DE102016218388A1 - Transmission actuator for a manual transmission - Google Patents

Abstract

The invention relates to a transmission actuator for a manual transmission, which has at least the following components: a first shift shaft and a second shift shaft, each with at least one shift finger, wherein the first shift shaft together with the at least one first shift finger and the second shift shaft together with the second shift finger each translational and rotary for selecting and switching at least one gear is movable; - A first actuator and a second actuator, each comprising a lifting unit for translational movement of a respective shift shaft and a rotary unit for rotationally moving the respective shift shaft; wherein the first shift shaft is designed as a hollow shaft and the second shift shaft is arranged coaxially in the first shift shaft, wherein at least one of the lifting units and / or at least one of the rotary units is hydraulically actuated. With the gear actuator proposed here is a space and energy-saving fast circuit of a double shift can be implemented.

Description

• – eine erste Schaltwelle und eine zweite Schaltwelle mit jeweils zumindest einem Schaltfinger, wobei die erste Schaltwelle zusammen mit dem zumindest einen ersten Schaltfinger und die zweite Schaltwelle zusammen mit dem zweiten Schaltfinger jeweils translatorisch und rotatorisch zum Auswählen und zum Schalten jeweils zumindest eines Gangs bewegbar ist;
• – eine erste Stelleinheit und eine zweite Stelleinheit, umfassend jeweils eine Hubeinheit zum translatorischen Bewegen einer jeweiligen Schaltwelle und eine Dreheinheit zum rotatorischen Bewegen der jeweiligen Schaltwelle; wobei die erste Schaltwelle als Hohlwelle ausgeführt ist und die zweite Schaltwelle koaxial in der ersten Schaltwelle angeordnet ist, wobei zumindest eine der Hubeinheiten und/oder zumindest eine der Dreheinheiten hydraulisch betätigbar ist.

The invention relates to a transmission actuator for a manual transmission, which has at least the following components:

• - A first shift shaft and a second shift shaft, each having at least one shift finger, wherein the first shift shaft is movable together with the at least one first shift finger and the second shift shaft together with the second shift finger in each case translationally and rotationally for selecting and switching at least one gear;
• - A first actuator and a second actuator, each comprising a lifting unit for translational movement of a respective shift shaft and a rotary unit for rotationally moving the respective shift shaft; wherein the first shift shaft is designed as a hollow shaft and the second shift shaft is arranged coaxially in the first shift shaft, wherein at least one of the lifting units and / or at least one of the rotary units is hydraulically actuated.

From the prior art gear actuators for actuating a gearbox are known in which by means of a single switching shaft, a respective gear of the gearbox is selectable and switchable. By means of an engaged gear, which is thus selected and connected, a torque from a transmission input shaft to a transmission output shaft with a set transmission ratio can be transmitted. Such a gearbox is usually preceded by a friction clutch, so that selecting and switching can be done powerless. The switching shaft is configured to carry out both a translatory movement and a rotational movement, wherein one of the movements is used for selecting and in each case other movement is used for switching. For this purpose, the switching shaft on a firmly connected shift finger, which is so positioned by a, for example, translational movements to a gear or a gear associated shift rail, that the gear or the shift rail by means of each other, for example, rotational, insertable is. Such a transmission actuator is known, for example, as a so-called active interlock transmission actuator (compare: 8th LuK Symposium 2006, ed .: LuK GmbH & Co. oHG, chapter: "Electromotive Actuators for Dual Clutch Transmissions", page 144 to page 145 ). In this gear actuator, the translatory movement is used for selecting and the rotary movement for switching. An alternative in which the rotational movement is used for selecting and the translational movement for switching is exemplified in FIG 2 of the FR 2 814 524 A1 shown.

The task of a gear actuator, which meets the requirements of the motor vehicle market, is to consume little energy and, in particular, to have a low peak power and to require a small installation space. In the known state of the art therefore electromagnetic or electromechanical actuators are used. These also have a very fast reaction time. Also, it has already been possible to represent a power consumption of less than 20 W [Watt] and average power consumption of only 12 W [Watt] with an electromechanical actuator. Disadvantages here are the high costs, in particular due to the rising magnet prices.

On this basis, the present invention has the object, at least partially overcome the known from the prior art disadvantages. The features of the invention will become apparent from the independent claims, to which advantageous embodiments are indicated in the dependent claims. The features of the claims may be combined in any technically meaningful manner, for which purpose the explanations of the following description as well as features of the figures may be consulted which comprise additional embodiments of the invention.

• – eine erste Schaltwelle mit zumindest einem ersten Schaltfinger, wobei die erste Schaltwelle zusammen mit dem zumindest einen ersten Schaltfinger translatorisch und rotatorisch zum Auswählen und zum Schalten zumindest eines Gangs eines Schaltgetriebes bewegbar ist;
• – eine zweite Schaltwelle mit zumindest einem zweiten Schaltfinger, wobei die zweite Schaltwelle zusammen mit dem zumindest einen zweiten Schaltfinger translatorisch und rotatorisch zum Auswählen und zum Schalten zumindest eines Gangs eines Schaltgetriebes bewegbar ist;
• – eine erste Stelleinheit, umfassend eine erste Hubeinheit zum translatorischen Bewegen der ersten Schaltwelle und eine erste Dreheinheit zum rotatorischen Bewegen der ersten Schaltwelle;
• – eine zweite Stelleinheit, umfassend eine zweite Hubeinheit zum translatorischen Bewegen der zweiten Schaltwelle und eine zweite Dreheinheit zum rotatorischen Bewegen der zweiten Schaltwelle, wobei die erste Schaltwelle als Hohlwelle ausgeführt ist und die zweite Schaltwelle koaxial in der ersten Schaltwelle angeordnet ist, wobei zumindest eine der Hubeinheiten und/oder zumindest eine der Dreheinheiten hydraulisch betätigbar ist.

The invention relates to a transmission actuator for a manual transmission, preferably a double transmission, which has at least the following components:

• A first shift shaft having at least one first shift finger, wherein the first shift shaft is translatable and rotatable together with the at least one first shift finger for selecting and for shifting at least one gear of a gearbox;
• A second shift shaft with at least one second shift finger, wherein the second shift shaft is translatable and rotatable together with the at least one second shift finger for selecting and for switching at least one gear of a gearbox;
• - A first actuator, comprising a first lifting unit for translational movement of the first switching shaft and a first rotary unit for rotationally moving the first switching shaft;
• A second adjusting unit, comprising a second lifting unit for translational movement of the second switching shaft and a second rotary unit for rotational movement of the second switching shaft, wherein the first switching shaft is designed as a hollow shaft and the second switching shaft is arranged coaxially in the first switching shaft, wherein at least one of Lifting units and / or at least one of the rotating units is hydraulically actuated.

The gear actuator is configured to select and switch a plurality of gears simultaneously and / or independently of each other. This is particularly advantageous for fast switching operations and / or double gearboxes. The gear actuator has for this purpose a first shift shaft and a second shift shaft. Each switching shaft has at least one associated shift finger, which is firmly connected to the respective shift shaft. The first shift shaft is translatable together with the at least one first shift finger for selecting and rotationally for switching at least one, preferably exactly one, gear of a gearbox or rotationally for selecting and translationally for switching at least one, preferably exactly one, gear of a gearbox. The second switching shaft is translationally and rotatively coupled with the at least one second shift finger for selecting and rotationally for switching at least one, preferably exactly one, gear of a gearbox or rotationally for selecting and translationally for switching at least one, preferably exactly one, gear of a gearbox movable.

The first switching shaft is translationally and rotationally movable by means of a first adjusting unit. The second switching shaft is translationally and rotationally movable by means of a second actuator. The respective actuator has for this purpose a lifting unit and a rotary unit. By means of the lifting unit is a translational movement of the respective shift shaft and by means of the rotary unit is a rotational movement of the respective shift shaft executable. The actuating unit preferably forms a (compact) structural unit, particularly preferably both actuating units together form a (compact) structural unit.

A lifting unit is in this case formed by a solenoid, an electromechanical drive or a hydraulic piston. A rotary unit is in this case formed by a rotary piston or translated piston, which in turn can be driven by means of a covered lifting magnet, a covered electromechanical drive or a hydraulic piston included. At least one of the lifting units and / or one of the rotating units comprises a hydraulic drive. A hydraulic drive has the advantages that a fast response can be achieved and the size, at least in the immediate vicinity of the relevant actuator, so the slave unit, is less than the size of a corresponding electromagnetic or electromechanical drive. In addition, an existing hydraulic pressure source for example, other functional units of the gearbox and / or a (related) friction clutch and / or other components of a drive train can be used. In a preferred embodiment, the control electronics is integral with the control electronics of other functional units. In one embodiment, the pressure source comprises a switchable direction reversal, so that the pressure source can be switched into a vacuum source or (active) pressure sink. Alternatively, the pressure source is designed as a volume flow source or (active) volume flow sink. In the following, for the sake of simplicity, it is primarily spoken of a pressure source, but the preceding embodiments are included.

According to a further advantageous embodiment of the gear actuator, the lifting units are hydraulically actuated.

As a result of the same design of both lifting units, it is possible to save further space, as well as to reduce the manufacturing effort by the same or at least similar components. Also, the pressure source or the controller, for example, a valve logic, be executed the same or similar for both lifting units, so that the development effort and manufacturing costs can be reduced.

According to a further advantageous embodiment of the gear actuator, the rotary units are hydraulically actuated.

As a result of the same design of both rotating units, it is possible to save further space, as well as to reduce the manufacturing effort by the same or at least similar components. Also, the pressure source or the control, for example, a valve logic, are executed the same or similar for both rotating units, so that the development effort and production costs can be reduced.

Particularly preferably, the lifting unit and the rotary unit of an actuating unit are designed hydraulically. Most preferably, both actuators are completely hydraulically actuated. As a result, special space advantages can be achieved and the production cost can be further reduced.

According to a further advantageous embodiment of the gear actuator, at least one of the lifting units or at least one of the rotating units comprises at least one return spring.

By means of the use of a return spring, the line expenditure and the tax expense can be reduced. Particularly preferably, the return spring is set up such that a shift finger by means of the return spring force from the switched position to a neutral position or into a blocking position is feasible. Particularly preferably, a return spring is used in a hydraulically actuated lifting unit or rotary unit.

According to a further advantageous embodiment of the gear actuator comprises at least one of the lifting units and / or at least one of the rotary units, which is adapted for the switching movement, a double-sided return spring for returning or holding the shift finger in a (r) neutral position.

By means of the use of a return spring on both sides of the control effort is reduced by the two-sided return spring holds the lifting unit or the rotary unit without concerns an operating force, for example a hydraulic pressure in a neutral position. The correct position is ensured even without monitoring the currently applied operating force, for example, the hydraulic pressure, or without application of a (hydraulic) force by means of the two-sided return springs. Also, this total power consumption of the gear actuator can be reduced.

According to a further advantageous embodiment of the gear actuator is at least one of the lifting units and / or at least one of the rotary units, which is preferably set up for the switching movement, hydraulically freely actuated.

In a hydraulically free operation pressure chambers are provided on both sides of the hydraulic piston, which can be supplied via separate lines. Such a hydraulic piston is movable almost without force in both directions without taking into account the actuating force to be exerted. Preferably, the separate lines are coupled via a corresponding valve logic such that at a pressure increase in the one pressure chamber, the pressure or the volume in the other pressure chamber low resistance or proactively reduced.

To hold the piston in a desired position, in one embodiment, the lines are blocked, and in another embodiment the lines are connected to a common supply line so that the pressure in both pressure chambers is the same. The latter embodiment has the advantage that leaks can be compensated and / or an indirect (external) pressure measurement, for example at the pressure source, can be made.

According to a further advantageous embodiment of the gear actuator, at least one deployment finger is provided for each associated gear.

In this preferred embodiment is ensured by a corresponding mechanism, namely the delivery fingers, that no colliding passages are inserted. For example, the first shift shaft is associated with a first gear, a third gear and a fifth gear, and the first shift shaft thus has at least two deployment fingers, so that it is ensured when inserting, for example, the first gear that the third gear and the fifth gear means of this Auslegefinger or by means of a single Auslegefingers designed so are not switched. In other words, in this preferred embodiment, by selecting a gear, the at least one shift finger at the selected gear and the deployment fingers or a single one of the deployment fingers are positioned at the respective non-selected gears. This applies accordingly for the second switching shaft. Alternatively, the first shift shaft and the second shift shaft no gear or a shift rail permanently assigned, but freely as needed and under the required safety restrictions a gear assignable. Here, too, the number and arrangement of the deployment fingers is preferably set up in such a way that the respective undesired passages are securely designed, ie not inserted.

• – eine erste Getriebeeingangswelle;
• – eine zweite Getriebeeingangswelle;
• – eine Getriebeausgangswelle;
• – zumindest zwei erste Gänge zum Übersetzen eines Drehmoments von der ersten Getriebeeingangswelle auf die Getriebeausgangswelle, wobei jeder erste Gang jeweils ein unterschiedliches erstes Übersetzungsverhältnis aufweist;
• – zumindest zwei zweite Gänge zum Übersetzen eines Drehmoments von der zweiten Getriebeeingangswelle auf die Getriebeausgangswelle, wobei jeder zweite Gang jeweils ein unterschiedliches zweites Übersetzungsverhältnis aufweist;
• – einen Getriebeaktor nach einer Ausführungsform gemäß der obigen Beschreibung, wobei die ersten Gänge mittels der ersten Schaltwelle betätigbar sind und die zweiten Gänge mittels der zweiten Schaltwelle betätigbar sind.

According to a further aspect of the invention, a double gearbox for a drive train is proposed, which has at least the following components:

• A first transmission input shaft;
• A second transmission input shaft;
• A transmission output shaft;
• At least two first gears for translating a torque from the first transmission input shaft to the transmission output shaft, each first gear having a different first gear ratio;
• At least two second gears for translating a torque from the second transmission input shaft to the transmission output shaft, each second gear each having a different second gear ratio;
• - A gear actuator according to an embodiment according to the above description, wherein the first gears are actuated by means of the first shift shaft and the second gears are actuated by means of the second shift shaft.

The double gearbox is designed to hold two gear ratios in parallel by two gears can be inserted at the same time. The first gears are assigned to a first partial transmission and the second gears to a second partial transmission. By means of the first partial transmission is the first Transmission input shaft with the transmission output shaft translating torque-transmitting connectable and by means of the second partial transmission, the second transmission input shaft with the transmission output shaft translating torque-transmitting connectable. Preferably, the total existing gears on all mutually different gear ratios, in the case of a reverse gear at least the sign after.

In a preferred embodiment, a shift shaft is assigned in each case to a partial transmission, so that both partial transmissions are completely independent of each other. Alternatively, the shift shafts are assigned to multiple gears of both partial gearboxes fixed, so that several courses are inserted and interpreted simultaneously. In a further alternative, each gear or gears are selectable and switchable by two partial transmissions by means of a single shift shaft, so that any combination can be actuated.

According to the further aspect of the invention, a drive train for a motor vehicle is proposed, which has a drive unit with an output shaft, at least one consumer, and a double shift transmission according to one embodiment as described above, wherein the output shaft for transmitting torque by means of the double gear with the at least one consumer connectable with variable translation.

The drive train is set up to transmit a torque provided by a drive unit, for example an energy conversion machine, preferably an internal combustion engine or an electric drive machine, and output via its output shaft to at least one variable-transmission consumer. An exemplary consumer is at least one drive wheel of a motor vehicle and / or an electric generator for providing electrical energy. Conversely, a recording of an inertial energy introduced, for example, by a drive wheel can also be implemented. The at least one drive wheel then forms the drive unit, wherein its inertial energy by means of the double gear on an electric generator for recuperation, so for the electrical storage of the braking energy, with a suitably equipped drive train is transferable.

The geared actuator set up for the double shift transmission proposed here has a particularly low overall volume and, at the same time, can be operated at least as dynamically in comparison with purely electromagnetic or electromechanical actuators. Most preferably, the pressure source for a hydraulically operated friction clutch or dual clutch is also available for the gear actuator, whereby further space can be saved.

According to a further aspect of the invention, a motor vehicle is proposed, which has at least one drive wheel which can be driven by means of a drive train according to the above description.

Most motor vehicles today have a front-wheel drive and therefore preferably arrange the drive unit, for example an internal combustion engine or an electric drive machine, in front of the driver's cab and transversely to the main drive direction. The space is particularly low especially with such an arrangement and it is therefore particularly advantageous to use a manual transmission, in particular a double shift, small size.

This problem is exacerbated in passenger cars of the small car class according to European classification. The functional units used in a passenger car of the small car class are not significantly reduced compared to passenger cars larger car classes. Nevertheless, the available space for small cars is much smaller. The drive train described above has a double gearbox or a hydraulic gear actuator of particularly small size. At the same time components of the periphery can be used together, whereby the overall space compared to a conventional double gearbox is further reduced.

Passenger cars are assigned to a vehicle class according to, for example, size, price, weight and power, and this definition is subject to constant change according to the needs of the market. In the US market, cars of the class small cars and microcars are classified according to European classification of the class of Subcompact Car and in the British market they correspond to the class Supermini or the class City Car. Examples of the micro car class are a Volkswagen up! or a Renault Twingo. Examples of the small car class are an Alfa Romeo Mito, Volkswagen Polo, Ford Fiesta or Renault Clio.

The above-described invention will be explained in detail in the background of the relevant technical background with reference to the accompanying drawings, which show preferred embodiments. The invention is not limited by the purely schematic drawings in any way, it being noted that the drawings are not dimensionally accurate and are not suitable for the definition of size ratios. It is shown in

1 a first circuit diagram of a gear actuator;

2 a second circuit diagram of a gear actuator;

3 a third circuit diagram of a gear actuator;

4 a fourth circuit diagram of a gear actuator;

5 a fifth circuit diagram of a gear actuator;

6 a sixth circuit diagram of a gear actuator;

7 : a double gearbox with double clutch; and

8th : a powertrain in a motor vehicle with manual transmission.

In 1 is a circuit diagram of a gear actuator 1 shown in which a first shift shaft 3 for actuating a first shift rail 54 and a second shift rail 55 , as well as a second shift shaft 8th for actuating a third shift rail 56 and a fourth shift rail 57 are provided. The second shift shaft 8th is designed as a hollow shaft, in which the first shift shaft 3 is arranged coaxially. In the present example, the first shift shaft 3 a first shift finger 4 , a first delivery finger 26 and a second deployment finger 27 on. The second shift shaft 8th here also has a second shift finger 9 , a third delivery finger 28 and a fourth delivery finger 29 on. By means of the first shift finger 4 the first shift shaft 3 Here is the first shift rail 54 inserted and the second shift rail 55 by means of the second deployment finger 27 designed. By means of the second shift finger 9 the second shift shaft 8th Here is the fourth shift rail 57 inserted and the third shift rail 56 by means of the third extension finger 28 designed. In a preferred embodiment, a shift rail is associated with two gears each, wherein by means of a shift finger, the shift rail for engaging a gear in one direction and to insert another gear in another direction, preferably in the opposite direction, from a, for example, central, neutral position is displaceable. This can be operated with four shift rails up to eight gears. The first shift shaft 3 and the second shift shaft 8th have a first actuator 14 or a second actuator 17 on. The first actuator 14 includes a first lifting unit 15 , By means of which the first shift shaft 3 translational (here in the image plane up and down) is movable, so that the first shift finger 4 a desired shift rail 54 or 55 is assigned. In this case, therefore, the selection is carried out by means of a translational movement. The first actuator 14 also includes a first turntable 16 , By means of which the first shift shaft 3 rotatory (here in the image plane around the image vertical axis) is movable, so that the first shift finger 4 the selected shift rail, here the first shift rail 54 , deflects (here in the image plane to the left) and thus one of the first shift rail 54 assigned gear is engaged. In this case, therefore, the switching is carried out by means of a rotary movement. The second actuator 17 includes a second lifting unit 18 , by means of which the second switching shaft 8th translatory (here in the image plane up and down) is movable, so that the second shift finger 9 a desired shift rail 56 or 57 is assigned. The second actuator 17 further comprises a second rotary unit 19 , by means of which the second switching shaft 8th rotatory (here in the image plane around the image vertical axis) is movable, so that the second shift finger 9 the selected shift rail, here the fourth shift rail 57 , deflects (in the image plane to the right) and thus one of the fourth shift rail 57 assigned gear is engaged. In this case also the selection by means of a translatory movement and the switching by means of a rotary movement is carried out. This selection mechanism and switching mechanism of a respective shift shaft preferably corresponds to that of the previously known active interlock transmission actuator. The fixed assignment of the switching shafts 3 and 9 to the shift rails 54 and 55 respectively 56 and 57 is a preferred embodiment, but not mandatory. In the present example, the lifting units 15 and 18 formed by lifting magnets or an electromechanical drive. The rotation units 16 and 19 each comprise a hydraulic piston, which from an external pressure source 62 are supplied. The pressure source 62 is hereby preferably (partially) switchable into a pressure sink, so that when resetting the first rotary unit 16 and / or the second rotary unit 19 by (partial) switching the restoring force of the return spring 20 respectively 21 is greater than the resulting pressure force of the pressure provided in the pressure chamber. With a partial switching here the unit-specific or line-specific switching is meant. For example, the first turntable is 16 continue with a restoring force of the first return spring 20 overcoming pressure applied while at the second rotary unit 19 the pressure is reduced so far that the second shift finger 9 due to the restoring force of the second return spring 21 is twisted. The translational movement of the hydraulic piston of the rotary units 16 and 19 Here, for example, by means of a pivoting piston or a corresponding rotation ratio, for example, a rack-gear pairing, in a rotational movement of the corresponding shift shaft 3 respectively 9 implemented. In the present example, the first turntable 16 a first Return spring 20 and the second turntable 19 a second return spring 21 on. A necessary valve logic is, for example, in 3 and 4 shown.

In 2 to 6 are more circuit diagrams of a gear actuator 1 in which the selection mechanism and switching mechanism for the better overview as well as in 1 is executed. Reference is made in this respect to the above description. However, the possible embodiments are not limited to this mechanics.

In 2 are both actuaries 14 and 17 completely hydraulic, with the first lifting unit 15 a first return spring 20 , the first turntable 16 a third return spring 22 , second lifting unit 18 a second return spring 21 and the second turntable 19 a fourth return spring 23 having. Hereby use the first lifting unit 15 and the second lifting unit 18 also a common external pressure source 62 , which also here (partially) in a pressure sink is switchable.

In 3 is a similar embodiment as in 2 shown here, where here is the first turntable 16 and the second turntable 19 having free hydraulic piston. In these so no spring elements for applying a restoring force are provided. Here, a valve logic is still shown, via which the actuators 14 and 17 are controllable. The first lifting unit 15 is from a simple first valve 58 controllable which is switchable between a closed position (the illustrated position) and an open position. The second lifting unit 18 is also from a simple second valve 59 controllable, which is the first valve 58 equivalent. The free piston of the first turntable 16 is from a third valve 60 controllable with three switching positions, namely a holding or blocking position, in which here both pressure chambers with the pressure source 62 are further connected to a position to the rear and a position for the forward actuation of the first rotary unit 16 , The free piston of the second turntable 19 is from a fourth valve 61 controllable with three switch positions, which the third valve 60 equivalent. The symmetry between the actuators shown here 14 and 17 , as well as the associated valves 58 to 61 form a preferred embodiment, but not a limitation. In one embodiment, the pressure source is 62 for the first valve 58 and the second valve 59 each, so partially, in a pressure sink switchable. In contrast, the pressure source is preferred 62 for the third valve 60 and for the fourth valve 61 only for providing, preferably constant, pressure or a, preferably constant, volume flow established.

In 4 is a similar embodiment as in 3 shown here, where here is the first turntable 16 from a third return spring 22 and a fifth return spring 24 and the second turntable 19 from a fourth return spring 23 and a sixth return spring 25 be kept in a neutral position. Thus, no pressurization is necessary to the shift finger 4 respectively 9 from the switched position to a neutral selection position, the neutral position due. This is reflected accordingly in the valve logic. The first valve 58 has a first passage position and a first actuation position, in which case the first passage position is just switched. Likewise, the second valve 59 a (here switched) second passage position and a second operating position. Are both valves 58 and 59 in the Durchlassstellung, then the first turntable 16 from the third return spring 22 and the fifth return spring 24 transferred to a (r) neutral position or held, because the pressure chambers are both connected to a sink. The first shift finger 4 is not switched and a dialing is freely executable. The position of the first pilot valve 63 has no influence on the first turntable in this state 16 , which is then in the neutral position. The first pilot valve 63 has a (first) blocking position and a (first) open position. Is the first pilot valve 63 in the locked position, then the first lifting unit 15 regardless of the position of the first valve 58 and the second valve 59 blocked. This blocking position of the first pilot valve 63 is preferably set when the first shift finger 4 , which is held in a neutral position, has been guided to a desired position, in which by turning the first shift finger 4 from the neutral position out a shift rail is actuated. When the first pilot valve 63 is transferred to the open position and the first valve 58 and second valve 59 are in the passage position, is on the first lifting unit 15 a pressure or negative pressure, depending on the condition of the pressure source 62 or pressure sink 62 , exercised. The first lifting unit 15 is thus moved. Because the first shift finger 4 then forcibly located in a neutral position, the first shift shaft 3 collision-free movable and a desired shift rail, for example, the second shift rail 55 , approachable. After reaching the desired shift rail, the first shift finger 4 turned in the desired direction by the first valve 58 (Operation to the right) or the second valve 59 (Actuation to the left) is transferred to the operating position and the other valve 59 respectively 58 is left in the passage position. The first lifting unit 15 is thereby blocked and thus locked in the desired position. In addition, in one embodiment, the first pilot valve 63 transferred into the locked position, before the first valve 58 or the second valve 59 is switched to the operating position, and transferred after switching back to the open position. The pressure source 62 represents in the state of operation of the first rotary unit 16 always over pressure ready. The second actuator 17 is here by a functionally identical structure of the third valve 60 , the fourth valve 61 , the second pilot valve 64 and their lines wired the same and just as operable.

In 5 is a combination of the embodiment according to the 1 and the 3 shown, in which case the first valve 58 and the second valve 59 for the blocking position, the pressure supply lines to the two pressure chambers of the first rotary unit 16 or the second rotary unit 19 shut down.

In 6 an embodiment is shown in which both the lifting units 15 and 18 as well as the rotating units 16 and 19 are formed with free hydraulic piston. Each of these free hydraulic piston has a similar valve 58 to 61 on which as in 3 are shown executed and thus in the blocking position in each case both pressure chambers with the same pressure from the common pressure source 62 supply. The pressure source 62 In this case, it is preferably set up solely to provide an overpressure.

In 7 is a manual transmission 2 , designed as a double gearbox, with an upstream double clutch 45 shown. At the far left of the picture is a drive unit 35 indicated by a cylinder and a connecting rod, via which a torque about the coupling axis 41 on an output shaft 36 is deliverable. The torque is over the first part clutch 46 on the first transmission input shaft 30 and thus on the first part manual transmission 39 and / or the second part clutch 47 on the second transmission input shaft 31 and thus on the second part manual transmission 40 transferable. To extinguish rotational irregularities in an interfering resonant frequency range, a first centrifugal pendulum remains 48 and a second centrifugal pendulum 49 intended. The first part manual transmission 39 This includes a first gear 5 , a third gear 6 and a fifth gear 7 , wherein in each case a Stirnradpaarung is provided. The transmission input side gears of a Stirnradpaarung are with the first transmission input shaft 30 firmly connected and the gear output side spur gears are by means of a first shift dog shift sleeve pair 50 or a second shift dog shift sleeve pair 51 detachable with a transmission output shaft 32 connectable and are permanently engaged with the transmission input side spur gears. The second part manual transmission 40 This includes a second gear 10 , a fourth gear 11 , a sixth gear 12 and a reverse gear 13 , wherein also here each a Stirnradpaarung is provided. The transmission input side spur gears of a Stirnradpaarung are connected to the second transmission input shaft 31 firmly connected and the gear output side spur gears are by means of a third shift dog shift sleeve pair 52 or a fourth shift dog shift sleeve pair 53 detachable with the transmission output shaft 32 connectable and are permanently engaged with the transmission input side spur gears. A shift dog shift sleeve pair is each operable by means of an associated shift rail, namely the first shift dog shift sleeve pair 50 from the first shift rail 54 , the second shift dog shift sleeve pair 51 from the second shift rail 55 , the third shift dog shift sleeve pair 52 from the third shift rail 56 and the fourth shift dog shift sleeve pair 53 from the first shift rail 57 , The first shift dog shift sleeve pair 50 has (only) two positions, namely a neutral position and a connection position for the right pair of spur gears, namely the first gear 5 , The remaining shift dog shift sleeve pairs 55 to 57 each have three possible positions, namely a neutral position, a connection position for the left Stirnradpaar and a connection position for the right Stirnradpaar. In the connection position, the respective spur gear with the transmission output shaft 32 firmly connected, so that a torque via the associated gear on the transmission output shaft 32 is transferable. To illustrate the three possible positions of a shift dog shift sleeve pair, the associated shift rails are preferably aligned such that they from a neutral position in which a gear can be selected by means of a shift finger for switching in a first direction and in another second preferred opposite, direction are displaced, the first direction of a gear, for example, the second gear 10 , and the second direction another gear, for example, the fourth gear 11 , assigned.

In 8th is a powertrain 33 comprising a drive unit 35 , shown here as an internal combustion engine, an output shaft 36 , a manual transmission 2 and one by means of the transmission output shaft 32 torque transmitting connected left drive wheel 37 and right drive wheel 38 , shown schematically. The powertrain 33 is here in a motor vehicle 34 arranged, wherein the drive unit 35 with its motor axis 44 transverse to the longitudinal axis 43 in front of the driver's cab 42 is arranged.

With the gear actuator proposed here is a space and energy-saving fast circuit of a double shift can be implemented.

LIST OF REFERENCE NUMBERS

1

 gear actuator

2

 manual transmission

3

 first shift shaft

4

 first shift finger

5

 first course

6

 third gear

7

 fifth gear

8th

 second shift shaft

9

 second shift finger

10

 second gear

11

 fourth gear

12

 sixth gear

13

 reverse gear

14

 first actuator

15

 first lifting unit

16

 first turntable

17

 second actuator

18

 second lifting unit

19

 second turntable

20

 first return spring

21

 second return spring

22

 third return spring

23

 fourth return spring

24

 fifth return spring

25

 sixth return spring

26

 first delivery finger

27

 second delivery finger

28

 third delivery finger

29

 fourth delivery finger

30

 first transmission input shaft

31

 second transmission input shaft

32

 Transmission output shaft

33

 powertrain

34

 motor vehicle

35

 power unit

36

 output shaft

37

 left drive wheel

38

 right drive wheel

39

 first part manual transmission

40

 second part manual transmission

41

 coupling axis

42

 cab

43

 longitudinal axis

44

 motor axis

45

 Double coupling

46

 first part clutch

47

 second part clutch

48

 first centrifugal pendulum

49

 second centrifugal pendulum

50

 first shift dog shift sleeve pair

51

 second shift dog shift sleeve pair

52

 third shift dog shift sleeve pair

53

 fourth shift dog shift sleeve pair

54

 first shift rail

55

 second shift rail

56

 third shift rail

57

 fourth shift rail

58

 first valve

59

 second valve

60

 third valve

61

 fourth valve

62

 pressure source

63

 first pilot valve

64

 second pilot valve

QUOTES INCLUDE IN THE DESCRIPTION

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

Cited patent literature

• FR 2814524 A1 [0002]

Cited non-patent literature

• 8th LuK Symposium 2006, ed .: LuK GmbH & Co. oHG, chapter: "Electromotive Actuators for Dual-Clutch Transmissions", page 144 to page 145 [0002]

Claims (10)

Gear actuator ( 1 ) for a manual transmission ( 2 ), comprising at least the following components: - a first shift shaft ( 3 ) with at least one first shift finger ( 4 ), wherein the first shift shaft ( 3 ) together with the at least one first shift finger ( 4 ) translationally and rotationally for selecting and switching at least one gear ( 5 . 6 . 7 ) of a manual transmission ( 2 ) is movable; A second shift shaft ( 8th ) with at least one second shift finger ( 9 ), wherein the second shift shaft ( 8th ) together with the at least one second shift finger ( 9 ) translationally and rotationally for selecting and switching at least one gear ( 10 . 11 . 12 . 13 ) of a manual transmission ( 2 ) is movable; A first actuator ( 14 ), comprising a first lifting unit ( 15 ) for translational movement of the first switching shaft ( 3 ) and a first rotary unit ( 16 ) for rotationally moving the first switching shaft ( 3 ); A second actuator ( 17 ), comprising a second lifting unit ( 18 ) for translational movement of the second switching shaft ( 8th ) and a second rotary unit ( 19 ) for rotationally moving the second switching shaft ( 8th ), wherein the first shift shaft ( 8th ) is designed as a hollow shaft and the second switching shaft ( 8th ) coaxial in the first shift shaft ( 3 ), wherein at least one of the lifting units ( 15 . 18 ) and / or at least one of the rotary units ( 16 . 19 ) is hydraulically actuated. Gear actuator ( 1 ) according to claim 1, wherein the lifting units ( 15 . 18 ) are hydraulically actuated. Gear actuator ( 1 ) according to claim 1 or 2, wherein the rotary units ( 16 . 19 ) are hydraulically actuated. Gear actuator ( 1 ) according to one of the preceding claims, wherein at least one of the lifting units ( 15 . 18 ) or at least one of the rotary units ( 16 . 19 ) at least one return spring ( 20 . 21 . 22 . 23 . 24 . 25 ). Gear actuator ( 1 ) according to claim 4, wherein at least one of the lifting units ( 15 . 18 ) and / or at least one of the rotary units ( 16 . 19 ), which is set up for the switching movement, a double-sided return spring ( 22 . 23 . 24 . 25 ) for resetting and / or holding the shift finger ( 4 . 9 ) into a neutral position. Gear actuator ( 1 ) according to one of claims 1 to 3, wherein at least one of the lifting units ( 15 . 18 ) and / or at least one of the rotary units ( 16 . 19 ), which is set up for the switching movement, is hydraulically freely actuable. Gear actuator ( 1 ) according to one of the preceding claims, wherein for each associated gear ( 5 . 6 . 7 . 10 . 11 . 12 . 13 ) at least one delivery finger ( 26 . 27 . 28 . 29 ) is provided. Double gearbox ( 2 ) for a drive train, comprising at least the following components: - a first transmission input shaft ( 30 ); A second transmission input shaft ( 31 ); A transmission output shaft ( 32 ); - at least two first courses ( 5 . 6 . 7 ) for translating a torque from the first transmission input shaft (16) 30 ) on the transmission output shaft ( 32 ), each first gear ( 5 . 6 . 7 ) each having a different first gear ratio; - at least two second courses ( 10 . 11 . 12 . 13 ) for translating a torque from the second transmission input shaft (16) 31 ) on the transmission output shaft ( 32 ), with every second gear ( 10 . 11 . 12 . 13 ) each having a different second gear ratio; A gear actuator ( 1 ) according to one of the preceding claims, wherein the first courses ( 5 . 6 . 7 ) by means of the first switching shaft ( 3 ) and the second gears ( 10 . 11 . 12 . 13 ) by means of the second switching shaft ( 8th ) are operable. Powertrain ( 33 ) for a motor vehicle ( 34 ), comprising a drive unit ( 35 ) with an output shaft ( 36 ), at least one consumer ( 37 . 38 ), and a double transmission ( 2 ) according to claim 8, wherein the output shaft ( 36 ) for torque transmission by means of the double gear ( 2 ) with the at least one consumer ( 37 . 38 ) is connectable with variable translation. Motor vehicle ( 34 ), comprising at least one drive wheel ( 37 . 38 ), which by means of a drive train ( 33 ) is drivable according to claim 9.

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