DE102005006431A1 - Valve assembly for controlling clutch or gear actuator of motor vehicle, has actuator, and pressure control valve and/or flow valve are arranged such that control valve and flow valve are in series connection with actuator - Google Patents

Abstract

The assembly has an actuator (2) for operating a clutch and/or a gear actuator. A tank (3)is provided for the supply of a hydraulic medium. A pressure control valve (5) and/or a flow valve (6) are arranged in addition to a safety valve such that the pressure control valve and the flow valve are in series connection with the actuator. A control device is provided for the pressure control valve and the flow valve. An independent claim is also included for a method of controlling a clutch or gear actuator of a motor vehicle.

Description

The The invention relates to a valve system for controlling a clutch or a gear selector of a motor vehicle, in particular of a dry clutch, with at least one actuator for actuating the Clutch, vzw. to open and / or closing the clutch, or for actuation the gear adjuster. The invention further relates to a method for controlling at least one clutch or a gear actuator a motor vehicle, in particular a dry clutch, wherein at least one actuator for actuation the clutch or for actuation the gear selector is driven, and wherein the clutch pressure or the Ganstellerdruck over varies the adjustment of the clutch or the gear selector.

in the State of the art from which the invention proceeds are for control in particular of "dryers" corresponding "pressure controls" known are in motor vehicles for controlling dry clutches pressure control valves or pressure switching valves in use. Pressure control valves hold the Pressure independent the size of one higher Form pressure or supply pressure constant, with pressure switching valves upon reaching a certain set pressure a current path for a release further workflow. About the pressure control valves bspw. can the forces be adjusted so that engaging a gear in the transmission preferably gentle on the synchronizer rings of a switching device takes place. Furthermore It is known in the art that the pressure of pressure control valves via a Adjusting screw with lock nut or alternatively via an electrical and / or electronic control can be influenced individually.

alternative a displacement control of the clutches is used, wherein the actuator usually by a defined amount is moved and thus - at accordingly rigid components - one relatively good reproducible change the coupling capacity established. The flow valves regulate the throttling effect Movement speed of the flow medium / hydraulic medium within the hydraulic circuit, thereby enabling shifting the couplings.

in the Prior art, from which the invention proceeds, are corresponding Method for controlling dry couplings by means of pressure controls or flow valves known. For this purpose, in the case of the flow valve as already mentioned - a path control the couplings used, the actuator is usually a amount is moved and thus - with correspondingly rigid components - a relative change the coupling capacity established. The flow valves used regulate over one Throttling effect the volume flowing through of the flow medium within the hydraulic circuit.

The Training this known in the art valve systems for Control of clutches, especially dry clutches is still not optimal. By friction influences from clutch and adjusting system there is a non-negligible Difference between the closing and the opening pressure in one and the same coupling position, so that a sensitive adjustment is difficult. Furthermore disadvantageous when using pressure control valves are the varying existing frictional forces on the clutch discs, which also still dependent are of the individual current operating situation of the clutch and usually can not be compensated fast enough. These increase the influence on the wear and tear This shortens the service life of a clutch and reduces maintenance costs elevated. The disadvantage with the used flow valves is that different differential pressures or pressure gradient above the Adjust the flow valve and thereby the flowing volume flow in the closing and opening direction is different, which again a problem in terms of Regressibility and in turn negative influence on the wear, the life and associated costs of the clutch and the transmission of Motor vehicle caused. Furthermore, a failure or a Failure / incident, in particular from the flow valve an impairment of the system state have the consequence, in particular the actuation of the actuator and thus the operation of the Clutch or the gear actuator could affect and possibly to lead to a vehicle standstill can, especially because the coupling can not be opened easily.

The known methods for controlling dry clutches, in particular for dry clutches of a motor vehicle, with at least one actuator for actuating the clutch and with at least one tank for providing a hydraulic medium have similar disadvantages. The applied to the valves differential pressures in the closing and opening direction of the coupling are very different and thus exert a negative influence on the controllability of the valve system. Likewise, the methods known in the prior art have a significant influence on the service life of a transmission due to the then under certain circumstances then heavily loaded synchronizer rings of a transmission, for example. By the corresponding actuation of the gear plate. In addition, the wear of clutches or synchronizer rings is increased by the absence of optimal control and thereby their life reduced or increased their cost. Finally, failures or a malfunction or an accident of a valve used can lead to impaired system conditions and possibly cause a vehicle standstill.

Of the Invention is therefore the object of the aforementioned Valve system or the known method for controlling clutches or of gear actuators in such a way and to develop, that control and / or control problems, in particular, caused avoided by force hysteresis in almost every operating situation be a wear of the Clutch and the transmission, in particular also the synchronizer rings to reduce and thereby extend their life, and reduce subsequent maintenance costs, with failures or Malfunctions / Incidents of used valves impairments of the Systems are avoided.

The previously indicated task will now be for the valve system solved, that at least one pressure control valve and at least one flow valve are arranged in series connection in front of the actuator and in addition a Safety valve is provided.

The Task for the method is now solved by combining at least one pressure control valve and at least one flow valve in series, the pressure control valve and / or the flow valve be controlled so that the currently applied to the flow valve supply pressure dependent on of himself over changing the adjustment Clutch pressure or gear actuator pressure is set and that a safety valve is arranged and / or controlled will, so when a fault the flow valve of existing pressure in the actuator pressure degradable is.

By the series connection of at least one pressure regulating valve and at least a flow valve is an arbitrary and stepless change, depending on the current requirements of the operation of the "total chain" between pressure control valve and flow valve possible. The so-called composition in series affects the respective Sizes "pressure" based on the pressure control valve and the "flow rate" with the flow valve in the respective current clutch situation or clutch position. About balancing pressure levels are situational adjustments of pressure control valve and flow control valve for explicit operating conditions of Clutch or Ganstellers given. For example, on the one hand a sensitive one Adjustment of the actuator with low pressure differences and throttled Flow area be set in the context of a micro-slip control. on the other hand However, the delivery movement of the clutch or the gear actuator can also by raising the regulated pressure and additional further opening the flow cross sections accelerated in the flow valve to quickly change of the transferable to the clutch To reach the moment. By the combination of a pressure control valve with a flow valve is not only on actuation the Clutch approached steplessly and the point of engagement optimally met, but also the switching point specified. By the approximation of Pressure difference in terms of closing and opening pressure due to the combination of pressure control valve and flow valve is an optimal control behavior guaranteed. This will make the switching operations gentle and infinitely allows with reduced wear and tear associated higher Life of the components. This improves the shifting comfort and the wear of the Coupling and the transmission reduced or increased their life and consequently the costs are reduced. Due to the additionally arranged safety valve become possible failures, Malfunctions or malfunctions of the compensated and thus optimal system states guaranteed so that the system at any time in the system state "clutch openly "convicted can and thus also vehicle stoppages are avoided. Thereby the aforementioned disadvantages are avoided.

It There are different possibilities now Invention in an advantageous manner to design and develop. Therefor may first to the claim 1 or the claim 17 downstream claims to get expelled. In the following, however, a preferred embodiment the invention with reference to the following drawings and the accompanying description be explained in more detail. In the drawing shows:

1 a schematic representation of the valve system for controlling clutches or gear actuators of a motor vehicle without the additional safety valve,

2 a schematic representation of the applied differential pressures in the closing and opening direction of a flow valve for a clutch, in a schematic representation, as already known

3 a schematic representation of the applied differential pressures in the closing and opening direction of a flow valve with Druckvor control or tracking with the aid of a pressure control valve according to the valve system according to the invention or the method,

4 a schematic representation of the valve system according to the invention for controlling clutches or gear actuators of a motor vehicle with the essential components, but here shown without the in 1 shown control device,

5 a schematic representation of a fault, namely with flow valve in the middle position are staying without safety valve,

6 a schematic representation of an accident, namely with flow valve in the middle position remain with reaction of a safety valve, which is designed as a check valve,

7 a schematic representation of the system with a safety valve designed as a slide valve in the closed position (with feedback),

8th a schematic representation of the accident, namely with flow valve in the middle position are staying with reaction of the safety valve, which is designed as a slide valve, shown in the open position,

9 a schematic representation with safety valve designed as a slide valve (without feedback) shown in the closed position, and

10 a schematic representation of the fault case with a flow valve in the middle position are permanently formed with reaction of the safety element as a slide valve (without feedback) shown in the open position.

In the 1 to 10 is - at least partially - a valve system 1 for controlling a clutch, not shown, in particular of dry clutches of a motor vehicle or for controlling a gear selector of a transmission, not shown. The valve system 1 has at least one actuator 2 for controlling the clutch or the gear selector and a - first - tank 3 for providing a hydraulic medium.

The disadvantages mentioned above are now avoided by having at least one pressure regulating valve 5 and at least one flow valve 6 in series connection in front of the actuator 2 are arranged and additionally provided a safety valve.

In addition, there is a control device 4 with at least one control connection to the pressure control valve 5 and at least one control connection to the flow valve 6 intended. The control device 4 is designed to evaluate various parameters. A multiplicity of parameters can be determined for the ideal switching of dry clutches or gear actuators, preferably the control device processes them 4 the engine speed, the transmission ratio, the accelerator pedal position, the engine torque, the activities of the brake, the transmission temperatures, the pressures or pressure differences, etc. About corresponding sensors of the control device 4 supplied the individual parameter values.

1 shows for clarification of the valve system 1 the system initially without the safety valve 12 , whereas 4 the simplified valve system 1 namely, without the representation of the control device 4 shows, however, with appropriately arranged safety valve 12 , So can the control device 4 another additional optional control connection to the safety valve 12 have, if this is not designed as a passive element, in particular not as a mechanical automatic pressure-dependent activating security element, but as an active element, by the external electronic control device 4 is activated or even directly as "normally open" (for example, in case of power failure) is formed.

As 1 shows, points the pressure control valve 5 at least a first discharge line 7 to the tank 3 and, to always have a corresponding supply pressure pV available, a first pressure line 8th for pressure supply. It is another connection to the flow valve 6 through a second pressure line 9 intended. Through a connection of the pressure regulating valve 5 with the flow valve 6 is always the optimized required actual pressure at the flow valve 6 guaranteed for the respective situational switching process or in particular by the control device 4 adjustable.

The flow valve 6 is via the second pressure line 9 with the pressure control valve 5 connected. Furthermore, a second discharge capacity 10 to the tank 3 provided and a third pressure line 11 to the actuator 2 , In addition is - how 4 - Shows a parallel fourth pressure line 13 - parallel to the flow valve 6 - with integrated safety valve 12 intended. The actuator 2 actuates directly and / or indirectly the clutch or the gear selector of the motor vehicle, preferably via the corresponding displacement of the here in the 1 or in the 4 each in the actuator 2 illustrated piston, wherein the actuator 2 or the arrangement of the piston in the 1 and 4 slightly varied.

The pressure control valve 5 is in series connection in front of the flow valve 6 arranged. Decisive is the combination of both valve characteristics in series or even taking into account the control device 4 for ideal tuning and the arrangement of the additionally provided safety valve 12 , Due to this fact, the pressure control valve 5 at the second pressure line 9 of the flow valve 6 provide a current operating pressure pV _(s) adapted to the operating situation and thus the switching operation or the actuation of the actuator 2 optimize.

In the particular embodiment illustrated here, the pressure regulating valve 5 in the to the flow valve 6 leading second pressure line 9 a specific supply pressure pV _(s) adapted to the respective operating situation. The pressure control valve 5 controls and / or controls the in the second pressure line 9 existing supply pressure pV _(s) such that this currently at the flow valve 6 applied supply pressure pV _{(s) is set} in dependence on the over the adjustment s changing clutch pressure pK _(s) or changing gear actuator pressure. The pressure control valve 5 has vzw. a shutter or a slide, via which in the second pressure line 9 applied supply pressure pV _(s) is adjustable accordingly. Preferably, the now at the flow valve 6 applied supply pressure pV _{(s) set} such that the quotient of the differential pressures, namely from the difference of the current supply pressure pV _(s) and the current clutch pressure pK _(s) and from the difference of the current clutch pressure pK _(s) or the gear actuator pressure and the tank pressure pT is substantially constant over the adjustment path s substantially. This will be described in more detail with reference to the explanation of the method according to the invention.

The 1 shows - as already mentioned - the valve system 1 , With the help of this valve system 1 Now appropriate clutches of a motor vehicle can be controlled. But it is also possible with the valve system shown here 1 to control a corresponding gear actuator of a transmission of a motor vehicle accordingly. This depends on the particular application. It is crucial that with the aid of the actuator shown here 2 that with the valve system 1 is activated or actuated, corresponding clutches or gear selector can then be operated.

In the following, the method will now be explained in more detail, but "only" based on the control of a clutch 2 and 3 shown curves / graphs are basically also for the control of a gear actuator, in which case not the clutch pressure pK _(s) , but just the gear actuator pressure would have to be shown. With the terms "clutch pressure" or "gear actuator pressure" and the corresponding in the clutch or in the gear plate, vzw. on the actuator 2 respective acting force is meant to be via the piston of the actuator 2 acts.

In the 2 and 3 are shown the supply pressure pV, the clutch pressure pK _(s) , the tank pressure pT and the specific set supply pressure pV _(s) . It can be clearly seen that, in particular, the clutch pressure pK _(s) changes correspondingly as a function of the adjustment path s. As 2 shows, the supply pressure pV is substantially constant here. The same applies to the tank pressure pT. This is compared to 3 different, which will be explained below.

In 2 are - as in the prior art known - the differential pressures occurring in terms of the closing and opening direction of a flow valve 6 schematically, without a pressure control valve 5 is shown in series. Clearly recognizable are the different differential pressures between the respective switching operations. Herein, for example, the pressure differences δpV1, δpT1, δpV2 and δpT2 that arise are indicated by arrows. It can be clearly seen that the quotient of the differential pressures, namely δpV1 / δpT1> δpV2 / δpT2, ie the quotients from the differential pressures, are correspondingly different.

3 now shows the control according to the method:

In 3 are the differential pressures in the closing and opening direction of the flow valve 6 with pressure pre-control or tracking with the help of the pressure control valve 5 shown schematically. Herein, the differential pressures δpV1, δpT1, δpV2, δpT2 that arise are also identified by corresponding arrows for different adjustment points S ₁ and S ₂ .

The disadvantages mentioned above are now avoided in that the previous differential pressures of the closing and opening pressure δpV1 / δpT1> δpV2 / δpT2 in the respective clutch positions by a pressure pilot control by means of at least one pressure control valve 5 in combination with at least one flow valve 6 now be optimally balanced.

The control device 4 can evaluate the currently available differential pressures and adapt them by means of control / regulation according to the operating conditions, whereby the differential pressures - as in 3 shown - be adapted to δpV1 / δpT1 = δpV2 / δpT2, so the quotients of the differential pressures are substantially constant. For this purpose, the control device controls and regulates 4 the pressure control valve 5 and the flow valve 6 , Additional parameters such as engine speed, transmission input position, accelerator pedal position, engine torque, brake activity, transmission temperatures, and other parameters may be controlled by the controller 4 be considered and processed. The control device 4 is vzw. as electrical / electronic control device 4 trained, vzw. a corresponding microprocessor. The control device 4 is capable of in the third pressure line 11 existing actual clutch pressure pK _(s) to measure or with the help of the pressure control valve 5 and the flow valve 6 , both vzw. have appropriate aperture, adjust accordingly. Furthermore, the volume flow through the flow valve 6 through the control device 4 influenced accordingly. It is also conceivable a corresponding change in the volume flow through the control of the flow valve 6 through the control device 4 to optimally adjust corresponding pressure differences.

To avoid accidents is the valve system according to the invention 1 additionally with a safety valve 12 executed. In 4 is the safety valve 12 as a check valve 14 executed. Conceivable are also versions of the safety valve 12 , namely as a slide valve 15 with feedback or as slide valve 16 without feedback or as active elements, for example as a solenoid valve. The embodiments as a slide valve 15 . 16 are in the 7 to 10 shown with the respective different positions open or closed, in the 9 and 10 explicitly for the slide valve 16 without feedback.

The safety valve 12 is in a parallel fourth pressure line 13 to the flow valve 6 provided in this embodiment, ie vzw. in a bypass line to the pressure flow valve 6 arranged. Imaginable but not in the 4 also shown are alternative arrangements, such as a completely separate and direct line to the actuator 2 to free the cylinder of oil in case of failure.

In the illustrated series connection, the pressure regulating valve 5 the pressure according to the requirements of the flow valve 6 situation specific available. The flow valve 6 represents an opening cross-section to the second pressure line 9 or second discharge line 10 ago, so that the hydraulic medium, vzw. Oil throttled according to the actuator 2 is added or removed. In the middle position of the flow valve 6 the working connection to the above-mentioned lines is sealed off, so that the working connections are completed and the oil in the cylinder of the actuator 2 is included. As long as the pressure in the pitch circle, ie between the pressure valve 5 and flow valve 6 is higher than in the cylinder of the actuator 2 has the safety valve 12 no influence. In normal operation is thus the safety valve 12 functionless and hindered by integration by means of the parallel fourth pressure line 13 in no way normal operation.

The failure, a malfunction so a malfunction of the pressure valve 5 or the flow valve 6 can be compensated in most cases by the still functioning other valve, so that the valve system 1 in the state "clutch open" can be transferred.

The 5 represents in particular the accident that the flow valve 6 is firmly seated in the "middle position" or the work connections are completed.Here now is the hydraulic medium, vzw., oil in the cylinder of the actuator 2 included and can not be drained. Since here, especially in a dual-clutch transmission, the second clutch can then no longer be used and a gear change to the operated by the blocked clutch gears is no longer possible, this incident can lead to a standstill of the motor vehicle.

6 schematically shows the reaction of the safety valve 12 , where now the pitch pressure of the second pressure line 9 vzw. is lowered to zero and a pressure gradient between the actuator 2 and safety valve 12 is built. By using a safety valve 12 with the embodiment as a check valve 14 happens the following: For example, the safety valve 12 as a check valve 14 formed with a spring-loaded ball. This releases the safety valve 12 as a check valve 14 not at the same pressure on both sides, but a hysteresis range can be set at which the check valve 14 despite slightly higher pressure in the actuator part remains closed. As a result, unintentional openings at smaller pressure peaks from the actuator 2 avoided. At the same time, this avoids a troublesome unnecessary operation and thus reduces the wear on the sealing seat and the loss of oil. In addition, this reduces the system efficiency is avoided. Another advantage is the flexible positioning of the safety valve 12 as vzw. spring-loaded check valve 14 due to the extensive position independence as well as the advantages of the acceleration insensitivity of the selected arrangement. If now the pressure within the second pressure line 9 is lowered to zero, the safety valve opens 12 or the check valve 14 and the hydraulic medium, vzw. the oil flows out of the actuator 2 in the pitch circle or the second pressure line 9 back and the clutch is opened.

Please note when setting the hysteresis range of the safety valve 12 as a check valve 14 of course the right sizing, which minimizes in the actuator 2 available for emptying pressure and sufficient dynamics for actuator reset allows. At a minimum pressure of 10 bar, for example, a triggering difference of 5 bar could be selected in order to obtain an effective and sufficient driving differential pressure for the flow of the hydraulic medium or the oil flow.

It is also advantageous for in the 4 and 6 illustrated embodiment, the simple function test. For this purpose, only the accident must be adjusted theoretically by the flow valve 6 on middle position and a lowering of the pitch circle pressure of the second pressure line 9 vzw. set to zero. Subsequently, then the piston of the actuator would have 2 - with correct function of the check valve 14 - open at a known speed. The module can therefore be easily checked for correct operation during commissioning.

The 7 and 8th show an alternative schematic representation of the incident with the flow valve 6 in center position remain with reaction of the safety valve 12 as a slide valve 15 formed with feedback. Due to the technical characteristics of a slide valve 15 can not build this leak-free. This has the consequence that constantly vzw. a small flow of oil through the slide valve 15 is passed as soon as a differential pressure is present. In the case shown, this means a constant loss of oil from the line of the actuator 2 , Such an arrangement is increasingly used in low-pressure applications, since there is usually sufficient pressure oil available because of a large-volume designed pump. The advantage of this use is that the oil in case of activation directly on a tank line in the second tank 17 can be drained and not via the pressure control valve 5 must flow out. This shows the 7 the closed and the 8th the opened state of the slide valve 15 ,

The 9 and 10 show an alternative schematic representation of the incident with the flow valve 6 in center position remain with reaction of the safety valve 12 as a slide valve 16 trained (without feedback), in 9 in closed and in 10 in open position. Here is dispensed with a feedback of the working pressure on the lower side of the slider. The slide valve 16 is held in closed position by pressure against a spring, regardless of the pressure in the cylinder of the actuator 2 pending. If the incident already mentioned above occurs in the middle position, the pressure in the second pressure line becomes 9 lowered and the slide valve 16 opens the line driven by the spring 18 to the second tank 17 , There is an increased differential pressure available because no throttle effect must be overcome and also no back pressure on the pressure control valve 5 can develop. Further advantageous over the poppet valves with larger spring forces and associated solid springs, for example against the safety valve 12 as a check valve 14 in that the opening cross-section can be chosen to be relatively large, since a consideration of the closing force of the spring is eliminated.

Conceivable are also versions of the safety valve 12 as active elements, such as solenoid valves, which then directly without the use of the pressure control valve 5 to be triggered. For example, the solenoid valves can then be designed to open normally and thus open automatically in the event of a power failure. This also makes it possible to save money, since this function no longer exists in the case of a fault "automatically or normally open in the event of a power failure" in the other valves 12 executed as an active element, a control line, not shown, be provided, so that the control device 4 After evaluation of various parameters and in various incidents the safety valve 12 - executed as an active element - triggers and thus enables an optimal system state.

To the 8th to 10 may still be executed with respect to the "feedback" that the slide valve 15 with feedback in the 7 and 8th is shown and the slide valve 15 without feedback in the 9 and 10 , where it is clearly visible that on the line 19 the lower side of the slide is relieved of pressure, as this with the second tank 17 connected is.

In the method for controlling at least one clutch or a gear selector of a motor vehicle, vzw. for the in 1 illustrated valve system 1 , now becomes the actuator 2 driven accordingly to actuate the clutch or the gear plate. This is done with the help of a tank 3 a hydraulic medium is provided, wherein the clutch pressure pK _(s) varies over the adjustment path s of the clutch or the gear actuator pressure and the tank pressure pT is substantially constant, as in the 2 and 3 shown. By the combination of the pressure control valve 5 and the flow valve 6 , which are connected in series, can the pressure control valve 5 and / or the flow valve 6 now be controlled so that the currently on flow valve 6 applied supply pressure pV _(s) , the vzw. in the second pressure line 9 exists, depending on the over the adjustment s changing clutch pressure pK _(s) or the gear actuator pressure is provided. This difference is from the comparison of 2 and the 3 clearly visible because 2 the non-applied procedure and 3 the applied inventive method shows.

As the 3 good to see, is now the current at the flow valve 6 applied supply pressure pV _{(s) set} such that the quotient (δpV1 / δpT1 = δpV2 / δpT2), namely the quotient of the respective differential pressures, namely the difference of the current supply pressure pV _(s) and the current clutch pressure pK _(s) and the Difference between the current clutch pressure pK _(s) and the actual tank pressure pT is substantially constant over the adjustment path s substantially. As a result, the disadvantages described above are avoided.

In addition, a "safety function" is realized.In the event of a malfunction, the flow valve 6 is no longer controllable and in a second pressure line 9 with the third pressure line 11 Connecting position is, for example, by pollution or, for example, by an unintentional continuous power due to an electrical fault is then using pressure control valve 5 the specific supply pressure pV _(s) degraded. This has the advantage that the actuator 2 can be relieved without the main pressure or supply pressure pV must be switched off. By means of this "safety function", the specific supply pressure pV _{(s) can be} partially lowered or completely lowered, without the supply pressure pV having to be modified.With actively closing couplings, the system can be transferred to the safe state "clutch open", without affect other sub-functions. In addition, the system could be driven as a pure pressure control with appropriate design of the clutch force characteristic (eg: monotonically increasing). Especially in systems with only one clutch, this would allow emergency operation.

Furthermore, in the method according to the invention also the case is realized that for the accident, when the flow valve 6 remains in the middle position and the working connection to the other lines is sealed off and thereby an inclusion of the oil in the piston of the actuator 2 done, now with the help of the safety valve 12 in conjunction with a parallel fourth pressure line 13 Again, the oil in the actuator 2 can be carried away and the state "clutch open" is realized .This is done by exploiting the pressure difference between the actuator 2 and the second pressure line 9 , By the appropriate pitch pressure vzw. is reduced to zero and by the built pressure gradient in combination with the safety valve 12 the oil from the cylinder of the actuator 2 over the safety valve 12 can leak and the clutch is opened again.

There are several practical embodiments of the safety valve 12 , Conceivable are passive elements such as check valves 14 or slide valves 15 . 16 but also active elements such as solenoid valves.

1

valve system

2

actuator

3

tank

4

control device

5

Pressure control valve

6

Flow valve

7

first relief line

8th

first pressure line

9

second pressure line

10

second relief line

11

third pressure line

12

safety valve

13

fourth pressure line

14

check valve

15

spool valve with feedback

16

spool valve without feedback

17

second tank

18

management

19

management

pV _(s)

specific supply pressure

pK _(s)

clutch pressure dependent on the adjustment path

pT

tank pressure

pV

supply pressure

s

adjustment

Claims (26)

Valve system ( 1 ) for controlling a clutch and / or a gear selector of a motor vehicle, in particular a dry clutch, with at least one actuator ( 2 ) for actuating the clutch, vzw. for opening and / or closing the clutch, or for actuating the gear selector, characterized in that at least one pressure regulating valve ( 5 ) and at least one flow valve ( 6 ) is counted in series connection in front of the actuator ( 2 ) and additionally a safety valve ( 12 ) is provided. Valve system according to the preceding claim, characterized in that a control device ( 4 ) with at least one control connection to the pressure regulating valve ( 5 ) and with at least one control connection to the flow valve ( 6 ) is provided. Valve system according to one of the preceding claims, characterized in that the STEU device ( 4 ) is designed to evaluate various parameters. Valve system according to one of the preceding claims, characterized in that the control device ( 4 ) for controlling and / or regulating the pressure regulating valve ( 5 ) and the flow valve ( 6 ) is trained. Valve system according to one of the preceding claims, characterized in that the pressure regulating valve ( 5 ) at least one first relief line ( 7 ) to the tank ( 3 ), at least one first pressure line ( 8th ) to the pressure supply (pV) and at least one second pressure line ( 9 ) to the flow valve ( 6 ) is provided. Valve system according to one of the preceding claims, characterized in that the flow valve ( 6 ) with the second pressure line ( 9 ) to the pressure control valve ( 5 ) and at least one second discharge line ( 10 ) to the first tank ( 3 ) or to another tank and at least one third pressure line ( 11 ) to the actuator ( 2 ) is provided. Valve system according to one of the preceding claims, characterized in that the actuator ( 2 ) directly and / or indirectly actuates the clutch or the gear plate. Valve system according to one of the preceding claims, characterized in that the pressure regulating valve ( 5 ) in series connection in front of the flow valve ( 6 ) is arranged. Valve system according to one of the preceding claims, characterized in that the flow valve ( 6 ) in series connection in front of the pressure regulating valve ( 5 ) is arranged. Valve system according to one of the preceding claims, characterized in that the pressure regulating valve ( 5 ) in the flow valve ( 6 ) leading second pressure line ( 9 ) provides a specific supply pressure (pV _(s) ) adapted to the respective operating situation. Valve system according to one of the preceding claims, characterized in that the pressure regulating valve ( 5 ) in the second pressure line ( 9 ) supply pressure (pV _(s) ) such controls and / or regulates that this currently at the flow valve ( 6 ) applied supply pressure (pV _(s) ) depending on the over the adjustment (s) of the clutch changing clutch pressure ₍ pK _(s) ) or in dependence on the adjusting path (s) of the gear selector changing gear actuator pressure is set. Valve system according to one of the preceding claims, characterized in that the current at the flow valve ( 6 ) supply pressure (pV _(s) ) is set such that the quotient of the differential pressures, namely the difference of the current supply pressure ₍ pV _(s) ) and the current clutch pressure ₍ pK _(s) ) or gear actuator pressure and from the difference actual clutch pressure (pK _(s) ) or gear actuator pressure and the tank pressure (pT) is substantially constant over the adjustment path (s) of the clutch or the gear selector substantially. Valve system according to one of the preceding claims, characterized in that the safety valve ( 12 ) as a check valve ( 14 ) is executed. Valve system according to one of the preceding claims, characterized in that the safety valve ( 12 ) as a slide valve ( 15 . 16 ) is executed. Valve system according to one of the preceding claims, characterized in that the safety valve ( 12 ) than by the control device ( 4 ) activatable active element, vzw. designed as a solenoid valve. Valve system according to one of the preceding claims, characterized in that the safety valve ( 12 ) in a fourth pressure line ( 13 ) parallel to the flow valve ( 6 ) is arranged or provided. Method for controlling at least one clutch or gear adjuster of a motor vehicle, in particular a dry clutch, vzw. for the valve system according to claims 1 to 16, wherein at least one actuator ( 2 ) is actuated to actuate the clutch or to actuate the gear selector, and wherein the clutch pressure (pK _(s) ) or the gear actuator pressure on the adjustment (s) of the clutch or the gear selector varies, characterized in that by combining at least one pressure control valve ( 5 ) and at least one flow valve ( 6 ) in series connection the pressure regulating valve ( 5 ) and / or the flow valve ( 6 ) are controlled so that the currently on the flow valve ( 6 ) applied supply pressure (pV _(s) ) in dependence on the adjustment path (s) changing clutch pressure ₍ pV _(s) ) or the gear actuator pressure is set and that a safety valve ( 22 ) is arranged and / or controlled so that in case of failure of the flow valve ( 6 ) in the actuator ( 2 ) existing pressure is degradable. Method according to claim 17, characterized in that a control device ( 4 ) to Control and / or control of the pressure regulating valve ( 5 ) and the flow valve ( 6 ) is provided and the control device ( 4 ) evaluates various parameters of the hydraulic circuit. Method according to one of claims 17 or 18, characterized in that the control device ( 4 ) the pressure control valve ( 5 ) and the flow valve ( 6 ). Method according to one of claims 17 to 19, characterized in that the pressure regulating valve ( 5 ) is controlled such that at the second pressure line ( 9 ) of the flow valve ( 6 ) a current supply pressure adapted to the operating situation (pV _(s) ) is provided. Method according to one of claims 17 to 20, characterized in that the current at the flow valve ( 6 ) supply pressure (pV _(s) ) is set such that the quotient (δpV1 / δpT1 or δpV2 / δpT2) from the differential pressures, namely from the difference between the current supply pressure (pV _(s) ) and the current clutch pressure (pK _(s)) or a gear actuator pressure and from the difference between the current clutch pressure (pK _(s)) or a gear actuator pressure and the tank pressure (pT) substantially over the adjustment (s) of the clutch or the gear plate is constant. Method according to one of claims 17 to 21, characterized in that in the event of a malfunction that the flow valve ( 6 ) is no longer controllable and in a second pressure line ( 9 ) and the third pressure line ( 11 ) connecting position, by means of the pressure regulating valve ( 5 ) the specific supply pressure pV _{(s) is} reduced. Method according to one of claims 17 to 22, characterized in that in an accident of the pressure flow valve ( 6 ) the specific supply pressure pV (s) in the second pressure line ( 9 ) and then via the safety valve ( 12 ) the pressure in the third pressure line ( 11 ) is degraded. Method according to one of claims 17 to 23, characterized in that the safety valve ( 12 ) as a check valve ( 14 ) is formed and the hydraulic medium in case of failure of the flow valve ( 6 ) via the as a check valve ( 14 ) trained safety valve ( 12 ) from the actuator ( 2 ) via the second pressure line ( 9 ) and the pressure control valve ( 5 ) is discharged into the tank. Method according to one of claims 17 to 24, characterized in that the safety valve ( 12 ) as a slide valve ( 15 . 16 ) is formed and in the event of malfunction of the flow valve ( 6 ) the hydraulic medium from the actuator ( 2 ) into a second tank ( 17 ) is derived. Method according to one of claims 17 to 25, characterized in that the safety valve ( 12 ) as a slide valve ( 16 ) is formed without feedback, so that in case of failure of the flow valve ( 6 ) the hydraulic medium from the actuator ( 2 ) into the second tank ( 17 ), wherein one side of the slider of the slide valve ( 16 ) with the second pressure line ( 9 ) and the other half of the slide valve relieves pressure, namely with the second tank ( 17 ) connected is.