Engine mount with insertable stop

Abstract

Bearing (1) for a motor vehicle, in particular engine bearing (1), with an inner part (3), an outer part (2) which comprises the inner part (3), and an elastomer body (31) which connects the inner part (3) and the outer part (2) via at least one spring body (32), wherein the outer part (2) has at least one opening (23) for receiving at least one stop body (4), and wherein the stop body (4) is inserted into the opening (23) in such a way that it reduces the distance of movement (Y, Z) of the inner part (3) relative to the outer part (2), characterized in that the spring body (32) is substantially conical around the direction of the weight force (G) such that the spring body (32) forms a recess (33) between the inner part (3) and the outer part (2), into which recess the stop body (4) is inserted through the opening (23).

Description

[0001] The invention relates to a bearing for a motor vehicle, in particular an engine bearing, according to the preamble of claim 1 and according to the preamble of claim 2.

[0002] Such bearings are already known from the prior art and are used in motor vehicles, for example, to mount the engine. Typically, the outer part of the bearing, which can also be referred to as the housing, is cylindrical, sleeve-like, or box-shaped, and the elastomer body has at least one spring element (spring strut) that connects the sleeve-like inner part to the outer part. The outer part is firmly connected to the frame of the motor vehicle.

[0003] The inner part can, for example, be connected to the elastomer body by vulcanization or could contain an insertion opening into which, for example, an insert holder can be inserted in the direction of the longitudinal axis A of the bearing (longitudinal direction or insertion direction).

[0004] For example, the engine of a motor vehicle can be attached to the insert holder in such a way that, when a bearing is installed in a motor vehicle, the direction of the main vibration direction of the engine, which generally corresponds to the direction of the weight force G, is essentially perpendicular to the longitudinal axis A of the bearing. The motor vehicle's engine is then resiliently mounted relative to the frame of the motor vehicle by the spring body, essentially in the direction of the weight force G of the bearing.

[0005] During the manufacture of such bearings, the inner part, including the spring body, can be inserted into a corresponding opening in the outer part. The inner part and spring body are already bonded together, e.g., by vulcanization. This requires that the opening in the outer part or its interior be geometrically designed in such a way that the insertion of the inner part is possible, i.e., that the insertion of the inner part is not blocked by elements of the interior or the opening in the outer part. This limits the design of the interior or the opening in the outer part.

[0006] A particular disadvantage here is that stop surfaces inside the outer part, which are intended to act against the inner part when the bearing is mounted and limit its movement, can only be provided to a limited extent. Thus, the options for providing the necessary stop surfaces for such bearings are limited in order not to hinder the insertion of the inner part.

[0007] These can contradict the requirement that permanent overlap between the outer part and the spring-mounted inner part must be ensured during operation of the bearing in order to prevent the bearing from tilting. Such tilting would result in bearing failure, i.e. a tilted bearing no longer has any spring action between the inner and outer parts and therefore no longer dampens vibrations of the engine relative to the vehicle frame. This can lead to failure of the suspension spring if there is no longer any overlap between the stop and the inner part. In the worst case, the suspension spring can be torn out of the housing.

[0008] DE 102011 000 538 A1 describes an elastic bearing with an inner part and with an outer part which at least partially surrounds the inner part and is designed as a bearing housing, in which the inner part and outer part are connected to one another by an elastomer body and are each designed as a single piece, wherein the inner part has at least one projection directed towards the inner wall of the outer part and the outer part has a receptacle or recess complementary thereto and the elastomer body and the elastomer support are designed such that the projection dips / engages in the recess in all loading directions of the bearing.

[0009] JP H-07 280 035 A describes that in an engine mount, both ends of a mounting rubber are attached to surfaces approximately opposite each other in the transverse direction within an outer cylinder. Spaces are defined at the upper and lower parts in the outer cylinder. An inner cylinder supported by the mounting rubber is provided. A stopper rubber is provided in the upper space of the outer cylinder in an attachable / detachable manner by a fastener (a screw). The elasticity of the entire engine mount is varied depending on the type of stopper rubber to be mounted in the upper space of the outer cylinder, thus enabling adaptation to various engines.

[0010] JP 2009 204 140 A describes a cylindrical anti-vibration device constructed by assembling a rubber-elastic body comprising a cylindrical member separately disposed around a shaft member and a connecting member connecting the shaft member to the cylindrical member. Stopper member-forming elements including stopper members are fitted into through-holes formed on the cylindrical member to form an assembly. The assembly is fixed to an inner peripheral surface of an outer tubular member, and thereby the shaft member is connected to the outer tubular member through the rubber-elastic body. The stopper members are positioned protruding toward the shaft member side from the outer tubular member side in cavity portions formed on the rubber-elastic body.

[0011] JP H-09 60 687 A describes a fluid-filled bushing whose outer fastening part is connected to the outer periphery of an inner fastening part via an elastic body. A plurality of fluid spaces, which are divided by the elastic body, communicate with one another via the first opening. A stopper arranged in the fluid space and protruding in the direction of vibration introduction is provided on the inner fastening part. A gap adjusting element opposite the stopper is provided on an outer fastening part. A gap between the stopper and the adjusting element forms the second opening. The gap adjusting element can be moved towards and away from the stopper, thereby making the opening characteristic of the second opening variable.

[0012] KR 100 471 858 B1 describes a roller rod mounting structure for an automotive engine, in which an insulator is arranged between the inner tube and the outer tube, and a stopper is positioned at a predetermined distance between the outer tube and the insulator to insulate the outer tube. In the roller rod mounting structure of a tube-mounted automotive engine, an actuator is coupled to the stopper to move the stopper toward the insulator, and an actuator is coupled to the stopper according to a detection signal when starting or when a large displacement occurs. Since it has a structure that includes an electronic control unit that controls the actuator, it is possible to effectively control shock vibrations when a large displacement occurs, such as during starting or sudden acceleration, while reducing driving noise during normal driving.

[0013] JP S-64 20 553 U describes another cylindrical anti-vibration device.

[0014] The object of the present invention is to provide a bearing, in particular an engine bearing, of the type described above, which has an enlarged usable stop surface and at the same time ensures a permanent overlap between the outer part and the spring-mounted inner part of the bearing.

[0015] The object is achieved according to the invention by the features of the characterizing part of claim 1 and claim 2. Advantageous further developments are described in the subclaims.

[0016] The invention is based on the finding that, in a bearing of the type described above, stops for limiting the vibration path of the spring body can be introduced into the interior of the bearing, namely after the inner and outer parts have been brought together. As a result, these stops do not block the insertion of the inner part into the outer part, since these stops are only inserted after this assembly step. By being subsequently inserted, these stops can engage behind elements of the inner part in the insertion direction (direction of the longitudinal axis A) and there act preferably essentially in the main vibration direction, e.g. the direction of the weight force G, of the bearing. The stops can be inserted into the corresponding openings, e.g. by inserting, screwing or the like.

[0017] The advantage here is that additional stops can be provided between the outer and inner parts of the bearing, which provide additional travel limitation for the vibration of the spring-mounted inner part relative to the outer part and thus ensure permanent overlap between the outer and inner parts during operation without restricting the assembly of the bearing, i.e., the insertion of the inner part into the outer part. The subsequent introduction of the additional stops also allows the contact surface between the outer and inner parts to be enlarged. This enables the design of new bearing designs.

[0018] The secure overlap of the outer and inner parts during operation prevents the outer and inner parts from jamming and thus the failure of the bearing.

[0019] Another advantage is that by subsequently inserting the additional stops, the inner part can be blocked relative to the outer part in the direction of the longitudinal axis A. This can prevent the inner part from accidentally being removed from the outer part.

[0020] According to one aspect of the invention, the outer part has at least one opening. A stop body is inserted into this opening in such a way that it reduces the distance of movement Y, Z of the inner part relative to the outer part.

[0021] It is advantageous that such a stop acts in at least one direction of vibration of the bearing and thus reduces the movement Y, Z in this direction according to the invention. Preferably, this restricts the movement Y, Z of the main direction of vibration of the bearing.

[0022] According to a further aspect of the invention, the elastomer body is provided substantially below the inner part in the direction of the weight force G.

[0023] The advantage here is that in general the direction of the weight force G is the main direction of vibration of such a bearing and therefore the restriction of the movement Y, Z should essentially take place in this direction.

[0024] According to a further aspect of the invention, the opening in the outer part is provided below the inner part in the direction of the weight force G.

[0025] Another advantage here is that in general the direction of the weight force G is the main direction of vibration of such a bearing and therefore the restriction of the movement Y, Z should essentially take place in this direction.

[0026] According to a further aspect of the invention, the spring body has a recess opposite the stop body.

[0027] The advantage here is that the design of this recess and the stop body in interaction allows the restriction of movement Y, Z to be determined. Furthermore, this recess creates a space between the spring body and the outer part into which the stop body can be inserted and mounted.

[0028] According to the invention, on the one hand, the spring body is designed to be substantially conical around the direction of the weight force G in such a way that the spring body forms a recess between the inner part and the outer part, into which the stop body is inserted through the opening.

[0029] This means that the spring body is conically shaped such that its central axis (axis of rotational symmetry) essentially corresponds to the direction of the weight force G. The corresponding recess, which can also be referred to as a cavity, is preferably also essentially conically shaped. Due to the recess within the spring body, it can also be considered a conical cylinder.

[0030] Such a cylindrical-conical design of the spring body is advantageous because, in addition to a high spring effect in the direction of the weight force G, it also allows high rigidity to be achieved in all directions of the plane perpendicular to the weight force G. This also allows a linear force line pattern of the spring body to be created.

[0031] According to the invention, the opening and the stop body are designed in such a way that the stop body can be inserted into the opening by inserting it.

[0032] The advantage here is that this allows for quick and easy installation of the stop body.

[0033] The opening and the stop body are designed in such a way that the stop body can be blocked against the outer part after being inserted into the opening by rotating it around the axis of the insertion direction.

[0034] The advantage of such a design is that the stop body can be securely seated inside the outer part through simple and quick assembly. This requires that the opening and the stop body do not block each other during insertion, and that the stop body is designed with projections or the like so that, after rotation, these rest against the outer part from the inside and hold the rotated stop body in the opening.

[0035] According to a further aspect of the invention, the opening is larger in a first direction of its plane than in the second direction of this plane which is perpendicular thereto, and the stop body has at least one projection which is aligned in the first direction of the opening when inserted and substantially in the second direction of the opening after rotation.

[0036] The advantage here is that a projection provides a simple and secure means of holding the twisted stop body in the opening. This projection and the corresponding opening in the outer part must be designed in such a way that the stop body, including the projection, can be easily, quickly, and reliably inserted through the opening and twisted, while simultaneously holding the twisted stop body securely in the opening.

[0037] Preferably, at least two projections are provided, which are located substantially opposite each other in the plane of the opening. This has the advantage of ensuring a uniform hold of the stop body in the opening.

[0038] According to a further aspect of the invention, the opening and the projection are formed at right angles.

[0039] This design is advantageous because rectangular bodies and recesses can be manufactured more easily, accurately, and quickly than contours and geometries that deviate from these. "Rectangular" also refers to a substantially rectangular recess with rounded corners.

[0040] Preferably, the opening of the outer part and the projection(s) of the stop body are formed at right angles. The stop body should be formed accordingly, i.e., if necessary, also at right angles or rectangularly. This allows a secure interaction of the projection(s) of the stop body with the opening of the outer part to be achieved in order to hold the twisted stop body in the opening.

[0041] According to a further aspect of the invention, the stop body has at least one holding element to limit the insertion of the stop body into the opening in the insertion direction.

[0042] This advantageously prevents the stop body from being completely inserted into the interior of the outer part during insertion, which may make it impossible to handle it from the outside, especially to rotate it. In other words, the stop should be able to be inserted a defined distance through the opening into the interior of the outer part and should not be loosely located inside the outer part. This is achieved by a corresponding retaining element.

[0043] This also has the advantage that it can fix the stop body against the outer part from the outside, for example, to securely maintain the rotated orientation of the stop body. For this purpose, the retaining element can be designed with at least one, preferably two, inclined flanks to clamp itself against the outside of the outer part when the stop body is rotated.

[0044] Preferably, the holding element is flat, preferably designed as a flat plate at the lower end of the stop body, in order to increase the overall height of the stop body outside the outer part as little as possible.

[0045] An embodiment and further advantages of the invention are explained below in conjunction with the following figures. Fig. 1 a side schematic sectional view of the bearing in the assembled state; Fig. 2 a perspective view of a stop body; Fig. 3 a perspective view of the bearing in disassembled state; Fig. 4 a perspective view of the bearing after inserting the inner part into the outer part from the front; Fig. 5 a perspective view of the bearing after insertion of the inner part into the outer part from below; Fig. 6 a perspective view of the bearing after insertion of the stop body into the outer part from below; Fig. 7 a perspective view of the bearing after insertion of the stop body into the outer part from the front; and Fig. 8 a perspective view of the bearing after turning the stop body in the outer part from the front.

[0046] Fig. 1 shows a side schematic sectional view of the bearing 1 in the assembled state.

[0047] The bearing 1 has an outer part 2 or housing 2. The outer part 2 essentially encloses an interior space 20, which has an insertion opening 21, a vibration opening 22, and a stop opening 23. The insertion opening 21 is provided essentially in the direction of the longitudinal axis A of the bearing 1 and is dimensioned such that an inner part 3 can be inserted into the interior space 20 through this insertion opening 21. The vibration opening 22 is provided in the upper side of the outer part 2, i.e., on the side of the outer part 2 opposite the direction of the weight force G as the main vibration direction. A corresponding guide element 36 of the inner part 3 engages in this vibration opening 22 after the inner part 3 has been inserted into the outer part 2, cf. e.g. Fig. 3 and Fig. 4.

[0048] In this vibration opening 22 or through it, the inner part 3 can vibrate during operation in the axis of the weight force G (main vibration direction), with the inner part 3 being guided by the guide element 36 in the vibration opening 22. The bearing 1 is designed such that the inner part 3 is always reliably guided by the guide element 36, i.e. that the inner part 3 can travel a maximum of the vibration distance X relative to the outer part 2 in order to prevent the guide element 36 from being moved out of the vibration opening 22. This would lead to the inner part 3 jamming in the outer part 2 and thus to the failure of the bearing 1.

[0049] The outer part 2 further comprises a plurality of mounting elements 24, which in this embodiment are designed as openings 24, cf. Fig. 3. Screws or bolts, for example, can be passed through these openings 24 in order to fasten the outer part 2 to the body of a motor vehicle.

[0050] The inner part 3 can also be referred to as the spring-loaded part 3 of the bearing 1. The inner part 3 has an insertion opening 30 for receiving an insert holder (not shown). Via such an insert holder, the engine of a motor vehicle can be connected to the bearing 1 and supported in a vibration-damped manner via the bearing 1, which is attached to the body via its outer part 2.

[0051] The inner part 3 further comprises an elastomer body 31, which is connected to the insertion opening 30. In this exemplary embodiment, this connection is realized by vulcanizing the elastomer body 31 to a metal body that forms the insertion opening 30. However, other connections are also possible.

[0052] The elastomer body 31 has a spring body 32, which is provided between the insertion opening 30 and the outer part 2 in the direction of the weight force G. In this embodiment, this spring body 32 is conical, so that its axis of rotational symmetry essentially corresponds to the direction of the weight force G, see e.g. also Fig. 3. In this way, the spring body 32 forms a recess 33 opposite the inside of the outer part 2, which can also be referred to as a cavity 33.

[0053] The side of the spring body 32 facing away from the insertion opening 30 has a support element 35, which can be made of metal. This support element 35, in the inserted state of the inner part 3, lies on the inner side of the outer part 2 and supports the inner part 3 against the outer part 2 in a vibration-damping manner via the spring body 32. The support element 35 has an insertion stop 34 that limits the insertion of the inner part 3 into the outer part 2 in the insertion direction, i.e., in the direction of the longitudinal axis A, in order to achieve a defined positioning of the inner part 3 in the outer part 2.

[0054] The bearing 1 further has a stop body 4, see also Fig. 2 in detail. The stop body 4 has a base body 40, on one side of which, with which the stop body 4 can be inserted into the corresponding stop opening 23 of the outer part 2, two mutually opposite projections 41 are formed, see e.g. perspective view of a stop body in Fig. 2. These projections 41 are arranged and designed such that they do not hinder insertion of the stop body 4 into the outer part 2. After rotation of the stop body 4 about the insertion axis, which essentially corresponds to the axis of the weight force G, these projections 41 engage the outer part 2 from the inside in such a way that they reliably prevent removal of the stop body 4 from or from falling out of the outer part 2.

[0055] The area between the two projections 41 serves as a stop surface 43, i.e., the inside of the spring body 32 can strike the surface 43. In this way, by inserting the stop body 4, the distance Y that the spring body 32 can travel relative to the outer part 2 due to vibration or loading is limited to the distance Z.

[0056] At its end opposite the stop surface 43, the stop body 4 has a holding element 42, which is preferably designed as a flat plate in order to keep the overall height of the stop body 4 outside the outer part 2 as low as possible. This holding element 42 is designed, e.g., as a square or rectangular plate 42, the dimensions of which are larger than the dimensions of the stop opening 23, so that it can be reliably prevented that the stop body 4 can be inserted completely or too far into the stop opening 23. Furthermore, the holding element 42 can preferably be designed such that, when the stop body 4 is rotated, the holding element 42 clamps the stop body 4 relative to the outer part 2 in order to securely hold the stop body 4 in the rotated position.

[0057] Bearing 1 can be installed as follows: Fig. Figure 3 shows a perspective view of the bearing 1 in the disassembled state. This means that the outer part 2, the inner part 3 and the stop body 4 are not connected to each other. In order to assemble the bearing 1, the inner part 3 is first inserted through the insertion opening 21 into the interior 20 of the outer part 2. This insertion takes place essentially in the direction of the longitudinal axis A. The inner part 3 is initially in the insertion direction (arrow of the Fig. 3) such that the support element 36 can be inserted into the vibration opening 22. The inner part 3 can then be inserted into the outer part 2 in the insertion direction without being tilted.

[0058] Fig. 4 shows a perspective view of the bearing 1 after inserting the inner part 3 into the outer part 2 from the front. Fig. Figure 5 shows a perspective view of the bearing 1 after the insertion of the inner part 3 into the outer part 2 from below. In this assembly step, the stop body 4 is inserted through the insertion opening 21 from the outside into the interior 20 of the outer part 2 (arrow of the Fig. 4 and Fig. 5). In this way, the projections 41 and the stop surface 43 are positioned in the recess 33 between the underside of the spring body 32 and the inside of the outer part 2, while the stop body with its holding element 42 rests against the outer part 2 from the outside, cf. the perspective view of the bearing 1 after the insertion of the stop body 4 into the outer part 2 from diagonally below the Fig. 6.

[0059] Fig. Figure 7 shows a perspective view of the bearing 1 after the insertion of the stop body 4 into the outer part 2 from the front. In this position, the stop body 4 is rotated around the axis of insertion (arrow of the Fig. 7), so that the projections 41 rest from the inside against the inside of the outer part 2, see the perspective view of the bearing 1 after turning the stop body 4 in the outer part 2 from the front of the Fig. 8.

[0060] In this state, the stop body 4 is securely held between the spring body 32 and the inside of the outer part 2 and positioned such that its stop surface 43 reduces the maximum oscillation path Y, Z of the inner part 3 relative to the outer part 2 such that the distance X is not exceeded and thus tilting of the bearing 1 is reliably prevented. List of reference symbols (part of the description) G Direction of the weight force A Longitudinal axis of bearing 1, perpendicular to the direction of the weight force G X Distance of the shrinkage path above the inner part 3 in the direction of the weight force G, which can be covered without tilting the bearing 1 Y maximum distance of the shrinkage path below the inner part 3 in the direction of the weight force G, which can be covered without stop body 4 Z maximum distance of the shrinkage path below the inner part 3 in the direction of the weight force G, which can be covered with the stop body 4 1 warehouse 2 Outer part or housing of bearing 1 20 Interior of the outer part 2 21 Insertion opening of the outer part 2 22 Vibration opening of the outer part 2 23 Stop opening of the outer part 2 24 Mounting element 3 Inner part or spring-loaded part of bearing 1 30 Insertion opening for an insert holder (not shown) 31 elastomer bodies 32 conical spring body of the elastomer body 30 33 Recess of the conical spring body 32 34 Insertion limitation 35 Support element 36 Guide element 4 stop bodies 40 basic bodies 41 projections 42 holding elements 43 Stop surface

Claims

[1] Bearing (1) for a motor vehicle, in particular engine bearing (1), with an inner part (3), an outer part (2) which comprises the inner part (3), and an elastomer body (31) which connects the inner part (3) and the outer part (2) via at least one spring body (32), wherein the outer part (2) has at least one opening (23) for receiving at least one stop body (4), and wherein the stop body (4) is inserted into the opening (23) in such a way that it reduces the distance of movement (Y, Z) of the inner part (3) relative to the outer part (2), characterized by , that the spring body (32) is substantially conical around the direction of the weight force (G) such that the spring body (32) forms a recess (33) between the inner part (3) and the outer part (2), into which recess the stop body (4) is inserted through the opening (23). [2] Bearing (1) for a motor vehicle, in particular engine bearing (1), with an inner part (3), an outer part (2) which comprises the inner part (3), and an elastomer body (31) which connects the inner part (3) and the outer part (2) via at least one spring body (32), wherein the outer part (2) has at least one opening (23) for receiving at least one stop body (4), and wherein the stop body (4) is inserted into the opening (23) in such a way that it reduces the distance of movement (Y, Z) of the inner part (3) relative to the outer part (2), characterized by , that the opening (23) and the stop body (4) are designed such that the stop body (4) can be inserted into the opening (23) by insertion, wherein the opening (23) and the stop body (4) are designed such that the stop body (4) can be blocked relative to the outer part (2) after insertion into the opening (23) by rotating it about the axis of the insertion direction. [3] Bearing (1) according to claim 1 or 2, wherein the outer part (2) has at least one opening (23), and wherein a stop body (4) is inserted into this opening (23) in such a way that it reduces the distance of movement (Y, Z) of the inner part (3) relative to the outer part (2). [4] Bearing (1) according to one of the preceding claims, wherein the elastomer body (31) is provided substantially below the inner part (3) in the direction of the weight force (G). [5] Bearing (1) according to claim 3 or 4, wherein the opening (23) in the outer part (2) is provided below the inner part (3) in the direction of the weight force (G). [6] Bearing (1) according to one of the preceding claims, wherein the spring body (32) has a recess (33) opposite the stop body (4). [7] Bearing (1) according to one of the preceding claims, wherein the opening (23) is larger in a first direction of its plane than in the second direction of this plane perpendicular thereto, and wherein the stop body (4) has at least one projection (41) which is oriented in the first direction of the opening (23) upon insertion and substantially in the second direction of the opening (23) after rotation. [8] Bearing (1) according to claim 7, wherein the opening (23) and the projection (41) are formed at right angles. [9] Bearing (1) according to one of the preceding claims, wherein the stop body (4) has at least one holding element (42) to limit the insertion of the stop body (4) into the opening (23) in the insertion direction.

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