Hydro-damper bush bearing

Abstract

The invention relates to a hydraulic damping bush bearing, comprising a core which extends along a central longitudinal axis of the bush bearing and which accommodates a fastening element, an outer bush which surrounds the bearing on the outer circumferential side and which fixes the bush bearing in the accommodation, an elastomer which is arranged between the outer bush and the core, a pair of axial chambers which has at least two axial chambers which are offset in the axial direction, the axial chambers being fluidically connected to one another by at least one axial channel, a pair of radial chambers which has at least two radial chambers which are offset in the radial direction, the radial chambers being arranged between the axial chambers in such a way that they completely separate the axial chambers from one another, the pair of radial chambers being fluidically connected to one another by at least one radial channel, the elastomer comprising at least two diaphragms which are fixed in material-fit connection on the inner connecting part on the radially inner side and on the outer connecting part on the radially outer side, each diaphragm having a first arm, a second arm and a base which connects the two arms to one another.

Description

Technical Field

[0001] This invention relates to a hydraulic damping bushing bearing (Buchsenlager). Background Technology

[0002] Hydraulic damping bushing bearings with two damping operating directions are basically known and are often used, for example, in motor vehicles, to radially and / or axially dampen shocks and / or eliminate vibrations.

[0003] However, existing known solutions for axial-radial damped bearings, as described for example in DE102016212485B4 and EP2906852B1, have decisive drawbacks. These shortcomings and disadvantages are particularly evident in the axial damping and the simultaneously compact structural form.

[0004] To achieve good damping or ablation, a high loss angle is required in the dynamic characteristic curve. For this, in addition to sufficient channel cross-section, high pumping performance is particularly necessary between the corresponding, fluid-filled working chambers, especially between the corresponding axial working chambers. For example, in DE102016212485B4, the flow-connecting channel between the axial chambers is implemented as a borehole extending axially in the core, and therefore its length is limited by the core geometry. Furthermore, the external axial diaphragms defining the axial chambers outward are implemented with a uniform wall thickness, allowing them to easily bulge outward when high internal pressure exists in the axial chambers. Therefore, the axial pumping action and thus the overall axial damping of this design are limited. Conversely, increasing the pumping action in the illustrated design would result in an increase in the internal pressure within the axial chambers. However, this overpressure condition cannot be controlled because the design lacks installation space for, for example, integrating an overpressure valve (especially in the axial direction). Summary of the Invention

[0005] The object of this invention is to overcome these and other disadvantages of the prior art and to provide an optimized bushing bearing with improved axial damping or reduction as well as simultaneously high radial damping, and a more robust structure. Furthermore, the bearing described in this invention should allow for greater design freedom in the dimensional design of the channel (especially the axial channel), and the integration of an overpressure valve.

[0006] A hydraulically damped bushing bearing includes: a core extending along the central longitudinal axis of the bushing bearing and adapted to receive a fastening element; an outer bushing surrounding the bearing on its outer circumferential side and adapted to secure the bushing bearing in a receiving member; an elastomer disposed between the outer bushing and the core; an axial chamber pair having at least two axially offset chambers, the axial chambers being fluidly interconnected via at least one axial channel; and a radial chamber pair having at least two radially offset chambers, the radial chambers being arranged between the axial chambers in such a way that they completely separate the axial chambers from each other, wherein the radial chamber pairs are fluidly interconnected via at least one radial channel; wherein the elastomer includes at least two diaphragms, the diaphragms being radially inner with... An inner connecting portion and an outer connecting portion materially fixed on the radially outer side; wherein each of the two diaphragms has a first arm, a second arm, and a base connecting the two arms to each other; wherein the base is configured such that it describes the apex of the connected arm; wherein the average thickness of the first arm is at least twice the average thickness of the second arm; wherein the cross-section of the arm, which is at least twice as thick on average, continuously expands from the base; wherein the elastomer has another vulcanized body comprising two support blocks and two axially spaced intermediate diaphragms, the intermediate diaphragms being materially fixed on the radially inner side to the core and on the radially outer side to a retainer; according to the invention, the at least two diaphragms at least partially define the axial chamber from the outside in the axial direction.

[0007] The elastomer of the bushing bearing described in this invention preferably consists of three separate vulcanizates extending radially between the core and the outer bushing. It is made of an elastic material, specifically defining the static stiffness of the bearing and contributing to the formation of the flow-guiding chambers and channels of the bushing bearing. This elastomer is preferably designed to support damping under axial and radial loads in such a way that, together with other bearing components, it ensures pumping performance between corresponding chambers during dynamic motion, and thus plays a decisive role in the fluid damping or vibration reduction of the bushing bearing.

[0008] The outer bushing of the bushing bearing described in this invention surrounds the elastomer and the entire bushing bearing from the outside or the outer circumferential side. The outer bushing is typically used to secure and position the bushing bearing in an external support or housing, thereby forming a stable connection with the surrounding structure.

[0009] The first and second diaphragms of the bushing bearing described in this invention are flexible components within an elastomer, fixed to radially inner and outer connections. They define an axial chamber in the axial direction and allow elastic movement, which facilitates fluid movement and thus contributes to fluid damping.

[0010] The base of the first and second diaphragms is the connection point of two arms of a diaphragm, forming or defining its apex. The arms preferably extend substantially in or inclined relative to the axial direction. The base is preferably configured to stabilize the diaphragm structure and facilitate the transition between the arms. This advantageously increases the expansion stiffness of the diaphragm, thereby supporting damping capacity in the axial direction.

[0011] The arm is two parts of a diaphragm that extend axially and obliquely relative to the axial direction from the base. According to the invention, the first arm is thicker and fixed radially inward to the inner connecting portion, while the second, thinner arm is fixed radially outward to the outer connecting portion. Preferably, the first arm may be oriented obliquely relative to the axial direction, while the second arm may be oriented primarily in the axial direction. This arrangement advantageously promotes expansion stiffness under high internal pressure, as occurs during impact, and thus promotes damping of such impact-like loads or reduction of vibrations generated by impact. This is especially true because this particular diaphragm geometry has a large order of expansion stiffness depending on the internal pressure. Under high internal pressure, the first arm rests against the outer connecting portion, thereby advantageously making the diaphragm as a whole more expansion stiff.

[0012] The other centrally arranged vulcanized body in the bushing bearing of the present invention is an additional portion of the elastomer, vulcanized separately from the two diaphragms of the elastomer. It includes the support block of the bushing bearing of the present invention and forms radial chambers together with the internal intermediate diaphragms. The two radial chambers are connected by at least one radial channel, thereby forming a radial damping system. The elastomer is arranged radially between the core and the cage and is fixed in a material-fitting connection with both. Simultaneously, the two internal intermediate diaphragms define axial working chambers inward in the axial direction and are therefore part of the axial damping system. Furthermore, the other centrally arranged vulcanized body, with its diaphragms, especially the support block, makes a significant contribution to the static stiffness of the bushing bearing.

[0013] The support blocks are another supporting structural element of the vulcanizate, establishing a connection between the core and the cage in a direction transverse to the radial working direction. They thus separate the radial working chambers from each other, make a significant contribution to the stiffness of the elastomeric bearing in the second non-hydraulic damped radial direction, and provide support for the channels in the bushing bearing.

[0014] Due to the bushing bearing described in this invention, improved axial damping under high radial damping is advantageously achieved through the separate chamber arrangement and the special construction and orientation of the first and second diaphragms. The axial and radial chambers are separated by specific axial and radial channels and are interconnected in a flow-guided manner. This specific arrangement advantageously enables optimized damping characteristics that can be adjusted over a wide range, resulting in better vibration control compared to prior art, which typically involves only simple damping chambers without targeted channel guidance. The diaphragms of this invention, with their specific arm geometry and reinforced base, further provide improved expansion stiffness and simultaneously high service life, particularly for the first and second diaphragms. This diaphragm construction advantageously allows it to withstand higher pressures and provides improved pumping performance, which enhances the damping and mitigation characteristics and durability of the bushing bearing. Due to the independent axial and radial channel guidance within the elastomer of the bushing bearing, fluid flow can be directed in a targeted and controlled manner, thereby adjusting the dynamic characteristics of the bushing bearing. This advantageously improves damping characteristics. The coordinated arm thickness described in this invention allows for an advantageously designed bend line for the first diaphragm, which helps the diaphragm support itself externally under high internal pressure, thereby generating high pumping performance while protecting the much thinner second diaphragm from overload. In summary, the bushing bearing described in this invention thus has the potential to significantly improve the damping of bearings known in the prior art.

[0015] Preferably, the core of the bushing bearing may have a central recess, which may be configured as a through hole or configured to allow the bushing bearing to be tightened at the end face using a blind hole or a threaded fitting. The central recess in the core advantageously provides flexible tightening options for the bushing bearing and improves the accessibility of maintenance work. Installation is further simplified by the possibility of tightening via a blind hole or threaded fitting, and the bearing can be used more widely.

[0016] Preferably, the first and second diaphragms can be separate vulcanizates. Individual vulcanization of the diaphragms allows for customization to meet specific requirements. Furthermore, the complex arm geometries of the two diaphragms can be manufactured using simple opening and closing molds, resulting in cost-effective manufacturing overall. In addition to the arm geometry, the use of separate vulcanization molds allows for a very high degree of design freedom overall, which advantageously leads to particularly robust diaphragms and simultaneously high pumping performance.

[0017] According to another preferred embodiment of the invention, the elastomer can consist of three vulcanizates assembled together, wherein two axially outer diaphragms each form a vulcanizate, and a third vulcanizate can be formed from another vulcanizate having two support blocks and two inner intermediate diaphragms. The elastomer composed of three vulcanizates assembled together significantly simplifies production and increases the modularity of the bushing bearing. Separate vulcanization of the diaphragms and support blocks advantageously allows for targeted adjustments to material properties. For example, an elastomer compound individually adjusted according to desired characteristics can be used for each diaphragm and the third vulcanizate containing the support blocks. For example, a high Shore hardness compound can be used for the first and second diaphragms to obtain high pumping performance, while the Shore hardness of the elastomer compound used in the central third vulcanizate can be adjusted only according to the necessary overall characteristics and radial damping characteristics, since particularly high environmental resistance is not required. This can advantageously lead to higher functional reliability.

[0018] Preferably, the first arm, on average at least twice as thick, can have a first length, and the second arm can have a second length, wherein the first length can be at least twice the second length. The different arm lengths ensure optimized curvature and elongation distribution of the first and second diaphragms in the bushing bearing. The longer arm improves expansion stiffness, especially under high internal pressures. Its preferably inclined extension relative to the axial direction further ensures high pumping performance. When the pressure in the chamber is particularly high, the first arm can preferably support itself on the outer circumferential side, thereby protecting itself from overload, while the shorter arm can provide sufficient flexibility during axial deflection of the bushing bearing without significantly reducing overall pumping performance. This configuration can positively contribute, in particular, to the durability and load-bearing capacity of the first and second diaphragms, and thus the entire bushing bearing.

[0019] According to another preferred embodiment of the invention, the base may be oriented axially toward the radial chamber. This orientation of the base toward the radial chamber advantageously optimizes the support of the first diaphragm on the outer connection under high internal pressure. Since overpressure (positive internal pressure) is more critical than negative pressure (negative internal pressure), the bearing can be further preferably designed such that the first arm of the first and / or second diaphragm, preferably the first arm of both the first and second diaphragms, rests against the outer connection on its outer circumferential side under the more critical pressure, i.e., under overpressure in the axial chamber, thereby protecting itself from overload. By further oriented the thicker arm inward, it is advantageous to generate only compressive load in the thinner outer arm, without tensile load, under high internal pressure (e.g., up to 8 bar). This is particularly gentle for the service life of the thinner arm. In contrast, the negative pressure in the opposing axial chamber is less critical, as the pressure difference here can be up to 1 bar (e.g., 0 bar vacuum versus 1 bar ambient pressure). Therefore, overall damping efficiency can be advantageously maximized and the load on the diaphragm reduced. Conversely, if the base is oriented in the opposite direction, i.e., axially away from the radial chamber, overpressure will result in high, critical tensile stress in the thin second arm, while less critical negative pressure will cause the first arm to abut against the outer connection, resulting in less critical compressive stress in the elongated second arm. Therefore, the preferred embodiment of the invention, with the base axially oriented towards the radial chamber, provides a robust solution for high overpressure in the axial chamber, while maintaining high pumping performance, and thereby accompanied by more effective axial damping of the bushing bearing.

[0020] Preferably, the first arm, which is at least twice as thick on average, can be formed as the radially inward arm and fixed to the inner connection, while the second arm can be formed as the radially outward arm and fixed to the outer connection. This measure has proven particularly advantageous because it maximizes the pumping performance of the bushing bearing. Designating the thicker arm as the radially inward arm and the thinner arm as the radially outward arm improves the structural integrity or expansion stiffness of the first and second diaphragms of the bushing bearing. Therefore, the thicker, inward-facing arm improves the axial pumping performance of the bushing bearing.

[0021] Preferably, the bushing bearing may have a special channel half-shell structure that extends circumferentially around the elastomer, ensuring that the axial and radial channels form two independent, unconnected channels. This special channel half-shell structure clearly separates the axial and radial channels from each other. This structure improves damping reliability because fluid movement in the axial and radial directions is controlled independently. This avoids undesirable hydraulic interactions between the channels and contributes to precisely specified and effective damping performance.

[0022] More preferably, the axial channel may extend partially along the channel half-shell structure and / or elastomer and / or cage in the axial direction and partially in the circumferential direction to fluid-guide the pair of axial chambers, wherein the portion of the axial channel formed in the axial direction may be formed on the elastomer. Because the portion of the axial channel formed in the axial direction is formed on the elastomer, an improved seal relative to other channel sections of the channel structure can be advantageously achieved and realized. The axial channel being guided along portions of the channel half-shell structure and / or elastomer and / or cage allows for flexible control of fluid flow and, in particular, allows for more precise damping adjustments in the axial direction. By arranging the channel along different structural elements, available installation space can be optimally and flexibly utilized for the channel.

[0023] According to another alternative preferred embodiment, a portion of the axial channel formed in the axial direction may also be formed on the channel half-shell structure.

[0024] According to another preferred embodiment variation, the radial channel may extend circumferentially along the channel half-shell structure and / or the cage to fluidly connect the radial chamber pairs. The radial channel's alignment along the channel half-shell structure and / or the cage advantageously ensures an undisturbed connection of the radial chambers. Because the radial channel extends circumferentially and preferably substantially parallel to the axial channel, it can be made particularly long without interacting with the axial channel. This ensures high damping in the radial direction.

[0025] Preferably, the channel half-shell structure may have a first channel half-shell and a second channel half-shell, wherein the channel half-shell of the channel half-shell structure can form at least one additional, separate overpressure valve channel, which can flowably connect the first working chamber half and the second working chamber half to each other. The channel half-shell structure, or a structure with at least one additional overpressure valve channel, can eliminate pressure peaks between the working chambers. The possibility of additional pressure balancing between the two working chamber halves improves the robustness of the bushing bearing and prevents structural damage.

[0026] Preferably, an overpressure channel is conceivable to be equipped with a vertical overpressure valve that can open in both directions. Alternatively, the channel can be conceivable to be equipped with a ramp valve or fin valve that opens only in one direction, but is more robust than a vertically positioned valve. The fin valve should be understood as a valve that closes the outlet opening of the overpressure channel from the orifice in the channel half-shell with a slight preload, the orifice being located on the fluid chamber side. It is laterally positioned on the elastomer and can be flipped radially inward from the opening like a fin to allow fluid to flow out of the overpressure channel, while blocking and disallowing fluid flow in the opposite direction.

[0027] Preferably, the channel half-shell structure may have first and second channel half-shells, wherein the channel half-shells may form at least two additional, separate overpressure valve channels that can flowably connect the first and second working chamber halves to each other. Through multiple or at least two overpressure valve channels, the bushing bearing can flexibly respond to varying pressure conditions, particularly when the valve is designed as a finned valve. Additional pressure regulation can advantageously be achieved in the opposite direction, resulting in a more uniform load on the bearing, which further improves damping capacity and service life.

[0028] According to another preferred embodiment variation, at least one overpressure valve passage may be closed at its end or in its extension by a first resilient overpressure valve, wherein the first resilient overpressure valve opens only when a pressure differential exists in the two operating directions. Such a valve may be referred to as a finned valve or a ramp valve. The first resilient overpressure valve on at least one overpressure valve passage protects the bushing bearing during sudden pressure spikes. Because the valve opens only when a pressure differential exists, the load on the bearing is effectively reduced. This targeted pressure control results in improved damping efficiency and enhanced stability of the overall system.

[0029] According to another preferred embodiment, at least two overpressure valve passages can be closed at their ends by resilient overpressure valves, wherein each overpressure valve opens only when a pressure difference exists in one operating direction, and the operating directions of the two overpressure valves can correspond to opposite pressure differences. Such a valve can be referred to as a finned valve. The overpressure valves, responding to opposite pressure differences, enable selective and precise pressure regulation. Therefore, the system is effectively protected against different load directions, and functional reliability is improved even under varying pressure conditions and load directions.

[0030] Preferably, two overpressure valves are arranged radially opposite and axially staggered on the sidewalls of a single support block of the elastomer. Each valve corresponds to an overpressure channel guided across the support block. Since they are arranged on only one support block, an axial channel can advantageously be constructed on the other support block. Because these valves are arranged on opposite sides of a support block, they are located in different radial fluid chambers and can therefore compensate for pressure peaks from both radial fluid chambers, with each valve opening only in one operating direction. This arrangement prevents unilateral loading and reduces the risk of material damage, which improves the durability and efficiency of the bushing bearing.

[0031] According to another preferred embodiment, the resilient overpressure valve can be configured as a pivotable valve element that closes the overpressure valve passage in the closed position and pivots to the open position when a predetermined differential pressure limit in the radial chambers is exceeded, thereby flowably connecting the radial chambers to each other. The resilient overpressure valve is oriented circumferentially, and the pivoting movement radially outward can be limited by a channel half-shell structure. Due to this pivoting movement, these valves can also be referred to as finned valves. The pivotable resilient overpressure valve exhibits low elongation even when fully open, thus providing a particularly robust solution. This ensures controlled opening movement of the valve and its long service life.

[0032] Therefore, each overpressure valve can be laterally positioned on the support block or on the side wall of a support block. The overpressure valve does not have to share installation space with the channel, and a larger opening cross-section can be provided. The larger opening cross-section can effectively eliminate particularly high pressure peaks.

[0033] Preferably, a portion of the axial channel formed in the axial direction can be partially laterally defined by the chamber wall within the elastomer region, wherein the chamber wall forms a third resilient axial overpressure valve, and an additional overpressure valve passage can be released by bending under high axial pressure differentials. The lateral definition of the axial channel by the chamber wall and the additional resilient overpressure valve (axial) ensure targeted pressure relief even under high axial loads. This configuration, in addition to other overpressure valve passages, further protects the bearing from overstress and maintains its damping characteristics even under extreme axial loads.

[0034] According to another preferred embodiment variation, the additional overpressure valve passage can be configured to form a parallel short circuit, through which an additional connection can be established between the portion of the axial passage formed in the axial direction and the portion of the axial passage formed in the circumferential direction. The additional overpressure valve passage can advantageously function as a parallel short circuit, which can effectively eliminate pressure. This connection between the different, existing portions of the axial passage facilitates rapid pressure adjustment, thereby improving the bushing bearing's response, especially to sudden load changes.

[0035] Preferably, the channel half-shell structure may include a portion of an axial channel formed in the circumferential direction, a radial channel, and an overpressure valve channel connecting the radial chamber, wherein the portion of the axial channel, the radial channel, and the overpressure valve channel formed in the circumferential direction may be spaced apart in the axial direction and arranged parallel to each other on the outer surface of the channel half-shell structure. By compactly arranging the axial channel, radial channel, and overpressure valve channel in parallel within the channel half-shell structure, space is saved and efficiency is improved. This construction optimizes flow guidance and contributes to the stability of damping performance because the channels do not interfere with each other.

[0036] According to another preferred embodiment, the invention specifies that at least one axial channel may include a cross-section in the channel half-shell structure and / or cage, the cross-section being configured to be larger than the cross-section of at least one radial channel in the channel half-shell structure and / or cage. This allows for more effective and better axial damping, particularly through bushing bearings. Because the cross-section of the axial channel can be made particularly large, a large amount of fluid can be excited in the damping channel to reduce axial vibration, resulting in a high loss angle and a significant damping effect.

[0037] More preferably, a portion of the axial channel formed in the axial direction can be formed on the end face of a support block at the same height as the channel half-shell structure, wherein the portion of the axial channel formed in the axial direction can be arranged on a support block without a resilient overpressure valve. Positioning the axial channel on the end face of the support block allows for simple design of the channel geometry. Conversely, if the overpressure valve is arranged laterally on the same support block with the axial channel positioned thereon, the corresponding overpressure channel must intersect the axial channel on another plane to keep the channels clearly separated from each other. However, such a solution would be expensive. Therefore, the solution proposed according to the preferred embodiment variant for positioning the overpressure valve and the axial channel on different support blocks is particularly cost-effective and space-saving. Overall, this advantageously supports a compact construction of the bushing bearing in a cost-effective manner.

[0038] According to another preferred embodiment variation, the overpressure valve passage can be arranged axially between a portion of the radial passage and a portion of the axial passage formed circumferentially, wherein a central stop region can be provided in the channel half-shell structure, offset circumferentially relative to the overpressure valve passage. A robust channel half-shell is achieved by centrally arranging the relatively pressure-insensitive stop region at a position offset circumferentially relative to the overpressure valve passage. These stop regions effectively restrict movement and improve the structural stability of the bushing bearing, wherein the channel half-shell does not bear pressure in the channel region. The stop region in the channel half-shell is located in the direct load path between the stop member on the core (on which a rubber coating may also be provided) and the outer bushing.

[0039] More preferably, the radial chambers can be arranged diametrically opposite each other, preferably in the radial direction, which is the primary radial direction of motion of the bushing bearing. This diametrically opposite arrangement of the radial chambers optimizes pumping performance under radial load. This orientation enables uniform vibration damping with a high loss angle and ensures improved stability in the primary radial direction of motion of the bushing bearing.

[0040] According to another preferred embodiment, the resilient overpressure valve can be a finned valve, which can be connected on at least one side, preferably three sides. The resilient overpressure valve, in the form of a finned valve, provides flexible and robust pressure regulation through its multi-sided connection. Because they are arranged laterally on the support block and do not compete for mounting space with other components, they can be made longer, allowing for well-distributed elongation and thus providing a robust valve. Furthermore, manufacturing and implementing the resilient finned valve as part of the central elastomer is particularly cost-effective, thereby reducing manufacturing and material costs. This configuration also allows for rapid adaptation to changing pressure conditions, which improves the efficiency and reliability of the bushing bearing in dynamic applications. Attached Figure Description

[0041] Other features, details, and advantages of the invention will become apparent from the following description of embodiments based on the accompanying drawings. In the drawings:

[0042] Figure 1a A schematic perspective view of a bushing bearing according to the invention is shown, without a channel half-shell and without a core, wherein a portion of an axially extending channel in the elastomer is viewed from top.

[0043] Figure 1b Show Figure 1a The schematic perspective view of the bushing bearing according to the invention shown has a channel half-shell, wherein a portion of the axially extending channel in the elastomer is viewed from top.

[0044] Figure 1c Show Figure 1a Another schematic perspective view of the bushing bearing according to the invention shown has a channel half-shell and is viewed from above as an overpressure valve channel and the end of the half-shell;

[0045] Figure 2a A schematic cross-sectional view of the bushing bearing according to the invention is shown, having a vertical section along plane AA in the axial direction;

[0046] Figure 2b Another schematic cross-sectional view of the bushing bearing according to the invention is shown, having a vertical section along the plane BB in the axial direction;

[0047] Figure 3a A schematic sectional view (top view) of the bushing bearing according to the invention is shown, having a horizontal section along the plane CC in the radial direction;

[0048] Figure 3b A schematic sectional view (top view) of the bushing bearing according to the invention is shown, having a horizontal section along the plane DD in the radial direction;

[0049] Figure 4a Show Figure 2a , Figure 2b and Figure 3a , Figure 3b The diagram shown is an unfolded schematic of the channel half-shell, used to illustrate the channel half-shell structure and channel geometry (with an overpressure valve channel) of the first embodiment of the bushing bearing according to the present invention.

[0050] Figure 4b Show Figure 2a , Figure 2b and Figure 3a , Figure 3b The diagram shown is an unfolded schematic of the channel half-shell, used to illustrate the channel half-shell structure and channel geometry (with an overpressure valve channel) of another embodiment of the bushing bearing according to the present invention.

[0051] Figure 4c Show Figure 2a , Figure 2b and Figure 3a , Figure 3b The diagram shown is an unfolded schematic of the channel half-shell, used to illustrate the channel half-shell structure and channel geometry (with an overpressure valve channel) of another embodiment of the bushing bearing according to the present invention.

[0052] Figure 4d Show Figure 2a , Figure 2b and Figure 3a , Figure 3b The diagram shown is an unfolded schematic of the channel half-shell, illustrating the channel half-shell structure and channel geometry (having two opposite overpressure valve channels) of another embodiment of the bushing bearing according to the present invention.

[0053] List of reference numerals

[0054] L-shaped center longitudinal axis (bearing bushing)

[0055] R Radial (for bushing bearings, transverse)

[0056] A. Axial (Bushing bearing, longitudinal / height direction)

[0057] U-shaped circumferential direction (bearing bushing)

[0058] 2. First axial end (bulb bearing)

[0059] 3. Second axial end (bulb bearing)

[0060] 4 cores (internal components)

[0061] 4' Center notch (core)

[0062] 5. Internal connection part (pump plate)

[0063] 5' External connecting part (ring)

[0064] 6 Outer bushing

[0065] 7. First working chamber half

[0066] 8. Elastomers (supporting springs, damping elements)

[0067] 9. Second working chamber half

[0068] 10. Bushing bearing (hydraulic damping)

[0069] 11. Cage

[0070] 12 First diaphragm (elastomer)

[0071] 13 Second diaphragm (elastomer)

[0072] 14 First Axial Chamber (Fluid Chamber, First Axial End)

[0073] 16 Second Axial Chamber (Fluid Chamber, Second Axial End)

[0074] 17. Radial chamber (fluid chamber, located in the middle between axial chambers)

[0075] 18. Support block (elastic body)

[0076] 18' Sidewall (Support Block)

[0077] 19. Internal intermediate membrane (elastomer)

[0078] 20-channel half-shell structure (cage structure)

[0079] 21. Stop area (pressure insensitive)

[0080] 21' Rubber Coating

[0081] 21'' Stop

[0082] 22 First resilient overpressure valve (radial)

[0083] 22' Inlet of the first valve element

[0084] 23 Second resilient overpressure valve (radial)

[0085] 23' Inlet of the second valve element

[0086] 24. Axial channel (damping channel, fluid connection of axial chamber)

[0087] 25 Overpressure valve passage

[0088] 26 First Channel Half Shell

[0089] 26' Chamber wall (interior, first half-shell)

[0090] 27 Radial Channel (Damping Channel, Fluid Connection of Radial Chamber)

[0091] 28 Second Channel Half Shell

[0092] 28' Chamber wall (interior, second half-shell)

[0093] 29. Half-shell end (rubber element)

[0094] 30 Third resilient overpressure valve (axial)

[0095] 46 First Arm

[0096] 48 Second Arm

[0097] 50 base Detailed Implementation

[0098] exist Figure 1a , Figure 2a and Figure 3a The bearing generally indicated and shown as 10 is a hydraulic damping bushing bearing 10, which includes a core 4 that extends along the central longitudinal axis L of the bushing bearing and is adapted to accommodate fastening elements.

[0099] Especially according to Figure 2a , Figure 2b , Figure 3a and Figure 3b As can be seen in the view, an outer bushing 6 surrounds the bushing bearing 10 on its outer circumference and is adapted to secure the bushing bearing 10 in a receiving member. Elastomers 8, 12, 13, 18, and 19 are arranged between the outer bushing 6 and the core 4.

[0100] The bushing bearing has a pair of axial chambers, each having at least two axial chambers 14, 16 staggered in the axial direction A, the axial chambers being interconnected in a flow-conducting manner via at least one axial channel 24. Additionally, there is a pair of radial chambers, each having at least two radial chambers 17 staggered in the radial direction R, the pair of radial chambers arranged between the axial chambers 14, 16 in such a manner that they completely separate the axial chambers 14, 16 from each other. The pair of radial chambers is interconnected in a flow-conducting manner via at least one radial channel 27.

[0101] The elastomer 8 includes two diaphragms 12 and 13, which are materially fixed to an inner connecting portion 5 on their radially inner side and an outer connecting portion 5' on their radially outer side. Each of the two diaphragms 12 and 13 has a first arm 46, a second arm 48, and a base 50 connecting the two arms 46 and 48 to each other, wherein the base 50 is configured such that it describes the apex of the respective connected arm 46 or 48 (see especially...). Figure 2a ).

[0102] The elastomer 8 has another vulcanizate comprising two support blocks 18 and two axially spaced intermediate diaphragms 19, which are radially innerly connected to the core 4 and radially outerly connected to a retainer 11 in a material-fitting manner (see especially). Figure 2b Two diaphragms 12 and 13 define axial chambers 14 and 16 from the outside, at least partially in the axial direction A.

[0103] Especially in Figure 2a and Figure 2b The document clarifies that the bases 50 of the two diaphragms 12 and 13 can be oriented toward the radial chamber 17 in the axial direction A, and the first arm 46, which is at least twice as thick on average, can form a radially inner arm fixed to the inner connecting portion 5, while the second arm 48 can form a radially outer arm fixed to the outer connecting portion 5'.

[0104] The bushing bearing 10 can have a special channel half-shell structure 20. The precise orientation or channel geometry of the individual fluid channels in the half-shell structure is particularly important. Figures 4a to 4d The series of figures illustrate this. The channel half-shell structure 20 can extend around the elastomer 8 in the circumferential direction U, and ensure that the axial and radial channels 24, 27 form two independent, unconnected channels.

[0105] The axial channel 24 may extend partially along the channel half-shell structure 20 and / or the elastomer 8 and / or the cage 11 in the axial direction A and partially in the circumferential direction U to fluidly connect the axial chamber pair, wherein a portion of the axial channel 24 formed in the axial direction A may be formed on the elastomer 8 (see especially). Figure 1a , Figure 1b , Figure 3a and Figure 3b ).

[0106] In addition, the radial channel 27 may extend along the channel half-shell structure 20 and / or the retainer 11 in the circumferential direction U to fluidly connect the radial chamber pair.

[0107] The channel half-shell structure 20 may have first and second channel half-shells 26, 28, wherein the channel half-shells 26, 28 of the channel half-shell structure 20 may form at least one additional, separate overpressure valve passage 25, which may flowably connect the first working chamber half 7 and the second working chamber half 9 to each other. The separation and bridging of the overpressure valve passage 25 between the working chamber halves 7, 9 is particularly important in… Figure 3a This is explained in the text.

[0108] At least one overpressure valve passage 25 may be closed at its end or in its extension by a first resilient overpressure valve 22, wherein the first resilient overpressure valve 22, as shown, can only open when there is a pressure differential in one working direction. Alternatively, a vertical valve (not shown) may be used within the course of the overpressure valve passage 25, wherein the vertical valve (not shown) can open in both working directions. The passage half-shell structure 20 may also be configured such that it forms at least two additional, separate overpressure valve passages 25, which can flowably connect the first working chamber half 7 and the second working chamber half 9 to each other.

[0109] At least two overpressure valve passages 25 can be used as follows Figure 4d The end is closed by resilient overpressure valves 22 and 23, wherein each of the overpressure valves 22 and 23 can only be opened when there is a pressure difference in one working direction, and the working directions of the two overpressure valves 22 and 23 can correspond to opposite pressure differences.

[0110] At least one overpressure valve 22 (see Figure 3a ) or at least two overpressure valves 22, 23 (see Figure 4d They can be arranged radially opposite and axially staggered on the sidewalls 18' of a single support block 18 of the elastomer 8.

[0111] At least one resilient overpressure valve 22 or resilient overpressure valves 22, 23 may be configured as a pivotable valve element (see Figure 3a The resilient overpressure valves 22 and 23 close the overpressure valve passage 25 in the closed position (or at least one resilient overpressure valve 22 closes the overpressure valve passage 25), and pivot to the open position when a predetermined differential pressure limit in the radial chamber 17 is exceeded, so as to connect the radial chambers 17 to each other in a flowable manner. The resilient overpressure valves 22 and 23 may be oriented in the circumferential direction, and the pivoting movement to the radially outward direction may be limited by the channel half-shell structure 20.

[0112] A portion of the axial channel 24 formed in the axial direction A can be partially laterally defined by the chamber wall within the region of the elastomer 8, wherein the chamber wall forms a third resilient axial overpressure valve 30, and an additional overpressure valve channel 25 can be released by bending under high axial pressure differential (see especially). Figure 1a ).

[0113] The additional overpressure valve passage 25 can be configured to form a parallel short circuit, through which an additional connection is established between a portion of the axial passage 24 formed in the axial direction A and a portion of the axial passage 24 formed in the circumferential direction U. Figures 4a to 4d ).

[0114] The channel half-shell structure 20 may include a portion of an axial channel 24 formed in the circumferential direction U, a radial channel 27, and at least one overpressure valve channel 25 connecting to the radial chamber 17, wherein the portion of the axial channel 24 formed in the circumferential direction U, the radial channel 27, and the at least one overpressure valve channel 25 may be spaced apart in the axial direction A and arranged parallel to each other on the outer surface of the channel half-shell structure 20.

[0115] Especially in Figure 2a and Figure 2b As can be seen, at least one axial channel 24 may include a cross section in the channel half-shell structure 20 and / or the retainer 11, the cross section being configured to be larger than the cross section of at least one radial channel 27 in the channel half-shell structure 20 and / or the retainer 11.

[0116] A portion of the axial channel 24 formed in the axial direction A can be formed on the end face of the support block 18 at the same height as the channel half-shell structure 20, wherein the portion of the axial channel 24 formed in the axial direction A can be arranged on the support block 18 on which the elastic overpressure valves 22 and 23 are not arranged.

[0117] At least one overpressure valve passage 25 may be arranged in the axial direction A between a portion of the radial passage 27 and the axial passage 24 formed in the circumferential direction U, wherein a central stop region 21 may be provided in the channel half-shell structure 20 in the circumferential direction, staggered relative to the at least one overpressure valve passage 25. Corresponding stops 21'' and rubber covering layers 21' may be provided radially oppositely.

[0118] exist Figures 4a to 4b The unfolded diagrams shown in the series of figures illustrate the channel geometry of the channel half-shell structure 20 having an axial channel 24 in the elastomer 8 or the support block 18.

[0119] An intermediate segment is inserted between the channel half-shells 26 and 28, wherein each intermediate segment is arranged between the ends 29 of the half-shells.

[0120] exist Figure 4a In the middle section between the half-shell ends 29, a retainer 11 extending to the outer bushing 6 is formed.

[0121] Figure 4b An implementation method is described, wherein the intermediate section can be configured as an elastomer, similar to the axial channel 24.

[0122] exist Figure 4c As shown, the middle section can be formed entirely by two channel half-shells 26 and 28 bridging each other.

[0123] Alternatively, the middle section could be constructed as an elastic body.

[0124] exist Figure 4d The variation with two overpressure valve passages 25 described above is illustrated in the text. For example, in... Figure 4b In this variant, the middle section can also be constructed as an elastic body.

[0125] In addition, the core 4 may have a central recess 4' which is configured as a through hole or configured so that the bushing bearing can be tightened at the end face by a blind hole or by a threaded joint.

[0126] The elastomer 8 may consist of three vulcanizates assembled together, wherein two axially outer diaphragms 12, 13 each form a vulcanizate, and the third vulcanizate may be formed by another vulcanizate having two support blocks 18 and two inner intermediate diaphragms 19.

[0127] At least two diaphragms 12, 13 can be separate vulcanizates. An arm 46, on average at least twice the thickness, can have a first length, and a second arm 48 can have a second length, wherein the first length can be at least twice the second length. The composition of the elastomeric composite of the two diaphragms 12, 13 and / or the third vulcanizate, or the two support blocks 18 and the two inner intermediate diaphragms 19, can be different. In particular, their Shore hardness can be different.

[0128] The radial chambers 17 can be arranged diametrically opposite each other, preferably in the radial direction R, which is the main radial direction of movement of the bushing bearing 10. The resilient overpressure valves 22, 23, 30 can be configured as finned valves, which can be connected at least on one side, preferably on three sides.

[0129] The present invention is not limited to the aforementioned embodiments, but can be varied in many ways.

[0130] In summary, this presents a solution with the potential to double the damping of known bushing bearings while providing a robust solution with sufficient contact surface.

[0131] All features and advantages derived from the specification and drawings, including construction details, spatial arrangements and method steps, are essential to the invention, either individually or in various combinations.

Claims

1. A hydraulic damping bushing bearing (10), the hydraulic damping bushing bearing (10) comprising: A core (4) extending along the central longitudinal axis (L) of the hydraulic damping bushing bearing (10) and adapted to receive a fastening element; an outer bushing (6) surrounding the hydraulic damping bushing bearing on its outer circumferential side and adapted to secure the hydraulic damping bushing bearing (10) in a receiving element; an elastomer (8, 12, 13, 18, 19) disposed between the outer bushing (6) and the core (4); an axial chamber pair having at least two axial chambers (14, 16) staggered in the axial direction (A), the axial chambers being interconnected in a flow-conducting manner via at least one axial channel (24); and a radial chamber pair having at least two radial chambers staggered in the radial direction, the radial chambers being disposed between the axial chambers (14, 16) such that the radial chambers connect the axial chambers (14, 16) in a flow-conducting manner. 16) Completely separated from each other, wherein the radial chambers are interconnected in a flow-conducting manner via at least one radial channel (27), wherein the elastomer (8) comprises at least two diaphragms (12, 13), the diaphragms being fixed in a material-fitting connection to the inner connecting portion (5) on the radially inner side and to the outer connecting portion (5') on the radially outer side, wherein each of the two diaphragms (12, 13) has a first arm (46), a second arm (48), and a connection for holding the two arms (46, 18) together. 48) Interconnected bases (50), wherein the bases (50) are configured such that the bases (50) describe the apex of the connected arms (46, 48), wherein the average thickness of the first arm (46) is at least twice the average thickness of the second arm (48), wherein the cross-section of the arm (46) which is at least twice as thick on average continuously expands from the base (50), wherein the elastomer (8) has another vulcanizate comprising two support blocks (18) and two axially spaced intermediate diaphragms (19), the intermediate diaphragms being fixed in a material-fitted connection to the core (4) on the radially inner side and in a material-fitted connection to the retainer (11) on the radially outer side, characterized in that the at least two diaphragms (12, 13) at least partially define the axial chambers (14, 16) from the outside in the axial direction (A).

2. The bushing bearing according to claim 1, characterized in that, The base (50) is oriented in the axial direction (A) toward the radial chamber (17).

3. The bushing bearing according to claim 1 or 2, characterized in that, On average, the first arm (46), which is at least twice as thick, forms the radially inner arm and is fixed to the inner connecting part (5), wherein the second arm (48) forms the radially outer arm and is fixed to the outer connecting part (5').

4. The bushing bearing according to any one of the preceding claims, characterized in that, The bushing bearing (10) has a specific channel half-shell structure (20) that extends around the elastomer (8) in the circumferential direction (U) and ensures that the axial channel (24) and the radial channel (27) form two independent, unconnected channels.

5. The bushing bearing according to claim 4, characterized in that, The axial channel (24) extends partly in the axial direction (A) and partly in the circumferential direction (U) along the channel half-shell structure (20) and / or along the elastomer (8) and / or along the retainer (11) to fluidly connect the axial chamber pair, wherein the portion of the axial channel (24) formed in the axial direction (A) is formed on the elastomer (8).

6. The bushing bearing according to claim 4 or 5, characterized in that, The radial channel (27) extends in the circumferential direction (U) along the channel half-shell structure (20) and / or along the retainer (11) to fluidly connect the radial chamber pair.

7. The bushing bearing according to any one of claims 4 to 6, characterized in that, The channel half-shell structure (20) has a first channel half-shell (26) and a second channel half-shell (28), wherein the channel half-shells (26, 28) of the channel half-shell structure (20) form at least one additional, separate overpressure valve channel (25), which connects the first working chamber half (7) and the second working chamber half (9) to each other in a flow-guided manner.

8. The bushing bearing according to any one of claims 4 to 6, characterized in that, The channel half-shell structure (20) has a first channel half-shell (26) and a second channel half-shell (28), wherein the channel half-shells (26, 28) form at least two additional, separate overpressure valve channels (25), which connect the first working chamber half (7) and the second working chamber half (9) in a flow-guided manner.

9. The bushing bearing according to claim 7, characterized in that, The at least one overpressure valve passage (25) is closed at its end or in its extension by a first resilient overpressure valve (22), wherein the first resilient overpressure valve (22) can only be opened when there is a pressure difference in one working direction.

10. The bushing bearing according to claim 8, characterized in that, The at least two overpressure valve passages (25) are closed at their ends by resilient overpressure valves (22, 23), wherein each of the overpressure valves (22, 23) can only be opened when there is a pressure difference in one working direction, and the working directions of the two overpressure valves (22, 23) correspond to opposite pressure differences.

11. The bushing bearing according to claim 10, characterized in that, The two overpressure valves (22, 23) are arranged radially opposite and axially staggered on the sidewall (18') of the single support block (18) of the elastomer (8).

12. The bushing bearing according to any one of claims 9 to 11, characterized in that, The resilient overpressure valves (22, 23) are configured as pivotable valve elements that close the overpressure valve passage (25) in a closed position and pivot to an open position when a predetermined differential pressure limit in the radial chambers (17) is exceeded, so as to connect the radial chambers (17) to each other in a flowable manner. The resilient overpressure valves (22, 23) are circumferentially oriented and their pivoting movement toward the radially outward direction is limited by the passage half-shell structure (20).

13. The bushing bearing according to claim 5, characterized in that, The portion of the axial channel (24) formed in the axial direction (A) is partially laterally defined by the chamber wall within the region of the elastomer (8), wherein the chamber wall forms a third elastic axial overpressure valve (30) and releases an additional overpressure valve channel (25) by bending under high axial pressure differential.

14. The bushing bearing according to claim 13, characterized in that, The additional overpressure valve passage (25) is configured to form a parallel short circuit, through which an additional connection is established between the portion of the axial passage (24) formed in the axial direction (A) and the portion of the axial passage (24) formed in the circumferential direction (U).

15. The bushing bearing according to claims 5 and 7, characterized in that, The channel half-shell structure (20) includes a portion of the axial channel (24) formed in the circumferential direction (U), the radial channel (27), and at least one overpressure valve channel (25) connecting the radial chamber (17), wherein the portion of the axial channel (24) formed in the circumferential direction (U), the radial channel (27), and the at least one overpressure valve channel (25) are spaced apart in the axial direction (A) and arranged parallel to each other on the outer surface of the channel half-shell structure (20).

16. The bushing bearing according to claim 15, characterized in that, The at least one axial channel (24) includes a cross section in the channel half-shell structure (20) and / or in the retainer (11), the cross section being configured to be larger than the cross section of the at least one radial channel (27) in the channel half-shell structure (20) and / or in the retainer (11).

17. The bushing bearing according to claims 5 and 11, characterized in that, The portion of the axial channel (24) formed in the axial direction (A) is formed on the end face of the support block (18) with the same height as the channel half-shell structure (20), wherein the portion of the axial channel (24) formed in the axial direction (A) is arranged on the support block (18) without the elastic overpressure valves (22, 23) arranged thereon.

18. The bushing bearing according to claim 5, characterized in that, The at least one overpressure valve passage (25) is arranged in the axial direction (A) between the radial passage (27) and the portion of the axial passage (24) formed in the circumferential direction (U), wherein a central stop region (21) is provided in the channel half-shell structure (20) in the circumferential direction, offset from the at least one overpressure valve passage (25).

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