Patent Application
20090261541
The invention relates to a hydropneumatic axle suspension for vehicles, in particular for their front axle, which interacts with at least one suspension cylinder which is connected both with its ring side and also with its piston side to a hydraulic accumulator which can be triggered by the control electronics by means of a valve unit which can be assigned to it.
The prior art includes hydropneumatic axle suspensions which are readily available commercially and which have a so-called level control. When the axle load increases, the vehicle body sinks due to the changing pressures in the respective suspension cylinder, and a level control valve is then actuated until the piston sides of the suspension cylinders as hydropneumatic actuators have reached the original starting level again. As the axle load decreases, the body can be raised accordingly and the level control valve connects the piston chambers of the suspension cylinders in use at the time to the tank line of the fluid system until the original level is restored.
In a development of this idea, DE 102 32 769 A1, which constitutes the generic prior art, discloses a hydropneumatic axle suspension for vehicles with dramatically changing axle loads, in particular for front axles on truck tractors with hydraulic suspension cylinders which are connected to hydropneumatic accumulators, a suspension circuit of the piston chambers which is pressure-controlled by way of a level control means, and a pressure-controlled suspension circuit of the annuli, a load-sensing pump which can be set by way of a control line (load sensing line) by a control pressure for generating pressure, and a pressure control valve which keeps the pressure level constant in the suspension circuit of the annuli. In the known solution, the pressure control valve is a proportionally controlled valve which is triggered by a control current from an electrical control device as control electronics in order to proportionally control the axle spring rate as a function of at least one sensor signal between the constant annulus pressure level in partial regions and if necessary to override a selectable constant pressure in order to represent a given axle spring rate.
In the illustrated known solution, the annulus pressure is proportionally controlled in partial regions between the constant annulus pressure levels for more rapid pressure matching of the suspension accumulator and a proportional valve is hydraulically connected such that there is load sensing control with pressure relief for a control pump. In the level position the two suspension circuits of the piston and ring sides in the known solution are kept at the set pressure level free of leaks by means of two pressure-tight 2/2-way valves and in the level control process are switched accordingly so that the special resettable hydraulic check valves, which were necessary in the past, can be omitted. In addition to the automatic changing of the spring rate by automatic annulus pressure control, it is possible in the known solution to intentionally change the pressure level in the annulus as necessary by external intervention in order to be able to match the spring rate to the given operating conditions. In order to be able to transmit the current pressure values in the piston chambers of the two suspension cylinders to the control electronics, a pressure sensor is connected to them and the latter is protected against overloading by the pressure limiting valve of the fluid system.
With the known solution, an inherently economical solution of small geometry is devised for the control block of an axle suspension which enables a high level of comfort and, in addition, inputs with respect to the individual spring rate which is to be set. In spite of these advantages, the known solution, however, for triggering the system requires a proportional pressure control valve and a shuttle valve which must transmit the higher pressure which prevails in one fluid branch to the control line (load-sensing line) for triggering a load-sensing pump. In addition to the two 2/2-way valves, additional valve components are therefore required which are expensive and can also endanger the operating reliability of the axle spring control by their failure.
On the basis of this prior art, therefore the object of the invention is, while retaining the advantages of the most similar known solution, to further improve it such that in order to reduce costs and to increase operating reliability, additional valves can be omitted. This object is achieved by a hydropneumatic axle suspension with the features of claim 1 in its entirety.
In that, as specified in the characterizing part of claim 1, the ring side of the suspension cylinder is connected to a pressure sensor which transmits its measured pressure values to the control electronics, and in that the ring-side pressure sensor is connected to the output side of the valve unit which can be assigned to the ring side of the suspension cylinder, both the shuttle valve and also the proportional pressure control valve can be omitted; this helps cut production and maintenance costs. The actual triggering takes place with commercial 2/2-way valves which enable economical implementation of the circuit and which are considered highly reliable.
In the known generic solution, the proportional pressure control valve is used to set the ring-side pressure, for each activation of the level control the ring-side pressure on the suspension cylinder also being reset, with the result that in this respect unintentionally existing leakage flows can enter as a disadvantageous factor. In the solution of the suspension according to the invention, for a comparable suspension characteristic it is based on a constant pressure on the ring side of the suspension cylinder in the respective level position. In this respect then, compared to known solutions, a correction of the ring-side pressure is not necessary. Only when the suspension characteristic changes is the ring-side pressure briefly changed, so that in this regard fewer leakage losses arise. Nor is adaptation of the hydraulics to different ring pressures necessary, since the ring-side pressures are “set” accordingly as parameters in the software of the control electronics.
In addition to other advantages which arise from the reduced number of control and switching valves, with the solution according to the invention it is possible to check the precharge pressure p0 in the hydropneumatic accumulators so that regular testing with the otherwise necessary measurement engineering effort can be eliminated. Depending on length of operation of the accumulators used and the frequency of their actuation, a working gas travels from the gas side of the accumulator to its fluid side, and the accompanying losses which lead to a reduction of the precharge pressure p0 in the accumulator adversely affect the working capacity of the entire hydraulic system. On the basis of the approach according to the invention, the hydraulic system is first connected depressurized and as soon as a volumetric flow is routed to the hydropneumatic accumulator, the pressure jumps to the precharge pressure p0 of the hydropneumatic accumulator and then continues to rise according to the characteristic of this accumulator. This applies especially when the volumetric flow is supplied to the lower accumulator, that is, it is supplied to the ring-side accumulator, and if in the implemented circuit a volumetric flow is supplied to the upper or piston-side accumulator, both hydropneumatic accumulators for the suspension cylinder are checked at the same time.
In one especially preferred embodiment of the hydropneumatic axle suspension, there is also a pressure sensor on the piston side of the respective suspension cylinder, so that in this respect load-dependent adjustment of the suspension characteristic is possible. A path measurement sensor for the piston rod unit of a suspension cylinder facilitates the desired level regulation for the control electronics.
Other advantageous embodiments of the axle suspension according to the invention are the subject matter of the other dependent claims.
The hydropneumatic axle suspension according to the invention will be detailed below using one embodiment as shown in the drawings. The single FIGURE in a schematic which is not to scale here shows the basic structure of the circuit in the form of a block diagram.
The hydropneumatic axle suspension for vehicles shown in the FIGURE is designed especially for their respective front axle (not detailed). This front axle interacts with at least one suspension cylinder 10, several, generally two suspension cylinders 10 being assigned to one axle of the vehicle. For the sake of simplicity, however, this hydropneumatic axle suspension is detailed only with respect to one suspension cylinder 10. The suspension cylinder 10 has one piston side 12 and one ring side 14. The indicated sides 12, 14 are separated from one another via a conventional piston rod unit 16. The respective position of the piston rod unit 16 can be detected via a path measurement system s with measured values which are transmitted to the control electronics 18.
Both the piston side 12 and also the ring side 14 are connected by way of hydraulic supply lines 20, 22 to a hydraulic accumulator 24, 26 which is also referred to as a hydropneumatic accumulator, accumulator or the like in the technical jargon. The hydropneumatic accumulators 24, 26 shown in the FIGURES are shown only schematically, but they are of conventional design. In particular, within the accumulator housing there extends a separating element, for example, in the form of an elastically pliable fluid membrane which separates a gas storage chamber from a fluid chamber which is connected to the line 20, 22 which can be assigned to it to carry fluid. The piston-side pressure sensor DA-K and the ring-side pressure sensor DA-R are connected to the end of the respective supply line 20, 22 and transmit the measured pressure values to the control electronics 18.
Furthermore, for the hydropneumatic axle suspension according to the invention, there are two valve units 28, 30 which, made as 2/2-way valves, can be actuated by the control electronics 18. These directional control or switching valves are conventional in the prior art, so that they will no longer be detailed here. As shown in the FIGURE, the respective valve unit 28, 30 is shown in its blocking position, for which two check valves 32 which act hydraulically in opposition block fluid-tight blocking of the suspension cylinder 10 relative to a hydraulic supply unit 34.
Furthermore, it is provided that the input side 36 of the valve unit 30 with an output side 38 connected to the ring side 14 of the suspension cylinder 10 is connected via a connecting line 40 to the input side 42 of the other valve unit 28 which has an output side 44 connected to the piston side 12 of the assignable suspension cylinder. The terminology referring to inputs and outputs is arbitrary and can also be reversed as required by reversing the fluid direction so that relative to the fluid flow the output side can become the input side and the input side can become the output side. But the aforementioned terminology was chosen to be able to make reference relative to the interconnection.
A load-sensing line LS, which, made as a type of control line, can tap the respective hydraulic pressure prevailing in the connecting line 40, discharges into the connecting line 40 between the two valve units 28, 30. Depending on the load situation which is being established within the hydropneumatic axle suspension, the load sensing line LS then triggers a hydraulic pump P which is made preferably as a load sensing pump. To connect the indicated pump P a 3/2-way control valve unit 46 is used which can be triggered by the control electronics 18 and which connects the load sensing line LS to the tank T unpressurized, as shown in the FIGURE.
Furthermore, into the connecting line 40 between the junction 48 of the load sensing line LS and the respective valve unit 28, 30 there is a cross-sectional constriction 50 in the form of a diaphragm, throttle or nozzle.
With the illustrated hydraulic circuit in addition to the control electronics 18, with a few components for the implemented variable suspension for large axle loads correction of the ring-side pressure is only necessary when required, so that fewer leakage losses arise; this leads to favorable performance results and to a reliable structure. The indicated circuit in terms of basic structure manages with only two valve units 28, 30; this on the one hand mechanically simplifies the circuit and makes it economical, and moreover also contributes to increasing the operating reliability. Furthermore, adaptation of the hydraulics to different ring pressures is not necessary, since acquired as ring-side pressures from the pressure sensor DA-R, they are “set” directly as parameters into the software. The basic structure of the circuit also manages without a pressure sensor DA-K for the piston side 12; when using such a pressure sensor DA-K, however, load-dependent setting of the suspension characteristic is additionally possible. The illustrated path measurement system s allows level control for the entire vehicle body, but also is not absolutely necessary for actual ring-side pressure value detection.
The pressure PRO on the ring side 14 of the respective suspension cylinder 10 is given at the level position of the suspension. Depending on the geometrical cylinder dimensions and the accumulator parameters V0 and P0, the ring-side pressure changes when the cylinder position changes. If the piston rod unit 16 of the suspension cylinder 10 is retracted, the necessary volume on the ring side 14 is taken from the ring-side accumulator 26 and the ring-side pressure drops. If the piston rod unit 16 is extended, the displaced volume on the ring side 14 is taken up by the ring-side accumulator 26 and the ring-side pressure rises. The dependency of the ring-side pressure on position is detected and taken into account in the solution according to the invention, for example, via the path measurement system. The ring-side pressure is measured, for example, by way of the pressure sensor DA-R as PRM and is compared to the theoretical ring-side pressure PRS. Here the theoretical ring-side pressure PRS is determined from the following parameters:
Cylinder ring area AR
Accumulator size V0
Precharge pressure P0
Ring-side specified pressure in level position PRO
Cylinder position s
The gas volume at the level position is then determined as follows:
V
1
×P
RO
=V
0
×P
0
It follows therefrom:
If the computed pressure PRS is thus equal to the measured pressure PRM, no further correction is necessary; with the systems conventional to date this cannot be represented in this way.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2005 062 246.1 | Dec 2005 | DE | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/EP2006/009260 | 9/23/2006 | WO | 00 | 5/29/2008 |
