body and the working chambers, since no additional space needs to be provided for the decoupling channel and the decoupling element in the spring functional component. With a sufficiently large wall thickness of the outer sleeve and / or sufficiently small dimensions of the decoupling recess, the outer contour of the outer sleeve can be substantially cylindrical, and the decoupling recess can be formed in the inner wall of the outer sleeve.However, the outer contour of the outer sleeve can also have a bulge or protrusion to provide the necessary space for the decoupling recess or the decoupling channel and the decoupling element in the outer sleeve. The outer sleeve can then have an asymmetrical shape. The outer sleeve can have a fastening section, for example, for fastening a motor vehicle part that is to be connected to a motor vehicle body. It is also conceivable to provide two decoupling recesses in the outer sleeve, each with decoupling channels and decoupling elements arranged therein, wherein the decoupling recesses can be formed opposite one another, in particular diametrically opposite one another, in the outer sleeve, which enables a particularly symmetrical design of the hydroelastic bearing.

[0018] The decoupling channel can be formed in the outer sleeve, in particular in the material of the outer sleeve. The outer sleeve can also have a decoupling receptacle for receiving the decoupling element. Alternatively, the decoupling channel can be formed in a decoupling insert that is inserted or placed into the decoupling recess, wherein the decoupling insert can have the decoupling receptacle for receiving the decoupling element. The decoupling channel can also be limited or closed radially inward by the spring function component, and not by the material of the outer sleeve or the decoupling insert.

[0019] Preferably, the decoupling recess is formed radially outwardly relative to the spring function component.

[0020] Due to the decoupling recess located radially outwardly of the spring function component, additional installation space can be provided for the decoupling channel and the decoupling element at a suitable location, for example on the outer circumference of the spring function component between the two working chambers, whereby the dynamic properties of the hydroelastic bearing can be better adjusted without influencing the function of the spring function component.

[0021] According to a first alternative, the hydroelastic bearing further comprises a decoupling insert which is at least partially inserted into the decoupling recess, or according to a second alternative, the hydroelastic bearing may further comprise a decoupling insert which is at least partially inserted into the decoupling recess, wherein the decoupling channel is or can be formed in the decoupling insert, and wherein the decoupling element is or can be arranged in the decoupling insert.

[0022] The shape of the decoupling insert can be adapted radially outward and axially to the contour of the decoupling recess, and radially inward, the shape of the decoupling insert can be adapted to the outer contour of the spring function component. The decoupling insert can be clamped between the inner wall of the outer sleeve or the decoupling recess and the outer wall of the spring function component. The decoupling channel can extend through the decoupling insert, with the ends of the decoupling channel each opening into one of the working chambers. A decoupling receptacle for movably or immovably receiving the decoupling element can be formed in the decoupling insert.

[0023] According to the first alternative, the decoupling insert comprises two insert parts, and the decoupling element is arranged between the two insert parts, or according to the second alternative, the decoupling insert can comprise two insert parts, and the decoupling element can be arranged between the two insert parts.

[0024] The two insert parts can each have a partial section of the decoupling channel formed therein. The two insert parts can be assembled together to form the decoupling insert, wherein the decoupler receptacle can be formed between the two insert parts. The decoupling insert can also have more than two insert parts, which, when assembled, complement each other to form the decoupling insert.

[0025] According to the first alternative, the decoupling element can be an elastomer plate or a clamped elastomer membrane, or according to the second alternative, the decoupling element is an elastomer plate or a clamped elastomer membrane.

[0026] The decoupling element can be an elastomer plate or a clamped elastomer membrane with a substantially rectangular shape. The decoupling element can have a circumferential bead in the edge region, which surrounds a surface section with a smaller wall thickness. In particular, this surface section with the smaller wall thickness can be arranged in the flow path of the decoupling channel, so that the damping fluid impinges on both opposite sides of this surface section during operation of the hydroelastic bearing.

[0027] According to the first alternative, an impact surface of the decoupling element onto which the damping fluid impacts may be inclined at a predetermined angle to an axial direction of the hydroelastic bearing and / or to a radial direction of the hydroelastic bearing, or according to the second alternative, an impact surface of the decoupling element onto which the damping fluid impacts is inclined at a predetermined angle to an axial direction of the hydroelastic bearing and / or to a radial direction of the hydroelastic bearing.

[0028] By adjusting the inclination of the decoupling element relative to the hydroelastic bearing and the resulting inclination of the vibration direction of the decoupling element relative to the hydroelastic bearing, the dynamic properties of the hydroelastic bearing can be further influenced and adjusted. An inclined arrangement of the decoupling element also enables further configurations of the decoupling channel, particularly with regard to the channel layout.

[0029] The damping fluid preferably impacts the impact surface substantially perpendicularly. The decoupling element has two opposing impact surfaces, which are preferably arranged parallel to each other. Both impact surfaces can be inclined at a predetermined angle to the axial direction of the hydroelastic bearing and / or to one of the radial directions of the hydroelastic bearing.

[0030] Preferably, at least one overpressure passage is formed in the decoupling element.

[0031] The overpressure passage is closed up to a predetermined or predeterminable pressure applied to the decoupling element. At a pressure above the predetermined or predeterminable pressure, the overpressure passage opens and connects both sides of the decoupling channel and thus also both working chambers. Due to the overpressure passage, the decoupling element and the decoupling channel can additionally function as a pressure relief valve, which prevents the diaphragm of the working chambers of the spring function component from bursting under high loads. The overpressure passage can be designed as a linear or cross-shaped slot in the decoupling element. The decoupling element can have multiple overpressure passages.

[0032] Preferably, at least one stop knob is formed on the decoupling element.

[0033] The stop knob can improve the acoustic properties of the hydroelastic bearing. The stop knob can be configured such that when the decoupling element swings back and forth in the decoupler mount, the stop knob strikes the inner wall of the decoupler mount, thereby reducing impact noise. The decoupling element can have multiple stop knobs.

[0034] Preferably, the flow path of the damping fluid from one working chamber to the other working chamber via the decoupling channel does not have any steep changes in direction, in particular no corners.

[0035] For the function of the decoupling channel and the decoupling element, namely to reduce the dynamic stiffening of the hydroelastic bearing at low amplitudes, a flow path in the decoupling channel with smooth directional transitions is particularly advantageous. Smooth or flow-optimized transitions without steep changes in the direction of the damping fluid result in less turbulence, which in turn can lead to dynamic stiffening. By providing the decoupling recess in the outer sleeve, the hydroelastic bearing can be designed in such a way that the damping fluid can be guided from one working chamber via the decoupling channel to the decoupling element, and on the other side from the decoupling element via the decoupling channel into the other working chamber, without steep changes in direction.

[0036] Preferably, the hydroelastic bearing has a plurality of decoupling channels connecting the working chambers, wherein the decoupling element is arranged in flow paths of all decoupling channels.

[0037] The hydroelastic bearing can, for example, have 2, 3, 4, 5, 6, or more decoupling channels. The decoupling channels can be arranged parallel to one another and extend, for example, in the axial direction or in the circumferential direction of the hydroelastic bearing. The decoupling element preferably extends in the decoupling receptacle in such a way that it blocks the flow paths of all decoupling channels. However, multiple decoupling elements can also be provided, for example, one decoupling element per decoupling channel.

[0038] Embodiments of the invention are described in detail below with reference to the accompanying figures. It is understood that the invention is not limited to these embodiments, and that individual features of the embodiments can be combined to form further embodiments.

[0039] They show: Fig. 1 a perspective view of a hydroelastic bearing according to a first embodiment, as well as a spring function component thereof; Fig. 2 a sectional view of the hydroelastic bearing from Fig. 1 in axial direction; Fig. 3 a perspective view of an insert part of a decoupling insert and a decoupling element of the hydroelastic bearing from Fig. 1; Fig. 4 an alternative embodiment of the decoupling element from Fig. 3 in a plan view; Fig. 5 a perspective view of the decoupling insert of the hydroelastic bearing from Fig. 1; Fig. 6 a perspective view of an outer sleeve of the hydroelastic bearing from Fig. 1; Fig. 7 a perspective view of the outer sleeve of Fig. 6 with inserted decoupling insert; Fig. 8 a sectional view of the hydroelastic bearing from Fig. 1 transverse to the axial direction; Fig. 9 an enlarged view of the decoupling channel and the decoupling element from Fig. 8; Fig. 10 is a sectional view of a hydroelastic bearing according to a second embodiment transverse to the axial direction; Fig. 11 a sectional view of a hydroelastic bearing according to a third embodiment transverse to the axial direction, as well as perspective views of the outer sleeve and the decoupling element thereof; Fig. 12 is an exploded view of a hydroelastic bearing according to a fourth embodiment; Fig. 13 a sectional view of the hydroelastic bearing from Fig. 12 transverse to the axial direction; Fig. 14 is an exploded view of a hydroelastic bearing according to a fifth embodiment; Fig. 15 a sectional view of the hydroelastic bearing from Fig. 14 in axial direction; Fig. 16 is an exploded view of a hydroelastic bearing according to a sixth embodiment; Fig. 17 a sectional view of the hydroelastic bearing from Fig. 16 transverse to the axial direction; Fig. 18 is an exploded view of a hydroelastic bearing according to a seventh embodiment; Fig. 19 a sectional view of the hydroelastic bearing from Fig. 18 transverse to the axial direction; Fig. 20 a graphical representation of the loss angle of the hydroelastic bearing as a function of the excitation frequency in the low frequency range and at high amplitudes for different configurations; Fig. 21 a graphical representation of the loss angle of the hydroelastic bearing as a function of the excitation frequency in the high frequency range and at low amplitudes for different configurations; Fig. 22 a graphical representation of the dynamic stiffness of the hydroelastic bearing as a function of the excitation frequency in the high frequency range, at low amplitudes and with a large decoupling area for different configurations; Fig. 23 a graphical representation of the dynamic stiffness of the hydroelastic bearing as a function of the excitation frequency in the high frequency range, at low amplitudes and with a small decoupling area for different configurations.

[0040] Fig. 1 to 9 show a hydroelastic bearing 1 according to a first embodiment and components thereof in different views. Fig. 1 shows a perspective view of a hydroelastic bearing 1 according to the first embodiment and a spring function component 2 thereof, which together with the outer sleeve 3, into which the spring function component 2 is pressed, forms the hydroelastic bearing 1.

[0041] In the present embodiment, the outer sleeve 3 is a solid or thick-walled fastening sleeve or bushing for fastening the hydroelastic bearing 1 to a motor vehicle part to be connected to the motor vehicle body. Alternatively, however, the outer sleeve 3 can also be the motor vehicle part itself to be connected to the motor vehicle body, which has a corresponding, essentially cylindrical receptacle for receiving the spring function component 2. The outer sleeve 3 can be made of steel, aluminum, or plastic, for example. The diameter of the outer sleeve 3 can be, for example, approximately 30 mm to approximately 150 mm.

[0042] The spring function component 2 has an outer mounting connection 5 which radially surrounds the inner mounting connection 4 and is coupled to the outer sleeve 3, a spring body 6 made of vulcanized elastomer which at least partially delimits the at least two working chambers 7, 7 and couples the inner and outer mounting connections 4, 5 to one another in order to allow relative mobility between the inner and outer mounting connections 4, 5, and a support frame 8 made of a rigid material which surrounds the inner mounting connection 4, wherein each of the at least two working chambers 7 opens into at least one radial opening 9 which is open to the radial outside of the spring function component 2 and is closed by the outer sleeve 3 which is coupled to the outer mounting connection 5.

[0043] The spring functional component 2 has the internal mounting connection 4 for mounting the hydroelastic bearing 1, in particular on a vehicle body, and the external mounting connection 5 for mounting the spring functional component 2 to the outer sleeve 3. For assembly, the spring functional component 2 can be pressed axially into the outer sleeve 3. The internal mounting connection 4 can be formed by an inner fitting made of a rigid material, such as plastic or metal, preferably aluminum. Alternatively, it is possible to realize the internal mounting connection 4 exclusively by a recess in the spring body 6 of the hydroelastic bearing 1, without using a rigid inner fitting. The external mounting connection 5 is the circumferential outer side of the spring functional component 2, which is designed such that it can be firmly pressed into the outer sleeve 3, like a fastening bushing of the motor vehicle component.To attach the outer sleeve 3 to the motor vehicle part, the outer sleeve 3 has a fastening section 11 comprising two fastening plates arranged parallel to one another with mounting holes through which threaded bolts can be passed. The damping channel 10 is formed in the spring function component 2 and fluidically connects the two working chambers 7 to one another. The damping channel 10 is formed on the radial outer surface of the spring function component 2 or the external mounting connection 5. The damping channel 10 is limited or closed radially outwardly by the outer sleeve 3. Upon deflection or displacement of the internal mounting connection 4 relative to the outer sleeve 3 or the external mounting connection 5, the volumes in the working chambers 7 change, so that the damping fluid flows from one of the working chambers 7 into the other of the working chambers 7, whereby the desired damping is generated by the flow losses.

[0044] The sleeve-shaped support frame 8, which surrounds the internal mounting connection 4, is made of a rigid material, such as plastic or metal, preferably aluminum. Depending on the design of the bearing 1, the support frame 8 can be cylindrical, oval, or polygonal. The support frame 8 defines an axial direction and, as a stiffening sleeve, is designed to be closed in a ring shape, at least in sections, in order to form a sufficiently rigid cage structure that stabilizes or stiffens the spring body 6. The support frame 8 can form the external mounting connection 5 or be essentially rigidly connected to it.

[0045] The spring body 6 is made of elastomer material and partially delimits the at least two working chambers 7 for receiving the damping fluid. The spring body 6 comprises or consists of vulcanized elastomer. The spring body 6 is, in particular, vulcanized to the support frame 8 through a vulcanization process. If the internal mounting connection 4 is designed as a rigid inner sleeve, the spring body 6 can be vulcanized to the rigid inner sleeve. For improved adhesion, the metal and / or plastic parts can be provided with an adhesive before vulcanization. The surfaces can also be pre-coated with a primer. The vulcanized connections from the spring body 6 to the support frame 8 and, if applicable, to the inner sleeve constituting the internal mounting connection 4 represent mechanically resilient and non-detachable surface connections.The working chambers 7 can communicate with each other via the damping channel 10 to allow an exchange of damping fluid between the working chambers 7. The damping channel 10 can be delimited or closed in the radial direction by the outer sleeve 3 coupled to the external mounting connection 5. The spring body 6 couples the internal mounting connection 4 to the support frame 8 in such a way that relative mobility between the internal mounting connection 4 and the support frame 8 is permitted. Due to the elastic relative mobility between the internal mounting connection 4 and the support frame 8, the working chambers 7 are deformed depending on the load, resulting in a fluid flow exchange between the working chambers 7, which has a dissipating effect. The support frame 8, the external mounting connection 5, and the outer sleeve 3 can be essentially rigidly connected to each other.

[0046] The hydroelastic bearing 1 has a decoupling insert 12 arranged in a decoupling recess 13 in the outer sleeve 3. The decoupling insert 12 can be made of plastic or metal. The decoupling insert 12 comprises two insert parts 14 or halves, which, when assembled, form the decoupling insert 12. To simplify assembly, the insert parts 14 each have mounting pins 15 and mounting recesses 16 that interlock during assembly. In the connecting area of ​​the two insert parts 14, i.e., between the two insert parts 14, the decoupling insert 12 has a decoupling receptacle 17 for receiving a decoupling element 18. The decoupling receptacle 17 is designed as a flat recess in the respective insert parts 14, which is adapted to the shape of the decoupling element 18 and into which the decoupling element 18 can be inserted.

[0047] The decoupling insert 12 has four decoupling channels 19 formed therein. Sections of the four decoupling channels 19 are each formed in the insert parts 14. The decoupling insert 12 has two common inlet and outlet openings 20, which each connect the ends of the decoupling channels 19 on one side. The two common inlet and outlet openings 20 are each connected to a radial opening 9 of a working chamber 7, so that the decoupling channels 19 are connected to the working chambers 7.

[0048] The decoupling element 18 is designed in the form of a substantially rectangular plate. The decoupling element 18 is arranged in the decoupling receptacle 17 such that the long edge of the decoupling element 18 extends parallel to the axial direction of the hydroelastic bearing 1, and the short edge of the decoupling element 18 extends in the radial direction of the hydroelastic bearing 1. The decoupling element 18 has a circumferential, outer bead 21 that surrounds an impact surface 22 of the decoupling element 18. The decoupling element 18 is arranged such that the damping fluid in the decoupling channels 19 impinges on the impact surfaces 22 on both sides of the decoupling element 18 during operation. As shown in Fig. As shown in Figure 3, the decoupling element 18 has stop nubs 23 on the impact surface 22, which are preferably arranged between impact areas of the damping fluid of the respective decoupling channels 19. The stop nubs 23 are designed to abut against an inner wall of the decoupler receptacle 17 during operation in order to reduce noise generation. Fig. Figure 4 shows a variant of a decoupling element 18 in which, in addition to the stop nubs 23, overpressure passages 24 are provided in the impact areas of the damping fluid of the respective decoupling channels 19. The overpressure passages 24 are configured to allow the damping fluid to flow through the decoupling element 18 above a predetermined or predeterminable pressure of the damping fluid in the respective decoupling channel 19, thereby implementing the function of an overpressure valve.

[0049] Fig. 6 and Fig. 7 shows the outer sleeve 3 with the decoupling recess 13, once with and once without the inserted decoupling insert 12. The decoupling recess 13 is open radially inward. In the axial direction and in the radial outward direction, the decoupling recess 13 is delimited by the material of the outer sleeve 3. The decoupling recess 13 has a crescent-shaped cross-section that is essentially constant in the axial direction. In the area of ​​the decoupling recess 13, the outer sleeve 3 has a radially outwardly projecting bulge 25 in order to provide the necessary installation space for the decoupling recess 13 in the material of the outer sleeve 3.

[0050] The shape of the decoupling insert 12, in particular its outer contour, is adapted to the shape of the decoupling recess 13. The decoupling channels 19 formed in the decoupling insert 12 can be partially delimited radially outwardly by the inner wall of the decoupling recess 13. The decoupling channels 19 are each substantially shorter, for example, approximately 0.1 to approximately 0.4 times as short, than the damping channel 10. The cross-section of the decoupling channels 19 transverse to the flow direction is substantially larger than the cross-section of the damping channel 10. Thus, the sum of the cross-sections of all decoupling channels 19 can be approximately 2 to approximately 10 times as large as the cross-section of the damping channel 10.

[0051] As in Fig. As shown in Figure 9, the decoupler holder 17 has a gap width t sp By adjusting the gap width t sp relative to the thickness t EEBy adjusting the decoupling element 18, particularly in the area of ​​the bead 21, the vibration behavior of the decoupling element 18 and thus the dynamic vibration behavior of the hydroelastic bearing 1 can be adjusted. For example, the decoupling element 18 can be clamped firmly and immovably in the decoupling receptacle 17, or the decoupling element 18 can be arranged in the decoupling receptacle 17 so that it can move in the flow direction of the decoupling channel 19, whereby the degree of mobility, i.e., the play, is adjustable. The play of the decoupling element 18 in the decoupling receptacle 17 has a strong influence on the dynamic behavior of the hydroelastic bearing 1.

[0052] The elastic deformability of the decoupling element 18 and / or the movable arrangement of the decoupling element 18 in the decoupler receptacle 17 enables the damping fluid to flow into and out of the decoupling channel 19 during operation, particularly at low excitation amplitudes. The fluid flows into and out of the decoupling channel 19 as well as the oscillating displacement of the internal mounting connection 4 relative to the outer sleeve 3 due to the external excitation are indicated by arrows.

[0053] Fig. 10 shows a sectional view of a hydroelastic bearing 1 according to a second embodiment. The second embodiment differs from the first embodiment in that the decoupling element 18 is lower than in the first embodiment. Lower here means that the short edge of the essentially rectangular decoupling element 18 is shorter than in the first embodiment. Accordingly, the decoupling insert 12 and the decoupling recess 13 of the outer sleeve 3 are narrower than in the first embodiment, so that the bulge 25 is also smaller. The outer sleeve 3 of the second embodiment therefore has a nearly symmetrical outer contour. The dynamic behavior of the hydroelastic bearing 1 can be changed by changing the dimensions of the decoupling element 18 and / or the decoupling channel 19.

[0054] Fig. 11 shows a sectional view of a hydroelastic bearing 1 according to a third embodiment, as well as perspective views of the outer sleeve 3 and the decoupling element 18 thereof. The essential difference of the third embodiment compared to the first and second embodiments is that the decoupling channels 19 and the decoupling receptacle 17 are formed in the material of the outer sleeve 3 itself. The decoupling channels 19 are delimited or formed by partition walls running in the circumferential direction of the outer sleeve 3 within the decoupling recess 13. The decoupling receptacle 17 is formed by a depression in the material of the outer sleeve 3 running perpendicular to the decoupling channels 19 in the axial direction of the outer sleeve 3. The decoupling channels 19 are delimited radially inward by the spring function component 2.The hydroelastic bearing 1 according to the third embodiment has no decoupling insert, which can reduce the manufacturing costs.

[0055] Fig. 12 and Fig. 13 show a fourth embodiment of a hydroelastic bearing 1. The essential difference from the previous embodiments is that the decoupling element 18 is arranged in the decoupling insert 12 rotated by approximately 90° around its longitudinal axis. The decoupling insert 12, in particular the configuration of the decoupling channels 19 and the decoupler receptacle 17 therein, are adapted accordingly. The decoupling insert 12 is divided in the circumferential direction of the outer sleeve 3 into two essentially equal-sized insert parts 14 or halves. The decoupling channels 19 in one of the insert parts 14, ie on one side of the decoupling element 18, are delimited radially inwards by the spring function component 2, and the decoupling channels 19 in the other of the insert parts 14, ie on the other side of the decoupling element 18, are delimited radially outwards by the inner wall of the decoupling recess 13 of the outer sleeve 3.During operation, the decoupling element 18 oscillates in the radial direction. Changing the arrangement of the decoupling element 18 changes the dynamic behavior of the hydroelastic bearing 1.

[0056] Fig. 14 and Fig. 15 show a fifth embodiment of a hydroelastic bearing 1. The fifth embodiment represents a variant of the first embodiment. In the fifth embodiment, the decoupling element 18, in particular the impact surface or the longitudinal axis thereof, is arranged at an angle α to the axial direction of the hydroelastic bearing 1. In the first embodiment, however, the decoupling element 18 is arranged parallel to the axial direction of the hydroelastic bearing 1. The angle α can, for example, be set in a range from approximately 1° to approximately 90°, preferably in a range from approximately 5° to approximately 30°, wherein the dynamic behavior of the hydroelastic bearing 1 can be changed by adjusting the angle α. Compared to the radial direction of the hydroelastic bearing 1 at the position of the decoupling element 18, the decoupling element 18, in particular the impact surface or the width axis thereof, is arranged oraligned. The decoupling insert 12, in particular the decoupling receptacle 17 and the decoupling channels 19 thereof, are designed to match the arrangement of the decoupling element 18.

[0057] Fig. 16 and Fig. 17 shows a sixth embodiment of a hydroelastic bearing 1. The sixth embodiment represents a variant of the fourth embodiment. The essential difference between the sixth embodiment and the fourth embodiment is that the decoupling element 18 is arranged in a decoupling insert 12, which is divided into two differently sized insert parts 14 or halves in the radial direction of the outer sleeve 3. The radially outer insert part 14 is lid-shaped and smaller than the radially inner insert part 14. The decoupling insert 12 according to the sixth embodiment facilitates the assembly of the hydroelastic bearing 1.

[0058] Fig. 18 and Fig. 19 show a seventh embodiment of a hydroelastic bearing 1. The seventh embodiment represents a variant of the sixth embodiment. In the seventh embodiment, the decoupling element 18, in particular the impact surface or the width axis thereof, is arranged at an angle β to the tangential direction of the hydroelastic bearing 1 at the position of the decoupling element 18. In the sixth embodiment, however, the decoupling element 18 is arranged parallel to the tangential direction of the hydroelastic bearing 1. The tangential direction is perpendicular to the radial direction of the hydroelastic bearing 1 at the position of the decoupling element 18. The angle β can, for example, be set in a range from approximately 1° to approximately 89°, preferably in a range from approximately 5° to approximately 20°, wherein the dynamic behavior of the hydroelastic bearing 1 can be changed by adjusting the angle β.The decoupling element 18, in particular the impact surface or its longitudinal axis, is arranged or aligned substantially parallel to the axial direction of the hydroelastic bearing 1. The decoupling insert 12, in particular the decoupling receptacle 17 and the decoupling channels 19 thereof, are configured to match the arrangement of the decoupling element 18. The inclination β of the decoupling element relative to the tangential direction can also be combined with an inclination α relative to the axial direction according to the fifth embodiment.

[0059] Fig. Figure 20 shows a graphical representation of the loss angle of the hydroelastic bearing as a function of the excitation frequency in the low frequency range and at high amplitudes for different configurations k1, k2, k3 and k4 of the hydroelastic bearing, and Fig. Figure 21 shows a graphical representation of the loss angle of the hydroelastic bearing as a function of the excitation frequency in the high frequency range and at low amplitudes for the various configurations k1, k2, k3, and k4. According to configuration k1 of the hydroelastic bearing, no decoupling channel with a decoupling element is provided. According to configuration k2, a decoupling channel with a decoupling element is provided, wherein the decoupling element receptacle is designed relative to the thickness of the decoupling element such that only a small amount of mobility or play exists for the decoupling element in the decoupling element receptacle. In configuration k3, the play of the decoupling element is increased compared to configuration k2, and in configuration k4, the play of the decoupling element is the largest of all configurations. The remaining design of the hydroelastic bearing is the same for all configurations, so that the Fig. 20 to 23 illustrate the influence of the play of the decoupling element on the dynamic behavior of the hydroelastic bearing.

[0060] As in Fig. As can be seen in Figure 20, the difference in the loss angle, as an indicator of the attenuation, is relatively small for the different configurations at high excitation amplitudes. At low excitation amplitudes, as in Fig. However, as shown in Figure 21, the difference in the loss angles between the different configurations is very large. This shows that the dynamic behavior of the hydroelastic bearing in the low amplitude range can be specifically adjusted by configuring the decoupling channel and the decoupling element.

[0061] Fig. 22 and Fig. 23 show graphical representations of the dynamic stiffness of the hydroelastic bearing as a function of the excitation frequency, where the difference between the designs of the hydroelastic bearing for Fig. 22 and Fig. 23 in the size or in the size ratio of the decoupling element and the decoupling channel. In Fig. Figure 22 shows a case where the decoupling area is large and the ratio of the decoupling channel cross-section to the decoupling channel length is also large. Fig. Figure 23, however, shows a case where the decoupling area is small and the ratio of the decoupling channel cross-section to the decoupling channel length is also small. The decoupling area refers to the impact area of ​​the decoupling element. The configurations k1, k2, k3, and k4 are as described above. Fig. 22 and Fig.Figure 23 shows that the dynamic stiffness can be precisely adjusted in terms of both magnitude and frequency as needed. The fact that in some configurations the dynamic stiffness initially drops to a value below the static stiffness is due to the so-called "notch effect." List of reference symbols 1 hydroelastic bearing 2 spring function component 3 Outer sleeve 4 Internal mounting connection 5 External mounting connection 6 spring bodies 7 Working chamber 8 supporting frames 9 Radial opening 10 Damping channel 11 Fastening section 12 Decoupling insert 13 Decoupling recess 14 Insert 15 mounting pins 16 Mounting recess 17 Decoupler holder 18 Decoupling element 19 Decoupling channel 20 common inlet and outlet opening 21 bulge 22 Impact area 23 stop studs 24 Overpressure passage 25 bulge t sp Gap width t EE Thickness of the decoupling element α angle relative to axial direction k1 Configuration without decoupling channel and decoupling element k2 configuration with small play of the decoupling element k3 Configuration with medium play of the decoupling element k4 Configuration with large play of the decoupling element

Claims

[1] Hydroelastic bearing (1), comprising a spring function component (2) and an outer sleeve (3) coupled to the spring function component (2), wherein the spring function component (2) comprises an internal assembly connection (4) and at least two working chambers (7) filled with a damping fluid and connected via at least one damping channel (10), so that upon deflection of the internal assembly connection (4) relative to the outer sleeve (3), the damping fluid flows at least partially from one working chamber (7) into the other via the damping channel (10), wherein the working chambers (7) are further connected via at least one decoupling channel (19), wherein a decoupling element (18) is arranged in a flow path of the decoupling channel (19), and wherein the decoupling channel (19) and the decoupling element (18) are at least partially arranged in a decoupling recess (13) provided for this purpose in the outer sleeve (3), wherein the bearing (1) further comprises a decoupling insert (12) which is at least partially inserted into the decoupling recess (13), wherein the decoupling channel (19) is formed in the decoupling insert (12), and wherein the decoupling element (18) is arranged in the decoupling insert (12), wherein the decoupling insert (12) comprises two insert parts (14), and the decoupling element (18) is arranged between the two insert parts (14). [2] Hydroelastic bearing (1), comprising a spring function component (2) and an outer sleeve (3) coupled to the spring function component (2), wherein the spring function component (2) comprises an internal assembly connection (4) and at least two working chambers (7) filled with a damping fluid and connected via at least one damping channel (10), so that upon deflection of the internal assembly connection (4) relative to the outer sleeve (3), the damping fluid flows at least partially from one working chamber (7) into the other via the damping channel (10), wherein the working chambers (7) are further connected via at least one decoupling channel (19), wherein a decoupling element (18) is arranged in a flow path of the decoupling channel (19), and wherein the decoupling channel (19) and the decoupling element (18) are at least partially arranged in a decoupling recess (13) provided for this purpose in the outer sleeve (3), wherein the decoupling element (18) is an elastomer plate or a clamped elastomer membrane, wherein an impact surface (22) of the decoupling element (18) onto which the damping fluid impacts is inclined at a predetermined angle (α, β) to an axial direction of the hydroelastic bearing (1) and / or to a radial direction of the hydroelastic bearing (1). [3] Hydroelastic bearing (1) according to claim 1 or 2, wherein the decoupling recess (13) is formed radially outwardly relative to the spring function component (2). [4] Hydroelastic bearing (1) according to one of the preceding claims, wherein at least one overpressure passage (24) is formed in the decoupling element (18). [5] Hydroelastic bearing (1) according to one of the preceding claims, wherein at least one stop knob (23) is formed on the decoupling element (18). [6] Hydroelastic bearing (1) according to one of the preceding claims, wherein the flow path of the damping fluid from one working chamber (7) to the other working chamber (7) via the decoupling channel (19) does not have any steep changes in direction, in particular does not have any corners. [7] Hydroelastic bearing (1) according to one of the preceding claims, comprising a plurality of decoupling channels (19) connecting the working chambers (7), wherein the decoupling element (18) is arranged in flow paths of all decoupling channels (19).

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