DE10149531A1 - Hydraulic actuation systems - Google Patents

Abstract

A hydraulic actuation system for an automatic transmission system comprises: an accumulator (275); a reservoir (278); a clutch slave cylinder (22) in the form of a single-acting tappet with a single working chamber (23) for controlling the engagement of a clutch (14); a hydraulic gear shift actuator (114, 115) for controlling gear engagement, the hydraulic gear shift actuator (114, 115) including a double acting plunger with a piston (116, 117) defining first and second working chambers (118, 119) , the working area of the piston (116, 117) opening to the first working chamber (118) being smaller than that opening to the second working chamber (119); a main control valve (120) connected between the first position, in which the clutch slave cylinder (22) and the second working chamber (119) of the gear shift actuator (114, 115) are connected to the accumulator (275), and a second position, in which the Clutch slave cylinder (22) and the second working chamber (119) of the gear shift actuator (114, 115) are connected to the reservoir (278), can be switched; wherein the working chamber (23) of the clutch slave cylinder (22) is connected to the main control valve (120) via a clutch control valve (122), the clutch control valve (122) between an open position in which the working chamber of the clutch slave cylinder (22) with the main control valve ( 120) ...

Description

This invention relates to hydraulic actuation systems and more particularly hydraulic actuation systems for automatic transmission systems.

In automatic transmission systems, for example, of the type described in WO 97/05410; WO 97/40300; GB 005186.2; GB 0024999.5 or GB 025000.1 is disclosed, the content of which is expressly contained in the disclosure of the present application is added, fluid pressure actuators for controlling the Actuation of a clutch actuator mechanism and / or one Gear shift mechanism used.

In such systems, electromagnetic control valves become control of fluid flow to and from the fluid pressure actuators used to actuate the clutch and gear shift mechanism control.  

As such systems become increasingly complex, they are usually three or four proportional flow control valves to control the system used. These control valves are typically multiple solenoid valves Bridges and openings. Furthermore, the valves usually have to be controlled to move between three or four positions. These valves are therefore relatively expensive and require complex electronic control systems, which clearly shows the total cost of the hydraulic actuation system increase.

The present invention provides a simplified hydraulic Actuating system ready, which has the cost and complicated construction of the system should decrease.

According to one aspect of the present invention, a hydraulic actuation system for an automatic transmission system comprises:
a hydraulic fluid source;
a hydraulic fluid reservoir;
a hydraulic clutch actuator for controlling engagement of a clutch, the hydraulic clutch actuator comprising a single acting plunger with a single working chamber;
a hydraulic gearshift actuator for controlling gear shifting, the hydraulic gearshift actuator comprising a double-acting plunger with a piston defining first and second working chambers, the working area of the piston opening to the first working chamber being smaller than that that opens to the second working chamber;
a main control valve, the main control valve being switchable between a first position in which the clutch actuator and the second working chamber of the gearshift actuator are connected to the pressure fluid source and a second position in which the clutch actuator and the second working chamber of the gearshift actuator are connected to the reservoir ;
wherein the working chamber of the clutch actuator is connected to the main control valve via a clutch control valve, the clutch control valve between an open position in which the working chamber of the clutch actuator is connected to the main control valve and a closed position in which the working chamber of the clutch actuator is separated from the main control valve , is switchable;
wherein the first working chamber of the gear shift actuator is connected to the hydraulic pressure fluid source via a first gear shift control valve, the first gear shift control valve between an open position in which the first working chamber of the gear shift actuator is connected to the hydraulic pressure fluid source and a closed position in which the first working chamber of the gear shift actuator is disconnected from the hydraulic pressure fluid source, is switchable; and
wherein the second working chamber of the gear shift actuator is connected to the main control valve via a second gear shift control valve, the second gear shift control valve between an open position in which the second working chamber of the gear shift actuator is connected to the main control valve and a closed position in which the second working chamber of the gear shift actuator is separated from the main control valve, is switchable.

The hydraulic actuation system described above replaces the complex ones proportional flow control valves that have been used so far  simple electromagnetic two-position control valves. If this too The use of multiple valves entails that Total system cost reduced and the electronic system used to Control of the valves is necessary, significantly simplified.

According to a preferred embodiment of the invention, two Gear shift actuators used, a selector actuator to control the Movement of a dialing mechanism in a first "election direction" and an Switch actuator for controlling the movement of the selector mechanism in one second "switching direction". Each of the selector and switching actuators is with the first and second gear control valves.

The invention will now be given by way of example only with reference to the accompanying Described drawings, of which:

Fig. 1 shows schematically a semi-automatic transmission system using a hydraulic actuation system according to the present invention;

FIG. 2 shows a gear selection mechanism and an associated shifting gate of the transmission system shown in FIG. 1;

Figure 3 shows schematically the hydraulic actuation system of the transmission system shown in Figure 1; and

Figure 4 shows curves of the state of the various valves, clutch engagement and gear shift for typical gear changes from first gear to second gear and from second gear to third gear using the actuation system shown in Figure 3.

Fig. 1 of the accompanying drawings shows a motor 10 with a starter and an associated starter circuit 10 a, which is coupled by the main drive friction clutch 14 with a multi-stage synchronous gear 12 with countershaft via a gear drive shaft 15 . Fuel is supplied to the engine through a throttle valve 16 which includes a throttle valve 18 which is actuated by the accelerator pedal 19 . The invention is equally applicable to a gasoline or diesel engine with electronic or mechanical fuel injection.

The clutch 14 is actuated by a release fork 20 which is actuated by a hydraulic slave cylinder 22 in the form of a single-acting plunger with a single working chamber 23 under the control of a clutch actuator control means 38 .

A gearshift lever 24 operates in a shifting link 50 which has two legs 51 and 52 which are connected by a transverse track 53 which extends from the end of the leg 52 to the middle between the ends of the leg 51 . The shift gate 50 defines five positions; "R" at the end of leg 52 ; "N" midway between the ends of cross track 53 ; "S" at the connection of leg 51 with the transverse track 53 ; and "+" and "-" at the ends of leg 51 . In the leg 51 , the lever 24 is biased into the middle position "S". The "N" position of the gear shift lever 24 corresponds to the neutral range; "R" corresponds to shifting into reverse gear; "S" corresponds to switching to a forward gear mode; a brief movement of the lever to the "+" position issues a command that the manual transmission be shifted up a gear ratio; and a brief movement of the gear shift lever 24 to the "-" position issues a command that the transmission be shifted down a gear ratio.

The positions of the lever 24 are sensed by a number of sensors; for example, microswitches or optical sensors, which are arranged around the switching link 50 . Signals from the sensors are passed to an electronic control unit 36 . An output from the control unit 36 controls a gear shift mechanism 25 that locks the gear ratios of the manual transmission 12 in accordance with the movement of the gear shift lever 24 by the vehicle operator.

In addition to the signals from the gear shift lever 24 , the control unit 36 receives signals from:
Sensor 19 a, which indicates the degree of actuation of the accelerator pedal 19 ;
Sensor 30 indicating the degree of opening of throttle valve 18 ;
Sensor 26 which indicates the engine speed;
Sensor 42 which indicates the speed of the clutch drive plate; and
Sensor 34 , which indicates the position of the clutch slave cylinder.

The control unit 36 uses the signals from these sensors to control the actuation of the clutch 14 during starting from a standstill and during a gear change, as described for example in the patents EP 0038113, EP 0043660, EP 0059035, EP 0101220 and WO 92/13208 whose content is expressly included in the disclosure of the present application.

In addition to the sensors mentioned above, the control unit 36 also receives signals from a vehicle speed sensor 57 , ignition switch 54 and brake switch 56 associated with the main brake system, for example the foot brake 58 of the vehicle.

A buzzer 52 is connected to the control unit 36 , which warns / draws attention to the vehicle operator when certain operating conditions occur. In addition to or instead of the buzzer 52 , a flashing warning light or other display means can be used. A gear indicator 60 is also provided to indicate the gear ratio selected.

As shown in FIG. 2, the gear shift mechanism 25 includes three shift rails 111 , 112 , 113 that are mounted parallel to each other for movement in an axial direction. Each shift rail 111 , 112 , 113 is associated with two of the gear ratios of the manual transmission 12 by a clutch release fork and a synchronizing unit in a conventional manner, so that the movement of the shift rails 111 , 112 , 113 in an axial direction causes shifting into one of the associated gear ratios, and the movement of the shift rails 111 , 112 , 113 in the opposite axial direction causes the shift into the other of the associated gear ratio ratios.

Usually a first and a second gear ratio are assigned to the shift rail 111 , so that when the shift rail 111 moves axially in a first direction it shifts into first gear, or when the shift rail 111 moves axially in a second direction it shifts to second gear; a third and fourth gear transmission ratio are assigned to the shift rail 112 , so that the shift rail 112 shifts when the shift rail 112 moves axially in the first direction, or shifts to fourth gear when the shift rail 112 moves axially in a second direction; and a fifth and a reverse gear ratio are assigned to the shift rail 113 , so that when the shift rail 113 is axially moved in the first direction, the gear is shifted to fifth gear, while when the shift rail 113 is axially moved in the second direction, the shift is shifted into the reverse gear.

A selector element 110 is mounted for movement in a selection direction X, transverse to the axes of the shift rails 111 , 112 , 113 , and in a shift direction Y, for movement axially to the shift rails 111 , 112 , 113 . The selector element 110 can thus be moved in the direction X along a neutral plane AB, so that it can be switched into a selected one of the shift rails 111 , 112 , 113 and brought into engagement therewith. The selector element 110 can then be moved in the direction Y to axially shift the engaged shift rail 111 , 112 , 113 in one direction in order to engage one of the associated gear ratios.

As shown in FIG. 3, the selector element 110 can be moved in the selector direction X by means of a selector actuator 114 actuated by liquid pressure along the neutral plane AB of the shifting gate shown in FIG. 2 in order to align the selector element 110 with one of the shift rails 111 , 112 , 113 , and thereby select a pair of gears that are assigned to this shift rail. The selector element 110 can then be moved in the shift direction Y by means of a shift actuator 115 actuated by liquid pressure in order to axially move the shift rails 111 , 112 , 113 in one direction for engagement with one of the associated gear ratio ratios.

The actuators 114 and 115 each comprise a double-acting plunger with pistons 116 and 117 , respectively, which divide the actuators 114 , 115 into two working chambers 118 , 119 , the working chambers 118 , 119 being arranged on opposite sides of each piston 116 , 117 . Actuating rods 114 a, 115 a extend from one side of the pistons 116 and 117 and are ready for operation with the selector actuator 110 for its movement in the selection and switching direction, X and Y, respectively. As a result of the connection of the actuating rods 114 a, 115 a with the pistons 116 , 117 , the working surface of the pistons 116 , 117 , which is exposed in the working chamber 118 , is smaller than the working surface of the pistons 116 , 117 , which is exposed in the working chamber 119 .

A master electromagnetic control valve 120 includes a two-way valve having an inlet 138 , an outlet 140 and an opening 142 . The inlet 138 of the main control valve 120 is connected to a hydraulic fluid source in the form of an accumulator 275 . An electrically driven positive displacement pump 223 is provided to charge the accumulator 275 via a check valve 276 . A pressure transducer 280 measures the pressure in the accumulator 275 and controls the electrically driven pump 223 via the control unit 36 to keep the pressure in the accumulator at an appropriate value. The outlet 140 from the main control valve 120 is connected to a reservoir 278 . When the solenoid 120 a of the main control valve 120 switched off, the valve 120 connects the outlet 140 to the opening 142, the valve 120 connects the inlet 138 with the opening 142 when the solenoid 120 is energized a.

The working chamber 23 of the clutch slave cylinder 22 is connected to the opening 142 of the main control valve 120 via an electromagnetic clutch control valve 122 . The clutch control valve 122 opens the working chamber 23 to the opening 142 when the solenoid 122 a of the clutch control valve is switched off, and separates the working chamber 23 from the opening 142 of the main control valve 120 when the solenoid 122 a is energized.

The working chambers 118 of the selector and switching actuators 114 , 115 are connected directly to the accumulator 275 by electromagnetic valves 144 and 146 , respectively.

The working chambers 119 of the selector and switching actuators 114 , 115 are connected to the opening 142 of the main control valve 120 by electromagnetic valves 145 and 147 , respectively.

The electromagnetic valves 144 , 145 , 146 and 147 are closed when switched off, separating the working chambers 118 from the accumulator 275 and the working chambers 119 from the opening 142 of the main control valve 120 ; and are open when energized, connecting the working chambers 118 to the accumulator 275 and the working chambers 119 to the port 142 of the main control valve 120 .

When the transmission is engaged and the clutch 14 is engaged, the main control valve 120 , clutch control valve 122 and gear control valves 144 , 145 , 146 and 147 are deactivated. Under this condition, the working chamber 23 of the clutch slave cylinder 22 is connected to the reservoir 278 by the valves 122 and 120 , so that the clutch 14 is engaged. The working chambers 118 , 119 of the selector and switch actuators 114 , 115 are closed by the valves 144 , 145 , 146 and 147 , thereby providing a hydraulic lock which prevents the movement of the selector and switch actuators 114 , 115 .

When a gear change is initiated, for example, by the driver of the vehicle, who briefly moves the gear shift lever 24 to the '+' position, or by automatic triggering, the main control valve 120 is energized, connecting the working chamber 23 of the clutch slave cylinder 22 to the accumulator 275 is, whereby hydraulic pressure is applied to release the clutch 14 . During this period, valves 144 , 145 , 146 and 147 remain switched off, so that working chambers 118 , 119 of selector and switching actuators 114 , 115 remain closed.

When the clutch 14 is released, the electromagnetic valve 122 is energized so that the connection between the working chamber 23 and the memory 275 is closed and the clutch 14 is clamped in the released position. When the clutch 14 is released and clamped, the electromagnetic valves 146 and 147 are energized and, depending on the gear currently engaged, the main valve 120 is controlled in order to connect the working chamber 119 of the switching actuator 115 to the reservoir 278 or the memory 275 . The excitation of the electromagnetic valves 146 and 147 while the opening 142 of the main control valve 120 is connected to the reservoir 278 creates a pressure differential over the piston 117 , whereby the rod 115 a is moved upward, as shown in Fig. 3, during the excitation of the electromagnetic valves 146 and 147 , while the opening 142 of the main control valve 120 is connected to the accumulator 275 , exerts a uniform pressure on both sides of the piston 117 , but the rod 115 a is moved downward due to the difference in area, as is shown in Fig. 3. A position sensor in the form of a linear potentiometer 127 is assigned to the rod 115 b and supplies a signal which indicates the position of the piston 117 . The currently engaged gear can thereby be shifted from the position corresponding to the currently engaged gear to a position corresponding to the neutral plane AB by moving the shift actuator 115 .

If the desired new gear is controlled by the same shift rail 111 , 112 , 113 as the released gear, for example when changing from the first to the second gear, the energized electromagnetic valves 146 , 147 can remain energized until the actuator 115 over the Position that corresponds to the neutral plane AB and has moved to the position that corresponds to the new gear. The electromagnetic valves 146 , 147 are then switched off so that the working chambers 118 and 119 are closed, whereby the selector actuator 115 is clamped in the required position. However, if the new gear is controlled by another shift rail 111 , 112 , 113 , for example when changing from second to third gear, the electromagnetic valves 146 , 147 are switched off when the piston 117 reaches a position that is the neutral level AB corresponds, so that the selector element 110 is clamped in the neutral plane KB. The electromagnetic valves 144 , 145 of the selector actuator 114 can now be energized and the main control valve 120 is controlled in the manner described above to move the rod 114 a in the correct direction to engage the shift rail 111 , 112 , 113 that corresponds to the desired new gear.

Here, too, a linear potentiometer 126 is assigned to the selector actuator 114 , the potentiometer 126 delivering a signal which indicates the position of the piston 116 . When the piston 116 is in a position that corresponds to the desired shift rail 111 , 112 , 113 , both electromagnets 144 and 145 are switched off, whereby the selector actuator 114 is clamped in the required position. The electromagnetic valves 146 and 147 can now be energized again and the main control valve 120 controlled to engage the new gear as previously described.

When the new gear is engaged, the electromagnetic valves 120 and 122 can be switched off, whereby the working chamber 23 of the clutch slave cylinder 22 is connected to the reservoir 278 and the clutch 114 can be engaged again. The rate at which the clutch is engaged again can be controlled to enable smooth starting, as described in EP 0038113; EP 0043660; EP 0059035; EP 0101220 or WO 92/13208 is described by quickly switching between the excited and switched-off state of the electromagnetic valve 120 .

According to a preferred embodiment of the invention, the positions of the selector and shift actuators 114 , 115 are calibrated for each of the gear ratios and the neutral plane AB, and the potentiometers 126 and 127 are used in a closed control system for controlling the main control valve 120 and the valves 144 , 145 , 146 and 147 are used to move the pistons 116 and 117 of the selector and shift actuators 114 , 115 to predetermined positions to release the currently selected gear and engage the new gear.

Fig. 4 shows typical gear changes from first to second gear and from second to third gear.

As shown in Fig. 4, the vehicle is initially in first gear with the clutch engaged. In this state, the main control valve 120 and valves 122 , 144 , 145 , 146 and 147 are turned off so that the clutch slave cylinder is connected to the reservoir and the selector and shift actuators 114 , 115 are clamped in a position corresponding to the first gear ,

Upon triggering a change from first gear to second gear at time t ₀ , the main control valve 120 is energized to connect the clutch slave cylinder to the accumulator 275 , thereby disengaging the clutch 14 .

When the clutch is disengaged at time t ₁ , valve 122 is energized to clamp the clutch in the disengaged position. The valves 146 and 147 are also energized, thereby exerting pressure on both sides of the piston 117 , so that the rod 115a moves downward, as shown in Fig. 3, whereby the shift rail 111 is released from the first gear and in the second gear is engaged.

When the second gear is engaged at time t ₂ , the valves 146 . and 147 turned off to clamp the selector and shift actuators 114 , 115 in a position corresponding to second gear. Then, the main control valve 120 and the valve 122 are turned off, whereby the clutch slave cylinder 22 is connected to the accumulator 278 , so that the clutch 14 is engaged again, the clutch being fully engaged at time t ₃ .

When a change from second gear to third gear is triggered at time t ₄ , the main control valve 120 is energized in order to connect the clutch slave cylinder 22 to the accumulator 275 , so that the clutch 14 is released.

When the clutch is released at time t ₅ , the valve 122 is energized to clamp the clutch 14 in its released position. Then, the main control valve 120 and the valves are energized 146 and 147 to the working chamber 118 of the select actuator 115 to the memory 275 and the working chamber 119 to connect to the reservoir 278, whereby the rod 115 a is moved upward and the shift rail 111 from the second gear is released.

When the second gear is released at time t ₆ and the selector 110 is aligned with the neutral plane AB, the valves 146 and 147 are turned off to clamp the shift actuator 115 in a position corresponding to the neutral plane AB. The main control valve 120 and valves 144 and 145 are then energized to apply pressure to both sides of the piston 116 of the selector actuator 114 , whereby the rod 114 a is moved to the right, as shown in Fig. 3.

If the selector element 110 at time t ₇ aligned with the shift rail 112, the valves 144 and 145 are turned off to the selecting clamp 114. The main control valve 120 is then turned off and the valves 146 and 147 are energized to move the shift rail 112 into engagement with the third gear.

When third gear is engaged at time t ₈ , valves 146 and 147 are turned off to clamp selector actuator 115 . Then valve 122 is turned off to reconnect clutch slave cylinder 22 to reservoir 278 and allow the clutch to be re-engaged.

According to a preferred embodiment of the invention, the main control valve 120 , the electromagnetic valves 122 , 144 , 145 , 146 and 147 , and / or the cylinders of the selector and switching actuators 114 , 115 , can be defined by a common housing, the bores / cylinders of the various components are correctly connected to one another through passages through the common housing. The valve / actuator unit formed in this way would have to be mounted on or next to the manual transmission 12 .

The electrically driven pump 223 , the accumulator 275 , the reservoir 278 and the control unit 36 can also be mounted with the valve / actuator unit or can be mounted remotely from it and connected to it for example by elastomeric pressure hoses.

Various modifications can be made without departing from the To distance invention. Although for example in the above Embodiment of the hydraulic circuit with reference to a semi-automatic cal transmission system has been described, the invention is equally at  fully automatic transmission systems or automatic Change gear systems applicable.

While in the exemplary embodiment described above the clutch slave cylinder 22 is connected directly to the main control valve 120 , a remote displacement valve with position detection means of the type disclosed in EP 0702760, the content of which is expressly included in the disclosure of the present application, can be inserted between the main control valve 120 and the clutch slave cylinder 22 his.

The claims filed with the application are proposed Formulations without prejudice to the achievement of further patent protection. The applicant reserves the right to make claims for further Submit combinations of features previously only in the description and / or the drawings.

Back references used in the subordinate claims refer to the further development of the subject of Main claim through the characteristics of the corresponding subordinate claim; they are not a waiver in relation to achieving one  independent object protection for the combination of features in understand the associated subordinate claims.

Since the subject of the subordinate claims with respect to the state of the Priority date technology represent separate and independent inventions may, the applicant reserves the right to subject them to make independent claims or declarations of resignation. Further they can also contain independent inventions that have a construction show by one of the items of the previous subordinate Claims is independent.

The exemplary embodiments are not intended to limit the invention understand. Rather, there is a large scope within the scope of the present disclosure Range of improvements and modifications, especially those Varia tion, elements and combinations and / or materials that the expert for example by combining individual with those in general Can find out the description and the exemplary embodiments, in addition to the features and / or elements or process steps described in described in the claims and contained in the drawings, possible with the aim of solving a task, resulting in a new item or new process stages or sequences of process stages  Combinable features leads, even if they are manufacturing, testing and Affect work processes.

The claims submitted with the application are drafted strikes without prejudice for obtaining further patent protection. The The applicant reserves the right to add more, so far only in the description and / or To claim drawings disclosed combination of features.

Relationships used in subclaims point to the others Training the subject of the main claim by the features of respective subclaim; they are not a waiver of attainment an independent, objective protection for the combinations of features to understand the related subclaims.

Since the subjects of the subclaims with regard to the prior art reserves the right to make its own independent inventions on the priority date Applicant before becoming the subject of independent claims or To make divisional declarations. You can continue to work independently Inventions contain one of the objects of the previous Have independent claims independent design.

The exemplary embodiments are not intended to limit the invention understand. Rather, there are numerous within the scope of the present disclosure  Changes and modifications possible, especially such variants, Elements and combinations and / or materials, for example, by com combination or modification of individual in connection with that in the general description and embodiments as well as the claims described features and elements contained in the drawings or process steps for the person skilled in the art with a view to solving the Task can be removed and combined to create a new one Subject or new process steps or process step sequences lead, also insofar as they relate to manufacturing, testing and working processes.

Claims (7)

1. Hydraulic actuation system for an automatic transmission system, comprising:
a hydraulic fluid source;
a hydraulic fluid reservoir;
a hydraulic clutch actuator for controlling engagement of a clutch, the hydraulic clutch actuator comprising a single acting plunger with a single working chamber;
a hydraulic gear shift actuator for controlling shifting into a gear, the gear shift actuator comprising a double-acting plunger with a piston defining first and second working chambers, the working area of the piston opening to the first working chamber being smaller than that, which opens to the second working chamber;
a main control valve, the main control valve between a first position in which the clutch actuator and the second working chamber of the gearshift actuator are connected to the pressure fluid source and a second position in which the clutch actuator and the second working chamber of the gearshift actuator are connected to the reservoir is switchable;
wherein the working chamber of the clutch actuator is connected to the main control valve via a clutch control valve, the clutch control valve between an open position in which the working chamber of the clutch actuator is connected to the main control valve and a closed position in which the working chamber of the clutch actuator is separated from the main control valve , is switchable;
wherein the first working chamber of the gear shift actuator is connected to the hydraulic pressure fluid source via a first gear shift control valve, the first gear shift control valve between an open position in which the first working chamber of the gear shift actuator is connected to the hydraulic pressure fluid source and a closed position in which the first working chamber of the gear shift actuator is disconnected from the hydraulic pressure fluid source, is switchable; and
wherein the second working chamber of the gear shift actuator is connected to the main control valve via a second gear shift control valve, the second gear shift control valve between an open position in which the second working chamber of the gear shift actuator is connected to the main control valve and a closed position in which the second working chamber of the gear shift actuator is separated from the main control valve, is switchable. 2. Hydraulic actuation system according to claim 1, wherein the Main control valve is in its second position when the Electromagnet is switched off. 3. Hydraulic actuation system according to claim 1 or 2, wherein the clutch control valve is in its open position when the Electromagnet is switched off.   4. Hydraulic actuation system according to claim 1, wherein the first and second gear control valve are in their closed positions, when the electromagnets are switched off. 5. Hydraulic actuation system according to one of the preceding Claims, wherein the gear shift mechanism two Gear shift actuators includes a selector actuator for movement a selector in a first direction and a switching actuator for Movement of the selector in a second direction, the Working chambers of the selector and switching actuators first and have second gear control valves. 6. Hydraulic actuation system according to one of the preceding Claims, wherein a plurality of the components by one common housing is defined, the components in appropriately through passages in the common housing are trained, are interconnected. 7. Automatic transmission system with a hydraulic Actuating system according to one of claims 1 to 6.