DE102014203389A1 - Control arrangement with compensation control unit - Google Patents

Abstract

The invention relates to a control arrangement (1), in particular for a vehicle clutch, with an actuator (2) which is movable and / or retained in at least two setting positions by means of a pressure medium, with at least one valve (3) for feeding, holding and / or discharge of the pressure medium, which is switchable between a closing switching position and at least a first flow-through switching position in which the valve (3) is opened with a first nominal diameter, and with a valve control unit (4) for determining the switching position of the valve (3) to move and / or hold the actuator (2) to a required parking position. According to the invention, the control arrangement (1) comprises an additional valve (11) and a compensation control unit (13), wherein the compensation control unit (13) is designed such that it can be opened to open the first nominal diameter (31) as a function of at least one wear parameter of the respective valve (3; 11), either the valve (3) or the additional valve (11) controls, so that the two valves (3; 11) wear in comparison to each other substantially equally.

Description

The present invention relates to a control arrangement according to the closer defined in the preamble of claim 1. Art.

From the DE 10 2009 027 070 A1 is a drive circuit for a pneumatic or hydraulic actuator, in particular a pneumatic or hydraulic actuator cylinder of a vehicle transmission, known. The control circuit has a plurality of valves, wherein depending on a switching position of the valves, a pneumatic or hydraulic control medium to the pneumatic or hydraulic actuator can be fed or discharged from the same. Furthermore, the drive circuit comprises an electronic unit, with the aid of which all valves can be controlled in order to determine their switching position and to keep the actuator in a defined setting position or to transfer it to a defined setting position. The drive circuit further comprises an additional electronics unit that controls at least one valve in the event of failure of the electronics unit such that the actuator retains or assumes a defined setting position.

Furthermore, from the US 4,527,679 A an automatic clutch unit with a pneumatically actuated servo cylinder for actuating a clutch known. The clutch assembly includes a proportional electropneumatic control valve that provides an amount of air, in response to a current magnitude, to adjust the clutch in accordance with a sluggish clutch adjustment pattern with respect to each case situation.

The problem underlying the invention is solved by the features of claim 1. Further advantageous embodiments will become apparent from the dependent claims and the drawings.

It is a control arrangement, in particular for a vehicle clutch of a commercial vehicle, proposed, wherein the control arrangement comprises an actuator, in particular for actuating the vehicle clutch, by means of a pressure medium, in particular by means of compressed air or oil, at least in two parking positions movable and / or in these durable is. The control arrangement further comprises at least one valve, in particular switching valve, for supplying, holding and / or discharging the pressure medium. The valve is switchable between a closing switching position and at least a first flow-through switching position in which the valve is opened with a first nominal diameter. Furthermore, the control arrangement comprises a valve control unit for determining the switching position of the valve in order to move the actuator into a required setting position and / or to keep it in this. The control arrangement comprises at least one additional valve, in particular redundant to the valve. The additional valve has a, in particular the same size, first nominal diameter. Alternatively, the nominal widths of the valve and the additional valve can also be formed differently in size. The valve and the auxiliary valve may preferably cope with the same task separately within the control arrangement. This may preferably be to allow a certain pressure medium flow for filling and / or emptying of the actuator.

Furthermore, the control arrangement comprises a compensation control unit. The compensation control unit is designed such that it can be used to open the first nominal diameter as a function of at least one wear parameter of the respective valve - i. the valve or the additional valve - either the valve or, in particular to this redundant, additional valve controls. The equalization control unit thus causes the two valves to wear substantially equally with each other.

As a result, the life of the control arrangement can be increased, since the load occurring over a certain period of time is divided equally between two valves. As a result, the control arrangement with the valve and the additional valve can perform twice as many operations as previously known control arrangements. This opens up additional possibilities to expand the valve control unit functionally, in particular in the manner that the finely tuned and corner frequencies of the clutch system are increased, which in turn, especially in the automotive sector, the ride comfort of the vehicle, especially the commercial vehicle can be improved.

It is advantageous if the additional valve to the valve redundant, especially cold redundant (cold redundancy), is formed. In this way, to increase the service life of the control arrangement, the load on both valves, in particular substantially uniformly. be distributed. It is also advantageous if the valve is designed as a switching valve.

The term "wear parameters" is to be understood as meaning variables of the respective valve by means of which indirectly or directly at least approximately the already existing wear of the respective valve can be deduced. Accordingly, it is conceivable, for example, to monitor the surface of the armature by means of a sensor by means of which the wear of the valve could be determined directly. Alternatively or additionally, it is also conceivable to use parameters - such as the number of previously performed anchor actuations, anchor cycles, a length of the distance traveled by the anchor stroke and / or an operating time of the armature (anchor suit), with which the remaining life of the respective Valve can be estimated indirectly.

It is advantageous if the control arrangement, in particular the compensation control unit, for determining and / or storing the valve wear parameter comprises a detection unit and / or a memory unit. The detection unit may preferably be a switching cycle counter, an armature lifting knife and / or a Schaltdauerermesser. The detection unit and / or the memory unit are in particular formed as part of the compensation control unit. By detecting and storing the valve wear parameters, the compensation control unit can advantageously deduce the wear already taken and / or the remaining service life of the valve and auxiliary valve, i. estimate at least approximately. For direct and / or exact detection of the wear already occurred, however, the detection unit can also be designed as a sensor. The compensation control unit compares the two determined values of the wear parameter of the two mutually redundant valves. It then determines the less worn valve of the two and sets this as the valve to be controlled for the next cycle.

For approximate estimation of the remaining life of the valve and the additional valve, it is advantageous if the compensation control unit as valve wear parameters, cumulative in particular, the number of completed armature switching cycles, the cumulative length of the covered Ankerhubweges and / or the cumulative operating time of the armature (total time of one Anchor suit). As a result, the load on the valve, in particular the respective valve armature, which has hitherto been carried out can advantageously be determined structurally in a simple and cost-effective manner. To be able to avoid errors in the estimation of the remaining service life, it is advantageous if the compensation control unit determines the at least one valve wear parameter from the first startup of the respective valve and / or for the at least one armature of the valve.

The design complexity of the control arrangement, in particular the programming technology implementation of the interaction between the valve control unit and the compensation control unit, can be kept low when the compensation control unit of the valve control unit is connected downstream. In this case, the valve control unit preferably determines in a first step the nominal width to be opened. In a subsequent second step, the compensation control unit then determines the valve to be opened with this nominal diameter, that is to say either the valve or the additional valve.

In order to be able to avoid overloading one of the two mutually redundant valves and at the same time also to minimize the necessary interventions of the compensation control unit, it is advantageous if the compensation control unit alternately turns the valve and the additional valve after a predetermined interval, in particular one Time and / or frequency interval, controls.

In order to avoid an overload of one of the two valves, it is advantageous if the compensation control unit, as soon as the valve wear parameter of the currently controlled valve has reached a threshold value, changes to the other valve. In this case, the threshold value may be a predetermined number of anchor actuations, armature cycles, a predetermined length of the anchor lifting travel to be covered and / or a predetermined operating time of the armature. The compensation control unit thus alternately controls the valve or the additional valve as a function of the defined threshold value. In this way, compared to a constant alternation, on the one hand, the workload of the compensation control unit can be kept low, since this performs the change between the two redundant valves only after a certain time window. On the other hand, this can reduce the risk of erroneous activation.

In an advantageous embodiment of the invention, the valve and / or the additional valve are each designed as a multiple valve, in particular multiple switching valve, or as a variable quantity control valve. As a result, the finely tunable coupling, in detail of the actuator driving the clutch, can be improved because several different nominal diameters are available for driving the actuator. At the same time an increase in the corner frequency is possible. Furthermore, the construction volume of the control arrangement can be reduced since at least two individual valves can be replaced by a multiple switching valve or a variable quantity control valve.

It is advantageous if the multiple switching valve has an axially movable hollow armature and an inner armature which is arranged coaxially movably in this hollow armature. Advantageously, the multiple switching valve by a displacement of the hollow armature and / or the inner armature in a closing switching position, and in a first flow-through switching position in which the multiple switching valve is opened with a first nominal diameter, and in a second flow-through switching position in which the multiple switching valve is opened with a second nominal size, switchable. Preferably, in this case, the second nominal diameter is greater than the first nominal diameter, wherein the second nominal diameter is in particular 2 mm to 5 mm. It may be provided that the multiple switching valve is switchable exclusively in this two switching position.

• – erste Nennweite des Ventils (+ vollständig geschlossenes Zusatzventil) oder erste Nennweite des Zusatzventils (+ vollständig geschlossenes Ventil);
• – erste Nennweite des Ventils + erste Nennweite des Zusatzventils;
• – erste Nennweite des Ventils + zweite Nennweite des Zusatzventils oder erste Nennweite des Zusatzventils + zweite Nennweite des Ventils;
• – zweite Nennweite des Ventils (+ vollständig geschlossenes Zusatzventil) oder zweite Nennweite des Zusatzventils (+ vollständig geschlossenes Ventil);
• – zweite Nennweite des Ventils + zweite Nennweite des Zusatzventils.

It is advantageous if both the valve and the additional valve are each designed as a multiple valve. Accordingly, both the valve and the additional valve each have at least a first nominal diameter and a second nominal diameter. Preferably, these first nominal diameters are identical to each other, as well as the second nominal diameters. Advantageously, with identical nominal widths, in particular for filling and / or emptying of the actuator, five possible mass flows / volume flows, in particular air mass flows, can be generated, which can be generated by means of eight different switching variants. Due to the additional mass flows / volume flows, the finely tuned control system can be improved. Furthermore, different control deviations can be eliminated as needed, more accurately and faster. The five different mass flows / volume flows result from the following nominal diameter combinations of the valve and / or the additional valve:

• - first nominal size of the valve (+ fully closed auxiliary valve) or first nominal size of the additional valve (+ fully closed valve);
• - first nominal size of the valve + first nominal size of the additional valve;
• - first nominal diameter of the valve + second nominal diameter of the additional valve or first nominal diameter of the additional valve + second nominal diameter of the valve;
• - second nominal size of the valve (+ fully closed auxiliary valve) or second nominal size of the additional valve (+ fully closed valve);
• - second nominal diameter of the valve + second nominal diameter of the additional valve.

Of these five mass flows advantageously three can be generated by means of two alternative switching variants. These redundant mass flows can advantageously be distributed with the compensation control unit to the valve and to this additional redundant valve that extends the life of the two valves.

• – erste Nennweite des Ventils + vollständig geschlossenes Zusatzventil;
• – erste Nennweite des Zusatzventils + vollständig geschlossenes Ventil;
• – zweite Nennweite des Ventils + vollständig geschlossenes Zusatzventil;
• – zweite Nennweite des Zusatzventils + vollständig geschlossenes Ventil;
• – erste Nennweite des Ventils + erste Nennweite des Zusatzventils;
• – erste Nennweite des Ventils + zweite Nennweite des Zusatzventils;
• – erste Nennweite des Zusatzventils + zweite Nennweite des Ventils;
• – zweite Nennweite des Ventils + zweite Nennweite des Zusatzventils.

If the nominal sizes of the valve and the additional valve are different from each other, the following eight nominal diameter combinations are available:

• - first nominal size of the valve + fully closed additional valve;
• - first nominal size of the additional valve + fully closed valve;
• - second nominal size of the valve + fully closed additional valve;
• - second nominal diameter of additional valve + fully closed valve;
• - first nominal size of the valve + first nominal size of the additional valve;
• - first nominal size of the valve + second nominal size of the additional valve;
• - first nominal diameter of the additional valve + second nominal diameter of the valve;
• - second nominal diameter of the valve + second nominal diameter of the additional valve.

It is advantageous if the valve and the additional valve are each designed as a variable quantity control valve. Advantageously, the variable flow control valve has an axially and / or steplessly movable armature and / or by means of an armature of the flow control valve is variably switchable between a closing switching position and a maximum flow-through switching position in a plurality of different flow-through switching positions. These are, in particular, discrete flow-through switching positions. As a result, the mass flows / volume flows can be variably adjusted, whereby the control quality of the control arrangement is improved. Furthermore, the clock cycle numbers and / or the travel distance to be covered by the armature can be significantly reduced. As a result, the tribological system of the valve can be relieved.

For selbigen reasons, it is advantageous if the hollow armature and / or the inner armature of the multiple switching valve - each in the same manner as the armature of the variable flow control valve - are infinitely variable and / or variable between their respective closing switching position and maximum flow-through switching position a plurality of different, in particular discrete flow-through switching positions can be switched. In such a cascaded, variable flow control valve, the advantages of the multiple switching valve, namely in particular the small installation space due to the cascaded nesting of the hollow armature and the inner armature, as well as the advantages of the variable flow control valve, in particular the improvement of the control quality could be combined.

Especially with large diameters, in the range of 4 mm, even a small anchor opening causes a large volume flow. As a result, the valve is not substantially finely adjustable. For this reason, it is advantageous if the hollow armature and / or the inner anchor of the multiple switching valve and / or the armature of the variable Flow control valve at its end facing the closing end has a throttle element. As a result, a lower mass flow / volume flow is effected with a small opening stroke, which in turn improves the finely controllable valve. In this regard, it is advantageous if the throttle element is designed as a cone.

In particular, in vehicle clutches, it is advantageous if the control arrangement for filling the actuator at least a first valve and / or for emptying the actuator has at least a second valve, preferably at least one, but in particular both, one, in particular redundant, additional valve is assigned.

The invention is explained in more detail with reference to drawings. Show it:

1 a schematic representation of the control loop of the control arrangement 1 for generating a mass flow for filling or emptying an actuator,

2a - 2c a schematic sectional view of a multiple switching valve in different switching positions,

3 a schematic representation of the interaction of valve and redundant additional valve, which are each designed as a multiple switching valve and by means of which five different mass flows of a pressure medium can be generated on the basis of eight switching variants,

4a and 4b a schematic sectional view of a variable quantity control valve in the closed and maximum open switching position with conical throttle element.

1 shows a schematic representation of a control arrangement 1 , The control arrangement 1 is intended in particular for a vehicle clutch of a commercial vehicle. It includes an actuator 2 which is movable by means of a pressure medium at least in a first actuating position and second actuating position, not shown here, and / or is stable in these actuating positions. The actuator 2 closes or opens the vehicle clutch when moving in its respective parking position. To the actuator 2 to move into the desired setting position, this can be filled or emptied with at least one pressure medium, in particular an oil or air mass flow, wherein in 1 as an example, the scheme for filling the actuator 2 is illustrated.

According to the in 1 illustrated control circuit for filling the actuator 2 indicates the control arrangement 1 Furthermore, a valve 3 on. The valve 3 is preferably designed as a switching valve or variable quantity control valve. By opening the valve 3 , can the actuator 2 the printing medium, not shown here, are supplied. This is the valve 3 switchable between a closing switching position and at least a first flow-through switching position. In the first flow-through switching position is the valve 3 opened with a first nominal size.

The situation-dependent switching position of the valve 3 is from a valve control unit 4 the control arrangement 1 certainly. For this purpose, the valve control unit receives 4 initially a particular driving situation-dependent reference variable 5 indicating the setting position of the actuator to be set 2 pretends. For setting this setting position or reference variable 5 determines the valve control unit 4 the necessary switching position of the first valve 3 and the duration in the first valve 3 with the corresponding nominal diameter 6 should be open. Based on these specifications, a target current 7 set one of the valve 3 associated first current regulator 8th is handed over as a reference variable. The first current regulator 8th now regulates under feedback of the actually applied actual current 9 the first valve 3 such that an anchor of the first valve 3 is raised by means of an electromagnetic coil such that the first valve 3 in its first nominal size 6 is open. This will cause the actuator 2 with one out of the nominal diameter 6 resulting mass flow or volume flow of the pressure medium filled so that it moves in the direction of the desired setting position. During this movement, the current setting position of the actuator 2 the valve control unit 4 as a controlled variable 10 fed back.

To the life of the control arrangement 1 To increase, this has an additional valve 11 on. The additional valve 11 is preferably to the valve 3 identically formed. The additional valve 11 and the valve 3 Thus, they preferably have at least one identical nominal width 6 on. The additional valve 11 is according to the previous description of the valve 3 can be controlled in an analogous manner. This is the additional valve 11 a second current regulator 12 assigned. The additional valve 11 can go to the valve 3 be designed redundant.

To over-stress one of the two valves 3 . 11 to avoid, assigns the control arrangement 1 a compensation control unit 13 on. The compensation control unit 13 is formed such that it is provided by the valve control unit 4 predetermined nominal diameter 6 determines, in particular depending on a wear parameter decides whether the valve 3 or the additional valve 11 to be controlled. This can be ensured be that the two valves 3 . 11 Compared to each other are claimed substantially equally and as a result, the overload of one of these two valves 3 . 11 is avoided.

The decision whether the valve 3 or the additional valve 11 is to be controlled, meets the compensation control unit 13 as a function of at least one wear parameter of the respective valve 3 . 11 , The wear parameter corresponds to a parameter of the respective valve 3 . 11 , by means of which directly or at least approximately indirectly to the already worn out wear of the respective valve 3 . 11 can be concluded. In particular, the number of armature switching cycles that have taken place so far, the cumulative length of the covered armature lifting travel and / or the cumulative operating time of the armature can serve as the wear parameter to be determined. Preferably, the compensation control unit determines at least one of these wear parameters from the first startup of the respective valve 3 . 11 ,

To determine the wear parameter, the compensation control unit 13 a detection unit 14 and a storage unit 15 on. The registration unit 14 Here, in particular, a switching cycle counter, an anchor lifting knife and / or a Schaltdauerermesser. The registration unit 14 determined both for the first valve 3 as well as for the first additional valve 11 the wear parameter and stores it in the memory unit 15 from. For calculating the cumulative value, by means of which the remaining life of the respective valve 3 . 11 can be determined, attacks the compensation control unit 13 on the in the storage unit 15 stored values, in particular the number of each within a time interval anchor switching cycles, back and cumulates them with the currently detected value. The cumulative value is then again for each of the two valves 3 . 11 in the storage unit 15 stored. By means of the cumulative values, the compensation control unit determines 13 approximately the remaining life of the valve 3 and the additional valve 11 and then determines which of the two valves 3 . 11 is to be controlled in order to ensure a substantially uniform wear of the two.

According to the preceding description, therefore, initially in a first step by the valve control unit 4 the opening size to be opened 6 and only in a subsequent second step of the compensation control unit 13 the valve to open, ie either the valve 3 or the additional valve 11 , certainly. The change between the two valves 3 . 11 can from the compensation control unit 13 be controlled threshold dependent. Accordingly, in the compensation control unit 13 , in particular in the storage unit 15 , a threshold value - in particular a predetermined interval of armature switching cycles, a predetermined length of the Ankerhubweges and / or a predetermined time window of the armature operating time - wherein the compensation control unit 13 always to the other valve 3 . 11 changes when the wear parameter of the currently controlled valve 3 . 11 has reached the threshold. The compensation control unit 13 is therefore designed such that the armature of the two mutually redundant valves 3 . 11 be driven equally often and thus wear evenly.

According to one embodiment of the invention, both the valve 3 as well as the additional valve 11 each as a multiple switching valve 16 be educated. Such a multiple switching valve 16 is in the 2a - 2c shown in a schematic sectional view in different switching positions. The multiple switching valve 16 can according to 2a in a closing switching position, according to 2 B in a first flow-through switching position and according to 2c be switched to a second flow-through switching position. In the closed switching position is the multiple switching valve 16 completely closed. According to a first small nominal diameter, in particular 2 mm, the multiple switching valve 16 in his in 2 B open shown first flow-through switching position. In a larger second nominal diameter, in particular 3.5 mm, is the multiple switching valve 16 opened in its second flow-through switching position.

According to 2a includes the multiple switching valve 16 a valve housing 17 that has an inlet opening 18 and an outlet opening 19 having. In the following, the arrangement of the inlet 18 and outlet opening 19 explained in more detail according to a first embodiment. It goes without saying that the inlet opening 18 and the outlet opening 19 in an alternative embodiment, one another may also be interchanged. In this case, then according to 2a illustrated inlet opening 18 as outlet opening and according to 2a illustrated outlet opening 19 formed as an inlet opening.

About the inlet opening 18 and outlet opening 19 can the valve body 17 to be flowed through with a pressure medium. For closing and opening the outlet opening 19 has the multiple switching valve 16 a hollow anchor 20 on. The hollow anchor 20 is in the valve body 17 between an in 2a shown first position and an in 2c formed second position axially movable. In his in 2a shown first position is the hollow anchor 20 with a frontally formed sealing surface 21 on an inner surface 22 of the valve housing 17 around outlet 19 at. To provide a reliable seal between the sealing surface 21 of the hollow anchor 20 and the inner surface 22 of the valve housing 17 To be able to ensure is the hollow anchor 20 by means of a first spring element 23 Fedebeaufschlagt in his in 2a shown pressed first position.

So that the multiple switching valve 16 can also be opened in a second nominal diameter, this has in addition to the hollow anchor 20 an inner anchor 24 on. This is just like the hollow anchor 20 axially, in particular coaxially to this, movable in the interior of the hollow armature 20 arranged. Preferably, the inner anchor 24 in the hollow anchor 20 axially guided. The inner anchor 24 serves to close and open a first passage opening 25 of the hollow anchor 20 , The first passage opening 25 extends from the inside of the hollow armature 20 to the outside. The first passage opening 25 is substantially coaxial with the outlet opening 19 , to the hollow anchor 20 and / or to the inner anchor 24 educated. In addition to this first passage opening 25 has the hollow anchor 20 a second passage opening 26 on. Analogous to the first passage opening 25 this also extends from the inner surface of the hollow armature 20 to its outer surface. In contrast to the first passage opening 25 is the second passage opening 26 but not on the front side of the substantially cylindrically shaped hollow armature 20 formed, but in the region of its lateral surface and / or in the region of its outlet opening 19 facing cavity end. The hollow anchor 20 and / or the inner anchor 24 may comprise one or more sealing elements not shown here, such as O-rings or other suitable elastomers, in particular in the region of the respective sealing surfaces.

The inner anchor 24 is between a in 2a shown first position and an in 2 B such as 2c shown second position axially movable. The inner anchor 24 has at its the first passage opening 25 opposite end of a second spring element 27 on. The second spring element 27 pushes the inner anchor 24 Spring loaded in its first position. When moving the inner anchor 24 from his in 2a shown first position in his in 2 B respectively. 2c shown second position is the second spring element 27 curious; excited.

In the in 2a shown closing switching position is the first passage opening 25 through the inner anchor 24 and the outlet opening 19 through the hollow anchor 20 locked. In this closing switching position, the valve housing 17 are not flowed through by the pressure medium. To the multiple switching valve 16 in his in 2 B shown first flow-through switching position or in his in 2c shown to switch the second flow-through switching position, has the multiple switching valve 16 an activation element 28 on. The activation element 28 is in the present embodiment, a magnetic coil which generates a different magnetic force depending on the current strength, by means of the hollow armature 20 and / or the inner anchor 24 can be raised. To the designed as a solenoid valve multiple switching valve 16 opening with its first small nominal size becomes the inner anchor 24 by means of the activation element 28 from his in 2a shown first position in his in 2 B shown raised second position. Here, the first passage opening 25 from the inner anchor 24 released so that the pressure medium the valve body 17 can flow in the scope of the first nominal diameter.

To the multiple switching valve 16 in its second, compared to the first nominal size larger, nominal diameter open, is in accordance with 2c not only the inner anchor 24 but also the hollow anchor 20 from his respective in 2a shown first position in its respective in 2c shown raised second position. As a result, the first passage opening 25 of the hollow anchor 20 through the inner anchor 24 locked. Through the raised hollow anchor 20 But now is the outlet opening 19 opened over its entire surface, leaving the valve body 17 flows through the pressure medium in its second nominal diameter.

• – Ventil 3 mit erster Nennweite 31a oder Zusatzventil 11 mit erster Nennweite 31b;
• – Ventil 3 mit erster Nennweite 31a + Zusatzventil 11 mit zweiter Nennweite 32b oder Ventil 3 mit zweiter Nennweite 32a + Zusatzventil 11 mit erster Nennweite 31b;
• – Ventil 3 mit erster Nennweite 31a + Zusatzventil 11 mit erster Nennweite 31b;
• – Ventil 3 mit zweiter Nennweite 32a oder Zusatzventil 11 mit zweiter Nennweite 32b;
• – Ventil 3 mit zweiter Nennweite 32a + Zusatzventil 11 mit zweiter Nennweite 32b.

3 schematically illustrates the different mass flows or volume flows 29a to 29e as well as switching variants 30 which is in a control arrangement 1 result in both the first valve 3 as well as the first additional valve 11 as a multiple switching valve 16 are formed. Accordingly, the two valves 3 . 11 an identical first nominal size 31a . 31b and an identical second nominal diameter 32a . 32b on. By means of the first valve 3 and first additional valve 11 Thus, five different mass flows or flow rates 29a to 29e be generated. These are:

• - Valve 3 with first nominal size 31a or additional valve 11 with first nominal size 31b ;
• - Valve 3 with first nominal size 31a + Additional valve 11 with second nominal diameter 32b or valve 3 with second nominal diameter 32a + Additional valve 11 with first nominal size 31b ;
• - Valve 3 with first nominal size 31a + Additional valve 11 with first nominal size 31b ;
• - Valve 3 with second nominal diameter 32a or additional valve 11 with second nominal diameter 32b ;
• - Valve 3 with second nominal diameter 32a + Additional valve 11 with second nominal diameter 32b ,

This results in five different mass flows or volume flows 29a to 29e , by means of eight different switching variants 30 can be generated. As a result, three of these are Mass flows or volume flows 29a . 29b . 29d designed redundantly, so that the compensation control unit 13 according to the previous description of the lifetime extension of the control arrangement 1 can change.

Alternatively, the two valves could 3 . 11 in an embodiment, not shown here to each other also have different diameters. In this case, eight different mass flows or volume flows could thus be generated by means of the eight different switching variants.

In addition to the valve explained in the previous description 3 with its redundant additional valve 11 for filling the actuator 2 can the control arrangement 1 according to an embodiment not shown here in addition to the emptying of the actuator 2 be formed in an analogous manner. In this case, the control arrangement rejects 1 for filling the actuator 2 a first valve with a redundant first additional valve and for emptying the actuator 2 a second valve with a redundant to this second additional valve. The compensation control unit therefore preferably ensures both a compensation between the first control valve and the first additional valve and between the second control valve and the second additional valve.

As an alternative to that in the 2a - 2c illustrated multiple switching valve 16 At least one of the valves and / or the additional valves can be used as a variable quantity control valve 33 be formed, which in different switching positions in the 4a and 4b is shown, wherein in the following description for compared to the multiple switching valve 16 effect same features and the same reference numerals have been used. If these features are not explained again in detail, their design and mode of action corresponds to the features already described above.

4a shows the variable flow control valve 33 in its closed position. It has an anchor 34 on, by means of a spring element 23 is pressed into its first position. The anchor 34 can according to 4b be raised to a maximum flow-through switching position, in the variable flow control valve 33 is open with its maximum nominal size. Due to the variable adjustability of the anchor 34 can the variable flow control valve 33 be switched between the closing switching position and the maximum flow-through switching position variable in a variety of different flow switching positions.

The anchor 34 indicates at its the outlet opening 19 facing the end of a throttle element 35 on. The throttle element 35 is conical. It extends in the in 4a shown closing switching position at least partially into the outlet opening 19 into it. The throttle element 35 causes a lower mass flow or volume flow with only a small stroke of the armature 34 , whereby the finer controllability of the variable flow control valve 33 is improved.

In addition to those in the 2a - 2c illustrated multiple switching valve 16 as well as in the 4a and 4b illustrated variable flow control valve 33 are also not shown here mixing valve variants conceivable. For example, the hollow anchor could 20 and / or the inner anchor 24 of the multiple switching valve 16 with one in the 4a - 4b be formed throttle element shown. Furthermore, it is also conceivable that additionally or alternatively the hollow anchor 20 and / or the inner anchor 24 of the multiple switching valve 16 not only in a first and a second position is movable, but in the same manner as the anchor 34 of the variable flow control valve 33 is movable in a variety of different lifting heights.

The present invention is not limited to the illustrated and described embodiments. Variations within the scope of the claims are also possible as a combination of features, even if they are shown and described in different embodiments.

LIST OF REFERENCE NUMBERS

1

 control arrangement

2

 actuator

3

 Valve

4

 Valve control unit

5

 command variable

6

 nominal width

7

 target current

8th

 first current regulator

9

 actual current

10

 controlled variable

11

 additional valve

12

 second current regulator

13

 Compensation control unit

14

 acquisition unit

15

 storage unit

16

 Multiple switching valve

17

 valve housing

18

 inlet port

19

 outlet

20

 hollow anchor

21

 sealing surface

22

 palm

23

 first spring element

24

 internal anchor

25

 first passage opening

26

 second passage opening

27

 second spring element

28

 energizer

29

 Mass flows or volume flows

30

 switching variants

31

 first nominal size

32

 second nominal diameter

33

 variable flow control valve

34

 anchor

35

 throttle element

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102009027070 A1 [0002]
• US 4527679A [0003]

Claims (13)

Control arrangement ( 1 ), in particular for a vehicle clutch, with an actuator ( 2 ), which is movable by means of a pressure medium at least in two setting positions and / or in these durable, with at least one valve ( 3 ) for supplying, holding and / or discharging the pressure medium, between a closing switching position and at least a first flow-through switching position, in which the valve ( 3 ) is openable with a first nominal diameter, is switchable, and with a valve control unit ( 4 ) for determining the switching position of the valve ( 3 ) to the actuator ( 2 ) to move into a required parking position and / or to keep him in this, characterized in that the control arrangement ( 1 ) an additional valve ( 11 ) with a first nominal diameter ( 31 ) and a compensation control unit ( 13 ), wherein the compensation control unit ( 13 ) is designed such that it is used to open the first nominal diameter ( 31 ) as a function of at least one wear parameter of the respective valve ( 3 ; 11 ), either the valve ( 3 ) or the additional valve ( 11 ), so that the two valves ( 3 ; 11 ) wear substantially equally with each other. Control arrangement according to the preceding claim, characterized in that the control arrangement ( 1 ), in particular the compensation control unit ( 13 ), for determining and / or storing the wear parameter, a detection unit ( 14 ), in particular a switching cycle counter, an Ankerhubwegmesser and / or a Schaltdauerermesser, and / or a memory unit ( 15 ). Control arrangement according to one or more of the preceding claims, characterized in that the compensation control unit ( 13 ) as wear parameters, in particular from the first start-up of the respective valve ( 3 ; 11 ) and / or for the at least one anchor ( 20 ; 24 ; 34 ) of the valve ( 3 ; 11 ), the accumulated number of armature switching cycles, the cumulative length of the armature travel traveled and / or the cumulative operating time of the armature ( 20 ; 24 ; 34 ). Control arrangement according to one or more of the preceding claims, characterized in that the compensation control unit ( 13 ), as soon as the wear parameter of the actuated valve ( 3 ; 11 ) has reached a threshold, to the other valve ( 3 ; 11 ) changes. Control arrangement according to one or more of the preceding claims, characterized in that the compensation control unit ( 13 ) of the valve control unit ( 4 ), wherein preferably the valve control unit ( 4 ) in a first step the opening nominal size ( 6 ) and the compensation control unit ( 13 ) in a subsequent second step that with this nominal diameter ( 6 ) openable valve ( 3 ; 11 ) certainly. Control arrangement according to one or more of the preceding claims, characterized in that the compensation control unit ( 13 ) the valve ( 3 ) and the additional valve ( 11 ) alternately to each other after a predetermined interval. Control arrangement according to one or more of the preceding claims, characterized in that the valve ( 3 ) and / or the additional valve ( 11 ) each as a multiple switching valve ( 16 ) and / or as a variable flow control valve ( 33 ) are formed. Control arrangement according to claim 7, characterized in that the multiple switching valve ( 16 ) an axially movable hollow anchor ( 20 ) and one in this hollow anchor ( 20 ) coaxially movably arranged inner anchors ( 24 ), and that the multiple switching valve ( 16 ) by a displacement of the hollow armature ( 20 ) and / or the inner anchor ( 24 ) in a closing switching position, and in a first flow-through switching position in which the multiple switching valve ( 16 ) with a first nominal diameter ( 31 ) is opened, and in a second flow-through switching position in which the multiple switching valve ( 16 ) with a second nominal diameter ( 32 ) is open, switchable. Control arrangement according to claim 7, characterized in that the variable flow control valve ( 33 ) a continuously movable armature ( 34 ) or that the variable quantity control valve ( 33 ) by means of an anchor ( 34 ) is variably switchable between a closing switching position and a maximum flow-through switching position in a plurality of different, in particular discrete flow-through switch positions. Control arrangement according to claim 8, characterized in that the hollow anchor ( 20 ) and / or the inner anchor ( 24 ) of the multiple switching valve ( 16 ) are infinitely movable and / or between their respective closing switching position and maximum flow-through switching position are variable in a variety of different, in particular discrete flow switching positions are switchable. Control arrangement according to one or more of claims 8 to 10, characterized in that the hollow anchor ( 20 ) and / or the inner anchor ( 24 ) of the multiple switching valve ( 16 ) or the anchor ( 34 ) of the variable flow control valve ( 33 ) at its opening to be closed and opened ( 19 ; 25 ) facing end a throttle element ( 35 ) having. Control arrangement according to claim 11, characterized in that the throttle element ( 35 ) is formed as a cone and / or at least partially in the closed switching position in the opening ( 19 ; 25 ) extends into it. Control arrangement according to one or more of the preceding claims, characterized in that the control arrangement ( 1 ) for filling the actuator ( 2 ) at least a first valve ( 3 ) and / or for emptying the actuator ( 2 ) has at least one second valve, wherein preferably at least one of the two valves a, in particular redundant, additional valve ( 11 ) assigned.

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