Hydraulic valve system of a parking lock device

An electrohydraulic transmission control system (1) includes a parking lock valve (2). The electrohydraulic transmission control system (1) is configured such that, during normal operation of the electrohydraulic transmission control system (1) in which at least one electrohydraulic pressure adjuster (EDSSYS) is actuatable with current, the parking lock valve (2) can be held in a defined operating state in which an actuation pressure (p_sys) acts on a parking lock cylinder (3) above a normal pressure level. The electrohydraulic transmission control system (1) is configured such that, during emergency operation of the electrohydraulic transmission control system (1) in which the at least one electrohydraulic pressure adjuster (EDSSYS) is not fed with current and the actuation pressure (p_sys) is at least temporarily set to an emergency pressure level higher than the normal pressure level by the at least one pressure source (7), a pressure level of the actuation pressure (p_sys) that holds the parking lock valve (2) in the defined operating state corresponds at least approximately to the emergency pressure level.

FIELD OF THE INVENTION

The invention relates generally to an electrohydraulic transmission control system having a parking lock valve.

BACKGROUND

The applicant's patent application DE 10 2015 211 298.5, which does not constitute a prior publication, discloses a hydraulic system of an automatic transmission having a hydraulically actuable parking lock unit. A parking lock valve is configured with multiple valve pockets formed in the region of a valve housing, by which an actuation pressure of the parking lock unit, which actuation pressure prevails in a manner dependent on a supply pressure, can be applied to said parking lock unit. The valve pockets can be placed in operative connection with one another, or separated from one another, by a valve slide which is longitudinally displaceable in the valve housing. The valve slide is spring-loaded in the direction of a first axial position which corresponds to a first operating state of the parking lock valve and in which, in turn, an actuation pressure can be applied to the parking lock unit at which the parking lock transitions into the engaged operating state. In the region of a control surface of the valve slide, a pressure signal which acts in the direction of a second axial position of the valve slide, which corresponds to a second operating state of the parking lock valve, can be introduced by applying an actuation pressure to the parking lock unit, which actuation pressure transfers a parking lock of the parking lock unit into the disengaged operating state.

If a fault arises in the transmission system during operation with the parking lock disengaged, which fault leads to the deactivation of the electrical supply of the transmission actuators, the automatic transmission switches to so-called hydraulic emergency operation. During hydraulic emergency operation the parking lock valve is held in the operating state which corresponds to the disengaged operating state of the parking lock, by the pressure in the primary system pressure circuit in the region of a control surface of the valve slide of the parking lock valve, which control surface corresponds to a differential surface between two facing face surfaces of two valve slide sections configured with different diameters, counter to the spring force, until the system pressure falls below a defined pressure threshold which is dependent on the size of the differential surface and on the spring force.

Said pressure threshold is configured for driving states in which a clutch gear logic is implemented without actuation of a shift element which is actuated by the pressure signal. In the absence of a pressure signal and in the presence of a simultaneously low torque to be transmitted via the automatic transmission, the hydraulic system is operated with a low system pressure level in order to improve an efficiency of the automatic transmission. This means that, for the least possible power consumption of the transmission system, it is sought to achieve the lowest possible system pressures in the consumption-relevant operating range. This however has the result that the self-holding pressure of the parking lock valve lies below the minimum system pressure level, because otherwise, the parking lock cannot, in the presence of low system pressures, be held any longer in the disengaged operating state by the system pressure.

Owing to the selection of the features of the characteristic curves of the actuators, the shift elements of the automatic transmission are, in emergency operation, actuated in unpressurized fashion, while the system pressure assumes its maximum value. In the event of a transition to hydraulic emergency operation, it is additionally the case that the electromechanical locking mechanism of the parking lock is deactivated, with the result that inadequate hydraulic actuation of the parking lock device during emergency operation results in an immediate actuation of the parking lock device in the direction of the engaged operating state.

To be able to briefly compensate undersupplied operating states of the hydraulic system during a normal operating state of the automatic transmission, and to be able to operate the automatic transmission with high spontaneity over a large operating range of a vehicle drivetrain, it is possible for the above-described primary system pressure circuit to be implemented with a hydraulic fluid volume accumulator known from DE 10 2013 209 932 A1. For this purpose, a hydraulic fluid volume is temporarily stored counter to a spring force of a spring device in the region of the hydraulic fluid volume accumulator, which hydraulic fluid volume can, in accordance with demand, be introduced into the line system of the hydraulic system downstream of a check valve device. During hydraulic emergency operation of the automatic transmission, the hydraulic fluid volume accumulator is fully charged by the system pressure set to a maximum, and is preloaded to its maximum pressure value.

If a vehicle in which the transmission is in hydraulic emergency operation is shut down, a transmission main pump driven by the drive machine conveys no further hydraulic fluid volume into the hydraulic system, as is known. The previously set maximum system pressure thereby collapses, until it reaches the maximum pressure level of the hydraulic fluid volume accumulator. From this point in time onward, all actuated pressures in the hydraulic system are determined by the discharge pressure of the hydraulic fluid volume accumulator, and as a result both the system pressure and a pressure set with a falling characteristic curve in the region of a system pressure regulator assume the same pressure level.

From said point in time onward the gradient with which the system pressure in the primary pressure circuit is dissipated is dependent only on the leakage of the primary pressure circuit, and is thus highly dependent on the present operating temperature of the transmission. In particular in the presence of low operating temperatures, the leakage volume flows of the primary pressure circuit are very small. Since the minimum discharge pressure of the hydraulic fluid volume accumulator is above the self-holding pressure threshold of the parking lock valve, the engagement of the parking lock after the shutdown of the vehicle is delayed, however, to an undesired extent.

SUMMARY OF THE INVENTION

In example embodiments, the present invention provides an electrohydraulic transmission control system having a parking lock valve, by which a transmission can be operated in an as far as possible optimized manner in terms of efficiency and with high spontaneity, and by which a parking lock can, even in the event of a transition to emergency operation, be transferred into the engaged operating state within defined operating times.

In the case of the electrohydraulic transmission control system according to example aspects the invention having a parking lock valve by which a parking lock cylinder of a parking lock device can be charged with an actuation pressure which can be set in an operating-state-dependent manner by at least one electrohydraulic pressure adjuster and/or one pressure source, it is possible for the parking lock valve to be held in a defined operating state in which the actuation pressure acts on the parking lock cylinder during normal operation of the electrohydraulic transmission control system during which the electrohydraulic pressure adjuster is actuable with current and during which the actuation pressure is above a normal pressure level.

According to example aspects the invention, the electrohydraulic transmission control system is configured such that the pressure level of the actuation pressure for holding the parking lock valve in the defined operating state during emergency operation, during which the electrohydraulic pressure adjuster is not fed with current and the actuation pressure is at least temporarily set to an emergency pressure level higher than the normal pressure level by the pressure source, corresponds at least approximately to the emergency pressure level.

In this way, it is ensured in a simple manner during the normal operation of the electrohydraulic transmission control system that the parking lock device can be held in the disengaged operating state by a low actuation pressure which has an efficiency-optimized pressure level. At the same time, the pressure level of the actuation pressure for holding a parking lock valve in the defined operating state is, during emergency operation, increased to a higher pressure level in relation to normal operation. It is thereby ensured that a shutdown of a vehicle during emergency operation, and a hydraulic fluid volume accumulator discharging into a primary pressure circuit, do not impede a desired spontaneous engagement of a parking lock device.

In an advantageous variant of the electrohydraulic transmission control system, the parking lock valve, during normal operation of the electrohydraulic transmission control system, can be charged with a pressure signal which is adjustable in the region of a further electrohydraulic pressure adjuster and which can be applied to the parking lock valve in the direction of the defined operating state thereof. Thus, during normal operation of the electrohydraulic transmission control system, not only the actuation pressure of the parking lock device prevails at the parking lock valve but also, during defined operating states, a further pressure signal by which the parking lock valve can be actuated in the direction of the operating state which holds the parking lock device hydraulically in the disengaged state. During such operating state profiles, the actuation pressure can, in relation to an operating state of the parking lock valve during which the parking lock valve is held in its defined operating state by the actuation pressure alone, be reduced to an extent which improves the efficiency of the transmission, and it is still possible for the parking lock valve to be arrested in the defined operating state.

If the parking lock valve, during normal operation of the electrohydraulic transmission control system, can be charged with a pressure signal which is adjustable in the region of an additional electrohydraulic pressure adjuster and which can be applied to the parking lock valve in a direction of action counter to the defined operating state, the parking lock valve can be transferred, counter to the self-holding action, into an operating state in which the actuation pressure in the region of the parking lock valve is isolated from the parking lock cylinder and the parking lock device can be engaged as desired.

In a refinement of the electrohydraulic transmission control system that is expedient in terms of costs and installation space, the parking lock valve, during normal operation of the electrohydraulic transmission control system, can be charged with a pressure signal which corresponds to an actuation pressure of a shift element and which can be applied to the parking lock valve acting in the direction of the defined operating state thereof. In this embodiment of the electrohydraulic transmission control system, the actuation pressure that has to be imparted in order to realize the self-holding action of the parking lock valve can, in the presence of a correspondingly applied actuation pressure of the shift element, likewise be reduced to an extent which increases efficiency, whereby the transmission control system can be operated with a low system pressure which is expedient in terms of efficiency, without causing an undesired engagement of the parking lock.

In further advantageous embodiments of the electrohydraulic transmission control system according to the invention, the parking lock valve, during normal operation and/or emergency operation of the electrohydraulic transmission control system, can be charged, respectively, with a pressure signal which is adjustable in the region of the electrohydraulic pressure adjuster and which can be applied to the parking lock valve in a direction of action counter to the defined operating state.

Thus, the self-holding function of the parking lock valve can be deactivated by the pressure signal which can be adjusted in the region of the electrohydraulic pressure adjuster, or the self-holding threshold of the parking lock valve in the defined operating state can be varied. Furthermore, according to the invention, the self-holding threshold of the parking lock valve can be varied, even during emergency operation, by the pressure signal which can be adjusted in the region of the electrohydraulic pressure adjuster, in such a way that, when a vehicle is shut down proceeding from emergency operation, the parking lock device can be transferred into its engaged operating state within desired short operating times.

If the pressure signal which can be adjusted in the region of the electrohydraulic pressure adjuster can additionally be applied in the region of a system pressure valve, the actuation pressure being adjustable by the system pressure valve in a manner dependent on the pressure signal and on a pressure provided by a further pressure source, it is the case, with corresponding design of the electrohydraulic pressure adjuster, that the actuation pressure assumes its maximum value during emergency operation with little outlay, and the parking lock valve is reliably transferred into its defined operating state, in which the parking lock device is held in its disengaged operating state. Furthermore, the self-holding threshold of the parking lock valve during emergency operation is set to a pressure level such that an evacuation of a hydraulic fluid volume accumulator, which occurs upon shutdown of a vehicle, does not prevent a desired engagement of the parking lock device within defined operating times.

In a further advantageous embodiment of the electrohydraulic transmission control system according to the invention, the pressure level of the actuation pressure for holding the parking lock valve in its defined operating state is configured to be higher than the emergency pressure level if the pressure source is in the form of a pump device which provides the emergency pressure level, because a pump device permanently provides a constant pressure level.

By contrast to this, the pressure level of the actuation pressure for holding the parking lock valve in its defined operating state during emergency operation is configured to be higher or lower than the emergency pressure level by a defined pressure offset value, or is equal to the emergency pressure level, if the pressure source is in the form of a pressure medium accumulator which temporarily provides the emergency pressure level.

Here, in the design variant of the electrohydraulic transmission control system in which the pressure level of the actuation pressure for holding the parking lock valve in the defined operating state is higher than the emergency pressure level, it is reliably ensured that the evacuation of the pressure medium accumulator or of the hydraulic fluid volume accumulator does not delay the engagement of the parking lock device, whereas, in the case of the two further design variants, in which the pressure level of the actuation pressure is less than or equal to the emergency pressure level, at least short delays can occur before the engagement of the parking lock device.

In the two latter design variants, the parking lock device is transferred into the engaged operating state at the latest when the actuation pressure generated in the electrohydraulic transmission control system as a result of the evacuation of the pressure medium accumulator or, more specifically, of the hydraulic fluid volume accumulator decreases below the pressure level of the actuation pressure for holding the parking lock valve in the defined operating state during emergency operation.

In an embodiment of the electrohydraulic transmission control system which is of structurally simple design and which can be actuated with little outlay, the parking lock valve includes a valve slide which is arranged in longitudinally displaceable fashion in a housing and which is acted on counter to the defined operating state of the parking lock valve, by a spring force of a spring device, and to which, in the region of control surfaces, the actuation pressure and the pressure signals can be applied.

The parking lock device can be actuated with little outlay, and a disengagement of the parking lock device can be prevented in a structurally simple manner, if the actuation pressure is, in a first switching position of the valve slide of the parking lock valve, isolated from the parking lock cylinder in the region of the parking lock valve.

If the actuation pressure of the parking lock device can, in a second switching position of the valve slide of the parking lock valve, be applied in the region of the parking lock cylinder and in the region of two facing control or face surfaces of two valve slide regions of the valve slide, the diameters of which differ from one another such that the actuation pressure results in an actuating force acting on the valve slide in the direction of the second switching position, the self-holding action of the parking lock valve can be realized with a small installation space requirement for the parking lock valve, and can be implemented by a one-piece, stepped valve slide.

In an embodiment of the electrohydraulic transmission control system which is likewise expedient in terms of installation space, the pressure signal which is adjustable in the region of the additional electrohydraulic pressure adjuster can be applied in the region of a control surface of the valve slide of the parking lock valve, such that, when the pressure signal is applied, an actuating force acting in the direction of the first switching position acts on the valve slide.

The electrohydraulic transmission control system according to the invention can be designed expediently in terms of installation space, by a one-piece, stepped valve slide in the region of the parking lock valve, if the pressure signal which is adjustable in the region of the additional electrohydraulic pressure adjuster can be applied in the region of a control surface of the valve slide of the parking lock valve, such that, when the pressure signal is applied, an actuating force acting in the direction of the first switching position acts on the valve slide.

In a refinement of the electrohydraulic transmission control system which can likewise be implemented with a one-piece, stepped valve slide of the parking lock valve, the pressure signal of the electrohydraulic pressure adjuster is, in the second switching position of the valve slide of the parking lock valve, applied in the region of two facing face surfaces of two valve slide regions of the valve slide, the diameters of which differ from one another such that an actuating force acting on the valve slide in the direction of the first switching position results from the actuation pressure.

In an embodiment of the electrohydraulic transmission control system according to the invention which is easy to operate, the electrohydraulic pressure adjuster is designed as a pressure adjuster with a falling pressure characteristic curve versus the actuation current, and the further electrohydraulic pressure adjuster and the additional electrohydraulic pressure adjuster are designed as pressure adjusters with a rising pressure characteristic curve versus the actuation current, whereas the actuation pressure increases with increasing pressure signal of the electrohydraulic pressure adjuster, the actuation pressure of the shift element during emergency operation being at least approximately equal to zero or having a pre-fill pressure level.

In an embodiment of the electrohydraulic transmission controller according to the invention which can be designed with greater degrees of freedom, the valve slide of the parking lock valve includes two separate valve slide parts which are arranged spaced apart from one another in an axial direction in the housing, and so that they are longitudinally displaceable relative to one another and between which the spring device is arranged, wherein the first valve slide part can be transferred into its first axial position by the second valve slide part.

In a structurally simple embodiment of the electrohydraulic transmission control system, the second valve slide part is spring-loaded by the spring device in the direction of a stop, and can be displaced counter to the spring force of the spring device, in the direction of the first valve slide part, by the pressure signal of the additional electrohydraulic pressure adjuster.

Both, the features specified in the patent claims and the features specified in the following exemplary embodiments of the electrohydraulic transmission control system according to the invention are suitable, in each case individually or in any desired combination with one another, for refining the subject matter according to the invention.

Further advantages and advantageous embodiments of the electrohydraulic transmission control system according to the invention will emerge from the patent claims and from the exemplary embodiments described in principle below with reference to the drawings, wherein, in the following description, for the sake of clarity, the same reference designations are used for structurally and functionally identical components.

DETAILED DESCRIPTION

FIG. 1shows a hydraulic layout of an embodiment of an electrohydraulic transmission control system1having a parking lock valve2, by which a parking lock cylinder3can be charged with an actuation or system pressure p_sys. The electrohydraulic transmission control system1is provided for actuating a transmission, preferably an automatic transmission, in which eight ratios for forward travel and at least one ratio for reverse travel can be realized. During the realization of the ratios, a power flow can be enabled between a transmission input shaft and a transmission output shaft in each case by selective activation and deactivation of shift elements A to E of the transmission. Furthermore, a so-called neutral operating state can be realized in the region of the transmission during which the power flow between the transmission input shaft and the transmission output shaft is disconnected through corresponding actuation of the shift elements A to E. Furthermore, a “parking operating state” can be realized by the transmission, during which the transmission output shaft is, in a manner known per se, held rotationally fixed by a parking lock device which can be actuated by the parking lock cylinder3.

The shift elements A to E can be charged with actuation pressures p_A to p_E which are adjustable in the region of valve devices KVA to KVE. In the non-actuated operating state, a pre-fill pressure p_VB1or p_VB2, respectively, prevails at the valve devices KVA to KVE. Furthermore, a converter lock-up clutch WK can be charged with an actuation pressure p_WK which is adjustable in the region of a converter clutch valve WKV. Electrohydraulic pressure adjusters EDSA to EDSE and EDSWK are assigned to each of the valve devices KVA to KVE and WKV, the system pressure p_sys which is adjustable in the region of a system pressure valve4prevailing at the electrohydraulic pressure adjusters EDSA to EDSE and EDSWK in the region of which in each case one pilot pressure p_EDSA to p_EDSE and p_EDSWK can be adjusted.

By a preferably mechanically driven pump device5, which constitutes a pressure source of the electrohydraulic transmission control system1, a supply pressure is provided, which prevails in the region of the system pressure valve4, when a drive machine of a vehicle drivetrain including the gearbox is active. At the system pressure valve4, a pilot pressure p_EDSSYS can be applied which is adjustable in the region of an electrohydraulic pressure adjuster EDSSYS, the pilot pressure p_EDSSYS acting in the same direction as a spring device6, to a valve slide41of the system pressure valve4, wherein, in the present case, the system pressure p_sys increases with increasing pilot pressure p_EDSSYS.

In order to be able, in certain operating situations of the transmission, to briefly compensate instances of undersupply from the pump device5, a hydraulic fluid volume accumulator7is provided, in the region of which a hydraulic fluid volume can be temporarily stored counter to the spring force of a spring device8, which hydraulic fluid volume can, in accordance with demand, be introduced into the line system of the electrohydraulic transmission control system1downstream of a check valve device9. In this way, a hydraulic supply can be provided to the transmission control system1as desired within short operating times.

In addition to the shift elements A to E, the transmission includes a launch component10which in the present case is designed as a hydrodynamic torque converter and which can be locked up, in a manner dependent on the operating state, by the converter lock-up clutch WK. The launch component10and the converter lock-up clutch WK can be actuated as desired not only by the converter clutch valve WKV but also by further valve devices11and12. Downstream of the valve device12there is provided a cooler13which is connected upstream of a lubricating circuit14.

In the actuated operating state of the shift elements A to E, the valve devices KVA to KVE are pilot-operated by the electrohydraulic pressure adjusters EDSA to EDSE, in each case by pilot pressures p_EDSA to p_EDSE, in such a way that the system pressure p_sys prevailing in each case in the region of the valve devices KVA to KVE is applied, having been correspondingly converted as required, in the region of actuation pistons (not illustrated any more detail) of the shift elements A to E, in each case as actuation pressure p_A to p_E. Here, the system pressure p_sys corresponds in each case to the maximum actuation pressure p_A to p_E that can be realized.

In order to be able to charge the parking lock cylinder3, in accordance with demand, with the system pressure p_sys for disengaging the parking lock device or for hydraulically holding the parking lock device in the disengaged state via the parking lock valve2with the system pressure p_sys, the pilot pressure p_EDSA, which is adjustable in the region of the electrohydraulic pressure adjuster EDSA, can be applied in the region of a control surface21of a valve slide VS2of the parking lock valve2. Here, the valve slide VS2of the parking lock valve can be transferred from its first switching position illustrated inFIG. 2a, which corresponds to an engaged operating state of the parking lock device, via an intermediate position illustrated inFIG. 2binto the second switching position shown in more detail inFIG. 2c, which corresponds to a disengaged operating state of the parking lock device.

In addition to the pilot pressure p_EDSA and the system pressure p_sys, which simultaneously constitutes the actuation pressure of the parking lock cylinder3, a pressure signal p_MVPS which is adjustable in the region of a further electrohydraulic pressure adjuster MVPS, which in the present case is designed as a solenoid valve, can be applied in the region of a spring chamber16of the parking lock valve2, in which spring chamber a spring device17of the parking lock valve2is arranged. In the present case, the spring chamber16is delimited by a housing18and by the valve slide VS2of the parking lock valve2, wherein the pressure signal p_MVPS can be applied in the region of a further control surface22of the valve slide VS2of the parking lock valve2, acting in the same direction as the spring force of the spring device17. Both the spring force of the spring device17and the pressure signal p_MVPS act on the valve slide VS2in the direction of its first switching position.

Furthermore, via a ball-type change-over valve19, that actuation pressure p_C or p_E of the shift element C or E respectively prevails at the parking lock valve2which presently has a higher value in each case. Here, in the second switching position of the valve slide VS2as illustrated inFIG. 2c, the actuation pressure p_C or p_E prevails in the region of two facing control surfaces23,24of two valve slide regions VS23and VS24. The diameter of the valve slide region VS23is smaller than the diameter of the valve slide region VS24, such that the actuation pressure p_C or p_E, like the pilot pressure p_EDSA, acts on the valve slide VS2in the direction of its second switching position, or, more specifically, the respectively prevailing actuation pressure p_C or p_E results in an actuation force or actuating force which acts on the valve slide VS2in the direction of its second switching position. In the first switching position of the valve slide VS2as illustrated inFIG. 2aorFIG. 2b, the actuation pressure p_C or p_E does not result in an actuation force in the direction of the second switching position, because the second valve slide region VS24separates the control surfaces23and24from the actuation pressure p_C or p_E.

In the second switching position of the valve slide VS2as illustrated inFIG. 2c, the system pressure p_sys additionally prevails at the control surfaces25and26of the second valve slide region VS24and of a third valve slide region VS22of the valve slide VS2. The diameter of the second valve slide region VS24is in turn smaller than the diameter of the valve slide region VS22. For this reason, the system pressure p_sys prevailing in the region of the control surfaces25and26in the second switching position of the valve slide VS2results in turn in an actuation force which acts on the valve slide VS2in the direction of its second switching position, which actuation force is equal to zero in the first switching position of the valve slide VS2as illustrated inFIG. 2abecause, in the first switching position of the valve slide VS2, the actuation pressure or the system pressure p_sys prevails neither at the control surface25nor at the control surface26.

In the present case, the control surfaces21to26of the valve slide VS2and the spring force of the spring device17are coordinated with one another such that, during normal operation of the electrohydraulic transmission control system1, in which the electrohydraulic pressure adjusters EDSA to EDSE, MVPS and EDSSYS can be fed with current, the parking lock device can be transferred into its engaged operating state or into its disengaged operating state in the manner described in more detail below.

Proceeding from the engaged operating state Pein of the parking lock device, and in the presence of a demand for disengagement of the parking lock device, the parking lock valve2, which is then in the operating state illustrated inFIG. 2a, is transferred into the operating state illustrated inFIG. 2cby application of the pilot pressure p_EDSA in the region of the control surface21. This has the effect that the system pressure p_sys prevailing at the parking lock valve2is transmitted via the parking lock valve2in the direction of the parking lock cylinder3, and a piston chamber20of the parking lock cylinder3is charged with the system pressure p_sys. Here, a piston30of the parking lock cylinder3is displaced from its position corresponding to the engaged operating state Pein of the parking lock device into the position corresponding to the disengaged operating state Paus of the parking lock device by the prevailing system pressure p_sys counter to a spring device (not illustrated in any more detail) of the parking lock device. When the position that corresponds to the disengaged operating state Paus of the parking lock device is reached, an electrically actuable locking device31arrests or stops the piston30, which is then held redundantly, both by the system pressure p_sys and by the locking device31, in the position that corresponds to the disengaged operating state Paus of the parking lock device.

Proceeding from the operating state of the parking lock valve illustrated inFIG. 2cwith a simultaneously disengaged parking lock device, during normal operation of the electrohydraulic transmission control system1, in the event of a demand for engagement of the parking lock device, the pilot pressure p_EDSA is reduced to zero and, at the same time, the pressure signal p_MVPS of the solenoid valve MVPS is applied to the valve slide VS2of the parking lock valve2in the region of the control surface22. Here, the control surfaces21,22,23,24,25,26of the valve slide VS2and the spring force of the spring device17are coordinated with one another such that the valve slide VS2can be transferred from the second switching position in the direction of the first switching position of the valve slide VS2by the spring device17and the pressure signal p_MVPS, despite the system pressure p_sys and clutch pressure p_C/E and pressure regulator pressure p_EDSA prevailing in the region of the control surfaces21,23,24,25,26, in which first switching position the piston chamber20of the parking lock cylinder3is connected via the parking lock valve2to a substantially unpressurized region50of the transmission, which is preferably an oil sump. Furthermore, the locking device31is switched into a deenergized state, and the piston30of the parking lock cylinder3is mechanically unlocked, whereby the piston30can be displaced by the spring device of the parking lock device into its position that corresponds to the engaged operating state Pein of the parking lock device.

In the present case, the control surfaces21to26of the valve slide VS2and the spring force of the spring device17are also coordinated with one another such that the valve slide VS2can be transferred from its first switching position into its second switching position by a pilot pressure p_EDSA of approximately three and a half (3.5) bar, counter to the spring force of the spring device17, if the pressure signal p_MVPS of the solenoid valve MVPS is substantially equal to zero or, more specifically, substantially corresponds to the ambient pressure of the transmission, which generally prevails in all regions of the parking lock valve2in addition to the pressure signals and which thus has no effect.

At the latest when the second switching position of the valve slide VS2is reached, the system pressure p_sys prevails again at the control surfaces23and24of the valve slide VS2. By the system pressure p_sys, the self-holding action of the parking lock valve2is activated if the system pressure p_sys is approximately seven (7) bar. If the actuation pressure p_C or p_E of the shift element C or E respectively prevails in the region of the control surfaces25and26in addition to the system pressure p_sys, the self-holding action of the parking lock valve2is activated already at a pressure of the system pressure p_sys of approximately two (2) bar, and the valve slide VS2can no longer be transferred into its first switching position by the spring device17alone.

During normal operation of the transmission control system1, through corresponding adjustment of the pilot pressure p_EDSA, the shift element A is charged with the actuation pressure p_A, and incorporated into the power flow, during the realization of the park operating state, the neutral operating state, the realization of the ratio for reverse travel, and during the realization of the ratios “1” and “2” for forward travel and for the realization of the ratios “7” and “8”. The pressure signal or the pilot pressure p_EDSA is therefore particularly suitable for transferring the parking lock valve2from the operating state illustrated inFIG. 2ain the direction of the operating state shown inFIG. 2ccounter to the spring device17in the manner described above. To prevent undesired disengagement of the parking lock by the then respectively prevailing pressure signal p_EDSA, the valve slide VS2is charged with the pressure signal p_MVPS in the region of its control surface22in the corresponding presence of a demand for engagement of the parking lock device.

Furthermore, either the shift element C or the shift element E is activated in each case in order to realize the ratio “1” to “8” for forward travel, for which reason in each case either the actuation pressure p_C or the actuation pressure p_E is available for holding the valve slide VS2of the parking lock valve2in the operating state illustrated inFIG. 2cand for enabling the parking lock device to be held in the disengaged operating state Paus also hydraulically, through corresponding charging of the parking lock cylinder3with the system pressure p_sys, in addition to the mechanical locking in the region of the locking device31.

If the current-feed of the electrohydraulic transmission control system1fails, this has the effect that the pilot pressures p_EDSA to p_EDSE fall to zero, owing to the configuration, described in more detail below, of the electrohydraulic pressure adjusters EDSSYS, MVPS and EDSA to EDSE, whereas the pressure signal p_EDSSYS assumes its maximum value. Furthermore, in the deenergized operating state of the solenoid valve MVPS, the pressure signal p_MVPS is also equal to zero.

This results from the fact that the pressure adjusters EDSA to EDSE are formed with a positive or rising pressure characteristic curve versus the actuation current, whereas the electrohydraulic pressure adjuster EDSSYS has a negative or falling pressure characteristic curve versus the actuation current. Thus, during hydraulic emergency operation of the electrohydraulic transmission control system1, the system pressure valve4is charged with the maximum pressure value of the pressure signal p_EDSSYS, whereby the system pressure p_sys assumes its maximum value for as long as the pump device5provides a corresponding supply pressure. This has the effect that the hydraulic fluid volume accumulator7is also charged with the maximum system pressure p_sys and gets filled completely.

A detent device34of the hydraulic fluid volume accumulator7is likewise deactivated in the event of an electrical failure of the electrohydraulic transmission control system1. The hydraulic fluid volume stored in the region of the hydraulic fluid volume accumulator7is introduced, upstream of the parking lock valve2, into the line system of the transmission control system1if the system pressure p_sys falls below a defined pressure level of the system pressure p_sys, which in the present case lies at approximately seven (7) bar. In this way, the system pressure p_sys is held at the pressure level of approximately seven (7) bar for a limited time period until leakages of the transmission control system1cause a pressure drop of the system pressure p_sys.

For as long as the pump device5provides an adequately high supply pressure, the self-holding action of the parking lock valve2remains active during emergency operation, and the valve slide VS2is held in the operating state shown inFIG. 2dby the prevailing system pressure p_sys. However, if a motor or drive machine which drives the pump device5is deactivated during emergency operation of the transmission control system1, the pressure level of the system pressure p_sys initially falls, for supply-related reasons, to the pressure level of approximately seven (7) bar provided by the hydraulic fluid accumulator7. This has the result that, in the event of the self-holding pressure threshold of the system pressure p_sys being undershot, the valve slide VS2is immediately transferred, by the spring device17, into its first switching position in which the system pressure p_sys is isolated from the parking lock cylinder3in the region of the parking lock valve2, and the piston chamber20of the parking lock cylinder3is ventilated in the direction of the unpressurized region via the parking lock valve2. Since the locking device31of the parking lock cylinder3is already deactivated during emergency operation, the parking lock device engages in the desired manner, and a vehicle is transferred into a safe operating state.

In the present case, the self-holding pressure threshold of the parking lock valve2effective during emergency operation of the transmission control system1during the deactivation of the pump-side pressure supply is greater than the system pressure p_sys provided by the hydraulic fluid accumulator7, whereby, in the event of a drop of the system pressure p_sys to the pressure level of the hydraulic fluid volume accumulator7, the parking lock valve2is immediately transferred by the spring device17, owing to the design, into the operating state illustrated inFIG. 2a, and the parking lock device is transferred into its engaged operating state.

FIG. 3shows an illustration, corresponding toFIG. 1, of a second exemplary embodiment of the electrohydraulic transmission control system1, which substantially corresponds to the transmission control system as perFIG. 1aside from the design of the parking lock valve2, for which reason substantially only the differences between the two embodiments will be discussed in more detail below on the basis of the illustrations as perFIG. 4atoFIG. 4d, and with regard to the further functioning of the transmission control system1as perFIG. 3, reference is made to the above description relating toFIG. 1andFIG. 2atoFIG. 2d.

The parking lock valve2of the transmission control system1as perFIG. 3includes, in turn, the three valve slide regions VS22, VS23and VS24, wherein the diameter of the valve slide region VS23is smaller than the diameter of the valve slide region VS24, which in turn is larger than the diameter of the valve slide region VS22, which, for ease of assembly of the parking lock valve2, is guided in the housing18in the region of a so-called reduction sleeve40, which in the present case is fixedly connected to the housing18.

The pressure signal p_EDSA of the electrohydraulic pressure adjuster EDSA can in turn be applied in the region of the control surface21of the valve slide VS2of the parking lock valve2, the pressure signal p_EDSA acting toward the second switching position of the valve slide VS2. Furthermore, the pressure signal p_MVPS of the solenoid valve MVPS can in turn be applied to the valve slide VS2, in the region of the control surface22of the valve slide VS2, acting in the same direction as the spring device17in the direction of its first switching position, whereas, in the second switching position of the valve slide VS2as illustrated inFIG. 4c, the system pressure p_sys prevails in the region of the control surfaces23and24of the valve slide regions VS23and VS24.

Furthermore, the pressure signal p_EDSSYS which is adjustable in the region of the electrohydraulic pressure adjuster EDSSYS prevails in the region of the control surfaces25and26of the valve slide regions VS24and VS22when the valve slide VS2of the parking lock valve2is situated in its second switching position.

Here, the control surfaces21to26of the valve slide VS2and the spring force of the spring device17of the parking lock valve2as perFIG. 4atoFIG. 4dare coordinated with one another such that, during normal operation of the transmission control system1as perFIG. 3, the valve slide VS2is, above a pressure level of three and a half (3.5) bar of the pressure signal p_EDSA of the electrohydraulic pressure adjuster EDSA, transferred from its first switching position into its second switching position, and held therein, counter to the spring force of the spring device17alone. Furthermore, the parking lock valve2is designed such that, during normal operation of the transmission control system, a pressure level of approximately two (2) bar of the system pressure p_sys is sufficient to activate the self-holding action of the parking lock valve2counter to the spring force of the spring device17, wherein, for this purpose, the pressure signal p_EDSSYS of the electrohydraulic pressure adjuster EDSSYS must be set to substantially equal to zero.

Owing to the valve boosting action that prevails in the region of the system pressure valve4, the self-holding pressure threshold amounts, in the case of pressure signals p_sys and p_EDSSYS simultaneously acting on the parking lock valve2, to a pressure level of the system pressure p_sys of approximately seven (7) bar, whereby, upon a transition from the normal operation of the transmission control system1to hydraulic emergency operation, the effect described in more detail below is achieved.

Since, during hydraulic emergency operation of the transmission control system1, both the pressure signal p_EDSA and the pressure signal p_MVPS are substantially equal to zero and both the pressure signal p_EDSSYS and the system pressure p_sys assume their maximum values, the parking lock valve2is, upon a transition of the transmission control system1to emergency operation proceeding from driving operation in a forward direction of travel, held in the operating state illustrated inFIG. 4dby the prevailing system pressure p_sys counter to the pressure signal p_EDSSYS likewise prevailing at the valve slide VS2. If the pressure supply from the pump device is deactivated or interrupted for example as a result of a shutdown of the drive machine, the system pressure p_sys and thus also the pressure signal p_EDSSYS abruptly decrease.

When the pressure level of the hydraulic fluid accumulator7is reached, the spring device8thereof expels the hydraulic fluid volume stored in the region of the hydraulic fluid accumulator7, whereby the pressure level of the system pressure p_sys and the pressure level of the pressure signal p_EDSSYS likewise prevailing at the parking lock valve2are of substantially the same magnitude and correspond to the expulsion pressure level of the hydraulic fluid accumulator7. This has the effect that the valve slide VS2is immediately transferred from its second switching position into its first switching position by the spring device17and by the prevailing pressure signal p_EDSSYS counter to the prevailing system pressure p_sys, and the parking lock device is transferred in the manner described above into its engaged operating state Pein without a delay.

Thus, it is also the case in the second embodiment of the transmission control system1as perFIG. 3that, owing to the different self-holding pressure levels which take effect during normal operation and during emergency operation of the transmission control system1, it is firstly possible to realize energy-optimized operation of a transmission, and secondly, it is possible to realize immediate engagement of the parking lock in the event of a shutdown of the drive machine during emergency operation.

FIGS. 5ato 5dshow an alternative embodiment of the parking lock valve2of the transmission control system1as perFIG. 3, in which the valve slide VS2includes two valve slide parts VS2A and VS2B, whereby the parking lock valve2is formed with a two-part, stepped valve slide VS2. In the operating state of the parking lock valve2illustrated inFIG. 5b, the two valve slide parts VS2A and VS2B are arranged spaced apart from one another in an axial direction, and so as to be longitudinally displaceable relative to one another, in the housing18. Here, the first valve slide part VS2A of the parking lock valve2as perFIG. 5atoFIG. 5dand the one-piece valve slide VS2of the parking lock valve2as perFIG. 4atoFIG. 4dhave substantially the same functionality and mode of operation, whereas the second valve slide part is provided merely for an actuation of the first valve slide part VS2A proceeding from the second axial position of the first valve slide part VS2A illustrated inFIG. 5din the direction of the first axial position illustrated inFIG. 5a.

The spring device17is arranged between the two valve slide parts VS2A and VS2B, whereby, in the presence of a correspondingly small pressure signal p_MVPS, the second valve slide part VS2B is transferred by the spring device17into the position shown inFIG. 5btoFIG. 5d, whereas, depending on the respectively acting pressure signals p_EDSA and p_EDSSYS, the first valve slide part VS2A is present either in the first or second axial position illustrated inFIG. 5aor inFIG. 5c. This results from the fact that the second valve slide part VS2B is spring-loaded by the spring device17in the direction of a stop45and can be displaced counter to the spring force of the spring device17, in the direction of the first valve slide part VS2A, by the pressure signal p_MVPS.

In the present case, the pressure signal p_EDSSYS can be applied in the region of the control surface25of the valve slide region VS24of the first valve slide part VS2A and in the region of the control surface26of the second valve slide part VS2B, whereas, in the second axial position of the first valve slide part VS2A of the valve slide VS2, the system pressure p_sys prevails in the region of the mutually corresponding control surfaces23and24of the valve slide region VS24and of the valve slide region VS23and additionally at a further control surface27of the valve slide region VS23of the first valve slide part VS2A, whereby the first valve slide part VS2A is acted on by an actuating force which results from the acting system pressure p_sys and which in turn acts in the direction of the second switching position of the first valve slide part VS2A.

It is also the case in the embodiment of the parking lock valve2illustrated inFIG. 5ato theFIG. 5dthat the control surfaces21to27and the spring force of the spring device17are coordinated with one another such that the parking lock valve2can be transferred into and held in the operating state illustrated inFIG. 5cby the pressure signal p_EDSA, counter to the spring force of the spring device17, above a pressure level of approximately three and a half (3.5) bar, if the pressure signal p_MVPS is substantially equal to zero. In the operating state of the parking lock valve2illustrated inFIG. 5c, the system pressure p_sys prevails in the region of the control surfaces23and24and27of the first valve slide region VS2A of the valve slide VS2, wherein the self-holding pressure level of the parking lock valve2corresponds, in the presence of a pressure signal p_EDSSYS equal to zero, to a system pressure p_sys of approximately two (2) bar, and the parking lock valve2can be held in the operating state illustrated inFIG. 5c, counter to the spring force of the spring device17, by the system pressure p_sys alone. With rising pressure signal p_EDSSYS, the self-holding pressure threshold corresponds to the sum of the system pressure p_sys and the pressure signal p_EDSSYS which prevails at the first valve slide part VS2A in a direction of action counter to the system pressure p_sys and which is approximately (seven) 7 bar. In a situation of the transmission control system1formed with the parking lock valve2as perFIG. 5atoFIG. 5din which the pressure signals p_EDSA and p_MVPS are substantially equal to zero, the pressure signal p_EDSSYS rises to its maximum pressure value owing to the falling pressure characteristic curve of the electrohydraulic pressure adjuster EDSSYS, which likewise results, owing to the design of the system pressure valve4described in more detail above, to a rise of the system pressure p_sys to its maximum value. Owing to the valve ratio of the system pressure valve4, it is thus the case that the self-holding action of the parking lock valve in the operating state illustrated inFIG. 5candFIG. 5dis ensured even during active emergency operation.

In turn, if the pressure supply from the pump is interrupted as a result of a shutdown of the drive machine of the transmission control system1, the system pressure p_sys and the pressure signal p_EDSSYS both fall abruptly to the pressure level of the hydraulic fluid accumulator7during active emergency operation. This means that the two pressures p_sys and p_EDSSYS are of substantially equal magnitude, and the parking lock valve2is immediately transferred by the spring device17into an operating state in which the parking lock cylinder3is ventilated in the direction of the unpressurized region via the parking lock valve2, and the parking lock device can be transferred into its engaged operating state as desired with high spontaneity.

REFERENCE DESIGNATIONS

1Electrohydraulic transmission control system2Parking lock valve3Parking lock cylinder4System pressure valve5Pump device6Spring device of the system pressure valve7Hydraulic fluid volume accumulator8Spring device of the hydraulic fluid volume accumulator9Check valve device10Launch component, torque converter11,12Valve device13Cooler14Lubrication circuit16Spring chamber17Spring device18Housing19Ball-type change-over valve20Piston chamber21Control surface22Further control surface23Control surface24Control surface25Control surface26Control surface27Control surface30Piston of the parking lock cylinder31Interlock device of the parking lock cylinder34Detent device of the hydraulic fluid volume accumulator40Reduction sleeve41Valve slide of the system pressure valve45Stop50Unpressurized regionA to E Shift elementEDSA to EDSE Electrohydraulic pressure adjusterEDSSYS Electrohydraulic pressure adjusterEDSWK Electrohydraulic pressure adjusterKVA to KVE Valve deviceMVPS Electrohydraulic pressure adjuster, solenoid valvep_A to p_E Actuation pressurePaus, Pein Operating state of the parking lockp_MVPS Pressure signalp_EDSSYS Pressure signalp_EDSA to p_EDSE Pilot pressurep_sys System pressurep_VB1, p_VB2Pre-fill pressurep_WK Actuation pressureVS2Valve slide of the parking lock valveVS22, VS23, VS24Valve slide regionVS2A, VS2B Valve slide partWK Converter lock-up clutchWKV Converter clutch valve