DE102008002422A1 - Hydraulic supply system for supplying a hydraulic consumer with at least one consumption range - Google Patents

Abstract

A hydraulic supply system for supplying a hydraulic consumer (12) having at least one consumable area (14, 16) with pressurized fluid comprises pressurized fluid from a reservoir (26) into a main pressurized line (24) supplying pressurized fluid source (18) and associated with each pressurized fluid Consumption (14, 16) of a hydraulic consumer (12) to be adjusted by a control fluid pressure main control valve (34, 36) for establishing and interrupting the connection between the main pressure line (24) and a consumption area (14, 16) and a pilot valve (38, 40) for applying the control fluid pressure to the main control valve (34, 36), wherein the pilot valve is fed via a pressure reducer (42) with an inlet pressure which is below the fluid pressure in the main pressure line (24).

Description

The The present invention relates to a hydraulic supply system, with which provided for example in vehicles hydraulic consumers with Pressure fluid can be supplied.

One such hydraulic consumer is, for example, as Gas spring shock absorbers configured torsional vibration damper assembly. This includes a primary page and one against the action of a damper fluid assembly with respect to primary about a rotation axis rotatable secondary side. The damper fluid assembly includes a damper fluid, which is arranged in at least one pressure chamber whose volume variable during relative rotation between the primary side and the secondary side is. Twisting the primary side and the secondary side in such terms each other, that reduces the volume of such a pressure chamber is, so damper fluid contained therein, for example a substantially incompressible fluid, such as. As oil, against displaced a resistance. The resistor may be provided by a flow restrictor or also a pressure storage arrangement, which is characterized by that from such a pressure chamber displaced damper fluid is tense. For example, such an accumulator assembly another, compressible damper fluid include that in suppression of the substantially incompressible damper fluid is compressed. Thus, the pressure of the pressure from such a pressure chamber increases displaced Damper fluids, so that one of the relative rotation between the primary side and the secondary side counteracting force is generated. To have this functionality in both To be able to obtain relative directions of rotation are for each direction of relative rotation independently working pressure chambers provided, for example, two in each case parallel pressure chambers.

Around the damping characteristic affect such a torsional vibration damper assembly to be able to Is it possible, the pressure chambers over, for example a rotary union in conjunction with a pressurized fluid source. This is to designed to provide a comparatively high fluid pressure, so that when reducing the volume of a pressure chamber and the concomitant increase in pressure of the damper fluid by bonding such a pressure chamber with the pressure fluid source of the fluid pressure even further increased can be and thus an even higher relative rotation between the primary side and the secondary side counteracting force can be generated. In such a Condition can then one or a plurality of pressure chambers whose volumes relative to the primary side relative to the secondary side to be enlarged in conjunction with a substantially pressureless reservoir for the damper fluid to be brought.

at an alternative embodiment of a torsional vibration damper assembly is activated by a relative rotation of the primary side relative to the secondary side Fluid delivery arrangement for example, a gear pump or the like, substantially incompressible damper fluid conveyed back and forth between two accumulator assemblies, so that the fluid pressure in one of the accumulator assemblies is increased while it decreases in the other accumulator assembly. Also here must the conveyor assembly against the increasing fluid pressure in the increased in their pressure accumulator assembly work, allowing the relative rotation between the primary side and secondary side a resistance is opposed. Even this resistance can be influenced by the fact that the accumulator assembly for Influencing the existing there fluid pressure in conjunction with a pressurized fluid source is brought.

A Such torsional vibration damper assembly Thus, in the case in which it deals with an external source of pressurized fluid To connect is a hydraulic consumer with two consumption ranges Each of these consumption areas includes either one or several pressure chambers for a respective relative rotational direction or a respective pressure accumulator arrangement.

It The object of the present invention is a hydraulic supply system for supplying a hydraulic consumer with at least one Provide consumption area with pressurized fluid, with which in simple but reliable way the required fluid pressure or the required amount of pressurized fluid can be provided.

According to one First aspect of the present invention, this object is achieved by a hydraulic supply system for supplying a hydraulic Consumer having at least one consumable area with pressurized fluid, comprising a pressurized fluid from a reservoir into a main pressure line supplying pressurized fluid source and in association with each with pressurized fluid to be supplied consumption range of a hydraulic consumer by a control fluid pressure to be adjusted main control valve for making and breaking the connection between the main pressure line and a consumption area and a pilot valve for docking the pilot fluid pressure to the main control valve, wherein the pilot valve via a pressure reducer is fed with an inlet pressure which is below the fluid pressure located in the main pressure line.

With this embodiment of a Hydraulikver In other words, the supply system is assigned a pair of control valves, namely a main control valve and a pilot control valve, for each consumption area. The main control valve is controlled or adjusted by the pilot valve by means of a control fluid pressure generated by the pilot valve, while the pilot valve is for example actuated electromagnetically and is under the control of a control device. This makes it possible to regulate comparatively large fluid pressures with comparatively small electrical powers, which permits the use of comparatively small valve arrangements. Further, since for each pilot valve by the Druckmin whose an inlet pressure is provided by tapping from the main pressure line, which is lower than the normally prevailing in the main pressure line fluid pressure, it can be ensured that for each pilot valve always substantially the same inlet pressure is present , so that a reliable control of the associated main control valve is ensured.

Around ensure that the fluid pressure in the main pressure line is a given operating pressure can not continue, will continue suggested that a pressure relief valve between the main pressure line and the reservoir is provided for limiting the pressure in the Main pressure line to the specified operating pressure.

Especially in conjunction with the previously described Torsionsschwingungsdämpferanordnungen it may be necessary for the consumption areas very quickly a comparatively high To provide pressure. Since the activation of a fluid pump to a comparatively large delay can result in providing the required pressure, It is further suggested that one with the main pressure line in Connection standing pressure accumulator is provided. That's it further advantageous when in the main pressure line between the pressure fluid source and the pressure accumulator a check valve is provided.

In the consumption of hydraulic consumers or the Main or pilot valves can especially when working with comparatively high fluid pressures will occur, leaks. In particular, if such a System works with a pressure accumulator, this would have to be designed so that he also lost the leaking fluid pressure or can compensate for the corresponding amount of fluid. To counteract this or due to leakage occurring unnecessarily large dimensioning of a pressure accumulator to be able to avoid It is further proposed that in the main pressure line, a switching valve is provided, which optionally the pressure fluid flow in the Main pressure line in both directions of flow releases or at most in a flow direction from the at least one main control valve releases back. It can, for example be provided that the switching valve in the flow direction to the at least a main control valve to downstream of the pressure relief valve is arranged.

The Pressure fluid source may be at least one by a pump drive motor drivable fluid pump include, for example, be provided can that the pump drive motor according to the pressure fluid requirement is activatable. This means that when the fluid pressure in the main pressure line due to the discharge of pressurized fluid to a consumed consumption area decreases and, for example, under falls a predetermined threshold, the pump drive motor is activated by a drive device is to nachzutpeisen again fluid and the fluid pressure in the main pressure line to raise.

at an alternative embodiment may be provided that the pump drive motor, the at least one fluid pump permanently drives and that the fluidity of the at least one fluid pump according to the pressure fluid requirement variable is. In such an embodiment, it becomes possible as Pump drive motor, for example, a drive unit in one Motor vehicle, so in general the internal combustion engine to use.

Around doing an excessive increase to avoid the fluid pressure in the main pressure line is the Fluidfördervermögen the at least one fluid pump varies accordingly, so that when the fluid pressure in the main pressure line a predetermined limit or limit range has reached, the fluid capacity of the at least one fluid pump can be shut down to virtually zero and thus the additional Load on the drive unit of a vehicle reduced as much as possible becomes.

at another alternative embodiment is proposed that the pump drive motor, the at least one fluid pump permanently drives and that a delivery control valve is provided, which according to the pressure fluid requirement, the amount of the at least one fluid pump in the main pressure line stopped fed fluids. Through the conveyor control valve can equally with constant activation in principle not in their fluidity variable fluid pump ensured Be that when the fluid pressure in the main pressure line in the desired Area is not continue to fluid from the fluid pump into the main pressure line is fed, but for example recirculated into the reservoir becomes.

According to one Another aspect may be provided that the pressure fluid source comprises two driven by a pump drive motor fluid pumps and each fluid pump is associated with a delivery control valve is. In this case, a first of the fluid pumps, a larger volume as the second fluid pump. The first fluid pump is used So in essence, big flow rates to generate, for example, to load a pressure accumulator. The second fluid pump has then essentially the task in already existing comparatively high pressure with a smaller fluid delivery volume to ensure the maintenance of the fluid pressure.

Around in the first fluid pump, so designed with a larger delivery volume Fluid pump to obtain a relatively short reaction time and thus as possible be able to respond quickly that the pressure in the main pressure line or one of these associated Pressure accumulator decreases sharply, it is proposed that the first fluid pump associated conveyor control valve dependent on from the signal of a pressure sensor associated with the main pressure line is switchable. This conveyor control valve So is under the control of a drive device, the as an input a the Pressure in the main pressure line receives the reproducing signal and Accordingly, control signals to the delivery control valve outputs to for that too ensure that the fluid delivered by the first fluid pump is either in the direction of Main pressure line is fed, if necessary, or is recirculated into the reservoir.

The The second fluid pump associated conveyor control valve may be formed as a pressure relief valve be.

According to one Another aspect of the present invention is the aforementioned Task solved by a hydraulic supply system for supplying a hydraulic Consumers with two hydraulic consumption areas with pressurized fluid, comprising a pressurized fluid from a pressurized fluid reservoir into a main pressure line supplying pressurized fluid source and in association with each consumption area a main control valve to be adjusted by a control fluid pressure for making and breaking the connection between the main pressure line and the respective associated consumption area, as well as in the flow direction on the consumption area to the upstream of each main control valve a flow control arrangement, further comprising a pilot valve arrangement, which in dependence from the fluid pressures generated in the consumption areas, the control fluid pressure and preferably to the one main control valve applies, which the consumption area associated with the lower fluid pressure.

at This configuration of the hydraulic supply system makes it possible to use two Consumption areas with corresponding fluid requirement solely by sensing the prevailing in these consumption fluid pressures with To feed pressurized fluid. There are no external control circuits required, for example, taking into account a the pressure corresponding to a signal representing a respective consumption range Control commands for generate a pilot valve or the like.

there For example, the configuration may be such that by applying the control fluid pressure at a main control valve this towards interrupting the connection adjustable between the main pressure line and the consumption area is. This means that basically the main control valves towards connecting the main pressure line to a respective one Consumable are biased so that when a control fluid pressure is applied to a main control valve, switching takes place in a condition where, on the one hand, the connection between the consumption area and the main pressure line is reduced or canceled, on the other hand, for example a connection between the consumption area and the essentially unpressurized reservoir is produced. This is especially in Compound with the above-explained with damper fluid working torsional vibration damper arrangements advantageous.

Becomes reduces the volume of a pressure chamber, so the pressure increases the damper fluid in, it is necessary, for example, by connecting with the main pressure line to raise the fluid pressure further to the torsional vibration damper harder to make and to counteract the relative rotation between primary side and secondary side reinforced. If the volume of a pressure chamber increases, the fluid pressure drops and it drops it is necessary to feed fluid essentially without pressure, for example, by establishing a connection with the fluid reservoir.

Around the two main control valves for the consumption ranges depending from the fluid pressures in Being able to control the consumption areas in a defined manner is further suggested the pilot valve arrangement comprises a control valve which the fluid pressure of the consumption area with the higher fluid pressure as input pressure receives and depending from the pressure difference between the fluid pressures of the two consumption areas applies the control fluid pressure to one of the main control valves.

In this case, the fluid pressure of the consumption area with the higher fluid pressure in a simple manner bereitge as input pressure for the control valve be set when the control valve, a shuttle valve is connected upstream, which applies the fluid pressure of the consumption area with higher fluid pressure than the inlet pressure to the control valve.

Around for that too take care of that the respective main control valves provided a defined fluid flow which is essentially independent of pressure fluctuations, which are generated by the consumption areas themselves, will continue proposed that at least one flow control arrangement, a flow restrictor and associated therewith a pressure differential adjustment assembly for adjustment comprises a substantially constant pressure difference across the flow restrictor.

Also in this aspect of the invention, the source of pressurized fluid may be at least comprise a fluid pump drivable by a pump drive motor, wherein the pump drive motor according to the pressure fluid requirement can be activated or the subsidy of the at least one fluid pump according to the pressure fluid requirement variable can be.

Further can be used to provide a defined fluid pressure in the main pressure line a pressure relief valve between the main pressure line and the Reservoir be provided to the pressure in the main pressure line to limit to a predetermined operating pressure.

Of the Main pressure line can be assigned to a pressure accumulator, too for states, in which very quickly a comparatively high pressure in a consumption range is required to provide a corresponding fluid pressure to be able to wherein it can further be provided that in the main pressure line between the pressure fluid source and the pressure accumulator a check valve is provided.

The The present invention further relates to a torsional vibration damper system, comprising a torsional vibration damper assembly having a primary side and one against the action of a damper fluid in terms of the primary side about a rotation axis rotatable secondary side, further comprising a Hydraulic supply system according to the invention for providing pressurized damper fluid for the torsional vibration damper arrangement.

The The present invention will be described below with reference to the accompanying drawings Figures detailed. It shows:

1 a circuit diagram-like representation of a hydraulic supply system;

2 one of the 1 corresponding circuit diagram-like representation of an alternative trained hydraulic supply system;

3 one of the 1 corresponding circuit diagram-like representation of an alternative trained hydraulic supply system;

4 one of the 1 corresponding circuit diagram-like representation of an alternative trained hydraulic supply system;

5 one of the 1 corresponding circuit diagram-like representation of an alternative trained hydraulic supply system;

6 one of the 1 corresponding circuit diagram-like representation of an alternative trained hydraulic supply system;

7 one of the 1 corresponding circuit diagram-like representation of an alternative trained hydraulic supply system;

8th one of the 1 corresponding circuit diagram-like representation of an alternative trained hydraulic supply system.

In 1 is a first embodiment of a hydraulic supply system generally with 10 designated. This hydraulic supply system 10 serves to make a hydraulic consumer 12 to supply with pressurized fluid. The hydraulic consumer 12 For example, it may be a torsional vibration damper arrangement in which the relative rotation of the primary side with respect to the secondary side takes place against the action of damper fluid under pressure. This damper fluid can be displaced in relative rotation between the primary side and the secondary side either from one or more of a respective relative rotational direction associated pressure chambers in a pressure accumulator or can be activated by a activatable during relative rotation conveyor assembly, such. As gear pump, between two accumulator assemblies back and forth. In this respect, such a hydraulic consumer effective Torsionsschwingungsdämpferanordnung has two consumption areas 14 . 16 each comprising either one or more pressure chambers, a pressure storage arrangement or the like.

The supply system 10 includes a source of pressurized fluid 18 with a fluid pump 20 and one the fluid pump 20 driving pump drive motor 22 , This can for example be designed as an electric motor and under the control of a in the 1 not shown drive device. With energized drive motor 22 and thus fluid in a main pressure line 24 promoting fluid pump 20 the fluid is made up of one in essence unpressurized reservoir 26 taken, for example, an oil sump in a vehicle. The fluid is passed through a filter 28 from the reservoir 26 promoted, which filter a check valve 30 is connected in parallel.

To ensure that the fluid pressure in the main pressure line 24 a predetermined limit, which may be, for example, in the range of 70 bar when assigned to a Torsionsschwingungsdämpferanordnung, is between the main pressure line 24 and the reservoir 26 a pressure relief valve 32 provided, which is set so that when the pressure in the main pressure line 24 reaches or exceeds a predetermined threshold, the connection to the reservoir 26 releases and thus does not allow a further increase in pressure.

The two consumption areas 14 . 16 of the hydraulic consumer 12 be with the over the main pressure line 24 supplied pressurized fluid via two main control valves 34 . 36 controlled or in conjunction with the main pressure line 24 brought. These main control valves 34 . 36 For example, they are designed as proportional directional valves and are between a state in which a respective consumption area 14 respectively. 16 in connection with the reservoir 26 is, and a state in which a respective consumption area 14 . 16 in conjunction with the main pressure line 24 is, adjustable. The two main control valves 34 . 36 are hydraulic, so by fluid pressure to operate and are under the control of a respective pilot valve 38 respectively. 40 , The pilot valves 38 . 40 in turn, for example, are electromagnetically actuated and are under the control of a drive device.

The control fluid pressure which the pilot valves 38 . 40 to the respective associated main control valves 34 . 36 for adjusting the same, in particular for placing in the connection to the main pressure line 24 producing position, create, generate the pilot valves 38 . 40 from an input pressure obtained by tapping the fluid pressure from the main pressure line 24 via a pressure reducing valve 42 provided. This inlet pressure is less than that normally found in the main pressure line 24 prevailing fluid pressure, so as to ensure that even if due to large pressure fluid demand the pressure in the main pressure line 24 decreases, the inlet pressure for the pilot valves 38 . 40 can be maintained at a predetermined, constant level and thus also by pressure fluctuations in the skin pressure line 24 the control characteristic for the main control valves 34 . 36 is not affected.

The two pilot valves 38 . 40 generate the control fluid pressure for the main control valves 34 . 36 in accordance with a control command, which is implemented by excitation of the respectively associated electromagnet arrangement. In this respect, the pilot valves 38 . 40 also be considered as servovalves, the proportional to the electrical excitation fluid pressure as the control fluid pressure to the main control valves 34 . 36 create and thus bring them into a state in which a defined, required fluid pressure from the main pressure line 24 to a respective consumption area 14 respectively. 16 is passed on. Become the main control valves 34 . 36 not energized, which means that even to a respective associated pilot valve 38 . 40 no excitation signal is applied, so are the pilot valves 38 . 40 by bias in a state in which one to the main control valves 34 respectively. 36 leading control line in connection with the reservoir 26 , so it is depressurized. This also causes the main control valves to move 34 . 36 by biasing in a defined state, in which, as in 1 represented, the respective consumption range 14 respectively. 16 in connection with the reservoir, that is essentially unpressurized.

An essential advantage of in the 1 shown supply system is that comparatively large pressures in the main pressure line 24 can be provided with relatively low electrical power can be controlled in which as the input force for the main control valves 34 . 36 no electromagnetic force, but a force generated from the fluid pressure itself is used.

The activation of the pilot valves 38 . 40 and thus also the adjustment of the main control valves 34 . 36 can take place in a Torsionsschwingungsdämpferanordnung explained above in that is detected by detecting the relative rotational state between the primary side and the secondary side, in which the consumption ranges 14 respectively. 16 the fluid pressure, for example, by conveying into an accumulator assembly or by reducing the volume of a pressure chamber or more pressure chambers increases, so that this consumption range then by connection to the main pressure line 24 reinforced can be fed with pressurized fluid and a further relative rotation between the primary side and the secondary side can be counteracted. The main control valve associated with the other consumption area remains in the main control valve 1 illustrated state, thus allowing the inclusion of substantially pressureless fluid from the reservoir 26 in the assigned consumption area. According to the demand for pressurized fluid, the pump drive motor also becomes 22 activated or adjusted in its speed to ensure that the required volume of pressurized fluid can be provided. Are both main control valves 34 . 36 in the 1 dargestell th state, in which so a connection between the main pressure line 24 and the two consumption areas 14 . 16 does not exist, the pump drive motor 22 be deactivated or operated so that only leakage losses are compensated.

In 2 is an alternative embodiment of a hydraulic supply system 10 shown. This corresponds in particular with regard to the pressure fluid supply of the consumption areas 14 . 16 used valves of the previously described embodiment, so that reference may be made to the relevant embodiments. In the following, only the existing differences to the above described embodiment will be discussed.

One recognizes in the 2 that the supply system 10 also an accumulator 44 having which of the main pressure line 24 is assigned or stores the existing pressure in this. Furthermore, the main pressure line 24 a pressure sensor 46 associated, which one the pressure in the main pressure line 24 and thus also the accumulator 44 generated corresponding signal and forwards to the drive device. Between the fluid pump 20 and the accumulator 44 there is a check valve 48 , which ensures that even when the fluid pump is deactivated 20 the accumulator 44 Do not backwards towards the reservoir 26 can empty.

By providing the accumulator 44 a system is created which can react very quickly to a need for pressurized fluid. Is in one of the consumption areas 14 respectively. 16 a corresponding fluid requirement exists, so is the associated main control valve 34 respectively. 36 controlled so that it connects to the main pressure line 24 produces, this spontaneously required fluid pressure by a corresponding relaxation of the pressure accumulator 44 be provided without simultaneously the fluid pump 20 must be put into operation, which would bring a corresponding inertia. Only then, if by the signal of the sensor 46 represented pressure in the main pressure line 24 falls below a certain level, the fluid pump 20 by activation of the pump drive motor 22 put into operation, on the one hand the accumulator 44 on the other hand ensure that even with prolonged pressure fluid requirement, a further drop in the fluid pressure in the main pressure line 24 will not occur. Reaches the fluid pressure in the main pressure line 24 again a predetermined limit pressure, the pump drive motor 22 be deactivated again.

Is as a hydraulic consumer 12 provided a Torsionsschwingungsdämpferanordnung described above, so the pressure accumulator 44 be designed so that it can provide the occurring during a load change fluid volume with the required pressure, without at the same time the fluid pump 20 is activated.

The accumulator 44 may be formed, for example, with a gas volume which, by a piston, a diaphragm or other separating member of the pressurized fluid in the main line 24 is separated and according to the pressure in the main pressure line 24 can be compressed. Of course, the accumulator 44 also include several such storage units.

The 3 shows an embodiment in which in the main pressure line 24 a switching valve designed as a directional control valve 50 is provided. This lies in the direction of flow on the main control valves 34 respectively. 36 to the downstream of the pressure relief valve 32 and also the accumulator 44 ,

The switching valve 50 , which is under the control of a drive device, that is, for example, is electromagnetically adjustable, is between the in 3 illustrated state in which the main pressure line against flow in the direction of the pressure accumulator 44 or the fluid pump 20 to the main control valves 34 . 36 is locked, a pressure release in the opposite direction, however, is possible, and a state in which the main pressure line 24 is released for flow in both directions, switchable.

With the switching valve 50 it becomes possible, then, if the two consumption ranges 14 . 16 do not need to be supplied with pressurized fluid, the range of pressure fluid supply, so the source of pressurized fluid 18 or the pressure fluid reservoir 44 from the pilot valves 38 . 40 or the main control valves 34 . 36 and the pressure reducing valve 42 to decouple. In this case, leaks occurring in these valves can not lead to a gradual emptying of the pressure accumulator 44 to lead. Be the pilot valves 38 respectively. 40 controlled by a drive device to control one or both main control valves 34 . 36 a respective assigned consumption area 14 respectively. 16 in conjunction with the main pressure line 24 to bring, so is also the switching valve 50 in his the main pressure pipe 24 releasing state switched.

In the 4 An embodiment of the hydraulic supply system is shown in which the source of pressurized fluid is a fluid pump 20 having variable fluid capacity. The fluid pump 20 is powered by a pump drive motor 22 in the way sentlichen permanently driven. For example, the pump drive motor 22 the drive unit of a vehicle, so for example an internal combustion engine to be. To make sure that when the fluid pressure in the main pressure line 24 reaches the specified operating pressure and also the accumulator 44 is fully charged, another pressure increase does not take place, is by a pressure from the main pressure line 24 tapping adjustment 52 on the fluid pump 20 acted to reduce their promotional assets, for example, set to zero. This adjustment 42 may be spring-biased, wherein the bias is the pressure given, from which a change in the conveying capacity of the fluid pump 20 is generated and thus ensures that the pressure does not increase further.

In particular, when the pump drive motor 22 also is the drive unit of a vehicle, the coupling of the fluid pump 20 with the drive motor 22 take place by a belt drive, a gear drive or the like.

It should be noted that, of course, in the other systems described above, such a configuration of the pressure fluid source 18 can be provided.

Another variation in the design of the pressure fluid source is in 5 shown. Again, the example formed as a planetary rotor pump fluid pump 20 through the pump drive motor 22 permanently driven, so essentially regardless of whether the pressure in the main pressure line 24 already at the operating pressure or still needs to be raised. To then, when the operating pressure is reached, a further promotion of pressurized fluid in the main pressure line 24 and thus to avoid further pressure increase is between the fluid pump 20 and the check valve 48 a conveyor control valve 54 intended. This is basically in the in 5 prestressed state in which the fluid pump 20 over the check valve 48 Fluid in the main pressure line 24 can dine. The delivery control valve 54 However, as fluid control pressure has the in the main pressure line 24 existing fluid pressure. If this reaches the operating pressure, then the conveyor control valve switches 54 in a state in which the fluid pump 20 from the main pressure line 24 is decoupled, so no more fluid in the main pressure line 24 is promoted, but the fluid in the reservoir 26 is recirculated.

It is realized with this embodiment, a mechanically comparatively simple to construct arrangement in which a pressure-dependent adjustment of the conveying capacity of the fluid pump is not required, however, however, it can be ensured that an excessive pressure increase in the main pressure line 24 is avoided. This system is self-regulating, so does not require to be generated by a drive device control commands for the conveyor control valve 54 ,

Another variation in the design of the pressurized fluid source 18 is in 6 shown. In this system, the source of pressurized fluid includes two fluid pumps 20 ' . 20 '' both by a common pump drive motor 22 , For example, again the drive unit of a vehicle to be driven. That is, both fluid pumps 20 ' . 20 '' can again be designed so that they are not variable in their conveyance or a variation of the capacity can only be achieved by changing the drive speed. Here, too, an excessive pressure increase in the main pressure line 24 or the accumulator 44 To avoid each fluid pump is a conveyor control valve 54 ' respectively. 54 '' assigned.

The two fluid pumps 20 ' . 20 '' are fundamentally different from each other. The fluid pump 20 ' serves with a relatively large volume very quickly large amounts of fluid in the main pressure line 24 or the accumulator 44 to dine. The fluid pump 20 '' has essentially the task at already very high pressure in the main pressure line 24 or in pressure accumulator 44 Compensate for pressure variations, so that the fluid pump 20 '' can be primarily designed to generate a high pressure at relatively low fluid delivery.

The fluid pump 20 ' associated conveyor control valve 54 ' which operates essentially as a pressure relief valve and upon reaching a certain limit pressure in the main pressure line 24 a connection between the fluid pump 20 ' and the reservoir 26 manufactures, thus the wei terhin of the fluid pump 20 ' conveyed fluid not in the main pressure line 24 but in the reservoir 26 to promote, is under the control of a drive device and is based on the output signal of the pressure sensor 46 to connect to the reservoir 26 driven. In this way, it is ensured that it is possible to react very quickly to a larger fluid requirement, so that with such an example, electromagnetically activated conveyor control valve 54 ' can be reacted faster than with conventional, due to their hysteresis comparatively sluggish pressure relief valves.

The effective only to compensate for comparatively small pressure fluctuations fluid pump 20 '' is a conventional pressure-dependent switching pressure relief valve as a delivery control valve 54 '' assigned. In order to continue a decoupling zwi between the two fluid pumps 20 ' . 20 '' to realize is in the flow path of the fluid pump 20 '' off after the turnoff to the conveyor control valve 54 ' leads, a check valve 56 provided, which is an inflow of the of the fluid pump 20 ' subsidized fluid in the delivery control valve 54 ' then, if this connects to the reservoir 26 releases, prevents. As the switching pressure of the delivery control valve 54 '' is higher than that of the delivery control valve 54 ' , the state in which by the fluid pump 20 ' over this conveyor control valve 54 '' Fluid in the reservoir 26 is returned, practically does not occur.

The fluid filter, together with the parallel check valve, acts as a depth filter between the two check valves 48 . 56 arranged.

It should be noted that in the hydraulic supply systems described above 10 Of course, consumers with more than two consumption areas can be served. Each consumption area is then a main control valve and associated with this a pilot valve.

An alternative embodiment variant of a hydraulic supply system designed according to the invention is shown in FIG 7 shown. Here, components or assemblies which correspond to components or assemblies described above in terms of design or function are designated by the same reference numeral by adding the appendix "a".

An essential difference from the previously described embodiments is that the connection for the main pressure line 24a with the two consumption ranges 14a . 16a provided valves or valve assemblies operate without control by a drive arrangement taking into account various operating parameters. The two main control valves 34a respectively. 36a For example, again be designed as proportional valves and adjusted by a control fluid pressure. Both main control valves 34a . 36a are biased to a state in which a connection of the main pressure line 24a with a respective consumption range 14a . 16a is made. By applying a control fluid pressure to a respective main control valve 34a . 36a this condition is canceled and a connection between the consumption area according to the control fluid pressure 14a respectively. 16a and the reservoir 26a produced.

To generate the control fluid pressure is a pilot valve arrangement 58a intended. This includes a shuttle valve 60a , which depends on the area of consumption 14a respectively. 16a or a line region between these and the respectively associated main control valve 34a . 36a prevailing fluid pressure in each case those of these line areas with an input area of a control valve 62a connects, in which the higher fluid pressure prevails. For this purpose, for example, a ball-like trained valve member between two valve seats back and forth be, between these valve seats then one to the control valve 62a leading tap line branches off.

The control valve 62a thus receives the in the consumption area 14a respectively. 16a or the leading there lead line area prevailing fluid pressure, which is the higher of the two pressures, as the inlet pressure. Furthermore, the control valve 62a adjustable depending on these two pressures. If the two pressures are equal to each other, then the control valve 62a in a neutral position, in which none of the main control valves 34a . 36a a control fluid pressure is applied, so this in the in 7 are shown positioning. For example, increases the fluid pressure in the consumption area 16a or leading to this line area, while, for example, in the other consumption area 14a or the line region leading there the pressure drops, then a valve spool of the control valve 62a acted upon by this pressure difference so that it is displaced from the neutral position and increasingly a connection between the input area, so the input pressure, and that main control valve 34a respectively. 36a that is the consumption area 14a assigned. The consequence of this is that this consumption area 14a increasingly with the reservoir 26a is connected while the other consumption area 16a at which the pressure rises, in conjunction with the main pressure line 24a is or remains.

In this way it is ensured that always the one consumption area 14a respectively. 16a with the main pressure line 24a in which the fluid pressure is to be increased, while the other of the consumption ranges 14a respectively. 16a with the reservoir 26 is connected, for example, to receive from there substantially unpressurized fluid.

It can also be seen that each main control valve 34a respectively. 36a a flow control arrangement 64a . 66a upstream. The flow control arrangements 64a . 66a have the function of making sure that one of pressure differential fluctuations in the consumption ranges 14a respectively. 16a can be generated, independent, substantially constant fluid flow is achievable. For this purpose, the flow control arrangements 64a respectively. 66a a flow restrictor 68a respectively. 70a as well as this upstream or downstream of a pressure compensator 72a . 74a on. The pressure compensators 72a . 74a sense the pressure in front of and behind the respectively assigned flow restrictor 68a . 70a and provide a substantially constant pressure differential and thus fluid flow across the flow restrictors 68a . 70a for sure. The pressure compensators can do this 72a . 74a for example, with a by the two mentioned pressures in front of or behind the respective associated flow restrictor 68a . 70a have acted upon pistons. These are under the additional bias of an example in their bias adjustable spring, the respect to the respective flow restrictor 68a respectively. 70a supports lower pressure. By this spring is the flow restrictor 72a . 74a kept in balance. At the same time, the spring force determines that via the flow restrictors 68a . 70a , which can also be referred to as measuring throttles, adjusting pressure difference and thus also the fluid flow through the flow restrictors 68a . 70a time.

This in 7 So illustrated system includes with the two main control valves 34a . 36a , the associated Strömungsregelananordnungen 64a . 66a and the pilot valve assembly 58a a hydraulically effective load detection circuit, which is able to do without additional external control, the two consumption areas 14a . 16a with the main pressure line 24a to connect or to the reservoir 26a to connect or to the consumption areas 14a . 16a via the main control valves 34a . 36a adjust applied fluid pressure. Any position sensors or rotary sensors which can detect a relative rotational movement between a primary side and a secondary side of a Torsionsschwingungsdämpferanordnung are therefore not required.

The source of pressurized fluid 18a in this embodiment comprises a fluid pump 20a with by an adjustment 52a variable funding. This adjusting device 52a can, similar to the previous with respect to the 4 described embodiment, a pressure-loadable piston, which is biased by a biasing spring against the pressure loading him. As a pump drive motor 22a For example, can serve a drive unit of a vehicle, which pump the fluid 20a regardless of the pressure fluid demand drives permanently, so that by varying the conveying capacity of the fluid pump 20 It is ensured that the pressure in the main pressure line 24a or the accumulator 44a does not exceed a predetermined operating pressure.

The adjusting device 52a is to vary the conveying capacity of the fluid pump 20a under the control of another pressure compensator 76a , This receives as input variables or input pressures on the one hand, the fluid pressure in the main pressure line 24a which, for example, shortly after the check valve 48a is tapped, and as a further input variable or as a further input pressure those fluid pressure in the consumption range 14a respectively. 16a or prevails there leading line region, which has the higher fluid pressure. For example, this pressure between the shuttle valve 60a and the control valve 62a be tapped and thus the input pressure of the control valve 62a correspond. This pressure is assisted by a bias spring, so that whenever the force generated by the biasing spring together with the input pressure of the control valve 62a through the main pressure line 24a provided pressure prevails, the pressure compensator 76a in the in 7 shown positioning is or will, in which the adjusting device 52a is depressurized and thus the fluid pump 20a is in a state of high fluidity. With increasing pressure in the main pressure line 24a the pressure balance arrives 76a in a state in which the adjustment 52a the pressure from the main pressure line 24a receives to the fluid pump 20a in a state of lower fluid capacity, for example, in a state with a fluid delivery capacity of zero, so that despite driven fluid pump 20a this essentially no further fluid in the main pressure line 24a promotes.

In the 8th shown embodiment largely corresponds to the foregoing with reference to the 7 described embodiment. A difference consists essentially in the design of the pressure fluid source 18a , This includes here a pump drive motor 22a which, for example, configured as an electric motor and under the control of a drive device and is only energized when passing through the pressure sensor 46a detected pressure in the main pressure line 24a falls below a predetermined limit, or is deactivated when the pressure exceeds a predetermined operating pressure. Since here also an accumulator 44a is provided, this hydraulic supply system 10a also on spontaneous pressure variations or pressure fluid requirements in the field of hydraulic consumers 14a respectively. 16a react.

Claims (26)

Hydraulic supply system for supplying a hydraulic consumer ( 12 ) with at least one consumption area ( 14 . 16 ) with pressurized fluid comprising a pressurized fluid from a reservoir ( 26 ) into a main pressure line ( 24 ) supplying pressurized fluid source ( 18 ) and associated with each consumable area to be supplied with pressurized fluid ( 14 . 16 ) of a hydraulic consumer ( 12 ) through a control fluid pressure to be adjusted main control valve ( 34 . 36 ) for making and breaking the connection between the main pressure line ( 24 ) and a consumption area ( 14 . 16 ) and a pilot valve ( 38 . 40 ) for applying the control fluid pressure to the main control valve ( 34 . 36 ), wherein the pilot valve via a pressure reducer ( 42 ) is supplied with an inlet pressure which is below the fluid pressure in the main pressure line ( 24 ) lies. Hydraulic supply system according to claim 1, characterized by a pressure limiting valve ( 32 ) between the main pressure line ( 24 ) and the reservoir ( 26 ) for limiting the fluid pressure in the main pressure line ( 24 ) to a predetermined operating pressure. Hydraulic supply system according to claim 1 or 2, characterized in that one with the main pressure line ( 24 ) associated pressure accumulator ( 44 ) is provided. Hydraulic supply system according to claim 3, characterized in that in the main pressure line ( 24 ) between the source of pressurized fluid ( 18 ) and the accumulator ( 44 ) a check valve ( 48 ) is provided. Hydraulic supply system according to one of claims 1 to 4, characterized in that in the main pressure line ( 24 ) On-off valve ( 50 ) is provided, which optionally the pressure fluid flow in the main pressure line ( 24 ) in both directions of flow or at most in a flow direction of the at least one main control valve ( 34 . 36 ) releases back. Hydraulic supply system according to claim 2 and claim 5, characterized in that the switching valve ( 50 ) in the flow direction on the at least one main control valve ( 34 . 36 ) to the downstream of the pressure relief valve ( 32 ) is arranged. Hydraulic supply system according to one of claims 1 to 6, characterized in that the pressure fluid source ( 18 ) at least one by a pump drive motor ( 22 ) drivable fluid pump ( 20 ; 20 ' . 20 '' ). Hydraulic supply system according to claim 7, characterized in that the pump drive motor ( 22 ) is activated according to the pressure fluid requirement. Hydraulic supply system according to claim 7, characterized in that the pump drive motor ( 22 ) the at least one fluid pump ( 20 ) and that the fluid capacity of the at least one fluid pump ( 20 ) is variable according to the pressure fluid requirement. Hydraulic supply system according to claim 7, characterized in that the pump drive motor ( 22 ) the at least one fluid pump ( 20 ; 20 ' . 20 '' ) permanently drives and that a conveyor control valve ( 54 ; 54 ' . 54 '' ) is provided, which according to the pressure fluid requirement, the amount of the at least one fluid pump ( 20 ; 20 ' . 20 '' ) adjusts fluid fed to the main pressure line. Hydraulic supply system according to one of claims 7 to 10, characterized in that the pressure fluid source ( 18 ) two by a pump drive motor ( 22 ) drivable fluid pumps ( 20 ' . 20 '' ) and each fluid pump ( 20 ' . 20 '' ) a conveyor control valve ( 54 ' . 54 '' ) assigned. Hydraulic supply system according to claim 11, characterized in that a first ( 20 ' ) of the fluid pumps ( 20 ' . 20 '' ) has a larger delivery volume than the second fluid pump ( 20 '' ). Hydraulic supply system according to claim 10 and claim 12, characterized in that the first fluid pump ( 20 ' ) associated conveyor control valve ( 54 ' ) in response to the signal from one of the main pressure lines ( 24 ) associated pressure sensor ( 46 ) is switchable. Hydraulic supply system according to claim 10 and claim 12 or 13, characterized in that the second fluid pump ( 20 '' ) associated conveyor control valve ( 54 '' ) is designed as a pressure relief valve. Hydraulic supply system for supplying a hydraulic consumer ( 12a ) with two hydraulic consumption areas ( 14a . 16a ) with pressurized fluid, comprising a pressurized fluid from a pressurized fluid reservoir ( 26a ) into a main pressure line ( 24a ) supplying pressurized fluid source ( 18a ) and assigned to each consumption area ( 14a . 16a ) a main control valve to be adjusted by a control fluid pressure ( 34a . 36a ) for making and breaking the connection between the main pressure line ( 24a ) and the respective assigned consumption area ( 14a . 16a ), as well as in the direction of flow to the consumption area ( 14a . 16a ) to upstream of each main control valve ( 34a . 36a ) a flow control arrangement ( 64a . 66a ), further comprising a pilot valve arrangement ( 58a ), which depend on the fluid pressures in the consumption areas ( 14a . 16a ) generates the control fluid pressure and preferably to that main control valve ( 34a . 36a ), which corresponds to the consumption area ( 14a . 16a ) associated with the lower fluid pressure. Hydraulic supply system according to claim 15, characterized in that by applying the control fluid pressure to a main control valve ( 34a . 36a ) this in the direction of breaking the connection between the main pressure line ( 24a ) and the consumption area ( 14a . 16a ) is adjustable. Hydraulic supply system according to claim 15 or 16, characterized in that the pilot control valve arrangement ( 58a ) a control valve ( 62a ), which determines the fluid pressure of the consumable area ( 14a . 16a ) receives with the higher fluid pressure as the input pressure and in dependence on the pressure difference between the fluid pressures of the two consumption ranges ( 14a . 16a ) the control fluid pressure to one of the main control valves ( 34a . 36a ) applies. Hydraulic supply system according to claim 17, characterized in that the control valve ( 62a ) a shuttle valve ( 60a ), which determines the fluid pressure of the consumption area ( 14a . 16a ) with higher fluid pressure than input pressure to the control valve ( 62a ) applies. Hydraulic supply system according to one of claims 15 to 18, characterized in that at least one flow control arrangement ( 64a . 66a ) a flow restrictor ( 68a . 70a ) and associated therewith a pressure difference adjustment arrangement ( 72a . 74a ) for setting a substantially constant pressure difference across the flow throttle ( 68a . 70a ). Hydraulic supply system according to one of claims 15 to 19, characterized in that the pressure fluid source ( 18a ) at least one by a pump drive motor ( 22a ) drivable fluid pump ( 20a ). Hydraulic supply system according to claim 20, characterized in that the pump drive motor ( 22a ) is activated according to the pressure fluid requirement. Hydraulic supply system according to claim 20, characterized in that the fluid conveying capacity of the at least one fluid pump ( 20a ) is variable according to the pressure fluid requirement. Hydraulic supply system according to one of claims 15 to 22, characterized by a pressure limiting valve ( 32a ) between the main pressure line ( 24a ) and the reservoir ( 26a ) for limiting the fluid pressure in the main pressure line ( 24a ) to a predetermined operating pressure. Hydraulic supply system according to one of claims 15 to 23, characterized in that a with the main pressure line ( 24a ) associated pressure accumulator ( 44a ) is provided. Hydraulic supply system according to one of claims 15 to 24, characterized in that in the main pressure line ( 24a ) between the source of pressurized fluid ( 18a ) and the accumulator ( 44a ) a check valve ( 48a ) is provided. A torsional vibration damper system comprising a torsional vibration damper assembly having a primary side and a secondary side rotatable about an axis of rotation against the action of a damper fluid with respect to the primary side, further comprising a hydraulic supply system ( 10 ; 10a ) according to one of the preceding claims for providing pressurized damper fluid for the torsional vibration damper assembly.