Method for running a clutch operating system

Abstract

This invention relates to a method for operating a clutch operating system, the clutch operating system comprising: a clutch hydraulically movable from a first position to a second position against a return force; a pressure source operable by an electric actuator; a piping system having piping and valves arranged in the piping; the piping hydraulically connecting the pressure source to the clutch, the valves being operable in an open state and operable in a closed state to disconnect the hydraulic connection between the pressure source and the clutch, the method comprising the steps of: moving the clutch toward the second position; switching the valve to a closed state; adjusting the actuator such that a pressure value is adjusted to a pressure value rating greater than zero, the pressure value representing the pressure in the piping system on the side of the valve facing the pressure source; the pressure value rating being reduced, in particular, by more than 50%, compared to the pressure value before the valve was switched to the closed state.

Description

Technical Field

[0001] The present invention relates to a method for operating a clutch operating system, a controller configured to perform the method, and a clutch operating system having such a controller. Background Technology

[0002] The following clutch operating system is known from the background art: the clutch operating system has a clutch that can be hydraulically moved from a first position to a second position against a return force; and the clutch operating system has a pressure source that can be operated by an electric actuator; and a conduit that hydraulically connects the pressure source to the clutch.

[0003] This clutch operating system is known from DE 10 2010 003 499 A1. Summary of the Invention

[0004] This invention is based on the knowledge that, for a clutch to be shifted to the second position over a longer period, the actuator must be continuously powered to maintain the pressure of the pressure source operating against the return force. This can lead to undesirable high current consumption. Furthermore, the actuator may be significantly heated and must be cooled accordingly to prevent damage. Providing a cam with a rest position to prevent the clutch from shifting back to the first position requires considerable structural space and is expensive due to the need for additional mechanical components. Moreover, in the event of an undesirable failure of the cam, the actuator, de-energized after reaching the rest position, may require a longer activation time until it can reliably resist the acting return force. Furthermore, it is possible that upon reactivation, the position sensor of the actuator, or the position sensor at the pressure source, must first be recalibrated, thereby compromising the actuator's adjustment accuracy in the event of the failure.

[0005] Therefore, there may be a need for a method for operating a clutch operating system that enables the compact construction and inexpensive implementation of the clutch operating system, while simultaneously allowing for lower current requirements from the actuator when holding the clutch against the return force. There may also be a need for the actuator to actively and precisely resist undesired movement in the shortest possible time during a malfunction of the clutch operating system (in which case the clutch is, for example, squeezed towards the first position by means of the return force). Furthermore, there may be a need to determine malfunctions in the clutch operating system at a low cost, ideally identifying different types of malfunctions and responding accordingly to the malfunction or different malfunctions. The method should also ideally be usable during normal operation (i.e., not just in the workshop or in a service or diagnostic mode), during which the clutch operating system is briefly switched to this normal operation.

[0006] The advantages of this invention are that the aforementioned requirements can be met by the technical solution of this invention. Advantageous embodiments are also described in this invention.

[0007] According to a first aspect of the present invention, a method for operating a clutch operating system is provided.

[0008] The clutch system, or clutch operating system, has the following features:

[0009] -- Clutch, which is hydraulically displaced from a first position to a second position against a return force;

[0010] -- A pressure source that can be operated by an electric actuator;

[0011] -- A piping system, including pipes and valves arranged in the pipes.

[0012] The pipeline hydraulically connects or couples the pressure source to the clutch, wherein the valve is open in the open state (valve open) and shut off in the closed state (valve closed or shut off) the hydraulic connection or coupling between the pressure source and the clutch.

[0013] The method comprises the following steps:

[0014] -- Move the clutch toward the second position;

[0015] -- Switch the valve to the closed state;

[0016] -- The actuator is adjusted or controlled such that the pressure value is adjusted to a pressure value rating greater than zero, which represents the pressure in the piping system on the side of the valve facing the pressure source, wherein the pressure value rating is reduced compared to the pressure value before the valve transitions to the closed state, wherein the state of the piping system is inferred from the pressure value.

[0017] The pressure rating can be reduced by, for example, by more than 50% compared to the pressure value before the valve transitions to the closed state.

[0018] The method advantageously enables the clutch to be held persistently in a defined position against the return force, wherein the actuator only needs to have or apply a small torque, a small force, etc., and therefore only a small amount of current needs to flow through the actuator (e.g., less than 50% of the maximum current required to move the clutch from the first position to the second position). Here, the defined position can be, for example, the second position of the clutch. This advantageously reduces the energy consumption of the actuator and also reduces the heating of the actuator. This advantageously reduces the risk of damage to the actuator. Here, a cam with a rest position for relieving the load on the actuator can be advantageously discarded. At the same time, the actuator is advantageously not completely de-energized, and thus a minimum pressure is generated in the pressure source. Furthermore, the adjustment of the actuator is opened. This advantageously allows the clutch not to be undetectably squeezed into the first position due to the return force in the event of a (small) leak in the valve, but can be immediately readjusted—thereby advantageously avoiding, for example, a bump in the vehicle, or a sudden pulling of the internal combustion engine. Furthermore, through a persistent, low power supply (and thus a persistent small overpressure in the first piping section between the pressure source and the valve), outward leakage in the first piping section (between the pressure source and the valve) can also be detected. Finally, accidental (full) opening of the valve can also be detected very quickly, and reverse adjustment can be performed rapidly and accurately because the actuator remains in a powered regulating or control mode. Similarly, larger leakage (a rupture in the piping) in the first piping section can be detected very quickly.

[0019] Furthermore, the high pressure is advantageously applied to the first pipeline section for only a short time at all times, thereby advantageously extending the life of the pipeline.

[0020] In the context of this application, the term "having" can in principle be understood as a synonym for the term "including".

[0021] In the context of this application, the piping system includes, for example, all the elements necessary to define the volume of hydraulic fluid, which is defined by a pressure source, a valve, and a first piping section disposed between the pressure source and the valve.

[0022] The first position of the clutch can be, for example, the clutch closed position (capable of transmitting torque). The second position of the clutch can be, for example, the clutch open position (disengaged, no torque is transmitted). In principle, the first position of the clutch can also be the clutch disengaged position, and the second position of the clutch can be the clutch closed position.

[0023] The pressure source can be constructed (by way of example only) as an active cylinder with an active cylinder piston. Alternatively, a pressure source that operates in a rotary manner can also be provided.

[0024] A driven cylinder with a driven piston can be arranged (by way of example only) at the end of the pipeline opposite to the pressure source.

[0025] The return force of the clutch from the second position to the first position can be provided, for example, by a spring device in or at the clutch. Alternatively or additionally, the return force can be induced or amplified by a spring device arranged, either in a driven cylinder arranged, exemplarily, between the clutch and the line, or at a driven cylinder arranged, exemplarily, between the clutch and the line.

[0026] For example, it can be configured such that: before the clutch is moved toward the second position, a transition of the valve to the open state occurs or is caused; or regardless of the actual position or state of the valve, a control signal or command is sent to move the valve to the open state. This can advantageously identify other fault scenarios or other functional failures. That is, if pressure is built up in the piping system after the command to open the valve from the pressure source, and this pressure (in the first piping section) rises faster or to a higher value than expected (e.g., as stored in the characteristic field), then this indicates a fault in opening the valve. The valve then, for example, may become clamped, or the valve may not open at all, or may only open partially.

[0027] For example, it can be configured such that after the valve is opened, the actuator is powered in such a way that the clutch is moved toward the second position.

[0028] The clutch operating system can be configured, for example, as follows: the actuator is an electric motor, such as a brushless DC motor. The actuator can be located directly at the pressure source, or coupled to the pressure source, and cause pressure formation at the pressure source. The actuator can be connected, for example, to the piston of the drive cylinder. Alternatively, the actuator can be connected to or coupled to the pressure source by means of a transmission device (e.g., a screw drive or push rod). For example, the actuator or the transmission device can be configured not to be self-locking, such that (when the valve is open) the return force can push the clutch from the second position to the first position when the actuator is not powered.

[0029] It can be configured that the method is executed or is capable of being executed in normal mode or normal operation. This could be, for example, the operation of a car, a truck, or a vehicle in motion. Normal mode or normal operation can be understood here as the method being executed not only in the workshop or when the vehicle is parked, or not only in diagnostic mode (which is briefly activated during the operation).

[0030] For example, the method can be configured to monitor the clutch operating system, either alternatively or additionally. This monitoring can, for example, monitor whether the clutch operating system and / or piping system is operating normally as specified, or whether it has one or more malfunctions.

[0031] The improved design specifies that the pressure rating is located between 0.1% and 20% of the maximum pressure value, which is necessary to move the clutch from the first position to the second position. Alternatively, the pressure rating, or the value of the pressure value, can be located between 0.1% and 20% of the pressure value (present when the clutch is in its defined position or the second position).

[0032] This advantageously leads to a significant reduction in the current consumption of the actuator, while simultaneously allowing for precise and long-term regulation of the actuator's current consumption. Sufficient pressure exists in the first piping section when the valve suddenly opens to quickly resist the displacement of the clutch towards the first position. Furthermore, the load on the first piping section is significantly reduced from persistently high pressure.

[0033] Alternatively, the pressure rating can be advantageously set to fall within the range of 0.2% to 15% of the maximum pressure value. This ensures sufficient pressure is always present at the lower end of the range to guarantee precise adjustment of the actuator.

[0034] Alternatively, the pressure rating can be advantageously set to be between 0.5% and 10% of the maximum pressure value. This advantageously results in a particularly large reduction in the current flowing through the actuator, and also allows for precise adjustment of the actuator at the lower end of the range.

[0035] The improved solution involves inferring the state of the piping system from the pressure value. This not only reduces the load on the actuator and the first piping section but also advantageously enables diagnostic solutions for the piping system, or the first piping section, including the valves. The improved solution, for example, advantageously provides a method for monitoring the clutch operating system.

[0036] For example, the adjustment of the actuator can be used to identify whether an (unexpected) pressure increase or decrease has occurred in the first pipeline section.

[0037] The pressure value can be detected or acquired, for example, during the adjustment or control of the actuator.

[0038] The improved solution specifies that the pressure value is pressure.

[0039] Therefore, the pressure value is advantageously directly relative to the actually relevant value (the pressure in the first piping section). Advantageously, there is therefore no need to indirectly measure the pressure.

[0040] The pressure relative to the pressure value can be obtained, for example, by means of a pressure sensor. Such a pressure sensor can be connected to, or disposed in, or located at, the pressure source. The pressure sensor can also be connected to, or disposed in, the first conduit section (located between the pressure source and the valve), or located in, the first conduit section.

[0041] In the improved scheme, it can be alternatively or additionally set that the pressure value corresponds to a current that flows through the actuator in order to operate the actuator.

[0042] This advantageously allows for the indirect acquisition of the pressure value (and thus the pressure in the first conduit section), and the separate pressure sensor can, in principle, be eliminated or used for reliability testing. Through this reliability testing, it is possible to determine, in principle, whether the current acquisition and pressure sensor are malfunctioning.

[0043] The actuator puts the pressure source into a state of establishing the hydraulic pressure, and the actuator also applies a specific force, or a specific torque. Knowing which torque or force is generated by which current flows through the actuator, the pressure in the piping system can therefore be deduced.

[0044] The current can be, for example, the current flowing through the actuator while it adjusts the pressure source to a rated position. This is the regulating current of the actuator. This can be done (by example only) as follows: after the valve is closed, the actuator gradually returns, thereby relieving the pressure in the first section of the pipeline (between the pressure source and the valve). If the actuator has moved back to the level of the rated pressure value, then the position of the actuator, or the position of the moving part of the pressure source (e.g., the position of the piston of the actuator cylinder), can be detected and maintained at the rated value. From this point in time, the actuator is (additionally) adjusted to the rated position, and if necessary, control or adjustment of the pressure value or the rated pressure value is stopped. The current flowing through the actuator, necessary to maintain the rated position, is detected here. This current (in this case, also) is related to the pressure value, thus allowing the pressure value to be inferred from the regulating or control current.

[0045] In the improved design, it can be alternatively or additionally configured that the pressure value corresponds to the positional change of the pressure source after the valve is closed, or the positional change of the moving part of the pressure source. Here, the positional change of the pressure source can be understood in particular as the positional change of the moving part of the pressure source. For example, the linear displacement of the piston of the active cylinder of an active cylinder.

[0046] This advantageously allows for the acquisition or detection of the pressure value without the need for a separate pressure sensor. If a separate pressure sensor is still installed, then the reliability of the pressure sensor's readings, as well as the reliability of the position change readings, can be tested. This also, in principle, makes it possible to disable the functions of the pressure sensor, or the position sensor (and, if necessary, the current sensor).

[0047] It goes without saying that, in principle, other parameters can also be used to acquire, detect, or measure the pressure value, as long as the parameter is related to the pressure in the first pipeline section.

[0048] The improved solution specifies that when the pressure value exceeds a first threshold, a first functional deficiency in the pipeline system is determined.

[0049] This allows for the advantageous implementation of diagnosis and / or monitoring of the piping system without additional expense.

[0050] The first functional deficiency could be, for example, a leak in a valve within the pipeline.

[0051] The first threshold may be higher than the pressure value rating, for example. For example, the first threshold may be higher than the pressure value rating by a maximum of 20%, or a maximum of 15%, or a maximum of 10%, preferably by a maximum of 5%, particularly preferably by a maximum of 3%, and particularly preferably by a maximum of 1%.

[0052] If the valve has a (small) leak, then after the valve is closed and the pressure in the first line section is relaxed to the rated pressure value, the pressure in the first line section will (slowly) rise. This can be determined, for example, by a pressure sensor (the rising pressure). Alternatively or additionally, it can be determined, for example, by the rising current consumption of the actuator when the actuator should maintain a rated position (which the actuator reaches when the rated pressure value is reached). Alternatively or additionally, it can be determined, for example, by the positional change of the active part of the pressure source. This can be determined, for example, by the movement of the active cylinder piston away from the valve because the active cylinder piston is pushed away by higher pressure; or in a centrifugal pump, the pump rotates against the direction of pressure build-up (which is then positive, causing the position value to increase and at some point exceed the first threshold). This positional change can be detected in particular when the actuator is not adjusted to the rated position.

[0053] The improved solution specifies that when the pressure value drops below a second threshold, a second functional deficiency in the pipeline system is identified.

[0054] This allows for the advantageous implementation of diagnosis and / or monitoring of the piping system without additional expense.

[0055] The second threshold may be, for example, less than the first threshold.

[0056] The second functional deficiency may be, for example, an outward leakage of the pressure source, or an outward leakage of the first pipeline section between the pressure source and the valve.

[0057] The second threshold may be, for example, lower than the pressure rating. For example, the second threshold may be lower than the pressure rating by a maximum of 10%, preferably by a maximum of 5%, particularly preferably by a maximum of 3%, and particularly preferably by a maximum of 1%.

[0058] If a (small) leak occurs in the pipeline, or in the first pipeline section, or in the valve, or in the pressure source, then the pressure in that first pipeline section drops, and therefore the pressure value also decreases. This can be achieved, for example, by a pressure sensor. It can also be achieved by reducing the regulating current of the actuator when it is adjusted to its rated position (the current will at some point become zero). Since the power supply to the actuator is also certain, the moving element of the pressure source moves in the direction of the valve (i.e., in the negative direction) (provided that no position adjustment of the actuator occurs).

[0059] The improved solution stipulates that when the pressure value changes over time beyond a third threshold, a third function deficiency in the pipeline system is identified.

[0060] This allows for the advantageous diagnosis and / or monitoring of the piping system without additional expense—by acquiring changes over time, it is advantageous to detect or identify particularly rapid changes that may be critical to the operation of the clutch operating system. Furthermore, this allows for a very good assessment of the severity of fault scenarios, for example, whether a motor vehicle (equipped with the clutch operating system) can continue operating independently (i.e., using onboard equipment) or should be stopped immediately.

[0061] The third functional failure can be, for example, a leak within the pipeline, a leak in the valve, or an unexpected (rapid) opening of the valve.

[0062] The third threshold can be designed, for example, as a positive change in the pressure value per unit time, that is, as an increase in pressure per unit time (a positive pressure gradient or pressure value gradient).

[0063] If, for example, the pressure value rises very rapidly in the first pipeline section, this may indicate that the valve has opened rapidly. This could occur, for example, when the valve experiences an unintended loss of control, or when the valve ruptures (internal), or when the current to a valve opened in a non-current state is interrupted (e.g., when a wire breaks).

[0064] If the pressure value changes only slowly during the time period, it may indicate only a small leak, such as a valve leak.

[0065] The improved solution specifies that when the pressure value changes over time and falls below a fourth threshold, a fourth functional deficiency in the pipeline system is determined.

[0066] This allows for the advantageous diagnosis and / or monitoring of the piping system without additional expense—by acquiring changes over time, it is advantageous to detect or determine particularly rapid changes that may be critical to the operation of the clutch operating system. Furthermore, this allows for a particularly good assessment of the severity of fault scenarios, for example, whether a motor vehicle (equipped with the clutch operating system) can continue operating independently (i.e., using onboard equipment) or should be stopped immediately.

[0067] The fourth threshold may be, for example, less than the third threshold.

[0068] The fourth threshold can be designed, for example, as a negative change in the pressure value per unit time, that is, as a decrease in pressure per unit time (a negative pressure gradient or pressure value gradient).

[0069] The fourth functional deficiency may be, for example, an outward leakage of the pressure source, an outward leakage of the first pipeline section between the pressure source and the valve, or an outward leakage of the valve.

[0070] A rapid decrease in the pressure value over time may indicate, for example, that the pressure source has a (large) outward leakage, or that the piping in the first piping section has a large outward leakage or has completely ruptured.

[0071] The improved scheme stipulates that a fault signal is provided when at least one of the aforementioned (four) functional failures is determined to exist. A fault signal can also be provided, in principle, when a reliability test of pressure values ​​obtained through different methods results in a value exceeding a threshold, such as when the absolute value of the difference between pressure values ​​from two sources or two sensors exceeds a predetermined threshold. For example, when the pressure obtained by means of a pressure sensor does not match the current consumption of the actuator, and / or does not match the location of the pressure source or the location of the moving part of the pressure source.

[0072] This can advantageously inform external controllers or the driver of a motor vehicle, for example, of a functional failure. Fault signals can be, for example, electrical signals, acoustic signals, visual signals (alarm lights), or tactile signals.

[0073] Alternatively or additionally, the clutch operating system is switched to a safe operating state when at least one of the aforementioned (four) functional failures is determined to be in effect. This can also be triggered in cases of unreasonable pressure values ​​from various sources.

[0074] This can advantageously reduce the danger, for example, to the operator of the clutch operating system or to a third party.

[0075] For example, in the event of a leak in the first pipeline section, the valve can be kept closed for as long as possible to maintain the clutch in the second position, since hydraulic fluid would leak out through the leak once the valve is opened. Instructions can be issued that a workshop should be located, or that the vehicle should be stopped as soon as possible depending on the amount of leakage.

[0076] In the event of a small internal leak in the valve, the operator of the vehicle may be directed to immediately seek a workshop. This is because, in principle, the second position of the clutch can be achieved, for example, by a higher power supply to the actuator.

[0077] Advantageously, the clutch is a motor vehicle clutch. This allows the vehicle to operate with very little energy consumption from the actuator.

[0078] For example, the clutch could be a disengagement clutch between the internal combustion engine and the electric motor in a parallel hybrid (motor) vehicle. For example, in the second position, the clutch disengages the internal combustion engine from the transmission, thereby enabling the vehicle to operate, for example, purely electric. Consequently, the vehicle's battery can advantageously be used for electric operation for a longer period because the actuator requires less current.

[0079] According to a second aspect of the invention, a controller is provided, for example, for running a clutch operating system.

[0080] The controller is configured to execute the method described above.

[0081] This advantageously creates a compact hardware implementation for installation, for example, in motor vehicles, thereby enabling particularly easy operation and / or monitoring of the clutch operating system.

[0082] According to a third aspect of the present invention, a clutch operating system is proposed.

[0083] The clutch system, or clutch operating system, has the following features:

[0084] -- Clutch, which is hydraulically displaced from a first position to a second position against a return force;

[0085] -- A pressure source that can be operated by an electric actuator;

[0086] -- A piping system, including pipes and valves arranged in the pipes.

[0087] The pipeline hydraulically connects or couples the pressure source to the clutch, wherein the valve is capable of opening in an open state and disconnecting the hydraulic connection or coupling between the pressure source and the clutch in a closed state. The clutch operating system further includes a controller as described above.

[0088] This advantageously results in a clutch operating system that operates with particularly high energy efficiency and is compact in construction. It also advantageously enables monitoring of the piping system or the clutch operating system, thereby resulting in a clutch operating system that operates with exceptional safety and efficiency. Attached Figure Description

[0089] Further features and advantages of the present invention will become apparent to those skilled in the art from the following description of exemplary embodiments, with reference to the accompanying drawings; however, these embodiments should not be construed as limiting the invention.

[0090] Figure 1 A schematic diagram of the drivetrain of a hybrid vehicle with a clutch operating system is shown.

[0091] Figure 2 Showing from Figure 1 A schematic diagram of the clutch operating system;

[0092] Figures 3a-3d Showing from Figure 2Different states of the clutch operating system;

[0093] Figure 4 The clutch operating system is shown in Figures 3a-3d A diagram illustrating the different parameters during the period of the state shown;

[0094] Figure 5 A schematic diagram of the adjustment of the actuator of the clutch system is shown;

[0095] Figure 6 A flowchart is shown for a method for running a clutch operating system. Detailed Implementation

[0096] Figure 1 A schematic diagram of a motor vehicle 80 (e.g., an automobile or truck) with a clutch operating system 10 is shown. The motor vehicle 80 has an internal combustion engine 1 and an electric motor 2, which can also operate as a generator and is also suitable for starting the internal combustion engine 1. A clutch operating system 10 with a clutch 3 is arranged between the internal combustion engine 1 and the electric motor 2 (see also...). Figure 2 The clutch 3 is configured herein as a disengaging clutch only by way of example. A transmission 4 (e.g., a gearbox or, if necessary, an automatic transmission with a torque converter) is adjacent to the motor 2; this transmission may have an additional clutch. A differential 5 is adjacent to it, via which the wheels 6 (only one wheel 6 is shown here) of the motor vehicle 80 are driven.

[0097] Figure 2 Showing from Figure 1 A schematic diagram of the clutch operating system 10. The clutch operating system 10 has:

[0098] -- Clutch 3, which is hydraulically movable from a first position P1 to a second position P2 against a return force (only the first position P1 is shown here).

[0099] -- Pressure source 7, which can be operated by an electric actuator 11;

[0100] -- Piping system 50, having a pipe 8 and a valve 9 arranged in the pipe 8, wherein the pipe 8 hydraulically connects a pressure source 7 to a clutch 3, wherein the valve 9 is capable of opening in an open state (valve 9 open) and shutting off in a closed state (valve 9 closed or shut off) the hydraulic connection between the pressure source 7 and the clutch 3.

[0101] In this embodiment, the pressure source 7 is implemented by an active cylinder 12 and an active cylinder piston 13 that can be movably moved therein. It goes without saying that other implementations are also possible.

[0102] At the clutch-side end of the conduit 8, a driven cylinder 14 with a driven piston 15 is provided, by way of example only. Hydraulic pressure can be transmitted to the clutch 3 via this driven cylinder, thereby allowing the clutch 3 to be moved, for example, from the first position P1 to the second position P2. In this embodiment, a spring 16 is provided in the driven cylinder 14, which applies a return force (which, if necessary, is added to the elastic force of the clutch 3) without pressure, thereby causing the driven piston 15 to be pressed to the left in the figure, and the clutch 3 to be pressed from the second position P2 or moved to the first position P1.

[0103] In the illustrated embodiment, the first position P1 can, for example, indicate the closed state of the clutch 3, and the second position P2 can, for example, indicate the open state.

[0104] The first pipeline section 18 is arranged between the pressure source 7 and the valve 9. The second pipeline section 19 is arranged between the valve and the clutch 3 (or, in this case, the driven cylinder 14).

[0105] An inlet (protruding upwards) for hydraulic fluid is indicated at the active cylinder 12, which can be connected to a container not shown here.

[0106] The clutch operating system 10 may also have a controller, not shown herein, on which a method for operating and / or monitoring the clutch operating system 10 can be executed.

[0107] exist Figures 3a-3d The text shows information from... Figure 2 The clutch operating system 10 has different states. Each state is represented by a circled number (1 to 4), which indicates the different states of the clutch system. Figure 4 It is also used to mark the state. Figures 3a to 3d Different shaded lines indicate different pressure levels in the piping system 50, specifically in the first piping section 18 and the second piping section 19. The denser the shaded lines, the higher the pressure.

[0108] exist Figure 3aThe original state is shown. The actuator 11 (which may be, for example, an electric motor or a brushless DC motor) is, for example, not powered and has no torque (no rotation arrow is shown in the actuator 11). The clutch 3, not shown here, is in the first position P1, and the valve 9 is in the open state, or has been switched to the open state. The pressure source 7 of the actuator 12, configured with the actuator piston 13, and the piping system 50 are (as far as possible) unpressurized (very sparse shaded lines). The actuator piston 13 is in the first case d1.

[0109] exist Figure 3b The diagram illustrates the following state in which the actuator 11 (e.g., with a current of 15A) is powered. The actuator now provides high torque or high force—this is indicated by a large rotating arrow in the actuator 11. The pressure source 7 applies high pressure to the piping system 50 (e.g., between 10 bar and 60 bar, such as 15 bar, 30 bar, 40 bar, or 50 bar), and the clutch 3 (not shown here) has moved toward the second position P2, for example, until it reaches the desired position, which could be, for example, the second position P2. The drive cylinder piston 13 is in the second case d2 (to the right of the first case d1 in this figure, where the axis of the case is shown to have a larger value from right to left). The second case can be used as a starting point, for example, the rated position d_Soll, for position adjustment or control of the actuator 11. The valve 9 remains open, thus filling the first piping section 18 with high pressure, for example, 15 bar or 30 bar. This is indicated by very dense shading. It is feasible to achieve maximum pressure on the path of the clutch 3 from the first position P1 to the second position P2.

[0110] exist Figure 3c The diagram illustrates the following state: in this state, valve 9 has already transitioned to the closed state; however, actuator 11 further utilizes... Figure 3b The current in the state is used to supply power (e.g., 15A). Therefore, the first conduit section 18 is also filled with high pressure (e.g., 15 bar, 30 bar, 40 bar, or 50 bar), see [link to documentation]. Figure 3b The clutch 3 will also remain in the absence of current in the actuator 11. Figure 3b At the position reached, the hydraulic fluid cannot flow back to the first pipeline section 18 due to the closed valve 9.

[0111] exist Figure 3dThe diagram illustrates a state in which the actuator 11 is adjusted such that the pressure value DG is adjusted to a pressure value rating DG_Soll greater than zero, whereby DG represents the pressure in the piping system 50 on the side of the valve 9 facing the pressure source 7 (e.g., in the first piping section 18). The pressure value rating DG_Soll is reduced here, for example, by a margin greater than 50%, compared to the pressure value DG before the valve 9 transitions to the closed state, for example, to approximately 10% of its maximum value, or to approximately 10% of the pressure value filled before the valve 9 is closed. This is illustrated by medium-density shading in the first piping section 18. In contrast, in the second piping section 19, a pressure from... Figure 3c High pressure (very dense shading).

[0112] For example, by means of a pressure sensor not shown here or by means of the current consumption of the actuator 11, the pressure value rating DG_Soll can be adjusted by the following method: from the pressure sensor not shown here or by means of the current consumption of the actuator 11. Figure 3c Starting from the state, the actuator 11 (e.g., in a fraction of a millimeter) returns slightly, thereby shifting the active cylinder piston 13 to the left. This allows the compressed hydraulic fluid in the first line section 18 to be released, and the pressure or pressure value in the first line section 18 to decrease.

[0113] The active cylinder piston 13 is currently in the third scenario d3.

[0114] The third case d3 reached when the pressure value DG_Soll is reached can then be stored, for example, as a modified rated case d_Soll,corr., and the actuator can be adjusted to that position, that is, adjusted such that the active cylinder piston 13 remains at the modified rated case d_Soll,corr.

[0115] This method advantageously and significantly reduces the current consumption of the actuator 11 (e.g., to 0.5A or 1A), compared to the current from... Figure 3b and Figure 3c Compared to the previous state, this also reduces the torque or force of the actuator 11, as shown by the small rotating arrow in the actuator 11. At the same time, the actuator 11 remains in the adjusted operating state and is able to respond quickly and accurately to sudden pressure changes in the piping system 50 (i.e., without recalibrating the position).

[0116] The adjustment can be additionally combined with adjustment limits, which are here represented by a minimum case d_min and a maximum case d_max. If, for example, during the position adjustment or position control and / or pressure value adjustment or pressure value control, it is determined that: for example, the regulating current of the actuator 11 increases above the first threshold or decreases below the first threshold, then a first functional failure or a second functional failure of the clutch operating system 10 can be inferred (as described earlier). Similarly, a functional failure of the clutch operating system 10 can be inferred when the maximum case d_max is exceeded or when the minimum case d_min is not exceeded.

[0117] Figure 4 The clutch operating system 10 is shown in Figures 3a-3d The diagram illustrates the different parameters during the period of the shown state. The top row shows the parameters from... Figure 1 Two different driving states of the motor vehicle (hybrid driving when clutch 3 is in the first position P1, and electric driving when clutch 3 is in the second position P2).

[0118] The next line shows the state of valve 9 (open state versus closed state).

[0119] The following three graphs consistently represent time on the X-axis. The vertical line (dashed line) indicates that... Figures 3a to 3d The state shown in the figure.

[0120] The top figure shows the change curve of the active cylinder piston 13 (shown on the y-axis). The active cylinder piston first moves from the first situation d1 to the second situation d2. Then, after the valve 9 is closed, the active cylinder piston returns to the third situation d3 by means of the return of the actuator 11. This third situation corresponds to the rated situation d_Soll for maintaining the pressure value rating DG_Soll (when the piping system 50 is not damaged).

[0121] The middle graph shows the pressure p (which corresponds to the pressure value DG) on the y-axis, or the pressure value DG—a solid line for the first conduit section 18 and a dashed line for the second conduit section. A steep rise is initially visible until the clutch 3 is moved into the second position P2. The pressure then decreases slightly (related to the spring characteristics of the clutch operating system 10). After the valve 9 is closed, the pressure p, or pressure value DG, in the second conduit section 19 remains constant, thus keeping the clutch 3 in the second position P2. In contrast, due to the reduced power supply to the actuator 11 and therefore the reduced pressure from the pressure source 7, the pressure p in the first conduit section 18 decreases to a value greater than zero, but is approximately 90% lower than the pressure before the valve 9 was closed.

[0122] The graph below shows the regulating current of the actuator 11 on the y-axis. This regulating current is almost identical to the curve of the pressure p in the first conduit section 18 from the middle graph. In the relaxed state, the actuator 11, however, remains powered and, in this embodiment, is regulated or controlled to the position of the drive cylinder piston 13, or the rated condition d_Soll.

[0123] As described above, the state of the piping system 50 (especially the first piping section 18 of the piping system, or the clutch operating system 10) can be inferred from changes in the pressure value DG (e.g., the regulating current consumed by the actuator 11 and / or the pressure of the pressure sensor and / or the active portion of the pressure source 7) or from the numerical value of the change in the pressure value DG over time. If a certain threshold is exceeded or not exceeded, this may indicate a malfunction or internal leakage in the piping 8 or valve 9, or it may indicate an external leakage in the piping 8 or pressure source 7.

[0124] Figure 5Shows a schematic diagram of the exemplary adjustment or control of the actuator 11 of the clutch operating system 10. As an input value, the second situation d2 of the master cylinder piston 13 is first pre-given as the nominal situation d_Soll. After closing the valve 9, the current flowing through the actuator 11 and / or the pressure of the pressure sensor in the first pipeline section 18 is detected and fed to a comparison element. There, the detected current I_Ist and / or the detected pressure p_Ist or the detected pressure value DG_Ist (exemplarily shown here: DG_Ist, I_Ist) is compared with a nominal value, which corresponds to the pressure value nominal value DG_Soll (here, exemplarily I_Soll or DG_Soll). As long as the two values are not the same, the comparison element changes the situation correction value d_corr such that the deviation is reduced (which then results in a new value d_Soll,corr.). This new value d_Soll,corr. is given to the actuator 11, and the generated current or pressure (or other values related to the pressure value DG) is detected again. Once there is no longer a deviation between the detected pressure value DG_Ist and the pressure value nominal value DG_Soll, the correction value d_corr remains constant. The resulting nominal position d_Soll,corr. is relative to the third situation d3 here.

[0125] When exceeding a certain threshold (for example, for the correction value d_corr or for the resulting nominal value d_Soll,corr.) in one direction or the other, a fault signal can be triggered, for example. In the case where the threshold exceeds "d_max" or the threshold does not exceed "d_min", this corresponds to the downward path and the check blocks ">d_max", "<d_min" and the adjacent block "diagnosis".

[0126] It can also be set that the detection of the diagnostic value only starts after the pressure value nominal value DG_Soll is reached for the first time or starts in other channels. Then it can be determined whether an unexpected change (if necessary, an unexpected change rate of the pressure value) has occurred in the pressure value DG starting from the initial state. If so, a fault signal can be triggered or issued, and / or a safe operating state can be activated.

[0127] Figure 6 Shows a flow chart for the method of operating and / or monitoring the clutch operating system 10.

[0128] The method has the following steps:

[0129] -- Move the clutch 3 200 degrees toward the second position P2;

[0130] -- Switch valve 9 to the closed state;

[0131] -- The actuator 11 of 400 is adjusted such that the pressure value DG is adjusted to a pressure value rating DG_Soll greater than zero, which represents the pressure in the piping system 50 on the side of the valve 9 facing the pressure source 7, wherein the pressure value rating DG_Soll is reduced by more than 50% compared to the pressure value DG before the valve 9 is switched to the closed state.

[0132] Alternatively, two steps 100 and 110, indicated by dashed lines and not important to the method, can be placed before steps 200, 300, and 400:

[0133] -- Switch valve 9 to the open state;

[0134] -- Powering the actuator 11 to the actuator 11 in such a way that the clutch 3 is moved toward the second position P2.

Claims

1. A method for running a clutch operating system, in, The clutch operating system (10) has: -- Clutch (3), which is hydraulically displaced from a first position (P1) to a second position (P2) against a return force; -- Pressure source (7), which can be operated by an electric actuator (11); -- Piping system (50), with pipes (8) and valves (9) arranged in the pipes (8); The pipeline (8) hydraulically connects the pressure source (7) to the clutch (3). The valve (9) is capable of opening in the open state and disconnecting the hydraulic connection between the pressure source (7) and the clutch (3) in the closed state. The method comprises the following steps: -- Move the clutch (3) toward the second position (P2) (200); -- Switch the valve (9) (300) to the closed state; -- Adjust (400) the actuator (11) such that the pressure value (DG) is adjusted to a pressure value rating (DG_Soll) greater than zero, the pressure value representing the pressure in the piping system (50) on the side of the valve (9) facing the pressure source (7); The pressure rating (DG_Soll) is reduced compared to the pressure value (DG) before the valve (9) is switched to the closed state. The state of the pipeline system (50) is inferred from the pressure value (DG).

2. The method according to claim 1, in, The pressure value rating (DG_Soll) is located between 0.1% and 20% of the maximum value of the pressure value (DG), and the pressure value rating is necessary to move the clutch (3) from the first position (P1) to the second position (P2).

3. The method according to claim 1 or 2, in, The pressure value (DG) is a pressure.

4. The method according to claim 3, in, The pressure is obtained by means of a pressure sensor connected to the pressure source (7) or to a first pipeline section (18) between the pressure source (7) and the valve (9).

5. The method according to claim 1 or 2, in, The pressure value (DG) corresponds to a current that flows through the actuator (11) to operate the actuator (11).

6. The method according to claim 5, wherein, The current is the current flowing through the actuator (11) during the process of the actuator (11) adjusting the pressure source (7) or the active part of the pressure source (7) to the rated position or rated condition (d_Soll).

7. The method according to claim 1 or 2, in, The pressure value (DG) corresponds to the position change of the pressure source (7) or the position change of the active part of the pressure source (7) after the valve (9) is closed.

8. The method according to claim 1 or 2, in, When the pressure value (DG) exceeds a first threshold, a first functional deficiency is determined in the piping system (50).

9. The method according to claim 8, wherein, The first functional failure is a leak in the valve (9) within the pipeline (8).

10. The method according to claim 1 or 2, in, When the pressure value (DG) drops below the second threshold, a second functional deficiency in the piping system (50) is determined.

11. The method according to claim 10, in, When the pressure value (DG) exceeds a first threshold, a first functional deficiency is determined in the piping system (50). Wherein, the second threshold is less than the first threshold, wherein the second functional failure is an outward leakage of the pressure source (7) or an outward leakage of the first pipeline section (18) between the pressure source (7) and the valve (9).

12. The method according to claim 1 or 2, in, When the change in the pressure value (DG) over time exceeds the third threshold, a third functional deficiency is determined in the piping system (50).

13. The method according to claim 12, in, The third functional failure is a leak within the pipeline (8) or the opening of the valve (9).

14. The method according to claim 1 or 2, in, When the change in pressure value (DG) over time drops below the fourth threshold, a fourth functional deficiency is determined in the piping system (50).

15. The method according to claim 14, in, When the change in the pressure value (DG) over time exceeds a third threshold, a third functional deficiency is determined in the piping system (50). Wherein, the fourth threshold is less than the third threshold. The fourth functional deficiency is either an outward leakage of the pressure source (7) or an outward leakage of the first pipeline section (18) between the pressure source (7) and the valve (9).

16. The method according to claim 8, in, When it is determined that at least one of the aforementioned functional deficiencies exists, then... -- Provide a fault signal; and / or -- Transition the clutch operating system (100) to a safe operating state.

17. The method according to claim 1 or 2, in, The clutch (3) is the clutch of the motor vehicle (80).

18. A controller for running a clutch operating system, wherein, The controller is configured to perform the method according to any one of claims 1 to 17.

19. A clutch operating system, wherein the clutch operating system has: -- Clutch (3), which is hydraulically displaced from a first position (P1) to a second position (P2) against a return force; -- Pressure source (7), which can be operated by an electric actuator (11); -- Piping system (50), with pipes (8) and valves (9) arranged in the pipes (8); in, The pipeline (8) hydraulically connects the pressure source (7) to the clutch (3). The valve (9) is capable of opening in the open state and disconnecting the hydraulic connection between the pressure source (7) and the clutch (3) in the closed state. -- The controller (11) according to claim 18.

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