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Abstract

bearing (2) - a spring body forming a first fixing point of the bearing (2), and - a basic body (8) with a first basic part (10) and a second basic part (12), - wherein the base body (8) forms a second attachment point (14) of the bearing (2), - wherein the first base part (10) has a cylindrical recess (16) extending in the longitudinal direction L of the bearing (2), into which the spring body is inserted to form a mechanical connection between the spring body and the first base part (8), and - wherein the first base part (10) and the second base part (12) are arranged one behind the other in the longitudinal direction L of the bearing and are mechanically connected to each other, characterized in that - the first base part (10) has a radially outer, annular seat (18) which has an annular contact surface (20) with radially inwardly projecting grooves (22), - the second base part (12) has an opening (24) with an adjacent ring section (26), - the second base part (12) has several pressure lamellae (28) which are each attached to the ring section (26) with a first end (30) facing the opening (24) and spaced radially inside from the ring section (26) with a second end (32) arranged opposite, - and the ring section (26) of the second base part (12) is pushed onto the contact surface (20) of the seat (18) of the first component (10) in such a way that the pressure lamellae (28) with their second ends (32) engage in the grooves (22) of the first base part (10).

Description

Storage

[0001] The invention relates to a bearing comprising a spring body forming a first mounting point of the bearing, and a base body comprising a first base part and a second base part, wherein the base body forms a second mounting point of the bearing, wherein the first base part has a cylindrical recess extending in the longitudinal direction of the bearing into which the spring body is inserted to form a mechanical connection between the spring body and the first base part, and wherein the first base part and the second base part are arranged one behind the other in the longitudinal direction of the bearing and are mechanically connected to each other.

[0002] Bearings are generally known from the prior art. The bearing according to the invention serves to support two separately designed components that are subjected to radial and / or axial forces. The bearing thus also serves to connect the two components. Depending on the direction of the forces absorbed by the bearing, it can be a radial bearing, an axial bearing, or a hybrid of the two.

[0003] To connect the bearing to the components, the bearing has two mounting points. A first mounting point is formed by the bearing's spring element. The spring element can be made of an elastic material. In particular, the spring element is made of an elastomer. Due to its elastic design, the spring element can be elastically deformed when forces are applied, allowing the components to perform a generally limited relative movement. This movement is limited by the corresponding counterforce of the spring element. The spring element can have damping and / or isolating properties with respect to the relative movement. Thus, the spring element can be designed as a mechanical isolator and / or as a spring-damper unit. The bearing is particularly preferably designed as a hydraulic bearing. In this case, the spring element can comprise a load-bearing spring and a hydraulic damper.In particular, two hydraulic chambers and a throttle channel connecting the hydraulic chambers are provided for this purpose, through which hydraulic fluid flows from the hydraulic chambers when the support spring is deformed by acting forces.

[0004] In addition to the spring element, the bearing has a base body that forms the bearing's second mounting point. This second mounting point can, for example, be a flange on the outer surface of the base body, allowing it to be attached to one of the components. One example application of the bearing is the mounting of a motor vehicle engine to a vehicle chassis. In this case, the bearing is a so-called engine mount. For this application, one of the two mounting points can be mechanically connected to the engine and the other to the vehicle chassis, particularly in a detachable manner.

[0005] The base body comprises a first base part and a second base part, the two base parts being arranged one behind the other in the longitudinal direction of the bearing and mechanically connected to each other. The first base part has a cylindrical recess extending longitudinally in the bearing, into which the spring element is inserted to form a mechanical connection between the spring element and the first base part. The recess is designed as a bore and / or a cylindrical passage in the longitudinal direction. Due to the multi-part design of the base body and the insertion of the spring element into the recess of the first base part, the bearing is particularly easy to assemble. This is especially true if the spring element is designed as a hydro-spring element. In this case, the spring element can be inserted as a unit into the recess of the first component, with one end of the spring element projecting beyond the first base part.Thus, a mounting point located at this end is accessible for attaching a component to be supported. Inserting the spring element into the recess can simultaneously establish a mechanical connection to the first base part. Alternatively or additionally, the spring element can have a mechanical connection to the second base part. This is because the second base part is positioned longitudinally behind the first base part within the bearing and is mechanically connected to the second component. Preferably, a mechanical connection between the second base part and the spring element can also be created and / or provided.

[0006] In principle, the second base part can serve as a housing for the spring element, particularly for covering and / or protecting it. Alternatively or additionally, as previously explained, the second base part can serve to transmit force between the spring element and the base part. Furthermore, the second mounting point of the bearing can be formed by the first base part and / or the second base part. A mechanical connection between the first and second base parts can therefore be subjected to high tensile forces.

[0007] German patent application DE 10 2011 081 469 A1 discloses a bearing for mounting components in motor vehicles. This patent discloses a bearing cap that is inserted into a cylindrical opening of the rest of the bearing. The bearing cap has spring plates with locking lugs on its end face, which engage in radially inner grooves of a base body of the rest of the bearing. In practice, however, this design has proven to be disadvantageous. Firstly, the locking lugs are subjected to tensile stress. Therefore, there is a risk that the holding pressure provided by the spring plates will no longer be sufficient to keep the locking lugs in the grooves. Secondly, under particularly high loads, the locking lugs can bend, causing the spring plates to slip out of the base body.On the other hand, the locking lugs engage in grooves inside a cylindrical recess in the base body, which is designed for a spring element intended to absorb external forces. This complicates the mechanical coupling of the spring element to the base body. Furthermore, the bearing cap is difficult or very complicated to remove if the spring element is accidentally inserted incorrectly into the corresponding recess or needs to be replaced. This is because the locking lugs of the bearing cap are concealed by the base body and the bearing cap itself after final assembly. Realigning or replacing the spring element would require destroying the bearing cap, and in particular, the associated locking lugs.

[0008] The object of the invention is to provide a bearing of the type mentioned above, which is designed to transmit large forces in the longitudinal direction and is easy to assemble or disassemble.

[0009] According to a first aspect, the problem is solved by the bearing according to the invention, comprising a spring body forming a first mounting point of the bearing, and a base body with a first base part and a second base part, wherein the base body forms a second mounting point of the bearing, wherein the first base part has a cylindrical recess extending longitudinally in the bearing, into which the spring body is inserted to form a mechanical connection between the spring body and the first base part, wherein the first base part and the second base part are arranged one behind the other in the longitudinal direction of the bearing and are mechanically connected to each other, wherein the first base part has a radially outer, annular seat having an annular contact surface with radially inwardly projecting grooves, wherein the second base part has an opening with an adjacent annular section.wherein the second base part has several pressure lamellae, each of which is attached to the ring section at a first end facing the opening and spaced radially inside from the ring section at a second end arranged opposite, and wherein the ring section of the second base part is pushed onto the contact surface of the seat of the first component in such a way that the pressure lamellae engage with their second ends in the grooves of the first base part.

[0010] The invention is based on the idea of ​​providing radially external grooves on the first base part, into which pressure-resistant lamellae – also referred to as pressure lamellae – of the second base part engage, in order to establish the mechanical connection between the first and second base parts in such a way that high compressive forces can act on the first base part from the spring element during bearing operation. The pressure lamellae can be designed as rod-shaped or plate-shaped elements. To create a corresponding pressure lamella-groove connection between the first and second base parts, the first base part has an annular seat radially externally, and the second base part has an annular section that borders an end-face opening of the second base part. The opening can thus be formed by the annular section.Furthermore, the seat and the ring section are designed such that the ring section can be slid onto the seat. The inner diameter of the ring section can correspond to an outer diameter of the seat. Particularly preferably, the seat and the ring section have corresponding cross-sectional contours, so that the seat guides the ring section when it is slid onto the seat. The cross-sectional contours can also have corners, teeth, and / or other discontinuous transitions to ensure a precise seating position when sliding onto the seat.

[0011] The grooves are preferably designed as locking grooves. For this purpose, the grooves can each have a rectangular wall contour or a differently shaped wall contour. In particular, the grooves each have a support surface or edge on a side facing the second base part in order to absorb forces from the pressure lamellae. The support surface or edge of the respective groove thus serves as a counter bearing for the respective pressure lamella.

[0012] According to the invention, the second base part has several pressure lamellae to enable a preferably uniform force distribution around the circumference. Each pressure lamella is attached to the ring section at its first end, which faces the opening of the second base part. Each pressure lamella can form an integral part of the ring section, as it can be pressed and / or punched out of the remaining ring section. When integrated with the ring section, the first end of the pressure lamella can be defined by a transition from which the pressure lamella inclines radially inwards away from the remaining ring section. The pressure lamellae can also be designed as pressure-resistant clips or as pressure-resistant beam elements. Each pressure lamella has a second end opposite its first end, thus facing away from the opening of the second component.Each pressure plate is designed so that its second end is inclined radially inwards, such that each second end faces the radially inner side of the ring section. The pressure plates are elastically deformable in the radial direction, particularly at their second ends. When the ring section of the second base part is pushed onto the contact surface of the first component's seat, the pressure plates engage with their second ends in the grooves of the first component. If external forces now act on the second base part via the spring element, the external force is distributed across the pressure plates that engage in the grooves. The pressure plates rest with their respective second ends on a support surface or edge of the groove, so that the force emanating from the spring element is transferred from the pressure plates to the groove.If the second mounting point of the bearing is located on the first base part, the force can then be transferred to the outer component attached at the second mounting point.

[0013] To transmit force between the second base part and the first base part, the pressure lamellae are subjected to compressive stress. Therefore, the pressure lamellae do not tend to slip out of the grooves unintentionally. Rather, when a pressure lamella is subjected to compressive stress, a force line runs from its corresponding first end to its corresponding second end, with each pressure lamellae preferably extending from its first end to its second end with a continuous contour. The pressure lamella preferably does not have a discontinuous transition to either end, such as a kink for a locking lug. Furthermore, the grooves can each have a radial inner boundary wall against which the second end of a pressure lamella abuts.

[0014] The inventive design of the bearing allows for particularly easy disassembly of the second base part. This is because the second base part, with its ring section, is pushed onto the seat of the first component from the outside. Thus, the pressure plates can be elastically deformed from the outside using a tool, allowing the second base part to be pulled off the first base part, particularly for servicing, replacing, and / or modifying the spring element or other components of the bearing.

[0015] According to a further aspect of the invention, the problem is solved by the bearing according to the invention, comprising a spring body forming a first mounting point of the bearing, and a base body with a first base part and a second base part, wherein the base body forms a second mounting point of the bearing, wherein the first base part has a cylindrical recess extending longitudinally along the bearing into which the spring body is inserted to form a mechanical connection between the spring body and the first base part, wherein the first base part and the second base part are arranged one behind the other in the longitudinal direction of the bearing and are mechanically connected to each other, wherein the first base part has a radially outer, annular seat comprising an annular contact surface, and the second base part has an opening with an adjacent annular section having grooves projecting radially outwards on the inside.the first base part has several pressure plates, each of which is attached to the contact surface with a first end facing away from the spring body and radially spaced from the contact surface with a second end arranged opposite it, and the ring section of the second base part is pushed onto the contact surface of the seat of the first component in such a way that the pressure plates engage with their second ends in the grooves of the first base part.

[0016] The second aspect of the invention is based on the same concept for solving the problem as explained for the first aspect. However, according to the second aspect, the pressure lamellae are not attached to the second base body but to the first base body. Correspondingly, the pressure lamellae do not project radially inwards but radially outwards. They are still subjected to pressure. Therefore, features, details, and advantages described in connection with the bearing according to the first aspect also apply to the bearing according to the second aspect, and vice versa, so that the disclosures relating to the bearings according to the individual aspects of the invention are always made analogously.Therefore, if the following discussion focuses on the storage system according to the first aspect, analogous designs and / or advantages should also apply to the second aspect of the storage system.

[0017] A preferred embodiment of the bearing is characterized by the fact that the pressure plates each have an at least substantially planar extent. Preferably, the extent refers to the length of each pressure plate from its first end to its second end. If a pressure plate is subjected to a compressive force, the corresponding force line can run in a straight line from the first end to the second end through the pressure plate. The pressure plate can therefore withstand particularly high compressive forces before buckling becomes a risk.

[0018] Another preferred embodiment of the bearing is characterized by an inner diameter of the ring section corresponding to an outer diameter of the contact surface. This allows the contact surface and the ring section to have at least substantially the same cross-sectional contour. In this case, the contact surface and the ring section, particularly the associated inner wall, form a fit. This is a technical fit, especially a clearance fit. The inner wall of the ring section and the contact surface preferably have a radial distance of between 0.01 mm and 5 mm, and more preferably between 0.5 mm and 1.5 mm. In this case, the inner diameter of the ring section would be twice the selected radial distance larger than the outer diameter of the contact surface.The aforementioned small radial distance between the ring section and the contact surface keeps the radial distance that the pressure plate has to overcome particularly small, allowing the pressure plate to have a preferably small tip angle to an inner wall of the ring section. This ensures a particularly high force transmission between the second base part and the first base part.

[0019] Another preferred embodiment of the bearing is characterized by the fact that the seat of the first base part has several retainers projecting in an L-shape beyond the contact surface, so that a segmented annular gap is formed between the contact surface and the retainers, into which the annular section of the second base part fits. A segmented annular gap is understood to be a circumferentially interrupted, ring-shaped gap. When the annular section of the second base part fits into the annular gap, the seat with the associated retainers provides radial and longitudinal axial fixation for the annular section. Radially, the annular section is bounded on the inner side by the contact surface. Radially, the annular section is bounded on the outer side by the L-shaped retainers. If compressive forces now act on the pressure plates, they cannot deform the annular section in the radial direction, in particular not radially outwards.Rather, the seat of the first base part ensures the radial stability of the ring section. The compressive forces acting on the pressure plates are transferred to the grooves, thus preventing the ring section from slipping in the corresponding longitudinal direction. In the opposite longitudinal direction, i.e., towards an inner end face of the annular gap, the L-shaped retainers prevent the ring section of the second base part from slipping. Preferably, the retainers form a stop for the ring section of the second base part on an inner end face in the longitudinal direction. For bearing assembly, the second base part with the associated ring section can be slid over the seat's contact surface until it reaches the stop formed by the retainers, at which point the pressure plates engage in the grooves.

[0020] Another preferred embodiment of the bearing is characterized by the fact that the first and second ends of each pressure plate are offset from each other radially by a distance of a certain amount, where this distance is greater than one wall thickness of the respective pressure plate and less than three times the wall thickness of the respective pressure plate. Each pressure plate is inclined radially inwards at its second end, such that the corresponding second end is radially spaced from the ring section and the corresponding first end. In practice, it has been found that particularly high compressive forces can be transmitted by means of the pressure plates when the acute angle between a respective pressure plate and the ring section is as small as possible. For the lower limit of the acute angle, the pressure plate was considered to be a tensioned rod.To prevent buckling, the pressure plate should not be aligned exactly in the longitudinal direction of the bearing. To achieve this, the second end of each pressure plate must be angled away from the ring section or its first end by at least its wall thickness (i.e., the thickness of the pressure plate in the radial direction). However, this acute angle should not be arbitrarily large. The larger the angle, the more the pressure plate bends around an axis tangential to the ring section. In practice, it has been found that this bending is negligibly small when the end distance is chosen to be up to three times the wall thickness of the respective pressure plate. Thus, this range for the end distance ensures that the pressure plate can withstand particularly high compressive forces.

[0021] Another preferred embodiment of the bearing is characterized by the fact that the seat of the first base part and the annular section of the second base part have corresponding guide elements to define the circumferential position of the second base part relative to the first. These guide elements can be formed by the pressure plates and the grooves. Alternatively and / or additionally, further guide elements can be provided. The guide elements serve to ensure the circumferential position of the second base part relative to the first base part. This ensures the desired arrangement of the two base parts relative to each other, thus enabling reliable operation of the bearing. In this case, the forces, especially the compressive forces acting on the pressure plates, can be transmitted as desired.Furthermore, it can be provided that the desired circumferential position determines the position of other bearing components, which are then also uniquely positioned during assembly based on the determinable circumferential position. This ensures reliable operation of the bearing.

[0022] Another preferred embodiment of the bearing is characterized by the fact that the holders and / or the pressure plates are spaced apart from each other in the circumferential direction.

[0023] This allows the pressure plates to be accessed from the outside, particularly with a tool. The pressure plates can therefore be elastically lifted out of the grooves to separate the second base part from the first. Such separation of the two base parts can be advantageous, for example, for replacing and / or maintaining at least one of the bearing components, especially one of the two base parts and / or parts of the spring body.

[0024] Another preferred embodiment of the bearing is characterized by the fact that the second base part, which is slid onto the first, is mechanically connected to the spring body, so that the first and second base parts secure the spring body to the base body. Although the spring body fits into the recess of the first base part, allowing it to be secured to the first base part at least in one longitudinal direction, this is not necessarily the case in the opposite longitudinal direction. Therefore, it can be advantageous for both base parts to provide longitudinal retention for the spring body, ensuring unambiguous fixation of the spring body to the base body.

[0025] Another preferred embodiment of the bearing is characterized by the fact that the first base part is designed as a metal die-cast part, in particular as an aluminum die-cast part. Since the first base part does not need to be deformed to attach the second base part to it, the first base part can be manufactured using a metal die-casting process. This reduces the manufacturing costs of the bearing, as production and assembly can be designed cost-effectively.

[0026] Another preferred embodiment of the bearing is characterized by the fact that the second base part is designed as a plastic injection-molded part. A second base part made of plastic has proven particularly advantageous in practice, as the pressure plates are then also made of plastic. This offers particularly high elastic deformability of the pressure plates. Thus, the second base part, along with its associated ring section, can be easily slid onto the contact surface of the first base part. The pressure plates temporarily deform elastically outwards in the radial direction, then spring back into the grooves upon contact of the ring section with the stop, so that the pressure plates engage in the grooves. Furthermore, a second base part made of plastic can be manufactured particularly easily, quickly, and cost-effectively.

[0027] The invention is described below, without limiting the general concept, with reference to exemplary embodiments and the drawings. Although the focus is primarily on the first aspect of the bearing, the features, details, and advantages described below naturally apply analogously to the bearing according to the second aspect of the invention, so that analogous reference is made to the disclosure. The drawings show: Fig. 1 a schematic, perspective view of the bearing in a first embodiment without spring body, Fig. 2 a schematic, perspective view of the first basic part made of Fig. 1, Fig. 3 a schematic, perspective view of the second base part made of Fig. 1, Fig. 4 an excerpt of a schematic representation of a transition area between the first base part and the second base part from Fig. 1, Fig. 5 a section of a cross-sectional view of the transition area between the first base part and the second base part from Fig. 1, Fig. 6 a schematic side view of the bearing in a second embodiment without spring body, Fig. 7 a schematic, perspective view of the camp from Fig. 6, Fig. 8 a schematic top view of the warehouse Fig. 6, Fig. 9 a section of a first cross-sectional representation of a transition area between the first base part and the second base part from Fig. 6, and Fig. 10 a section of a second cross-sectional representation of the transition area between the first base part and the second base part from Fig. 6.

[0028] From the overall view of Fig. 1, Fig. 2, Fig. 3, Fig. 4 to Fig. Figure 5 shows a first embodiment of the bearing 2 according to the invention. A further embodiment of the bearing 2 according to the invention can be seen in the Fig. 6, Fig. 7, Fig. 8, Fig. 9 to Fig. See section 10. Regarding the explanations concerning the Fig. 1, Fig. 2, Fig. 3, Fig. 4, Fig. 5, Fig. 6, Fig. 7, Fig. 8, Fig. 9 to Fig. Section 10 is referred to reciprocally where it makes sense, even if it is not explicitly mentioned at the given point.

[0029] The Fig. 1 and Fig. Figure 7 shows the bearing 2 according to the invention in a perspective, schematic view. The base body 8 is formed by the first base part 10 and the second base part 12, which is placed on top of the first base part 10. Further parts may be provided for the base body 8.

[0030] As can be seen from a further comparison with the Fig. As can be seen from figures 2 and 8, the base body 8, together with the associated first base part 10, forms a cylindrical recess 16 extending in the longitudinal direction L of the bearing 2. The recess 16 is preferably designed as a through bore. A spring element (not shown) can be inserted into the recess 16.

[0031] The bearing 2 has at least two mounting points, each of which can be connected to a component to be supported in order to fix the components relative to each other and / or to transmit forces between the components. A first mounting point is formed by the spring element (not shown). A second mounting point 14 is formed by the base body 8. As can be seen from the Fig. 1, Fig. 2, Fig. 7 and Fig. As can be seen from Figure 8, the first base part 10 preferably forms the second mounting point 14. The second mounting point 14 can be designed as a flange which has a bore in order to screw the second mounting point 14 to a component to be supported.

[0032] The spring element (not shown) is inserted into the recess 16 of the first base part 10 to form a mechanical connection between the spring element and the first base part 10. To fix the spring element to the base part 8, the first base part 10 and the second base part 12 are arranged one behind the other in the longitudinal direction L of the bearing 2 and mechanically connected to each other. Thus, the spring element is clamped between the two base parts 10, 12 to ensure longitudinal and / or radial fixation.

[0033] If compressive forces are now exerted on the spring element, corresponding forces also act on the second base part 12. The aim is to transfer the forces acting on the second base part 12 to the first base part 10, so that the first base part 10 can then transmit these forces to a coupled component via the second attachment point 14. The mechanical connection between the first base part 10 and the second base part 12 must therefore be designed to transmit high mechanical forces in the longitudinal axial direction.

[0034] According to the invention, the mechanical connection between the first base part 10 and the second base part 12 is established by a pressure plate-groove connection. The associated pressure plates 18 are subjected at least substantially to compressive forces in the longitudinal direction L of the bearing 2. For an explanation of the pressure plate-groove connection, a summary of the Fig. 2, Fig. 3, Fig. 4 to Fig. 5 referred to. A corresponding connection is also found in the Fig. 6, Fig. 7, Fig. 8 to Fig. As can be seen in Figure 9. To form the pressure plate-groove connection, the first base part 10 has an annular seat 18 on its radial outer side. The seat 18 of the first base part 10 serves to fasten the second base part 12. Therefore, the forces to be transmitted between the first base part 10 and the second base part 12 are introduced into and / or transmitted by the seat 18 of the first base part 10. To receive the second base part 12, the seat 18 has an annular contact surface 20. The contact surface 20 can be segmented, i.e., configured by a plurality of annular segment-shaped areas at one end face of the first base part 10. Grooves 22 can extend between the annular segment-shaped areas. The grooves 22 each project radially inwards. Each of the grooves 22 has a bearing edge 42 on one side facing the second base part 12.

[0035] The second base part 12 has an at least substantially hollow cylindrical shape, with the end face closed, in particular by a lid. The opposite end face of the second base part 12 is open, forming the opening 24. A ring section 26 adjoins the opening 24, thus forming part of the hollow cylindrical shell wall of the second base part 12.

[0036] To ensure that the mechanical connection between the first base part 10 and the second base part 12 remains accessible even after the bearing 2 has been mounted, and / or to guarantee the most trouble-free force transmission possible between the spring element and the first base part 10, particularly in the radial direction R, the second base part 12, with its annular section 26, is pushed onto the contact surface 20 of the first base part 10 from the outside. For the mechanical connection between the base parts 10 and 12, the second base part 12 has several pressure plates 28. The pressure plates 28 can be designed as plate-shaped detent elements, but without detent lugs. Each pressure plate 28 is attached to the annular section 26 at a first end 30 facing the opening 24. Preferably, the pressure plates 28 are formed integrally with the annular section 26. In this case, each pressure plate 28 begins to tilt radially inwards at its first end 30.Each of the pressure plates 28 also has a second end 32, which is arranged opposite the first end 30. Since the pressure plates 28 project radially inwards, every second end 32 of a pressure plate 28 is offset from the remaining annular section 26. In practice, it has proven particularly advantageous to select the distance in the radial direction R between the second end 32 of a pressure plate 28 and the annular section 26 or the first end 30, designated as the end distance E, such that the end section E is greater than the wall thickness W, i.e., the thickness of the respective pressure plate 28 in the radial direction R, and less than three times the aforementioned wall thickness W. A pressure plate 28 designed in this way, as is the case, for example, with the... Fig. As can be seen from Figure 6, it is neither prone to buckling nor to excessive bending. Rather, a pressure lamella 28 designed in this way is suitable for transmitting particularly high compressive forces between the second base part 12 and the first base part 10.

[0037] To enable the aforementioned transmission of pressure forces, the ring section 26 of the second base part 12 is pushed onto the contact surface 20 of the seat 18 of the first component 10. The pressure plates 28 are initially deformed elastically, radially outwards, and after traversing a distance L in the longitudinal direction of the bearing 2, they elastically return to their original shape, radially inwards, so that the pressure plates 28, with their respective second ends 32, engage in the opposing grooves 22 of the first component 10. The pressure plates 28 thus snap into the grooves 22.

[0038] When compressive forces act on the pressure lamellae 28, the respective second end 32 of each pressure lamella 28 abuts a bearing edge 42 of the groove 22 corresponding to that pressure lamella. The depth of the grooves 22 in the radial direction R preferably corresponds approximately to the end distance E in order to support the aforementioned alignment and / or configuration of the pressure lamellae 28. Alternatively, the depth of the grooves 22 can be configured such that a radially inner wall, at least in the area of ​​the bearing edge 42, of a respective groove 22 is separated from the first end 30 of the respective associated pressure lamella 28 by the end distance E, preferably with a maximum tolerance of twenty percent.

[0039] To ensure the spring-elastic property of each pressure plate 26, the pressure plates 26 are offset from each other in the circumferential direction U. A corresponding relationship can also be seen from the Fig. 8. Corresponding to the defective pressure lamellae 28, the grooves 22 are also arranged differently in the circumferential direction Q.

[0040] The pressure forces acting on the pressure lamellae 28 cause radially outward forces on the ring section 26. To prevent these radially outward forces from causing the ring section 26 to spread open, the seat 18 of the first component 10 has several L-shaped retainers 34 projecting beyond the contact surface 20, so that a segmented annular gap 36 is formed between the contact surface 20 and the retainers 34, into which the ring section 26 of the second base part 12 fits. A corresponding relationship is shown in the Fig. 2, Fig. 3, Fig. 5, Fig. 6, Fig. 7, Fig. 9 and Fig. The annular gap 36 is formed by several ring section gaps spaced apart from each other in the circumferential direction U. The retainers 34 prevent the ring section 26 from expanding outwards. Thus, the retainers 34 stabilize the ring shape of the ring section 26 in order to keep the pressure plates 28 dimensionally stable even under the influence of compressive forces.

[0041] Furthermore, the holders 34 form a stop 44 for the ring section 26, against which the ring section 26 abuts when slid onto the support surface 20, thus enabling particularly precise positioning of the second base part 12 in the longitudinal direction L relative to the first base part 10. The stop 44 is formed by the longitudinally inner wall sections 46 of the holders 34.

[0042] To ensure the relative positioning of the second base part 12 with respect to the first base part 10 in the circumferential direction U, the seat 18 of the first base part 10 and the ring section 26 of the second base part 12 have corresponding guide elements 38, 40. Such guide elements 38, 40 are Fig. 3 and Fig. 4 removable. By sliding the second base part 12 onto the first base part 10, the guide element 40 engages in a guide element 38 of the first base part 10, which is designed as a corresponding opening.

[0043] The engagement of the pressure plates 28 in the grooves 22 is evident from the overall view of the Fig. 9 and Fig. 10 can be found in the Fig.9 The second base part 12 with the ring section 26 was already brought close to the contact surface 20 of the first base part 10. If the second base part 12 and the first base part 10 are now pushed further together in the longitudinal direction L, the pressure lamellae 28 initially deform elastically in the radial direction R outwards, until the second base part 12 with the edge 48 at the opening 24 meets the stop 44, whereby the pressure lamellae 28 then snap radially inwards into the grooves 22. Reference symbol list E final distance L Longitudinal direction R Radial direction U circumferential direction W wall thickness 2 warehouses 8 basic bodies 10 first basic part 12 second basic part 14 second attachment point 16 Exclusion 18 seats 20 Plant area 22 Nut 24-hour opening 26 Ring section 28 pressure plate 30 first end 32 second end 34 holders 36 annular gap 38 Guide element 40 guide element 42 Support edge 44 stops 46 Wall section 48 Rand

Claims

[1] bearing (2) having - a spring body forming a first fixing point of the bearing (2), and - a basic body (8) with a first basic part (10) and a second basic part (12), - wherein the base body (8) forms a second attachment point (14) of the bearing (2), - wherein the first base part (10) has a cylindrical recess (16) extending in the longitudinal direction L of the bearing (2), into which the spring body is inserted to form a mechanical connection between the spring body and the first base part (8), and - wherein the first base part (10) and the second base part (12) are arranged one behind the other in the longitudinal direction L of the bearing and are mechanically connected to each other, characterized by , that - the first base part (10) has a radially outer, annular seat (18) which has an annular contact surface (20) with radially inwardly projecting grooves (22), - the second base part (12) has an opening (24) with an adjacent ring section (26), - the second base part (12) has several pressure lamellae (28) which are each attached to the ring section (26) with a first end (30) facing the opening (24) and spaced radially inside from the ring section (26) with a second end (32) arranged opposite, - and the ring section (26) of the second base part (12) is pushed onto the contact surface (20) of the seat (18) of the first component (10) in such a way that the pressure lamellae (28) with their second ends (32) engage in the grooves (22) of the first base part (10). [2] bearing (2) - a spring body forming a first fixing point of the bearing (2), and - a basic body (8) with a first basic part (10) and a second basic part (12), - wherein the base body (8) forms a second attachment point (14) of the bearing (2), - wherein the first base part (10) has a cylindrical recess (16) extending in the longitudinal direction L of the bearing (2), into which the spring body is inserted to form a mechanical connection between the spring body and the first base part (8), and - wherein the first base part (10) and the second base part (12) are arranged one behind the other in the longitudinal direction L of the bearing and are mechanically connected to each other, characterized by , that - the first base part (10) has a radially outer, ring-shaped seat (18) which includes a ring-shaped contact surface (20), - the second base part (12) has an opening (24) with an adjacent ring section (26) which has grooves (22) projecting radially outwards on the inside, - the first base part (12) has several pressure plates (28) which are each attached to the contact surface (20) with a first end (30) facing away from the spring body and spaced radially outside from the contact surface (20) with a second end (32) arranged opposite, - and the ring section (26) of the second base part (12) is pushed onto the contact surface (20) of the seat (18) of the first component (10) in such a way that the pressure lamellae (28) with their second ends (32) engage in the grooves (22) of the first base part (10). [3] Bearing (2) according to the preceding claim, characterized by that the pressure lamellae (28) each have an extent that is at least substantially planar. [4] Bearing (2) according to any one of the preceding claims, characterized by , that an inner diameter of the ring section (26) corresponds to an outer diameter of the contact surface (20). [5] Bearing (2) according to any one of the preceding claims, characterized by , that the seat (18) of the first base part (10) has several holders (34) projecting in an L-shape over the contact surface (20), so that a segmented annular gap (36) is formed between the contact surface (20) and the holders (34), into which the ring section (26) of the second base part (12) fits. [6] Bearing (2) according to any one of the preceding claims, characterized by , that a first and a second end (30, 32) of each pressure lamella (28) are offset from each other in radial direction R by an end distance E, wherein the end distance E is greater than a single wall thickness W of the respective pressure lamella (28) and less than three times the wall thickness W of the respective pressure lamella (28). [7] Bearing (2) according to any one of the preceding claims, characterized by, that the seat (18) of the first base part (10) and the ring section (26) of the second base part (12) have corresponding guide elements (38, 40) to define a circumferential position of the second base part (12) to the first base part (10). [8] Bearing (2) according to any one of the preceding claims, characterized by , that the holders (34) and / or the pressure lamellae (28) are spaced apart from each other in the circumferential direction U. [9] Bearing (2) according to any one of the preceding claims, characterized by , that the second base part (10, 12) pushed onto the first is mechanically connected to the spring body, so that the first and the second base part (10, 12) attach the spring body to the base body (8). [10] Bearing (2) according to any one of the preceding claims, characterized by , that the first base part (10) is designed as a metal die-cast part, in particular as an aluminium die-cast part. [11] Bearing (2) according to any one of the preceding claims, characterized by , that the second base part (12) is designed as a plastic injection molded part.

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