Hydraulic and pneumatic elastic support device for vehicles

Abstract

The present invention relates to a hydraulic-pneumatic elastic support device for a vehicle, in particular a rail vehicle, comprising a hydraulic cylinder assembly, a first spring section and a second spring section, wherein the hydraulic cylinder assembly has a hydraulic cylinder and a cylinder piston capable of reciprocating in the hydraulic cylinder, the first spring section is arranged at one of the two longitudinal ends of the hydraulic cylinder assembly, and the second spring section is arranged at the other of the two longitudinal ends of the hydraulic cylinder assembly, wherein the corresponding longitudinal ends of the hydraulic cylinder assembly and the associated spring sections are respectively designed so that they form an arc shape that arches inward toward the hydraulic cylinder assembly.

Description

Technical Field

[0001] The invention relates to a hydraulic-pneumatic elastic support device for a vehicle, in particular a rail vehicle, and a (railway) vehicle provided with the elastic support device. Background Art

[0002] Virtually all modern rail vehicles are equipped with air springs, since low vertical stiffness is required for comfort reasons, which in turn leads to level control. In addition, pneumatic brakes are usually installed, whereas wipers and doors are now mostly purely electric. For decades, automobile manufacturers have tried to do away with expensive compressed air supply, but a reasonable alternative to air suspension has not yet been found.

[0003] Every attempt to replace the air springs with a hydropneumatic spring support leads to a very expensive and complex mechanical solution, since, in addition to the purely vertical spring support, transverse spring support, longitudinal movements and rotations about all axes must also be implemented.

[0004] Therefore, the approach of simply replacing air springs has proven to be unsuccessful.

[0005] A device is known from the prior art, which is provided with a hydropneumatic elastic support in series with a rolling support (WO 2013 / 189999 A1). The advantage that can be derived from this prior art is that by selecting the form of the rolling support, practically any lateral characteristics can be produced, which can be linear, for example increasing, or also decreasing.

[0006] However, this solution known from the prior art also has disadvantages. In particular, the required rolling elements are mounted on the hydraulic cylinder via rolling bearings, which requires expensive and difficult implementation and additionally increases the risk of the bearings seizing when contaminated. Summary of the invention

[0007] Therefore, the object of the present invention is to provide a hydraulic-pneumatic elastic support device for a vehicle, which partially or completely overcomes the above-mentioned disadvantages, thereby realizing an improved elastic support device for a vehicle, in particular a rail vehicle. This is achieved by the elastic support device of the first aspect of the present invention. Here, advantageous design solutions are given in various embodiments.

[0008] The provision of a hydropneumatic elastic support is particularly advantageous when providing an integrated solution together with the chassis concept of the vehicle, since all the advantages and advantageous properties of the hydropneumatic elastic support additionally reduce the complexity of the chassis and overcome the disadvantages known from the prior art.

[0009] The invention describes a hydropneumatic spring system which replaces the two air springs of the chassis by means of spring struts. In addition, in an advantageous embodiment, an emergency spring support and a longitudinal driver are integrated, the transverse rigidity of which can be designed in virtually any linear manner and is suitable for all vehicle types, including vehicles with tilting technology. The invention thus opens the way to the development of "airless" trains which no longer require a compressed air supply and therefore have a smaller, lighter and more favorable chassis.

[0010] Here, according to the present invention, a hydraulic-pneumatic elastic support device for a vehicle, in particular a rail vehicle, comprises a hydraulic cylinder assembly, a first spring section, and a second spring section, wherein the hydraulic cylinder assembly has a hydraulic cylinder and a cylinder piston capable of reciprocating in the hydraulic cylinder, the first spring section is arranged at one of the two longitudinal ends of the hydraulic cylinder assembly, and the second spring section is arranged at the other of the two longitudinal ends of the hydraulic cylinder assembly, wherein the respective longitudinal ends of the hydraulic cylinder assembly and the associated spring sections are respectively designed so that they form an arc shape that arches inward toward the hydraulic cylinder assembly.

[0011] Here, the distal end regions of the first elastic section and the second spring section are arched toward the hydraulic cylinder assembly. In order to achieve the desired elastic support effect, the hydropneumatic elastic support device preferably rests with its arched end region on a correspondingly arched contact piece of the component to be elastically supported. If the elements to be elastically supported against each other are offset transversely to the longitudinal direction of the hydraulic assembly, the arcuate shape ensures a certain amount of play without significantly deteriorating the vertical damping properties.

[0012] According to an advantageous variant of the invention, the arc shape can be a circular arc shape preferably having its bottom or high point toward the longitudinal axis of the hydraulic cylinder assembly. Typically, the arc shape extends in the cross section of the elastic support device, thereby enabling a lateral offset of the elastic support device.

[0013] In addition, it can be provided that the hydraulic cylinder and the cylinder piston are respectively rigidly connected to a fixed disk, on which corresponding spring sections are arranged, wherein each fixed disk preferably has an arc shape (for example, a circular arc shape) in a cross section that descends inward toward the longitudinal axis of the hydraulic cylinder assembly, so that the arc shape has a position with the smallest spacing near the longitudinal axis of the hydraulic cylinder assembly or on the longitudinal axis of the hydraulic cylinder assembly.

[0014] Furthermore, according to the invention, the spring section can be a layered spring section (e.g. a rubber laminated leaf spring) which preferably has a plurality of layers arranged side by side, so that the plurality of layers are arranged perpendicularly to the longitudinal axis of the hydraulic component in order to achieve a high vertical compressive stiffness. In this case, a plurality of layered spring sections are arranged side by side on the fixing plate in a transverse direction. In this case, the individual layered spring sections arranged side by side are adjacent to each other.

[0015] Furthermore, according to an advantageous embodiment, a pressure accumulator, for example in the form of a bladder accumulator, a diaphragm accumulator or a spring accumulator, can be provided, which is connected to the chamber of the hydraulic cylinder assembly which can be compressed by the cylinder piston via a connecting passage, wherein the connecting passage preferably has a large passage cross section, thereby generating no or only a minimal buffering effect.

[0016] A pressure accumulator can be connected via a hydraulic cylinder and a chamber that can be compressed by the cylinder piston, which pressure accumulator influences the vertical damping properties of the elastic support depending on the pressure introduced into the chamber. In this case, the passage cross section of the passage to the pressure accumulator is dimensioned to be large enough to design the resulting damping effect to be negligibly small.

[0017] Furthermore, partitions or valves may be arranged in the connecting passages in order to passively or actively influence the vertical damping characteristics.

[0018] If, for example, a harder vertical damping behavior is desired, this can be achieved by reducing the passage cross section of the connecting passage, since only a very small amount of fluid can leave the piston chamber here when a force acts on the hydraulic cylinder.

[0019] According to an optional improvement of the present invention, it can be provided that the elastic support device also includes an inner cylinder piston in the hydraulic cylinder, which inner cylinder piston can be controlled by a separate fluid passage and is designed to change the size of the chamber of the hydraulic cylinder assembly that can be compressed by the cylinder piston, wherein the inner cylinder piston is preferably arranged between the bottom of the hydraulic cylinder and the end of the cylinder piston inserted into the hydraulic cylinder, and the separate fluid passage extends through the bottom of the hydraulic cylinder.

[0020] By providing an inner cylinder piston, the cylinder piston extending from the hydraulic cylinder can be moved out in a simple manner without having to abandon the damping properties for this purpose. The inner cylinder piston, which is usually arranged near the bottom of the hydraulic cylinder, can be moved away from the bottom of the hydraulic cylinder via a separate fluid passage, which leads to the cylinder piston being pushed out due to the constant pressure level existing in the compressible piston chamber of the cylinder piston. In this way, the height level of the components that are to be elastically supported against each other by the elastic support can be changed.

[0021] This is particularly advantageous in rail vehicles when the wheels have already experienced a certain amount of wear which results in a loss of height. Height compensation can then be achieved relatively simply by raising the inner cylinder piston, thereby enabling a constant height of the carriage which is elastically supported on the chassis.

[0022] According to an optional improvement of the present invention, it may be provided that the elastic support device is further provided with a hydraulic power unit so as to provide hydraulic fluid to the hydraulic cylinder assembly under a certain pressure, wherein the hydraulic power unit is preferably arranged on the hydraulic cylinder assembly.

[0023] Such a hydraulic power unit can be used in particular for changing the position of the inner cylinder, ie for level adjustment of the damping achieved by means of an elastic support.

[0024] The invention also relates to a vehicle, in particular a rail vehicle, comprising a car body and a chassis unit, wherein the car body is supported on the chassis unit via an elastic support system. The vehicle is characterized in that the elastic support system has a hydropneumatic elastic support device according to any of the above-mentioned solutions, which makes the car body located at the top contact with one of the two spring sections and makes the chassis unit arranged below the elastic support device contact with the other spring section.

[0025] In this case, it can be provided that the hydropneumatic spring support in the vehicle is oriented in such a way that the layered spring sections are arranged next to one another in the transverse direction of the vehicle.

[0026] Furthermore, it can be provided that the arc-shaped shape appears in a transverse section view of the vehicle.

[0027] According to an improved scheme of the present invention, it can be provided that the spring section pointing to the car body (i.e., the upper spring section) includes a plurality of spring section units spaced apart from each other in the longitudinal direction of the vehicle and the spring section pointing to the chassis unit (i.e., the lower spring section) preferably includes a plurality of spring section units spaced apart from each other in the longitudinal direction of the vehicle.

[0028] Thus, not only a single upper and / or lower spring section but also a plurality of upper and / or lower spring sections can be provided which are arranged offset with respect to one another in the longitudinal direction of the vehicle.

[0029] Furthermore, according to the invention, provision can be made for the elastic support to be arranged in the height of the vehicle in such a way that the lower spring section, ie, the spring section associated with the chassis unit, is located in the pitch center of the chassis.

[0030] This is advantageous for stabilizing the vehicle, since only the upper part of the spring support which is not arranged in the pitch center of the vehicle has to be provided with corresponding damping measures for counteracting the pitch, thereby achieving an overall less complex structure of the spring support.

[0031] Furthermore, according to a preferred modification of the invention, it can be provided that the upper spring section, ie the spring section associated with the car body, is supported directly on the car body, on a crossbeam or on a yoke which serves to integrate an emergency spring support.

[0032] It can also be provided that a conical spring, preferably made of rubber, is arranged between the hydraulic cylinder and the lower spring section in order to realize an emergency elastic support.

[0033] Furthermore, according to the invention, provision can be made for at least two, preferably four, conical springs to be arranged above the upper spring section, in series with the elastic support system, between the crossbeam or the car body and a yoke cooperating with the spring system, in order to realize an emergency elastic support device, wherein at least two conical springs are preferably arranged offset to one another in the longitudinal or transverse direction of the vehicle.

[0034] Furthermore, it can be provided according to the invention that a conical spring is provided as an emergency elastic support at the outer edge between the cross member and the car body and / or that an elastic cross member connected in series with a hydropneumatic elastic support is used as an emergency elastic support.

[0035] According to an improved solution of the invention, it can be provided that the spring section arranged at the top is in contact with the yoke, for which purpose the hydropneumatic elastic support device has a certain gap in the longitudinal direction of the vehicle, and the upper component of the elastic support device, the so-called bell-shaped piece, has at least one longitudinal damper, in particular in the form of a rubber spring with an internal stop, between the bell-shaped piece and the yoke connected to the car body to produce progressive longitudinal damping characteristics, wherein the yoke preferably surrounds the bell-shaped piece in a hood-like manner in the longitudinal direction of the vehicle.

[0036] Furthermore, the chassis unit can have stops for limiting the longitudinal movement of the hydraulic cylinder and the bell in order to transmit large impact forces in the longitudinal direction of the vehicle.

[0037] Furthermore, the hydraulic power unit can be arranged separately in the chassis unit or in the carriage. The advantage of being arranged in the carriage is that the hydraulic power unit can thus provide energy to each chassis unit connected to the carriage. Thus, in the case of a rail vehicle, usually at least two chassis units are connected to the carriage.

[0038] In addition, the vehicle can be provided with a generator which generates electrical energy from the pressure changes in the hydraulic cylinder assembly, wherein this energy is preferably used to supply the hydraulic power unit. This makes it possible, for example, for the hydraulic power unit to be self-sufficient with respect to the energy supply of the vehicle, since its entire energy requirement is covered by the generator. BRIEF DESCRIPTION OF THE DRAWINGS

[0039] Other features, details and advantages of the present invention can be obtained by referring to the following description of the accompanying drawings. In the accompanying drawings:

[0040] Figure 1 A cross-sectional view showing a hydropneumatic elastic support device in a lateral deflection state,

[0041] Figure 2 A transverse sectional view of a rail vehicle having a hydropneumatic elastic support device according to the invention is shown,

[0042] Figure 3 A total of six different variants of emergency spring supports for implementing a hydropneumatic spring support according to the invention are shown.

[0043] Figure 4 A longitudinal section showing a variant of the invention of a hydropneumatically elastic support in a vehicle, and

[0044] Figure 5 A cross-sectional view through a hydraulic cylinder assembly is shown, which includes an inner cylinder disposed between a cylinder piston and a hydraulic cylinder bottom for fluid level regulation. DETAILED DESCRIPTION

[0045] Figure 1 A cross-sectional view of a hydraulic-pneumatic elastic support device 1 in a transversely deflected state is shown, so that the longitudinal direction of the elastic support device 1 protrudes from the plane of the drawing. The elastic support device 1 comprises a hydraulic cylinder assembly 2, which has a hydraulic cylinder 3 and a cylinder piston 4 capable of reciprocating in the hydraulic cylinder. The piston chamber 10 (i.e., the chamber in the hydraulic cylinder 3 that can be compressed by the cylinder piston) is connected to the pressure accumulator 9 (in the Figure 1 ) is connected so that the desired damping characteristics are produced when a vertical force acts which causes the hydraulic cylinder 4 to be pushed in.

[0046] Both the hydraulic cylinder 3 and the cylinder piston 4 have, on their respective distal sections, a fixing disk 7 on which the spring sections 5 , 6 are arranged.

[0047] In the transverse section shown, the fixing plate 7 has an arc shape that rises outward from the longitudinal center axis of the hydraulic cylinder assembly 2. Here, on the fixing plate 7, on the side facing away from the hydraulic cylinder assembly 2, the corresponding spring sections 5, 6 are arranged respectively, which have a plurality of layers 8 that are offset from each other in the transverse direction. The layers arranged adjacent to each other in the transverse direction are movable in the case of transverse offset, but at the same time rigid in the vertical direction.

[0048] exist Figure 1 In the embodiment, the elastic support device 1 is laterally deflected by a length A. Figure 1 , the elastic support device 1 without transverse deflection is still partially drawn in order to better illustrate the elastic support device without deflection. Here, the arc-shaped ends of the respective spring segments 5 and 6 facing away from the hydraulic cylinder assembly 2 cooperate with the correspondingly shaped spring segment fittings 32, which have a convex shape extending toward the elastic support device when viewed in cross section and are connected to the corresponding distal areas of the spring segments 5 and 6. Here, the spring segment fittings 32 are rigid and do not have elastic properties, and their main task is to provide a connection between the spring and the element to be elastically supported.

[0049] Furthermore, in the case of the transverse deflection of the spring support 1 shown, the resulting deformation of the individual layers of the spring sections 5, 6 can be seen. This can be clearly seen, for example, in the lower spring section 6, because there the layer 8 arranged on the left is shown to be stretched and the layer 8 arranged on the right is shown to be compressed. Nevertheless, even in the case of a transverse deflection, vertical damping can in principle be achieved by the spring support.

[0050] Figure 2 A transverse section through a rail vehicle 15 with a hydropneumatic elastic support according to the invention is shown. It can be seen that the chassis 17 is elastically supported relative to the car body 16 by means of the elastic support 1. In this case, the spring strut 1 is arranged in the middle of the chassis 17. The actual hydraulic cylinder assembly 2 is arranged between two lamellar spring sections 5, 6. In this case, more than one upper lamellar spring section 5 can be provided, which are thus arranged offset in the longitudinal direction. Both the upper section 5 and the lower section 6 are designed as arcs, wherein the outer surfaces of the sections 5, 6 protruding from the hydraulic cylinder assembly 2 are formed to be concave relative to the hydraulic cylinder assembly 2. Any lateral rigidity can be achieved by correspondingly selecting the radius and shear rigidity of the sections 5, 6. The vertical rigidity is determined by the diameter of the piston 4 and the volume of the spring accumulator 9.

[0051] The other functions for the elastic support of the car body 16 are largely identical to those of the classic chassis 17 known from the prior art. Thus, a roll stabilizer 27, a progressive transverse elastic support 26 in the form of a rubber damper or transverse elastic roller, a transverse damper 25 and a vertical damper 24 are provided. The transverse damper 25 can generally be designed as a semi-active damper, an active transverse elastic support, an actuator for a hold-off device (a system for limiting the transverse displacement during driving through a bend, thereby preventing uncomfortable contact with a stop) or as a tilt actuator.

[0052] The vertical dampers 24 are advantageously implemented as linked or semi-active. In order to reduce or eliminate the negative influence of the friction of the piston, the two vertical dampers are controlled in a linked or semi-active manner so that they only damp the rolling movement, because the vertical damping is already achieved by friction. In addition, the vertical rigidity of the elastic support device 1 can be reduced to additionally reduce the influence of friction. By a corresponding design of the kinematics of the roll stabilizer 27 (the tilted state of the rod leads to the creation of a virtual rotation point in the area of ​​the center of gravity of the car body), a corresponding selection of the radii of the upper and lower lamellar spring sections 5, 6 and the optional use of an actuator instead of the lateral damper 25, roll compensation or fully active tilting can be achieved with the aid of the elastic support device 1 according to the invention.

[0053] The damping of the vertical movement can additionally be adjusted by selecting the passage cross section of the connection 11 from the hydraulic cylinder 3 to the spring accumulator 9 and / or the additional valve or a throttle in the connecting passage 11. The active adjustment of the damping valve is likewise variable.

[0054] In addition to the chassis unit 17 and the carriage 16 arranged thereon, Figure 2 In the figure, the elastic support device 1 arranged between them can be seen, which together with other stabilizing structures (e.g., roll stabilizer 27, lateral buffer 25, vertical buffer 24, etc.) realizes the entire spring system for vehicle 15. The wheel set 31 rolling on the guide rail 33 is connected to the chassis unit 17 via the wheel set guide 30 and the main buffer 29 and the main elastic support device 28, which only damp or elastically support the wheel 31 rolling on the guide rail 33.

[0055] The elastic support device 1 according to the invention is provided for vertical damping of a chassis unit 17 and a carriage 16 arranged thereon, the elastic support device 1 being directed with its upper spring section 5 toward the carriage 16 and with its lower spring section 6 toward the chassis unit 17. Figure 2In a simple embodiment shown, the upper spring section 5 is in direct contact with the car body 16 or the cross member 18 of the car body 16, while the lower spring section 6 is in direct contact with the chassis unit 17. However, it is clear to a person skilled in the art that one or more elements can also be inserted between the car body 16 or the chassis unit 17 and the respective spring section 5, 6 without losing the essential advantages of the invention.

[0056] In the event of failure of the hydraulic-pneumatic elastic support device 1, a so-called emergency elastic support device is required, which allows the vehicle to operate safely even if the hydraulic-pneumatic elastic support device 1 fails. The emergency elastic support device can be installed in series or in parallel with the elastic support device 1 according to the present invention.

[0057] Figure 3 Different possible design variants of the emergency spring support are shown, wherein the variants “c” and “f” are considered to be particularly advantageous in combination with the spring support 1 according to the invention.

[0058] Variant “a” does not have an emergency spring, but instead only shows that the elastic support device 1 is directly connected to the crossbeam 18 for fixing to the carriage 16 .

[0059] In a possible embodiment of the emergency spring shown in variant "b", the conical spring 20 is integrated in the cylinder piston 4. If the hydropneumatic elastic support 1 fails, for example because it has a leak, the cylinder piston 4 drops to the hydraulic cylinder bottom 14, but still has vertical damping properties because the conical spring 20 is integrated in the piston 4. In this case, the conical spring 20 is arranged between the side of the fixing plate 7 facing the hydraulic cylinder 3 and the section of the piston inserted into the cylinder 3.

[0060] In variant "c", two conical springs 20 are arranged offset in the transverse direction around the width center. The interaction with the upper spring section 5 of the spring support 1 is achieved via a so-called yoke 19, which is connected to the crossbeam 18 via two conical springs 20. These conical springs are arranged at the two end sections in the transverse direction of the yoke 19 and enable a series arrangement of the conical springs 20 and the hydropneumatic spring support 1. If the hydropneumatic spring support 1 fails, an emergency spring support is achieved via the two conical springs 20.

[0061] In this case, the yoke 19 with its two conical springs 20 can also be arranged rotated by 90°, so that the two conical springs 20 are spaced apart not in the transverse direction of the vehicle 15 but in the longitudinal direction of the vehicle.

[0062] In the embodiment of the emergency spring shown in variant “d”, two conical springs 20 are supported in the cross member 18 , wherein the conical springs 20 are directly integrated in the fastening to the car body 16 .

[0063] In variant "e", an elastic crossbeam 18' is used which can take over the function of an emergency spring in the event of failure of the hydropneumatic spring support 1. By placing the car body 16 on the elastic crossbeam 18', vertical damping is provided directly by the elasticity of the crossbeam 18'.

[0064] In variant "f", the hydraulic cylinder 3 is inserted directly into the conical spring which assumes the function of the emergency spring. The conical spring 20 is also connected to the lower lamellar spring section 6 via a so-called bell 21 .

[0065] The elastic support element of the emergency elastic support device is implemented as a conical spring 20 in the above-mentioned variants "b" to "f", which is preferably a rubber conical spring. However, other forms can also be considered, such as a pure rubber laminated leaf spring, etc.

[0066] Figure 4 A more detailed diagram shows the Figure 3 Implementation of variant “c” of , in which the two conical springs 20 are arranged offset with respect to one another in the longitudinal direction.

[0067] In the central area of ​​the chassis 17, a so-called longitudinal drive is usually arranged. It usually consists of a rotating pin, a sliding element or a so-called double body (Lemniskate). The longitudinal forces are transmitted via this structure, so that they can be transmitted independently of the rotational movement and the lateral stroke. A longitudinal drive that is independent of the elastic support device 1 according to the invention leads to an expensive and complex mechanical structure. It is therefore advantageous to integrate the longitudinal drive into the elastic support device 1. Therefore, Figure 4 A sectional view is shown along the longitudinal direction through the entire elastic support device 1 having the emergency elastic support device and the longitudinal driver.

[0068] The lower lamellar spring section 6 is designed as a single spring and is arranged in the pitch center of the chassis 17. The two upper spring sections 5 are arranged offset in the longitudinal direction of the vehicle 15, so that the hydraulic cylinder assembly 2 (which can also be called a spring strut) is stabilized in the vertical direction. Between the crossbeam 18 and the upper lamellar spring section 5, a so-called yoke 19 is arranged, which has an integrated emergency spring in the form of two conical springs 20 spaced apart in the longitudinal direction of the vehicle. In this case, the inner conical pin is directly attached to the crossbeam 18, and the conical section-shaped component of the conical spring 20 surrounding the pin is fixed to the yoke 19. For the actual longitudinal entrainment, two longitudinal dampers 22 and four longitudinal stops 23 are additionally provided.

[0069] In the present invention, the characteristics of the longitudinal drive member are divided into the following three parts:

[0070] a) There is a low stiffness when the movement is small, so that the chassis 17 can be optimally decoupled from the car body 16. This stiffness is formed by the shear stiffness of the upper and lower lamellar spring sections 5, 6. In addition, this characteristic is mainly effective in the state without driving force and braking force.

[0071] b) The elastic progressive behavior is defined here by the longitudinal damper 22. A stop 23 belonging to the longitudinal damper 22 is contacted here between the cylinder assembly 2 and the chassis frame 17. This behavior is effective primarily in the state with driving and braking forces.

[0072] c) Stops with very high rigidity occur, for example, when a longitudinal impact of the chassis mass of up to 5 g results in very high forces which can no longer be conducted via the elastic support 1 or via the rubber damper 22. At such high forces, all stops 23 come into play. The force then passes from the cross member 18 via the conical spring 20, the yoke 19 into the damper 22 with the inner stop 23, and is then transferred to the bell 21 and then directly to the frame 17 via the stop 23.

[0073] Figure 5 A sectional view of a hydraulic assembly 2 is shown, in which the function of level control is implemented by means of an internal cylinder 12 .

[0074] Apart from Figure 5 In addition to the implementation of the level control shown in , this can also be achieved by a mechanical level control valve. Thus, for example, the distance between the chassis 17 and the car body 16 can be measured and the pressure present in the spring accumulator can be changed according to the distance, so that the piston 4 is moved in or out of the cylinder 3. The distance measurement device of the chassis 17 and the car body 16 can be integrated in the vertical buffer 24, wherein, however, it is also possible to provide a separate distance measurement device in the area of ​​the vertical buffer, which distance measurement is preferably carried out in the middle of the vehicle 15.

[0075] Furthermore, a distance measuring device may also be integrated into the hydraulic cylinder assembly 2 .

[0076] For an operational height adjustment (so-called leveling), a height or distance measurement from the car 16 to the platform is performed (eg by radar, laser, etc.) and the spring is raised or lowered accordingly by means of an electric valve.

[0077] In order to carry out levelling or to compensate for wheel wear, the spacing between chassis unit 17 and carriage 16 must be adjustable.

[0078] As in Figure 5As can be seen in the sectional view of , a second piston 12 (i.e., the so-called inner piston 12) can be installed in the hydraulic assembly 2 for this purpose, which can be controlled by a separate oil supply system and control / regulating device. Here, the inner cylinder piston 12 is arranged between the hydraulic cylinder bottom 14 and the cylinder piston 4 extending from the cylinder 3. Via a separate fluid passage 13, the inner cylinder piston 12 in the hydraulic cylinder 3 can be moved so that the inner cylinder piston can reduce the piston chamber 10 available for the cylinder piston 4. As a result, the pressure in the pressure accumulator 9 and the piston chamber 10 will increase and cause the cylinder piston 4 to rise from the hydraulic cylinder 3.

[0079] For compensation of wheel wear and for leveling only quick connections are provided so that rapid height compensation can be achieved in a workshop using corresponding equipment by introducing the amount of fluid required for correct leveling below the bottom of the inner cylinder.

[0080] Alternatively or additionally, the fluid supply via the separate fluid passage 13 can also be automatically set according to the measured distance from the car body 16 to the platform or chassis unit 17. For this purpose, only the corresponding amount of fluid is introduced or discharged through the separate fluid passage 13, so that the desired height of the car body 16 is achieved.

[0081] A hydraulic power unit can be provided to generate hydraulic pressure which can be used, for example, for level regulation and for compensating for leakage. It can be arranged in a compact form directly on the hydraulic cylinder assembly 2 or can be arranged separately in the chassis unit 17. It is also conceivable to arrange it on the carriage 16, so as to connect the usually two chassis units 17 connected to the carriage 16 and thus provide a consumer of hydraulic fluid arranged there. Advantageously, an electrical and / or electronic control device is also advantageously integrated into such a hydraulic power unit.

[0082] Since only very little energy is required for level control and leakage compensation, the system can also be equipped with a self-sufficient energy supply.

[0083] Thus, the constant pressure variation in the hydraulic cylinder assembly 2 can be used, for example, as an energy source. This energy is used to charge the battery via a small generator, which ensures the power supply of the electronics, sensors, valves and pumps. The principle of the generator is preferably based on the use of the pressure variation in the hydraulic cylinder assembly 2, which is converted into electrical energy via a corresponding generator by means of small movements. The main features of the device are:

[0084] The invention also includes systems which are operated in an electrical network.

[0085] Reference numerals list

[0086] 1. Hydraulic and pneumatic elastic support device

[0087] 2 Hydraulic cylinder assembly

[0088] 3 Hydraulic cylinder

[0089] 4 cylinder piston

[0090] 5 Upper spring section

[0091] 6 Lower spring section

[0092] 7 Fixed plate

[0093] 8 Layers of spring segments

[0094] 9 Accumulator

[0095] 10 Compressible chamber of hydraulic cylinder assembly

[0096] 11 Connection Path

[0097] 12 Inner cylinder piston

[0098] 13 Separate fluid paths

[0099] 14 Hydraulic cylinder bottom

[0100] 15 Vehicles

[0101] 16 Carriage

[0102] 17 Chassis unit / chassis frame

[0103] 18 Beam

[0104] 18' Flexible Beam

[0105] 19 Yoke

[0106] 20 Conical spring

[0107] 21 Bell

[0108] 22 Longitudinal damper

[0109] 23 Stop for limiting longitudinal movement

[0110] 24 Vertical Buffer

[0111] 25 lateral buffer

[0112] 26 Lateral damper

[0113] 27 Roll Stabilizer

[0114] 28 Main elastic support device wheel set

[0115] 29 Main buffer wheel set

[0116] 30 Wheel guide

[0117] 31 Wheels

[0118] 32 Spring section fitting

[0119] 33 Rails

[0120] A Lateral deflection

Claims

1. A hydraulic and pneumatic elastic support device (1) for a vehicle (15), the elastic support device comprising: A hydraulic cylinder assembly (2) comprising a hydraulic cylinder (3) and a cylinder piston (4) capable of reciprocating in the hydraulic cylinder (3). a first spring section (5) arranged at one of the two longitudinal ends of the hydraulic cylinder assembly (2), and a second spring section (6) arranged at the other longitudinal end of the two longitudinal ends of the hydraulic cylinder assembly (2), wherein The corresponding longitudinal ends of the hydraulic cylinder assembly (2) and the associated spring sections (5, 6) are respectively designed so that they form an arc shape that is arched inwardly toward the hydraulic cylinder assembly (2).

2. The elastic support device (1) according to claim 1, wherein: The vehicle (15) is a rail vehicle.

3. The elastic supporting device (1) according to claim 1, wherein: The arc shape is a circular arc shape, and the circular arc shape has a bottom point or a high point of the circular arc shape toward the longitudinal axis of the hydraulic cylinder assembly (2).

4. The elastic support device (1) according to any one of claims 1 to 3, wherein: The hydraulic cylinder (3) and the cylinder piston (4) are respectively rigidly connected to a fixed disk (7), on which the corresponding spring sections (5, 6) are arranged, wherein the fixed disk (7) has an arc shape in cross section that descends inwardly toward the longitudinal axis of the hydraulic cylinder component (2), so that the arc shape has a position with the smallest spacing near the longitudinal axis of the hydraulic cylinder component (2) or on the longitudinal axis of the hydraulic cylinder component.

5. The elastic supporting device (1) according to claim 4, wherein: The arc shape is a circular arc shape.

6. The elastic support device (1) according to any one of claims 1 to 3, wherein: The spring sections (5, 6) are layered spring sections having a plurality of layers (8) arranged side by side, so that the plurality of layers (8) are arranged perpendicular to the longitudinal axis of the hydraulic cylinder assembly (2) to achieve a high vertical compressive rigidity.

7. The elastic supporting device (1) according to claim 6, wherein: The layered spring section is a rubber laminated leaf spring.

8. The elastic supporting device (1) according to any one of claims 1 to 3, wherein: The elastic support device is also provided with a pressure accumulator (9), which is connected to a chamber (10) of the hydraulic cylinder assembly (2) which can be compressed by the cylinder piston (4) via a connecting passage (11), wherein the connecting passage (11) has a large passage cross section, thereby generating no or only a minimal buffering effect.

9. The elastic supporting device (1) according to claim 8, wherein: The pressure accumulator (9) is in the form of a bladder accumulator, a diaphragm accumulator or a spring accumulator.

10. The elastic supporting device (1) according to claim 8, wherein: A diaphragm or a valve is also provided in the connecting passage (11) to passively or actively influence the vertical buffering characteristics.

11. The elastic supporting device (1) according to any one of claims 1 to 3, wherein: The hydraulic cylinder (3) also has an inner cylinder piston (12), which can be controlled by a separate fluid passage (13) and is designed to change the size of the chamber (10) of the hydraulic cylinder assembly (2) that can be compressed by the cylinder piston (4), wherein the inner cylinder piston (12) is arranged between the hydraulic cylinder bottom (14) and the end of the cylinder piston (4) inserted into the hydraulic cylinder (3), and the separate fluid passage (13) extends through the hydraulic cylinder bottom (14).

12. The elastic support device (1) according to any one of claims 1 to 3, further comprising a hydraulic power unit to provide hydraulic fluid to the hydraulic cylinder assembly (2) under a certain pressure, wherein: The hydraulic power unit is arranged on the hydraulic cylinder assembly (2).

13. A vehicle (15), comprising: Carriage (16), and A chassis unit (17), wherein: The carriage (16) is supported on the chassis unit (17) via an elastic support system. It is characterized in that The elastic support system has an elastic support device (1) according to any one of the preceding claims, wherein the elastic support device (1) brings the car body (16) located above into contact with one of the two spring sections (5, 6) and brings a chassis unit (17) arranged below the elastic support device into contact with the other of the two spring sections (5, 6).

14. The vehicle (15) according to claim 13, wherein: The vehicle (15) is a rail vehicle.

15. The vehicle (15) according to claim 13, wherein: The spring section (5) pointing toward the carriage (16) includes a plurality of separate spring section units spaced apart from one another in the longitudinal direction of the vehicle (15), and the spring section (6) pointing toward the chassis unit (17) includes a plurality of separate spring section units spaced apart from one another in the longitudinal direction of the vehicle (15).

16. The vehicle (15) of claim 13, wherein: The elastic support device (1) is arranged along the height of the vehicle (15) so that the lower spring section (6), that is, the spring section associated with the chassis unit (17), is located at the pitch center of the chassis unit (17).

17. The vehicle (15) of claim 13, wherein: The upper spring section (5), that is, the spring section associated with the car body (16), is supported directly on the car body (16), on a crossbeam (18) or on a yoke (19) which serves to integrate an emergency spring support.

18. The vehicle (15) of claim 13, wherein: A conical spring (20) made of rubber is arranged between the hydraulic cylinder (3) and the lower spring section (6) to realize an emergency elastic supporting device.

19. The vehicle (15) of claim 13, wherein: At least two conical springs (20) are arranged above the upper spring section (5), in series with the elastic support device (1), between a crossbeam (18) or the car body (16) and a yoke (19) cooperating with the elastic support device (1), to realize an emergency elastic support device, wherein the at least two conical springs (20) are arranged offset from each other in the longitudinal direction or the transverse direction of the vehicle (15).

20. The vehicle (15) of claim 19, wherein: Four conical springs (20) are arranged above the upper spring section (5), in series with the elastic support device (1), between a crossbeam (18) or the car body (16) and a yoke (19) cooperating with the elastic support device (1) to realize an emergency elastic support device, wherein the four conical springs (20) are arranged offset from each other in the longitudinal direction or the transverse direction of the vehicle (15).

21. The vehicle (15) of claim 13, wherein: A conical spring (20) is arranged at the outer edge between the cross beam (18) and the carriage (16) as an emergency elastic support device, and / or the elastic cross beam (18) connected in series with the elastic support device (1) is used as an emergency elastic support device.

22. The vehicle (15) of claim 13, wherein: The spring section (5) arranged at the top is in contact with a yoke (19), for which purpose the elastic support device (1) has a certain amount of play in the longitudinal direction of the vehicle (15), and an upper component of the elastic support device (1), a so-called bell-shaped piece (21), has at least one longitudinal damper (22) with an internal stop between the bell-shaped piece (21) and the yoke (19) connected to the car body (16) to produce a progressive longitudinal damping characteristic, wherein the yoke (19) surrounds the bell-shaped piece (21) in a hood-like manner in the longitudinal direction of the vehicle (15).

23. The vehicle (15) of claim 22, wherein: The at least one longitudinal damper (22) is in the form of a rubber spring.

24. The vehicle (15) of claim 22, wherein: The chassis unit (17) also has a stopper (23) for limiting the longitudinal movement of the hydraulic cylinder (3) and the bell (21) in order to transmit large impact forces in the longitudinal direction of the vehicle (15).

25. The vehicle (15) of claim 13, wherein: The elastic support device (1) also includes a hydraulic power unit to provide hydraulic fluid to the hydraulic cylinder assembly (2) under a certain pressure, wherein the hydraulic power unit is arranged on the hydraulic cylinder assembly (2); wherein the hydraulic power unit is separately arranged in the chassis unit (17) or in the carriage (16).

26. The vehicle (15) of claim 13, further comprising a generator that generates electrical energy from pressure changes in the hydraulic cylinder assembly (2).

27. The vehicle (15) of claim 26, wherein: The elastic support device (1) also includes a hydraulic power unit to provide hydraulic fluid to the hydraulic cylinder assembly (2) under a certain pressure, wherein the hydraulic power unit is arranged on the hydraulic cylinder assembly (2); wherein the electrical energy is used to supply the hydraulic power unit.

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