Vibration damper and motor vehicle with active chassis

Abstract

The invention relates to a vibration damper (1) having a damper piston which can be moved back and forth in a main cylinder in an axial direction relative to the main cylinder by means of a hydraulic medium, the main cylinder being arranged in a container cylinder (5), an intermediate cylinder being arranged between the main cylinder and the container cylinder (5), the main cylinder, the intermediate cylinder and the container cylinder (5) are coaxially arranged in a three-cylinder damper (2), the damper piston is arranged at one end of the piston rod, and the three-cylinder damper (2) is equipped with a hydraulic end position damper and has a central valve block (12) with two damping valve devices (8, 9) at the end thereof facing away from the piston rod. In order to improve the vibration damper (1) in terms of function and / or manufacturing technology, the central valve block (12) is partially surrounded by an air spring which is supported on an axial support ring (15) which is connected to the container cylinder (5) and the central valve block (12) in a bonded manner by means of a single main weld, the three-cylinder damper (2) has a gas compensation volume at the piston rod-side end thereof, which gas compensation volume is arranged in the annular space between the intermediate cylinder and the container cylinder (5).

Description

Technical Field

[0001] The present invention relates to a vibration damper, which has a damper piston, which can move back and forth in a main cylinder in an axial direction relative to the main cylinder by means of a hydraulic medium, wherein the main cylinder is arranged in a container cylinder, wherein an intermediate cylinder is arranged between the main cylinder and the container cylinder, wherein the main cylinder, the intermediate cylinder and the container cylinder are coaxially arranged in a three-cylinder damper, wherein the damper piston is arranged at one end of a piston rod, wherein the three-cylinder damper is equipped with a hydraulic end position damping member and has a central valve block with two damping valve devices at its end facing away from the piston rod. Background Art

[0002] German publication DE 11 2012 003932T5 of international publication WO 2013 / 042569 A1 and German patent DE 10 2019 108 092 B4 disclose motor vehicle shock absorbers in which the valve block is welded to the outer cylinder. German publication DE 10 2015 209179A1 discloses a cylinder for a motor vehicle shock absorber, wherein a fastening sleeve for accommodating an outer housing of a valve is fixed to a connecting surface of the cylinder with a material fit. German publication DE 10025 399A1 discloses a motor vehicle shock absorber, wherein the valve housing is welded to a reservoir. German publication DE 10 2012 009 220 A1 discloses a motor vehicle shock absorber, wherein a spring receiving ring is fastened with a material fit to a cylinder section for defining an auxiliary volume. Summary of the invention

[0003] The object of the present invention is to improve a vibration damper according to the preamble of claim 1 with regard to its function and / or production technology.

[0004] A vibration damper having a damper piston which can be moved back and forth in a main cylinder by means of a hydraulic medium in an axial direction relative to the main cylinder, wherein the main cylinder is arranged in a container cylinder, wherein an intermediate cylinder is arranged between the main cylinder and the container cylinder, wherein the main cylinder, the intermediate cylinder and the container cylinder are arranged coaxially in a three-cylinder damper, wherein the damper piston is arranged at one end of a piston rod, wherein the three-cylinder damper is equipped with a hydraulic end position damping element and has a central valve block with two damping valve devices at its end facing away from the piston rod. In the above vibration damper, the object is achieved in that the central valve block is partially surrounded by an air spring, which is supported on an axial support ring, which is connected to the container cylinder and the central valve block by a single main weld material fit, wherein the three-cylinder damper has a gas compensation volume at its end on the piston rod side, which is arranged in the annular space between the intermediate cylinder and the container cylinder. Thus, on the one hand, a vibration damper or shock absorber is provided, which enables a very comfortable operation of a motor vehicle equipped with the vibration damper or shock absorber both at high and low frequencies. Here, the structural space conflict caused by the combination of gas compensation volume and air spring on the three-tube damper is well resolved. At the piston-side end of the three-tube damper, the annular space between the intermediate tube and the container tube is effectively used to accommodate the gas compensation volume. The gas compensation volume is advantageously formed by an air bag, which contains a gas, such as air and is also called an air bag. The air bag is made of an airtight flexible material. The air bag or air bag is located between the intermediate tube and the container tube and is connected to the bayonet valve. During the operation of the vibration damper, the air bag ensures the separation between oil and gas. In addition, the air bag prevents oil from foaming. At the end of the three-tube damper facing away from the piston rod, a sufficiently large air volume can be provided for the air spring by partially surrounding the central valve block. Here, the resulting disadvantages of connecting the hydraulic line to the central valve block are deliberately taken into account. Advantageously, the two damping valve devices each include a non-return valve. One of the damping valve devices also includes a return valve. The other damping valve device advantageously includes a compression valve in addition to the non-return valve. The central valve block is preferably embodied as a milled part. By means of the main weld seam, the air spring can be stably supported axially on the lower end of the container barrel and the central valve block in a simple manner.

[0005] A preferred embodiment of the vibration damper is characterized in that the axial support ring has a rectangular annular cross section. As a result, the application of the weld seams to the axial support ring, the container barrel and the central valve block is significantly simplified.

[0006] Another preferred embodiment of the vibration damper is characterized in that the axial support ring is combined with a support sleeve which surrounds the container tube on the outside. As a result, on the one hand, the stability of the container tube is increased at this end by the axial support ring. In addition, in the installed state, the support sleeve allows a particularly simple formation of a tension protection for the air spring supported on the axial support ring.

[0007] Another preferred embodiment of the vibration damper is characterized in that the support sleeve has a chamfer on the outside at the end facing away from the axial support ring. This simplifies the assembly and fastening of the air spring.

[0008] Another preferred embodiment of the vibration damper is characterized in that the support sleeve is combined with an adapter, which is used to form an axial tension protection for the air spring mounted on the axial support ring. This significantly simplifies the assembly of the air spring.

[0009] Another preferred embodiment of the vibration damper is characterized in that the air spring has an air spring housing, which is fixed to the adapter in the axial direction by a snap-on or snap-lock connection. The snap-on or snap-lock hook for forming the snap-on or snap-lock connection is advantageously arranged on the air spring housing, in particular on the housing bottom of the air spring housing. The air spring housing and the adapter are advantageously made of plastic material. This allows cost-effective mass production, for example by injection molding.

[0010] Another preferred embodiment of the vibration damper is characterized in that the main weld seam is arranged on the annular surface of the axial support ring facing the central valve block. Thus, the welding of the axial support ring with the container barrel and the central valve block is simplified.

[0011] Another preferred embodiment of the vibration damper is characterized in that the main weld seam is arranged on the outer circumferential surface of the base block of the central valve block. The base block is, for example, in the form of a right cylindrical body. Advantageously, the main weld seam extends completely around the container barrel on the outside. Thus, a very stable fastening of the axial support ring on the container barrel and the central valve block is ensured in a simple manner.

[0012] The invention also relates to a motor vehicle having an active chassis comprising at least one vibration damper as described above. The claimed motor vehicle advantageously comprises a front axle and a rear axle, each of which is equipped with a motor-pump unit and two vibration dampers.

[0013] The present invention also relates to a container barrel, an intermediate barrel, a main barrel, a central valve block, an axial support ring, a support sleeve and / or an adapter for the above-mentioned vibration damper. The mentioned components can be purchased separately. BRIEF DESCRIPTION OF THE DRAWINGS

[0014] Further advantages, features and details of the invention emerge from the following description, which describes in detail individual exemplary embodiments with reference to the accompanying drawings. In the drawings:

[0015] Figure 1 A perspective view of a spring strut with a three-cartridge damper is shown;

[0016] Figure 2 A schematic cross-sectional view shows Figure 1 Three-tube damper;

[0017] Figure 3 The longitudinal section diagram shows Figure 1 A three-tube damper, wherein the container tube of the three-tube damper is not cut away and displayed;

[0018] Figure 4 shows a perspective view of a vibration damper having a three-cartridge damper which is surrounded by an air spring at the end facing the front axle;

[0019] Figure 5 A vibration damper with a three-tube damper assigned to a rear axle of a motor vehicle is shown; and

[0020] Figure 6 Shows Figure 3 An enlarged portion of the image, half of which is a longitudinal section. DETAILED DESCRIPTION

[0021] Figures 1 to 3 A spring strut 10 with a spring fork 11 is shown in different views. The spring strut 10 comprises a vibration damper 1 , which is also referred to as a shock absorber. The vibration damper 1 is designed as a three-tube damper 2 with a main tube 3 , an intermediate tube 4 and a reservoir tube 5 .

[0022] The spring strut 10 with the vibration damper 1 designed as a three-cartridge damper 2 is part of a hydraulic system which is used in a motor vehicle to form an active damping control device during operation of the motor vehicle. The motor vehicle preferably comprises four wheels, each of which is assigned a vibration damper 1 designed as a three-cartridge damper 2. A three-cartridge damper or vibration damper is also referred to as a damper for short. In an active chassis of a motor vehicle, the hydraulic damper forms a shock absorber.

[0023] The three-tube damper 2 is operated with a hydraulic medium. The hydraulic medium is preferably a hydraulic liquid, which is also referred to as hydraulic oil or simply as oil. In addition to the hydraulic damper volume, the hydraulic damper also comprises a gas compensation volume 21 .

[0024] The active damping adjustment device comprises a hydraulic actuator, which is hydraulically connected to the damper via a hydraulic line. The hydraulic actuator is used in the active chassis of the motor vehicle for targeted actuation or control of the hydraulic damper. For this purpose, the hydraulic actuator advantageously comprises a separate hydraulic pump for each damper. In each axle of the motor vehicle, two hydraulic pumps can be combined in a motor-pump unit. The hydraulic pumps assigned to the respective axle can advantageously be controlled individually via a common control unit.

[0025] exist Figure 2 In the embodiment, the damper piston 6 is guided in the main cylinder 3 of the three-cylinder damper 2 so as to be able to move back and forth downward and upward. A piston rod 7 is led out from the damper piston 6. Figure 2 The piston rod 7 extends upward through the sealing guide unit 32 and out of the three-tube damper 2. Figure 2 The upper end, not shown, is connected to the load-bearing structure of the motor vehicle.

[0026] The main cylinder 3, the intermediate cylinder 4 and the container cylinder 5 are arranged coaxially and have a gap in the radial direction. The annular space between the main cylinder 3 and the intermediate cylinder 4 can be used to allow the hydraulic medium to pass through, especially to return the hydraulic medium downward without the need for additional hydraulic lines. The annular space between the intermediate cylinder 4 and the container cylinder 5 is advantageously used to accommodate the gas compensation volume 21.

[0027] The gas compensation volume 21 is formed by a gas bag 22, which is formed at the piston rod-side end of the triple-tube damper 2, i.e. at Figure 2 The upper portion is accommodated between the intermediate cylinder 4 and the container cylinder 5. Radially inside the gas compensation volume 21, the piston rod 7 is surrounded in the main cylinder 3 by the hydraulic end position damping element 19 and the hydraulic extension stop 39.

[0028] In the main tube Figure 2 At the lower end, the three-cartridge damper 2 is equipped with a central valve block 12. Two damping valve devices 8 and 9 are integrated in the central valve block 12. The damping valve devices 8 and 9 each include a non-return valve.

[0029] Furthermore, the damping valve arrangement 8 comprises a restoring valve which is hydraulically connected via an annular gap 71 to the gap between the main cylinder 3 and the intermediate cylinder 4, which gap is designed as an annular space. Figure 2 The bottom is connected to the compression valve in the damping valve device 9 via a relatively large, centrally located through-opening 72 .

[0030] The central valve block 12 comprises a base block 13 , which is implemented as a solid cylinder, for example. The base block 13 is configured as a right cylindrical outer surface, for example. For example, the base block 13 is implemented as a milled part and is fastened at the lower end of the three-tube damper 2 .

[0031] The central valve block 12 further comprises two damping valve blocks 16, 17, which are substantially in the form of upright cylinders. The two damping valve blocks 16, 17 can be connected integrally to the base block 13. The damping valve blocks 16, 17 are used to accommodate and / or form the damping valve devices 8 and 9. The two damping valve blocks 16, 17 are arranged coaxially with each other and transversely to the longitudinal axis of the three-cartridge damper 2.

[0032] The central valve block 12 further comprises a connecting valve block 18. The connecting valve block 18 is implemented as a separate component and is fastened to the base block 13. In order to fasten the connecting valve block 18 to the base block 13 of the central valve block 12, two bolts 73, 74 are used, for example.

[0033] The design of the connecting valve block 18 as a separate component offers the advantage, in particular, that a packaging-dependent design of the vibration damper can be achieved with relatively little design effort, in particular in the case of installation in different motor vehicle variants or motor vehicle derivatives. Furthermore, the separate connecting valve block 18 can be designed and arranged on the base block 13 in such a way that the specific crash requirements for a motor vehicle equipped with the vibration damper 1 can be optimally met.

[0034] The positioning of the hydraulic connections 23, 24 is particularly important for the packaging-dependent design of the connecting valve block 18. The hydraulic connections 23, 24 on the connecting valve block 18 are used to connect the hydraulic lines 27, 28, such as in particular Figure 4 and Figure 5 As can be seen in FIG. Via hydraulic lines 27, 28, the three-tube damper 2 can be actively hydraulically actuated. For this purpose, the hydraulic lines 27, 28 are hydraulically connected to an active damping adjustment device 29, which is Figure 4 It is only shown by a rectangle.

[0035] exist Figure 4 and Figure 5 3 shows in perspective how a triple-cartridge damper 2 with a central valve block 12 can be designed at its lower end in a manner specific to the installation space, in particular when installed in a motor vehicle 30 with an active chassis 31 .

[0036] exist Figure 4 and Figure 5 Only with the help of Figure 4 The different parts 43 to 46 and Figure 5 The motor vehicle 30 shown in the various components 47 to 49, 53 to 56 in the drawings places high demands on the designer, especially because the hoses and lines, especially the hydraulic lines 27, 28, require sufficient free space with the surrounding components throughout the entire spring travel and steering travel during operation of the motor vehicle 30. In addition, the resulting bending radii and stretch lengths must be taken into account.

[0037] Additional design effort results from the fact that the vibration damper 1 designed as a three-tube damper 2 is also combined with an air spring 20, as in Figure 3 The air spring 20 is advantageously designed and arranged such that it surrounds the central valve block 12 starting from the lower end of the triple-cartridge damper 2. This maximizes the air spring space that can be formed with the air spring 20. Due to the larger volume, the air spring 20 can advantageously be designed to be softer. Furthermore, packaging advantages result from the design and arrangement of the air spring 20 on and around the central valve block 12.

[0038] The air spring 20 comprises an air spring housing 50, which has an upper housing part 51 and a lower housing part 52. The air spring housing 50 comprises a single, relatively large air volume. The air spring housing 50 extends around the lower end of the three-cartridge damper 2 having the central valve block 12. In the axial direction, the air spring housing 50 is arranged between the bellows 58 and the central valve block 12, which is partially surrounded by the lower housing part 52.

[0039] The air spring housing 50 is supported with its housing lower part 52 on the axial support ring 15, which is fastened to the lower end of the three-tube damper 2. The axial support ring 15 is combined with an adapter 14, which enables the air spring housing 50 to be fastened to the outside of the container tube 5 of the three-tube damper 2. The fastening of the air spring housing 50 to the adapter 14 is achieved, for example, by a snap connection or a latch connection.

[0040] like Figure 4 2 shows how the air spring housing 50 of the air spring 20 surrounds the central valve block 12 so that the connecting valve block 18 remains free. Figure 4 In FIG. 4 , the three-tube damper 2 is assigned to the front axle of the motor vehicle 30 . Component 43 is the brake air supply. Component 44 is the lower transverse control arm. Component 45 is the steering tie rod. Component 46 is the cardan shaft.

[0041] like Figure 4 1 shows how the air spring volume of the air spring 20 extends around the connecting valve block 18. Thus, the maximum air spring volume can be formed using the air spring housing 50. In addition, Figure 4 As shown, the connecting valve block 18 is designed so that, on the one hand, the connection of the hydraulic lines 27, 28 to the central valve block 12 is simplified. Furthermore, the locking screws 41, 42 of the shutoff valves 25, 26 integrated in the connecting valve block 18 are still accessible even when the air spring 20 is installed.

[0042] exist Figure 5In FIG. 3 , a three-tube damper 2 is assigned to the rear axle of a motor vehicle 30. Component 47 is a further hydraulic circuit. Component 48 is a brake caliper. Component 49 is a lower transverse link. Component 53 is a transverse link cover. Component 54 is a bracket with brake circuits. Component 55 is an upper transverse link. Component 56 is a wheel carrier.

[0043] like Figure 5 As shown, the connecting valve block 18 is designed in a targeted manner so that there is sufficient free space with the wheel carrier 56 during the entire spring travel and steering travel. In addition, the connecting valve block 18 and the hydraulic lines 27, 28 and the further hydraulic line 47 are designed so that there is sufficient free space with the brake periphery during the entire spring travel and steering travel.

[0044] Figure 6 Shown Figure 3 A partial view of the , half of which is a longitudinal section. Figure 6 As shown in the cross-sectional view, a small section of the base block 13 of the central valve block 12 is Figure 6 The end portion located at the top is arranged inside the container barrel 5. For this reason, the base block can be designed accordingly. Therefore, the positioning of the central valve block 12 relative to the container barrel 5 is simplified.

[0045] In the container 5 Figure 6 At the lower end, the axial support ring 15 is welded simultaneously to the container barrel 5 and the central valve block 12, in particular to the base block 13 of the central valve block 12, by means of a circumferential main weld seam 60. The main weld seam 60 thus connects the three components in a materially bonded manner.

[0046] The axial support ring 15 is combined with a support sleeve 61. The support sleeve 61 surrounds the container barrel 5 above the axial support ring 15. The support sleeve 61 is firmly connected to the container barrel 5. On the one hand, the support sleeve 61 is used to increase the stability of the container barrel 5 on its Figure 6 The stability at the lower end.

[0047] Furthermore, the support sleeve 61 serves to fasten the adapter 64 to the container sleeve 5. The adapter 64 serves to provide a tension protection for the air spring when the air spring housing 50 is placed on the axial support ring 15. The chamfer 62 simplifies the assembly of the adapter 64.

Claims

1. A vibration damper (1), comprising a damper piston (6), which can be moved back and forth in a main cylinder (3) by means of a hydraulic medium in an axial direction relative to the main cylinder (3), wherein: The main cylinder (3) is arranged in a container cylinder (5), wherein an intermediate cylinder (4) is arranged between the main cylinder (3) and the container cylinder (5), wherein the main cylinder (3), the intermediate cylinder (4) and the container cylinder (5) are coaxially arranged in a three-cylinder damper (2), wherein the damper piston (6) is arranged at one end of a piston rod (7), wherein the three-cylinder damper (2) is equipped with a hydraulic end position damping member (19) and has two damping valve devices (8, 9) at its end facing away from the piston rod (7). ), characterized in that the central valve block (12) is partially surrounded by an air spring (20), which is supported on an axial support ring (15), and the axial support ring is connected to the container tube (5) and the central valve block (12) by material fit via a single main weld (60), wherein the three-tube damper (2) has a gas compensation volume (21) at its end on the piston rod side, and the gas compensation volume is arranged in the annular space between the intermediate tube (4) and the container tube (5).

2. The vibration damper according to claim 1, characterized in that The axial support ring (15) has a rectangular annular cross section.

3. A vibration damper according to any one of the preceding claims, characterised in that The axial support ring (15) is combined with a support sleeve (61) which surrounds the container sleeve (5) on the outside.

4. The vibration damper according to claim 3, characterized in that The support sleeve (61) has a chamfer (62) on the outside at the end facing away from the axial support ring (15).

5. The vibration damper according to claim 3 or 4, characterized in that: The supporting sleeve (61) is combined with an adapter (64), and the adapter is used to form an axial tensile protection for the air spring (20) sleeved on the axial supporting ring (15).

6. The vibration damper according to claim 5, characterized in that The air spring (20) has an air spring housing (50) which is fixed to the adapter (64) in the axial direction by means of a snap connection or a latch connection.

7. A vibration damper according to any one of the preceding claims, characterised in that The main weld seam (60) is arranged on the annular surface of the axial support ring (15) facing the central valve block (12).

8. A vibration damper according to any one of the preceding claims, characterised in that The main weld (60) is arranged on the outer circumferential surface of the base block (13) of the central valve block (12).

9. A motor vehicle (30) having an active chassis (31) comprising at least one vibration damper (1) according to any one of the preceding claims.

10. A container cylinder (5), an intermediate cylinder (4), a main cylinder (3), a central valve block (12), an axial support ring (15), a support sleeve (61) and / or an adapter (64) for a vibration damper (1) according to any one of claims 1 to 8.

Images