Engine support with plate

Abstract

The present invention relates to an engine bracket with a plate, for a vehicle, preferably a commercial vehicle, wherein the engine bracket (10) comprises a support portion (12) for connecting to an engine, a support seat (14) for connecting to a vehicle body, and an elastic pad (16) connecting the support portion (12) to the support seat (14), wherein the engine bracket (10) is located in a transverse center plane (Q), a Y axis (Y) is provided in the transverse center plane, and the pad (16) can move along the Y axis, wherein the engine bracket (10) comprises a plate (18), which is arranged on the support seat (14) by at least one press-fit connection (20) to limit the movement of the pad (16) in the direction of the Y axis (Y), wherein the plate (18) comprises at least two segmented press-fit parts (22) for producing the at least one press-fit connection (20).

Description

Technical Field

[0001] The invention relates to an engine mount (motorlager). Background Art

[0002] The engine mount serves to support the engine relative to the vehicle body. To this end, the engine mount comprises a plurality of elastic elements which elastically absorb engine vibrations and thereby isolate them. The elastic mount is usually designed to withstand the forces of the motor in the direction of travel (X direction), such as inertial forces during braking and acceleration, and the weight of the motor in the vertical direction (Z direction). However, one or more elastic elements may also move in the transverse direction (Y direction) and in a combination thereof.

[0003] In order to limit the movement of one or more elastic elements, the engine mount may include one or more stop plates. The stop plates of the engine mount are used to ensure that the elastic elements do not directly collide with the vehicle body laterally, but instead come to bear against the stop plates. The plate protects the vehicle body and must be fixedly connected to the suspension in order to deliver the engine mount to the end customer. A snap-on connection could be a connection option here. If additional fastening points have to be implemented between the stop plate and the suspension seat, these plates are usually plugged onto the centering pins by means of a press fit. Since the centering pins are mostly castings, large deviations from the nominal dimensions caused by the casting make it difficult to adjust the fit.

[0004] Without a press fit, the stop plate is not fixed at all. If an interference fit is too tight, the stop plate can tear. An interference fit that is too tight also results in the stop plate being rigidly fixed to the suspension. The stop plate is then unable to follow operationally related distortions of the connecting structure, such as the suspension seat. A gap or relative movement occurs between the connecting structures, which can sometimes result in noise, wear or moisture penetrating the gap. Summary of the invention

[0005] The invention is therefore based on the object of providing an engine mount having a plate which allows fastening to a bearing block while restricting the cardanic degrees of freedom as little as possible.

[0006] Therefore, according to the present invention, an engine bracket for a vehicle, preferably a commercial vehicle, is proposed, the engine bracket comprising a support portion for connecting to an engine, a support seat for connecting to a vehicle body, and an elastic pad connecting the support portion to the support seat, wherein the engine bracket is located in a transverse center plane, the Y axis is arranged in the transverse center plane, and the pad can move along the Y axis, wherein the engine bracket comprises a plate member, which is placed on the support seat by at least one press-fit connection to limit the movement of the pad in the Y-axis direction, wherein the plate member comprises at least two segmented press-fit members for producing the at least one press-fit connection.

[0007] The Y-axis corresponds to the transverse direction of the vehicle in the usual installed state. However, directions deviating therefrom are not excluded. In the installed state, the engine bracket is fixedly connected to the vehicle body for mounting the engine. Although the segmented press fits fix the plate, they hardly restrict the universal freedom. Therefore, the press fit also hardly hinders the bending elasticity of the plate, so that no gap is formed between the bearing seat (lagerhalter) and the plate. In addition, the connection geometry can ensure sufficient tolerance compensation, so that a fixation that prevents the self-connecting geometry from slipping, for example, is reliably present. The press fit can achieve connection only by force fit, only by form fit or a combination thereof. If there is also a form fit, at least one press fit is inserted into the corresponding form fit.

[0008] The segments serve to better adapt or better follow the surface against which the press-fit parts come into contact. In principle, the press-fit parts can be placed against the surface independently of one another. Thus, a secure connection can be ensured and the dependency of high dimensional tolerance requirements can be reduced. The sheet metal part can be formed in one piece or even in a uniform material. With the invention, dimensionally relevant reworking of the connection geometry is no longer necessary.

[0009] According to a further development, these press-fits can be at least partially flexible. This allows for better tolerances for deviations from the nominal dimensions. The flexibility can be structural, for example by means of the geometric design of the press-fit and / or by the material. It is advantageous if only the press-fit is flexible and the remaining plate is rigid.

[0010] According to a refinement of the engine support, at least the two segmented press fits and / or at least two segmented press fits may have opposite directions of action and / or the plate may include at least one abutment on which the press-fit connection is formed. Due to the opposite directions of action, the plate can be centered with respect to the support seat and a uniform stress distribution can be achieved. If the plate is precisely centered with the aid of two press fits with opposite directions of action or, in other words, arranged opposite each other so that they fix a fastener or a pin without it resting against a third position, the two press fits act as a support with one degree of torsional freedom. This results in the plate being able to follow operation-related distortions of the connection structure very well.

[0011] However, the press fits can also be arranged so that they are offset by, for example, 120° relative to one another and are therefore equidistant. However, they can also be arranged unequally relative to one axis. The press fits can be arranged, for example, at +20°, one at -20° and one at 180°, so that a force balance can be present even though no press fit is opposite another press fit.

[0012] A refinement of the engine mount can provide that the bearing seat comprises at least one fastener and preferably a pin, which is preferably designed to be made of the same material as the bearing seat, and on which the at least one press-fit connection is formed. The plate can be placed onto the fastener, for example, in a fastening direction, thereby achieving the press-fit. The pin can protrude from the bearing seat in the Y direction, thereby simplifying the mounting of the plate. More than two pins are also conceivable.

[0013] Alternatively or additionally, it is conceivable that in the engine mount according to the invention, the pin is designed to be cylindrical or conical. The taper allows for easier installation, especially when the relative position tolerances of the pin are relatively large. For example, the cross-section of the pin can be designed to be circular, and / or the pin can include a projection or a cutout extending at least partially or over its entire length in the axial direction. For example, at least one press-fit and / or an abutment can be inserted into the projection or the cutout to achieve a press fit there. In addition, the pin can have a form-fitting element, into which at least one press-fit can be inserted.

[0014] According to the improved scheme, the plate may have at least one preferably continuous notch, preferably two press fits and / or at least one abutment are arranged in the notch. The pin can pass through the notch, and the press fit and / or the abutment then abut on the surface of the notch. The edge of the notch can follow the cross-sectional circumference of the pin at a uniform and consistent spacing in the circumferential direction. The at least two press fits can be relative to each other about the center of the notch. It is conceivable that the press fit is oversized with respect to the pin so that a reliable press fit is achieved at each position. It is conceivable that the press fit is distributed along the edge in the notch in a 90° area range of the arc, preferably 120°, more preferably 180°, and more preferably 225° area range. A gap can be formed between adjacent press fits, the width of which is 0.5 to 1.5 times the width of the adjacent press fits. The press fits can be equidistantly spaced from each other and / or have a uniform and consistent width. The press fits can be non-equidistantly spaced from each other and / or have an uneven and consistent width. The abutment can be formed by the plate itself and / or preferably protrude into a projection or cutout of the pin in a press fit. The plate can also have more than two such cutouts. It preferably has two cutouts, which are arranged and designed radially symmetrically with respect to a transverse center plane, wherein the transverse center plane can extend in the transverse direction.

[0015] According to a further development, the at least one continuous notch can be surrounded by an annular portion of the sheet metal, which is preferably inflexible. The annular portion itself can be formed by the sheet metal. The press fit can advantageously be supported on this inflexible portion.

[0016] According to an improved solution, the press-fit piece can be segmented in the circumferential direction about the axis. The axis can pass through the notch centrally. The gap between two adjacent press-fit pieces can extend along the axis.

[0017] According to another embodiment of the engine bracket, these press fits can be formed integrally with the plate, preferably in a material-uniform manner. The plate can thus be produced simply from plastic using an injection molding process. The press fits are preferably designed without undercuts. The absence of undercuts allows the use of simple injection molds, in which the otherwise complex but necessary three-part or more part structure of the injection mold can be dispensed with. Furthermore, the absence of undercuts allows or facilitates simple demoulding.

[0018] Alternatively or additionally, it is conceivable that in the engine mount according to the invention the plate comprises at least one hook, by means of which the plate can be locked to the bearing seat independently of the fixing of the plate to the at least one fastening element or pin.

[0019] According to a further development, these press-fit parts can be designed as hooks or partial spheres. The hooks or partial spheres can extend in the direction of the pins. The partial spheres or spherical support structures have a rotational degree of freedom when fastened. The sheet metal part can be moved in this degree of freedom relative to the connection geometry or the pins and can therefore follow the torsion of the vehicle body and the bearing well.

[0020] According to an improved solution, the hook may have an abutment tongue protruding from the base, wherein the abutment tongue may extend obliquely opposite to the fastening direction on the support seat. The hook base may extend along the axis through the notch and be formed integrally with the plate, preferably in a uniform material manner. The hook base may be clamped with the tongue-shaped member to form an angle in the range of 60° to 120° or a first angle, preferably a 90° angle. The surface of the hook base facing the tongue-shaped member may extend obliquely with respect to the axis, wherein the surface is clamped with the axis to form an angle in the range of 10° to 30° or a second angle, preferably a 20° angle. The central axis along which the abutment tongue extends may be clamped with the axis to form an angle in the range of 50° to 90° or a third angle, preferably a 70° angle. The free end of the tongue-shaped member may be designed to be spherical to achieve rotational freedom.

[0021] Alternatively or additionally, it is conceivable that in the engine mount according to the invention the suspension mount is a cast part and / or the sheet metal part is formed from plastic. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] Further features, details and advantages of the invention emerge from the wording of the claims and from the following description of exemplary embodiments in conjunction with the accompanying drawings, in which:

[0023] Figure 1is a longitudinal sectional view of an engine bracket according to the present invention,

[0024] Figure 2 Show according to Figure 1 A cross-sectional view of the engine bracket along line II-II,

[0025] Figure 3 A perspective view showing an engine bracket according to the present invention,

[0026] Figure 4 A perspective view showing a portion of a panel according to a first embodiment,

[0027] Figure 5 Show according to Figure 4 A cross-sectional view of a plate.

[0028] Figure 6 A perspective view showing a portion of a panel according to a second embodiment, and

[0029] Figure 7 Show according to Figure 6 Cross-sectional view of the plate.

[0030] Reference numerals list

[0031] 10 Engine mount

[0032] 12 Supporting part

[0033] 14 Support seat

[0034] 16 Pads

[0035] 18 Panels

[0036] 20 Press fit

[0037] 22 Press fit

[0038] 24 Pins

[0039] 26 Gap

[0040] 28 Hook

[0041] 30 Partial sphere

[0042] 32 Hook

[0043] 34 base

[0044] 36 Abutment tongue

[0045] 38 Butt

[0046] 40 Gap

[0047] 42 Recessed part

[0048] 44 Centering bulge

[0049] 46 Ring

[0050] α1 First angle

[0051] α2 Second angle

[0052] α3 The third angle

[0053] A axis

[0054] B Fastening direction

[0055] C Center axis

[0056] R Clearance

[0057] Q Transverse center plane

[0058] XX axis

[0059] XA Stop in X direction

[0060] YY Axis

[0061] YA Stop in the Y direction

[0062] ZZ axis

[0063] ZA Stop in Z direction DETAILED DESCRIPTION

[0064] In the figures, identical or mutually corresponding parts are respectively indicated by the same reference numerals and are therefore not described again unless inappropriate. Features that have already been described are not described again to avoid repetition and can be applied to all parts with identical or mutually corresponding reference numerals unless explicitly excluded. The disclosure contained in the entire specification can be applied to the same parts with the same reference numerals or the same component names according to the meaning. The position descriptions selected in the specification, such as top, bottom, side, etc., refer to the figures just described and shown and are transferred to the new positions according to the meaning when the position changes. In addition, individual features or feature combinations from the different embodiments shown and described can also be individual, creative or solutions of the present invention.

[0065] Figure 1The longitudinal section of an engine bracket 10 according to the invention is shown, the engine bracket comprising a support part 12, a support seat 14 and an elastic cushion 16 located therebetween. The engine bracket 10 is traversed by a transverse center plane Q and is oriented such that the X axis corresponds to the direction of travel, the Y axis corresponds to the transverse direction and the Z axis corresponds to the vertical direction. In the installed position, the support part 12 is firmly connected to the vehicle body and the support part 14 is firmly connected to the engine. The cushion 16 separates the two from each other. The cushion 16 can be moved in three spatial directions and combinations thereof, wherein its movement is limited by means of an X stop XA and a Z stop ZA with a gap R or a free path interposed in each case.

[0066] In order to limit the displacement of the cushion member 16 in the Y direction and prevent it from hitting the vehicle body, Figure 2 The plate 18 shown is placed on the engine support 10. Here too, a clearance R is provided, wherein the plate 18 serves as a Y stop YA. When the support part 12 protrudes to one side from the support seat 14, the plate 18 is arranged on the side of the support part 12 opposite thereto. In order to fasten it to the support seat 14, the plate 18 is placed in the fastening direction B onto a cylindrical pin 24 to achieve a press fit 20 there, wherein the pin 24 serves as a fastening element or connecting geometry.

[0067] This is Figure 3 14 is shown in a stereoscopic view. The cross section of the pin 24 is designed to be kidney-shaped or half-moon-shaped, where the recess 42 is arranged on the side pointing to the transverse center plane Q. The plate 18 has a hook 32, which is engaged behind the matching geometry on the suspension seat 14 in a form-fitting manner. The plate 18 also has a centering protrusion 44, which is inserted into the groove on the support seat 14 and limits the movement path of the plate 18 in the X direction. The plate 18 also has two continuous notches 26, each of which has a pin 24 passing through the notch. The notch 26 of the plate 18 is designed to be mirror-symmetrical about the transverse center plane Q. The segmented press-fit 22 is arranged in the notch 26, and the press-fit is pressed 20 with the surface of the pin 24 due to its own oversize.

[0068] Figure 4 and Figure 5 A first embodiment of a press-fit 22 in the form of a hook 28 is shown. The recess 26 is traversed by an axis A, which can extend in the direction of the Y axis. The edges of the recess 26 follow the kidney-shaped or crescent-shaped cross section of the pin 24 with a uniform gap in between. The press-fit 22 acts in this gap. The recess 26 is surrounded by an annular portion 46 of the plate 18, wherein the annular portion is non-flexible and is designed in the shape of a circular ring with respect to the axis A. In addition to the hook 28, the recess 26 also includes a convex abutment 38, which can be used to abut or press-fit against the pin 24.

[0069] Four hooks 28 are arranged in the notch in the same width and equidistant manner. Each hook 28 includes a base 34 and an abutment tongue 36 protruding from the base, wherein the two enclose a first angle α1 of 90°. The surface of the base 34 extends obliquely with respect to the axis A and encloses a second angle α2 of 20° with the axis. Each abutment tongue 36 extends along a central axis C, which encloses a third angle α3 of 70° with the axis A.

[0070] It can be seen that the hooks 28 are formed segmented relative to one another in the circumferential direction about the axis A. Gaps 40 are formed between adjacent hooks 28. Because of its thin design, the abutment tongue 36 is flexible, but at least more flexible than the plate 18. The hooks 28 are distributed over a 225° area of ​​the arc along the edge in the recess 26. It can also be seen that in the illustrated embodiment the two hooks 28 have opposite directions of action.

[0071] Figure 6 and Figure 7 A second embodiment of a press fit 22 is shown in the form of a partial sphere 30 . Two partial spheres 30 are opposite one another with respect to the recess 26 .

[0072] The invention is not limited to one of the above-described embodiments, but can be modified in various ways. All features and advantages from the claims, the description and the figures, including structural details, spatial arrangements and method steps, can be essential to the invention both individually and in very different combinations.

[0073] All combinations of at least two of the features disclosed in the description, the claims and / or the drawings fall within the scope of the invention.

[0074] To avoid repetition, features disclosed with respect to the apparatus should also be considered disclosed and claimable with respect to the method. Likewise, features disclosed with respect to the method should also be considered disclosed and claimable with respect to the apparatus.

Claims

1. An engine bracket for a vehicle, wherein: The engine bracket (10) comprises a support portion (12) for connecting to the engine, a support seat (14) for connecting to the body of the vehicle, and an elastic pad (16) connecting the support portion (12) to the support seat (14), wherein the engine bracket (10) is located in a transverse center plane (Q), a Y axis (Y) is provided in the transverse center plane, and the pad (16) can move along the Y axis, and is characterized in that the engine bracket (10) comprises a plate (18), which is arranged on the support seat (14) by at least one press-fit connection (20) so as to limit the movement of the pad (16) in the direction of the Y axis (Y), wherein the plate (18) comprises at least two segmented press-fit parts (22) for producing the at least one press-fit connection (20).

2. The engine bracket according to claim 1, characterized in that: The press fit (22) is at least partially flexible.

3. An engine mount according to any one of the preceding claims, characterized in that At least two of the segmented press fits (22) and / or at least two of the segmented press fits (22) have opposite directions of action, and / or the plate (18) comprises at least one abutment (38) on which the press fit connection (20) is formed.

4. The engine bracket according to claim 1, characterized in that: The support seat (14) includes at least one fastener.

5. The engine bracket according to claim 1, characterized in that: The plate (18) has at least one notch (26).

6. The engine bracket according to claim 5, characterized in that: The at least one continuous opening (26) is surrounded by an annular portion (46) of the plate (18).

7. The engine bracket according to claim 1, characterized in that: The press-fit part (22) is segmented in the circumferential direction about the axis (A).

8. The engine bracket according to claim 1, characterized in that: The press fit (22) is formed integrally with the sheet metal part (18).

9. The engine bracket according to claim 1, characterized in that: The press fit (22) is designed in the form of a hook (28) or a partial sphere (30).

10. The engine bracket according to claim 9, characterized in that: The hook (28) has an abutment tongue (36) protruding from a base (34), wherein the abutment tongue (36) extends obliquely opposite to a fastening direction (B) on the bearing seat (14).

11. The engine mount according to claim 1, characterized in that: The engine mount is for a commercial vehicle.

12. The engine mount according to claim 4, characterized in that: The bearing seat (14) comprises a pin (24) which is formed in a unified manner with the material of the bearing seat (14) and on which the at least one press-fit connection (20) is formed.

13. The engine mount according to claim 5, characterized in that: The plate (18) has at least one continuous recess (26), in which two segmented press-fit parts (22) and / or at least one abutment (38) are arranged.

14. The engine mount according to claim 6, characterized in that: The annular portion (46) is inflexible.

15. The engine mount according to claim 8, characterized in that: The press fit (22) is formed from a single material with the sheet metal part (18).

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