AXLE ARRANGEMENT FOR A MOTOR VEHICLE

Description

[0001] The present invention relates to an axle arrangement for a spring control arm for a motor vehicle according to the features in the preamble of patent claim 1.

[0002] Individual wheel suspensions for motor vehicles are known from the state of the art. These include multi-link axles, in which control arms are rotatably or pivotably coupled to a vehicle body at one end and are rotatably or pivotably coupled to a wheel carrier at the opposite end.

[0003] A lower control arm of a motor vehicle axle usually also has a mount for a spring and, optionally, a mount for a damper and / or vehicle stabilizer. Thus, the forces generated when the vehicle wheel compresses or rebounds are absorbed by the spring.

[0004] However, a corresponding spring link is usually an elongated, narrow component. A spring, on the other hand, is designed as a helical compression spring and has a larger diameter than the width of the spring link itself. Spring links are therefore usually widened in the area of ​​the spring mount. However, during compression or rebound, this leads to forces being introduced into the spring link in such a way that the spring link expands or contracts slightly. This effect is also known as breathing.

[0005] The spring link itself is faced with the conflicting objectives of being particularly rigid, but at the same time having a low component weight, so that the weight is particularly low on the unsprung wheel mass side, thus enabling high driving dynamics of the vehicle.

[0006] Spring control arms manufactured as formed sheet steel components are known from DE 10 2012 100 719 A1 and DE 10 2013 222 234 A1. However, these also have a wider cross-section in the area of ​​the spring mount.

[0007] From US 2015 / 115561 A1 a spring link according to the preamble of claim 1 is known, in which a spring seat plate is arranged on an open, widened hollow profile.

[0008] Furthermore, DE 10 2011 053 927 A1 discloses a spring link which is manufactured as an extruded component.

[0009] CN 204 172 635 U also discloses a spring link which is part of a vehicle suspension.

[0010] The object of the present invention is therefore to provide, based on the prior art, a spring link which is manufactured as a steel component and has a low dead weight and, at the same time, high rigidity.

[0011] The above-mentioned object is achieved with an arrangement for a spring link according to the features in patent claim 1.

[0012] The spring link for a motor vehicle is made of a steel material as an elongated, formed hollow profile with an open cross-section and has connection points at each of its ends. In particular, the spring link is manufactured as a sheet metal formed component from a sheet steel blank. It is characterized in that, in the installed position, the spring link is arranged with the opening of the hollow profile facing upwards, with a spring seat plate for accommodating a helical compression spring being coupled to the spring link on or in the opening. The invention thus relates to an axle assembly in which the spring link according to the invention is incorporated.

[0013] According to the invention, the spring link itself is thus designed as an open or partially open hollow profile. In particular, this has a U-shaped, C-shaped, or hat-shaped cross-section. The opening of the hollow profile points upwards relative to the vertical direction when the spring link is installed.

[0014] According to the invention, a spring seat plate is arranged on the opening or partially in the opening and coupled to the spring link. This coupling can be achieved, for example, by a thermal joining process, such as welding. The spring link itself can also be manufactured as an at least partially, in particular fully, tempered component. The spring link can also be manufactured by hot forming and press hardening.

[0015] The spring is particularly designed as a helical compression spring, with a portion of the helical compression spring resting with its coil, in particular with its final coil, on a spring support surface of the spring seat plate. The final coil of the helical compression spring, and hence the entire helical compression spring, is thus arranged above the spring link. Due to the upper-side arrangement, it is not necessary for the spring link to be widened. The cross-sectional profile is thus characterized by being approximately uniform over its length, i.e., tapering or narrowing in the longitudinal direction. However, the cross-section is not widened. The breathing effect is thus particularly avoided, so that the flow of force within the spring link is improved.

[0016] In particular, the cross-section of the spring link is constructed such that it has a web and legs protruding from the web. In the installed position, the web extends in particular in the horizontal direction and the legs are oriented in the vertical direction. According to the invention, the distance between the legs in the region of the spring seat plate is equal to or less than 1.2 times the distance between the legs in the region of an end or a connection point. In a preferred embodiment, the distance between the legs in the region of the spring seat plate is less than or equal to the distance between the legs in the region of the end or the connection point. Thus, the spring link is in particular not widened in the region of the spring seat. The distance between the legs can also be relative to the diameter of the helical compression spring or a receiving diameter.In the case of the receiving diameter, this is the diameter for accommodating the helical compression spring on the spring seat plate. In particular, the last coil of the helical compression spring is accommodated by the receiving diameter on the spring seat plate.

[0017] In these cases, in particular the distance between the legs in the area of ​​the spring seat plate, in particular the largest distance between the legs in the area of ​​the spring seat plate, corresponds to 0.5 times to 1.2 times, in particular 0.8 times to 1.1 times the diameter of the helical compression spring or the receiving diameter.

[0018] The legs themselves do not have to run completely vertically, but can also be arranged at an acute angle to the vertical direction. In particular, the distance between the legs increases toward the opening of the hollow profile. Thus, the legs are arranged in a V-shape relative to each other.

[0019] Furthermore, the hollow profile particularly preferably has laterally protruding flanges in the area of ​​the spring seat plate. This increases the contact surface and / or coupling surface of the hollow profile and the spring seat plate.

[0020] Furthermore, collars are preferably formed, particularly on the legs or flanges. The collars are preferably bent downward relative to the vertical direction. This further increases the rigidity, in particular the resistance to deflection in the vertical direction, of the spring link according to the invention.

[0021] Furthermore, the hollow profile is particularly preferably designed to be trapezoidal in its longitudinal direction, at least in some lengthwise sections, converging toward one another. The hollow profile tapers particularly toward one end, thus reducing the distance between the legs.

[0022] The connection points are designed as bearing eyes to accommodate rubber-metal bearings.

[0023] Furthermore, a connecting line through the connection points, in particular through the center of the connection points, preferably forms a line of action. The hollow profile has an arcuate profile relative to the line of action. In particular, the arcuate profile is oriented below the line of action in the installed position. Furthermore, the arcuate profile is preferably designed such that the spring seat plate with a spring support surface lies below the line of action. This also allows the force flow within the spring link to be optimized, so that, in particular, the forces acting during the compression process are better directed to the connection points and the aforementioned breathing effect is reduced.

[0024] To produce the spring link, a sheet steel blank is formed and / or bent or otherwise shaped. Various corrosion protection measures are also part of the invention. For example, a pre-coated blank can be processed. However, the manufactured spring link can also be coated using the cathodic dip coating process.

[0025] In particular, sheet thicknesses from 1.8 mm to 4.75 mm are processed, with the wall thickness of the spring seat sheet being greater than or equal to the wall thickness of the hollow profile itself, in particular greater than that of the sheet metal. Thus, for example, the hollow profile can be made from sheet metal with a wall thickness of 1.8 mm, and the spring seat sheet from a wall thickness of 2.3 mm.

[0026] The spring seat plate itself must be made of a thicker, and therefore more resistant to bending, sheet metal. Due to its geometric shape, the hollow profile itself can already possess a high section modulus against deflection in the installed position, especially relative to the vertical direction. Overall, this makes it possible to provide a spring link that combines a low component weight with a high section modulus against bending.

[0027] Furthermore, a reinforcement plate is coupled in and / or on the opening of the hollow profile, at least in sections along the longitudinal direction of the spring link. Preferably, several reinforcement plates are arranged in the spring link. This allows the spring link to be optimized depending on the stiffness requirements.

[0028] Furthermore, the spring seat plate particularly preferably has a bead oriented upward relative to a spring support surface in the installed position, so that the bead engages the inside of the helical compression spring, and in particular, the coil. Horizontal slippage of the helical compression spring is prevented by the bead. In particular, the coil lies partially above the legs in a vertical direction of a vertical force line. The spring forces generated, particularly during the compression process, can thus be diverted directly into an optimized force flow within the spring link.

[0029] Further advantages, features, properties, and aspects of the present invention are the subject of the following description. Preferred embodiments are illustrated in the schematic figures. These serve to facilitate understanding of the invention. They show: Figure 1 shows the spring link according to the invention in a perspective view, Figure 2 shows a schematic cross-sectional view with a helical compression spring in the area of ​​the spring seat plate, Figure 3 shows a side view of the spring link, Figure 4 shows a section line AA from Figure 3 , Figure 5 is a plan view of the spring link according to the invention and Figure 6 is a schematic view of a spring link bent downwards.

[0030] In the figures, the same reference symbols are used for identical or similar components, even if a repeated description is omitted for reasons of simplification.

[0031] Figure 1shows the spring link 1 according to the invention in a perspective view. This is designed as an elongated sheet metal component and has connection points 4, 5 at its respective ends 2, 3, so that it can be rotatably attached at one end 3 to a vehicle body (not shown in detail) and at the opposite end 2 to a wheel carrier (not shown in detail) or other axle component. The spring link 1 can also be attached to an axle subframe. Rubber-metal bearings are used for this purpose. However, these are not shown in detail for the sake of simplicity.

[0032] According to the invention, the spring link 1 is designed in cross-section as an open hollow profile and has an opening 6, wherein the opening 6 points upwards in the installed position relative to the vertical direction V. In the longitudinal direction 7 of the spring link 1, a spring seat plate 8 is arranged in sections on the opening 6. The spring seat plate 8 has a spring support surface 9 and a bead 10 extending upwards relative to the vertical direction V. Furthermore, a receptacle 11 is provided for coupling a damper (not shown in detail).

[0033] According to Figure 2, which shows a cross-sectional view in the area of ​​the spring seat plate 8 with helical compression spring 12, it can be clearly seen that the spring link 1 is designed as a hollow profile in cross-section. The bead 10 is not shown. An opening 6 which is located at the top in relation to the vertical direction V is closed off by the spring seat plate 8. The hollow profile has a web 14 and legs 15 which extend laterally from the web 14 in the vertical direction V. Laterally projecting flanges 16 are arranged at the end of the legs 15 and, in turn, at the end of the flanges 16 a collar 17 which is bent downwards in relation to the vertical direction is formed.

[0034] The wall thickness W6 of the spring seat plate 8 is greater than the wall thickness W1 of the hollow profile. The helical compression spring 12 itself, with its final coil 13, is arranged such that it is positioned above the legs 15 relative to the vertical direction V. A force introduced into the spring link 1 by the helical compression spring 12 is thus introduced directly into the legs 15 via the spring seat plate 8.

[0035] The largest distance A150 between the legs 15 preferably corresponds to 0.5 to 1.2 times, in particular 0.8 to 1.1 times, the diameter D12 of the helical compression spring 12 or a receiving diameter AD12. The invention thus also relates to an arrangement on a motor vehicle axle with a helical compression spring 12 and a spring link 1. A receiving diameter AD12 is preferably formed on the spring seat plate 8. This receiving diameter AD12 is suitable, in particular, for correspondingly receiving the last coil 13 of the helical compression spring 12.

[0036] Furthermore, it can be seen that the legs are arranged in a V-shape relative to one another, so that a lower distance A15U results in the vertical direction and increases in the direction of the opening 6 to the upper distance A15O.

[0037] It is clearly visible in the top view according to Figure 5that the distance A15 between the legs 15 in the area of ​​the spring seat plate 8 essentially corresponds to the distance A15 between the legs 15 in the area of ​​the end 3. The distance A15 in the area of ​​the spring seat plate 8 is a maximum of 1.2 times greater than the distance A15 between the legs 15 in the area of ​​the end 3. Towards the other end 2, the distance A15 between the legs 15 decreases, so that the spring link 1 is trapezoidal in section in its longitudinal direction 7 or the legs 15 are oriented towards each other. Furthermore, recesses 18 are provided to reduce weight and / or so that splash water does not accumulate inside the hollow profile, which would promote corrosion due to standing water.

[0038] Furthermore, a reinforcement plate 19 with additional stiffening is provided. This can also be clearly seen in the cross-sectional view according to Figure 4 . According to the side view of Figure 3It can be seen again that the collar 17, which is bent downwards relative to the vertical direction, is only formed in the area of ​​the spring seat plate 8 for additional stiffening. Furthermore, the flange 16 is, according to the plan view of Figure 5 in the area of ​​the spring seat plate 8, so that a thermal joining seam 20 can be produced, as indicated, for example. The spring link is shown again in a sectional view along the section line AA of Figure 3 in Figure 4 shown.

[0039] Figure 6 shows an alternative embodiment of a spring link 1 according to the invention. Here, an effective line W is represented by the connection points 4, 5. This line runs through the respective centers M of the connection points 4, 5. The spring link 1 now has a downwardly oriented, curved profile in the vertical direction V. This ensures that the spring support surface 9 lies below the effective line W. Reference symbol:

[0040] 1 - spring link 2 - end to 1 3 - end to 1 4 - connection point to 2 5 - connection point to 3 6 - opening 7 - longitudinal direction to 1 8 - spring seat plate 9 - spring contact surface to 8 10 - bead 11 - receptacle 12 - helical compression spring 13 - coil to 12 14 - web 15 - leg 16 - flange 17 - collar 18 - recess 19 - reinforcement plate 20 - thermal joint seam A15 -Distance to 15 A15O -Distance above A15U -Distance below AD12 -Holding diameter D12 -Diameter M -Center point V -Vertical direction W -Line of action

Claims

1. Axle arrangement for a motor vehicle, having a spring link (1) and a spring seat plate (8), wherein the spring link (1) is formed as an elongated, shaped hollow profile with an open cross-section in a U-shape or C-shape or hat shape with two opposing legs (15) from a steel material, and has attachment points (4, 5) at each of its ends (2, 3), wherein the spring link (1) is arranged in the installed position with its opening (6) of the hollow profile pointing upwards, wherein the spring seat plate (8) for receiving a helical compression spring (12) is coupled to the spring link (1) on and / or partially in the opening (6), wherein a reinforcing plate (19) is coupled in and / or on the opening (6) of the hollow profile at least in some lengthwise sections in the longitudinal direction of the spring link (1), wherein a distance (A15) of the legs (15) from one another in the region of the spring seat plate (8) is equal to or smaller than a 1.2 times distance (A15) of the legs (15) from one another in the region of an end (2, 3) or an attachment point (4, 5), characterised in that the attachment points (4, 5) are configured as bearing eyes and rubber-metal bearings are arranged in the bearing eyes.

2. Axle arrangement according to claim 1, characterised in that the distance (A15) of the legs (15) in the region of the spring seat plate (8) is less than or equal to the distance (A15) of the legs (15) in the region of the end (2, 3) or the attachment point (4, 5).

3. Axle arrangement according to claim 2, characterised in that a distance (A15) of the legs (15) from one another in the region of the spring seat plate (8) corresponds to 0.5 times to 1.2 times, preferably 0.8 times to 1.1 times, the receiving diameter (AD12) on the spring seat plate (8), wherein the receiving diameter (AD12) is suitable for receiving a helical compression spring (12).

4. Axle arrangement according to any one of claims 1 to 3, characterised in that the distance (A15) of the legs (15) increases in the direction of the opening (6), in particular the legs (15) are oriented at an angle to one another.

5. Axle arrangement according to any one of claims 1 to 4, characterised in that the hollow profile in the region of the spring seat plate (8) has laterally projecting flanges (16) and / or collars (17).

6. Axle arrangement according to any one of claims 1 to 5, characterised in that the hollow profile is configured in its longitudinal direction (7) to taper in trapezoidal form at least in some length sections, in particular towards one end (2).

7. Axle arrangement according to any one of claims 1 to 6, characterised in that a connecting line through the attachment points (4, 5) forms a line of action (W), wherein the hollow profile has an arcuate course with respect to the line of action (W).

8. Axle arrangement according to claim 7, characterised in that the arcuate course is oriented below the line of action and / or that the spring seat plate (8) has a spring support surface (9) which lies below the line of action.

9. Axle arrangement according to any one of claims 1 to 8, characterised in that a wall thickness of the hollow profile is configured to be from 1.8 mm to 4.75 mm and a wall thickness (W8) of the spring seat plate (8) is configured to be greater than or equal to the wall thickness (W1) of the hollow profile.

10. Axle arrangement according to any one of claims 1 to 9, characterised in that the spring seat plate (8) has a bead (10) oriented upwards relative to a spring support surface (9) in relation to the installation position, such that the bead (10) engages on the inside in the helical compression spring (12).