DE10023107A1 - Automated gearbox for motor vehicles has drive with linear piston/cylinder arrangement whose displacement axis is aligned parallel to change roller's rotation axis - Google Patents

Abstract

The gearbox has a number of gears with associated change couplings (18), at least one operated by an actuator (26) with a change roller (30) with at least one peripheral track and a fluid mechanical drive for the change roller. The rotary drive has a linear piston/cylinder arrangement (42) whose displacement axis (31) is aligned parallel to the change roller's rotation axis.

Description

The present invention relates to an automatable Ge drives for motor vehicles, with a plurality of gears, the Clutches assigned to insert and remove the same are, with at least one clutch for on and off shift at least one gear by means of an actuator bar, the actuator being a shift drum with at least one egg ner circumferential track, through the course of the clutch tion is actuated when the shift drum is rotated, and where with the actuator a fluid mechanical rotary drive for the Has shift drum.  

Such an automatable transmission is known from US-A- 5,411,448.

Furthermore, the present invention relates to an automatable Gearboxes for motor vehicles, with a plurality of gears, de NEN at least two clutches for inserting and removing the The same are assigned, which can be selected separately, the Clutches can be actuated by means of an actuator device are, the actuator means by means of a first movement gung selects one of the clutches and by means of a second Movement actuated the selected clutch, whereby the directions of the first and second movements approximately lower run right to one another, the actuator device being a first linear piston / cylinder arrangement for executing first movements and a second linear piston / cylinder arrangement for executing second movements, where is provided in a translation-rotation converter, such that that a linear displacement of the piston of the first piston / cylinder arrangement in a rotary movement of the piston of the second Piston / cylinder arrangement is implemented.

Such an automatable transmission is known from DE 196 15 267 C1 known.

With automatable transmissions for motor vehicles, esp especially for passenger cars, there is a trend towards egg automation of manual transmissions, which have a form provide conclusive power transmission. The reason is in the better efficiency compared to conventional automatic driven with hydrodynamic converter, and in lower cost.  In terms of comfort, almost the standards are reached, which a conventional automatic transmission offers.

From DE 196 15 267 C1 is a switching arrangement for a car matisable manual transmission known. To select a be tuned clutch will be a single-acting Piston / cylinder arrangement used. For switching operations using the selected clutch is a double-acting Kol ben / cylinder arrangement provided. This well-known switching arrangement is particularly suitable for implementing add-on Solutions, i.e. for the automation of existing hands manual transmission. The simple-acting piston / cylinder arrangement and the double acting piston / cylinder arrangement are one other arranged vertically.

Another automated manual transmission is known from DE 196 12 690 C1. This gearbox was created from the beginning developed for automation. It includes a switch roller that has a plurality of circumferential traces. Every order The catch coil is ge over a sliding block with a selector sleeve couples, and serves to actuate one or two clutch lungs.

The shift drum is driven by an electric motor that is arranged parallel to the shift drum. The drive takes place via a reduction gear.

The above-mentioned document US-A-5,411,448 relates to a Gearboxes for motorcycles. To actuate the clutches for A shift drum is provided for shifting gears in and out. The shift drum is on the one hand like a crank drive  Can be operated via a lever arm. At the end of the lever arm is a Gear sector provided. The gear sector meshes with one Idler gear. The idler gear also meshes with a drive gear. The Drive gear is ge with a pneumatic rotary drive couples. The pneumatic rotary actuator is a chamber with one Rotary piston formed. The rotary lobe is directly connected to the Drive gear connected. By a suitable introduction of Compressed air rotates the rotary lobe in the chamber. About the Drive gear and idler gear becomes the gear sector of the He bels rotated. Through the lever movement, the shift drum driven like a crank. Consequently, that can be Switch motorcycle gearboxes without the driver pressing the foot pedal must use.

The problem underlying the invention is a improved automated transmission for motor vehicles, ins Specify specifically for passenger cars.

This object is achieved according to a first aspect of the invention the automatable transmission mentioned at the beginning as the first solved for motor vehicles in that the rotary drive a li linear piston / cylinder arrangement, the stroke axis parallel lel is aligned with the axis of rotation of the shift drum.

The fluid mechanical rotary drive generally increases the height rer efficiency achieved than with an electromotive Rotary drive. A linear piston / cylinder arrangement is easy to seal and manufacture cheaper than a turn piston arrangement, and also has a better efficiency on. A coaxial arrangement of the stroke axis and axis of rotation is particularly preferred.  

The rotary drive is preferably a hydraulic swivel drive.

A rotary actuator, i.e. a rotary actuator with a limited Angle of rotation, can be structurally particularly favorable with a combine linear piston / cylinder arrangement.

It is particularly preferred if the rotary drive in the switch roller is integrated.

In this way, installation space is saved. Furthermore, all Liche rotating elements are rotatable about an axis.

It is particularly preferred if the piston / cylinder arrangement has a coupling device, the lifting movements of the Piston / cylinder arrangement in rotary movements of the shift drum puts.

It is particularly preferred if the coupling device a helical profile with a pitch angle in Has a range from 10 ° to 80 °, in particular from 30 ° to 50 °.

Self-locking becomes general at such pitch angles avoided. Furthermore, with a comparatively low Hü ben achieve relatively large angles of rotation. The slope angle be the translation of the hydraulic force into the rotation is correct torque of the drive. If the incline is too big, the stroke of the Ring piston too large, which is disadvantageous on installation space and Dyna mic affects. The efficiency drops at lower gradients and controllability is made more difficult.  

It is further preferred if the coupling device ver Rotation of the shift drum limited.

The maximum swivel angle that can be achieved by the limitation becomes due to the axial installation space (stroke of the ring piston), the effective Diameter of the helical profile and the pitch angle determined. With a small helix diameter becomes a short stroke achieved, the diameter in turn by the hydraulic key data (piston area) is determined.

The swivel angles are generally not limited to specific values limits, but can be used in a typical application Range from 230 ° to 250 °. It is also conceivable that the Swivel angle not through the coupling device, but alone formed by the maximum stroke of the piston / cylinder arrangement becomes.

According to a particularly preferred embodiment, the Piston / cylinder arrangement on an annular piston.

It is particularly preferred if the ring piston on one non-rotatable piston rod is axially movable.

An annular piston can ideally be used as a basic element Use a rotary translator. By the Be riding a non-rotatable piston rod, preferably is aligned coaxially to the shift drum, one can heavy-duty, yet compact construction of the Ak achieve tuators.  

It is particularly preferred if the piston rod is one Has hollow channel to the fluid line.

This is particularly useful if the Piston / cylinder arrangement is double-acting. The hollow channel then preferably serves to supply a pressure chamber that away from the end of the feed.

According to a further preferred embodiment, the ring piston on the piston rod by means of a first coupling device with limited rotation.

It is particularly preferred if the first coupling device is designed so that an axial stroke of the ring piston on the piston rod a rotary movement of the annular piston induced with respect to the piston rod, and vice versa.

In this way, the ring piston works together with the first Coupling device as a translation-rotation converter.

It is particularly preferred if the first coupling device a helical profile with a pitch angle in the range from 10 ° to 80 °, in particular from 30 ° to 50 ° has.

The advantages of such a pitch angle are already above specified.

According to a further preferred embodiment, the ring piston rotatably with the second coupling device Shift drum coupled.  

In this way, the shift drum during rotary movements of the Ring piston taken away.

It is also advantageous if the coupling device (s) each Weil have a coupling pin that in a corresponding Coupling groove engages.

In this way, the coupling devices can be small constructive effort robust and short radial design become.

It is particularly preferred if the piston / cylinder arrangement has a cylinder with an opening and a piston which is coupled through the opening to the shift drum.

The cylinder ensures high resilience Piston / cylinder arrangement. The coupling is made by the public in the cylinder.

It is particularly preferred if the cylinder is rigid with is connected to a piston rod on which the piston is mounted is.

This results in a particularly rigid overall Structure of the piston / cylinder arrangement.

It is particularly preferred if the cylinder consists of two parts forms is.  

In this way, the piston / cylinder arrangement can be easily assemble.

According to an alternative embodiment, the shift drum forms the cylinder of the piston / cylinder assembly.

This leads to a saving of components and also from sealing bodies.

According to a further preferred embodiment, the ring piston formed in two parts.

Due to the two-part shape, the ring piston can be ge low manufacturing costs with both an inside and egg provided an external groove.

According to a further preferred embodiment, the Piston / cylinder arrangement in the manner of a cartridge in front mounted in the shift drum.

In this way, the transmission can be inexpensive overall produce.

The object of the invention is achieved according to a second aspect the invention in the automati mentioned at the beginning solvable transmission for motor vehicles is solved in that the first linear piston / cylinder arrangement parallel to the second linear piston / cylinder arrangement is arranged and that the Translational rotation converter at least one helical Has profiling.  

This allows a particularly compact design of the Aktua gate device and the automatable transmission as a whole achieve. It is also possible to reduce the number of parts if necessary ren. The transmission can with a conventional manual transmission H-wiring diagram, the actuator system as an "add-on" solution rea is identified.

According to a particularly preferred embodiment of the two th aspect of the invention, the piston of the first Piston / cylinder arrangement on an outer groove and an inner groove, one of which is designed as a screw groove.

In this way, the translational rotation converter can be used a few parts.

Furthermore, it is particularly preferred if the helical Profiling has a paragraph at this point to allow stable selection angle.

Such a stable selection angle corresponds to a position of one Manual shift lever in the normally by elastic means established home position. In the basic position is a Dial angle set up that of the alley for the third / fourth Corresponds to a normal H gearbox.

It is further preferred if the second piston / cylinder arrangement concentrically within the first piston / cylinder arrangement is arranged.

The arrangement is particularly compact, it can possibly be a Pa Realize tronen construction.  

It is further preferred if the translational rotation converter has a coupling ring, the axial position of which is fixed and in the respective grooves of the pistons of the piston / cylinder orders takes effect.

This measure also serves to reduce the number of parts.

It is understood that the operation of the first and the second piston / cylinder arrangement can also be interchanged, that switched by swivel movements and by linear offset can be selected. Furthermore, the second aspect the invention allows an electromotive selection angle drive, so that there is a hybrid solution.

It is understood that the above and the following standing features to be explained not only in each specified combination, but also in other combinations or can be used alone, without the scope of to leave the present invention.

Exemplary embodiments of the invention are shown in the drawing 3 are shown and are described in more detail in the following description explained. Show it:

Fig. 1 is a schematic sectional view of a first imple mentation form of a transmission according to the first aspect of the invention;

FIG. 2 shows a development of the inner circumference of an annular piston of a piston / cylinder arrangement shown in FIG. 1;

Fig. 3 is a development of the outer circumference of the annular piston;

Fig. 4 is a sectional view of an alternative embodiment form of an actuator for the gearboxes shown in Fig. 1;

Fig. 5 shows a further alternative embodiment of an actuator for the transmission shown in Fig. 1;

Fig. 6 is an alternative piston ring;

Fig. 7 shows an alternative embodiment of a bearing egg ner shift drum and an associated actuator;

Fig. 8 shows an alternative embodiment of a sealing arrangement between the piston and cylinder of a piston / cylinder;

Fig. 9 is a schematic sectional view of an execution form of an actuator for a transmission according to the second aspect of the invention;

Fig. 10 is a schematic perspective view of a selector piston of the embodiment of Fig. 9;

FIG. 11a and 11b developments of the outer or the inner periphery of Wählkolbens of Fig. 10;

Fig. 12 is a schematic perspective view of a switching piston of the embodiment of Fig. 9;

Fig. 13 is a development of the outer circumference of the operating piston of Fig. 12; and

Fig. 14 is a plan view of a coupling ring of the actuator of Fig. 9.

A first embodiment of a transmission according to the first aspect of the invention is generally designated 10 in FIG. 1.

The transmission 10 is part of a drive train of a passenger car and is connectable via one or more starting and separating clutch (s) 12 to an engine 14 . The start-up and disconnect clutch (s) 12 is usually formed as a dry friction clutch or wet clutch, optionally as a double clutch. The engine 14 is typically an internal combustion engine.

At least the transmission 10 and the starting and separating clutch 12 are controlled by a common control device 16 . The control device 16 can be part of a central control of the motor vehicle, by means of which the engine electronics are also controlled.

In relation to the starting and separating clutch 12 , the control device 16 triggers opening and closing operations of the coupling by means of an actuator (not shown) at suitable times.

The transmission 10 is typically a multi-step transmission in front lay construction with a plurality of gear sets 20 corresponding to a plurality of gears, for. B. 4, 5, 6 or more courses.

Each wheel set has an idler gear 22 , one of which is shown in FIG. 1. The idler gear can be connected to a gear shaft 24 by means of a preferably positive-locking clutch 18 , which can be designed, for example, as a synchronous clutch, as a claw clutch, pull-wedge clutch, etc.

The clutch 18 is actuated by an actuator, which is generally designated 26 in FIG. 1. The actuator 26 is controlled by the control device 16 by means of a control line 28 .

The actuator 26 comprises a shift drum 30 which is rotatably mounted about an axis 31 . The shift drum 30 is rotatably supported within the housing 32 of the transmission 10 , for example by means of a bearing block 34 , which forms an axial bearing, and a La gerblockes 36 , which detects a radial bearing for the shift drum 30 bil.

The shift drum 30 also has a plurality of circumferential grooves 38 into which respective sliding blocks 40 engage, one of which is shown in FIG. 1. Each sliding block 40 is coupled to a shift sleeve (not shown), by means of which one or two shift clutches 18 can be actuated.

The circumferential grooves 38 are designed such that a rotational movement of the shift drum 30 triggers an axial movement of a respective sliding block 40 and thus an actuation process of a switching clutch 18 .

The circumferential grooves 38 consequently form control cams with control cams, which are arranged in a suitable manner over the circumference of the shift drum 30 , as is known per se in the prior art.

A rotary actuator, generally shown at 42, is used to initiate rotary movements of the shift drum 30 based on a linear piston / cylinder arrangement.

The shift drum 30 is designed as a hollow drum. The piston / cylinder arrangement 42 is received in the interior of the shift drum 30 .

The piston / cylinder arrangement 42 has a piston rod 44 which is arranged in a rotationally fixed manner coaxially with the shift drum 30 . On the piston rod 44 , an annular piston 46 is axially displaceably supported. The inner circumference of the annular piston 46 engages around the piston rod 44 . The outer circumference of the annular piston 46 lies against the inner circumference of the shift drum 30 . The shift drum 30 thus forms the cylinder of the piston / cylinder assembly 42 .

A pressure chamber A, B is formed on each of the two sides of the annular piston 46 . The piston / cylinder arrangement 42 can consequently be actuated equally dynamically in both directions of movement.

The control takes place by means of a valve device 48 , which receives control signals via the line 28 from the control device 16 . The valve device 48, which is shown only schematically in FIG. 1, supplies either the pressure chamber A or the pressure chamber B with hydraulic fluid which is conveyed under pressure by means of a pump from a reservoir. Hydraulic fluid, which is displaced from one of the pressure chambers A, B, is likewise fed back into the reservoir in a manner known per se.

On the inner circumference ( Fig. 2), the annular piston 46 is provided with a helical groove 50 . The annular piston 46 is provided with an axial groove 52 on the outer circumference ( FIG. 3).

A coupling pin 54 engages in the spiral groove 50 and is connected to the piston rod 44 in a rotationally fixed and axially immovable manner. Another coupling pin 56 engages in the axial groove 52 and is connected to the shift drum 30 in a rotationally fixed and axially immovable manner.

The helical groove 50 , which extends over the inner circumference of the annular piston 46 , has a pitch angle 59 to a plane perpendicular to the axis 31 of, for example, 40 °. The helical groove 50 extends over a swivel angle of, for example, 240 °.

The operation of the actuator 26 for the clutch 18 is as follows.

In an assumed initial state, as shown in FIG. 1, the clutch 18 is open. To close the clutch 18 , the control device 16 emits a signal via the line 28 to the valve device 48 . The valve device 48 connects the pressure chamber A with the hydraulic fluid supply. At the same time, a drain from the pressure chamber B is opened. Consequently, the annular piston 46 is moved to the right in the illustration of FIG. 1, as shown by an arrow indicated at 60. Due to the engagement of the coupling pin 54 in the helical groove 50, the annular piston 46 inevitably performs a rotary movement, as indicated by an arrow 62 in FIGS. 1 and 3. Due to the engagement of the coupling pin 56 into the axial groove 52, the shift drum is carried along in this rotational operation 30th By means of a suitable configuration of the circumferential groove 38 , the sliding block 40 is displaced to the right when the shift drum 30 is rotated, as indicated by an arrow 64 . The sliding block 40 takes a shift sleeve (not shown), whereby the clutch 18 is closed.

In order to subsequently open the clutch 18 again, the pressure chamber B is connected to the supply for hydraulic fluid, and the hydraulic fluid in the pressure chamber A is displaced until the initial state is reached again. For a rotation of the shift drum in the opposite direction, starting from the position in FIG. 1, the pressure chamber B would first be connected to the hydraulic fluid supply.

Another embodiment of an actuator 70 for actuating a clutch 18 is shown in FIG. 4.

In Fig. 4, elements having substantially the same structure as the elements shown in Fig. 1 are given the same reference numerals. Corresponding parts of the description should also refer to the components or functions shown in FIG. 4.

In the actuator 70 , the cylinder of the piston / cylinder arrangement 42 is not formed by the shift drum 30 itself, but by two cylinder sleeves 72 . The cylinder sleeves are each closed at one axial end and open at the other axial end. The cylinder sleeves 72 are mounted in the transmission so that the open ends face each other. An opening 73 is formed between the two cylinder sleeves 72 through which the coupling pin 56 engages.

At the axially opposite ends of the cylinder sleeves 72 , an end cap 76 is provided, which has an outer square 78 in order to facilitate a rotationally fixed mounting of the cylinder sleeve 72 in the transmission housing.

The cylinder sleeves 72 are each rotatably connected via a pin connection 74 and axially immovable to the piston rod 44 a related party.

The shift drum 30 is rotatably supported on the cylinder sleeves 72 by respective bearings 80 . As mentioned, the coupling to the ring piston 46 takes place by means of the coupling pin 56 through the opening 73 .

On one side (on the right in Fig. 4), the Zylin derhülse 72 is tightly closed by means of the associated end cap.

On the other hand, an oil guide ring 86 is provided between the other cylinder sleeve 72 and the end cap 76 . The oil guide ring forms two supply channels for the pressure chambers A, B. The one channel for the pressure chamber A is connected to an axial groove 82 on the outer circumference of the piston rod 44 . The other channel for the pressure chamber B is connected to a central cavity 84 of the piston rod 44 . In the area of the pressure chamber B, the piston rod 44 also has transverse openings 85 which connect the pressure chamber B to the cavity 84 .

The annular piston 46 is equipped with a sealing plate 90 on its opposite axial ends. An O-ring seat 92 for a seal to the inner periphery of the respective cylinder sleeve 72 and an O-ring holder 94 are respectively provided for sealing against the outer periphery of the piston rod 44 to the sealing plates 90th

Furthermore, the annular piston 46 is slidably mounted on the piston rod 44 by means of two slide bearings 96 . The slide bearings 96 are located at axially opposite ends, adjacent to the respective sealing plates 90 .

The sealing plate 90 are radially movable via a snap hook, not shown, on the respective slide bearing 96 and consequently connected to the annular piston 46 . Thus, a relief of the seals from shear forces in the circumferential direction is realized.

The sealing plates 90 are provided on their outer circumference, specifically on the side facing the annular piston 46 , with wiper rings or lips 98. The scraper rings 98 are used for wiping impurities from the inside of the cylinder sleeves 72 , which can enter through the opening 73 .

The annular piston 46 itself is formed in two parts and comprises an outer part 100 and an inner part 102 . The two parts 100 , 102 are joined together by pressing. The axial groove 52 is provided on the outer part 100 . The radial groove 50 is formed on the inner part 102 . The radial groove 50 is, as shown, preferably formed as opening 102 penetrating the inner part. Consequently, the helical groove 50 can also be made on the inner part 102 without machining from the inside.

The axial groove 52 , however, is formed on the outer part 100 as a blind groove in order to prevent contaminants from penetrating via the opening 73 into the area of the coupling between the piston rod 44 and the annular piston 46 . However, the axial groove 52 can also be designed as a continuous groove.

The operation of the actuator 70 corresponds to that of the actuator 26 .

In FIG. 5 another embodiment is shown of an actuator 110 for actuating a shift clutch 18.

If the actuator 110 has elements that are identical or similar to elements of the actuators 26 , 70 , the same reference numbers are used. Corresponding parts of the description are also intended to relate to the components and functions shown in FIG. 5.

The actuator 110 differs from the actuators 26 , 70 of FIGS. 1 and 4 initially in that a valve device 112 is integrated in the actuator 110 . The function of the valve device 112 corresponds to that of the valve device 48 . The valve device 112 is integrated in the illustration of FIG. 5 in the piston rod 44. However, you could also be integrated into an end cap 76 or in an adjacent portion of the housing 32 .

As in the embodiment of FIG. 1, the shift drum 30 is designed as a cylinder for the piston / cylinder arrangement 42 . The shift drum 30 is shaped for this purpose as a sleeve which is closed on one side.

At its closed end, the shift drum 30 is rotatably mounted on the piston rod 44 by means of an axial bearing 114 .

At its open end, the shift drum 30 is supported on a flange 115 of the piston rod 44 by means of a radial bearing 116 . Towards the pressure chamber A, only one ring seal 118 is provided between the flange 115 of the shift drum 30 and the piston rod 44 .

In Fig. 5, two sealing rings 120 are also shown, which aim at a seal between the piston rod 44 and the housing 32 , but are only provided if, instead of the valve 112 integrated in the piston rod 44 , an external valve is provided. The seals 120 then serve to mutually seal the oil supply channels for the pressure spaces A, B.

The coupling pin 56 is oil-tight with the shift drum 30 a related party. To simplify the seal, only one O-ring seat 92 for sealing against the inside of the shift drum 30 and only one O-ring seat 94 for sealing against the outer circumference of the piston rod 44 are provided on the annular piston 46 .

In contrast to the actuator 70 of FIG. 4, the inner part 100 of the annular piston 46 is provided at one end with a flange extending to the inside of the shift drum 30 . Accordingly, the outer part 100 is provided at the opposite end with a flange which extends up to the piston rod 44 and on which the O-ring receptacles 92 , 94 are seen before. The axial groove 52 is formed as an incision from the side opposite the flange of the outer part 100 . Likewise, the helical groove 50 is seen as an incision from the end opposite the flange of the inner part 102 .

The integration of the cylinder sleeves 72 , which are embodied separately in the embodiment in FIG. 4, in the shift drum 30 of the actuator 110 results in a further minimization of parts and weight compared to the actuator 70 . This allows ent to reduce either the outer diameter of the shift drum 30 . Al ternatively to this, with a constant outer diameter of the shift drum 30, the diameter of the annular piston to be increased 46th This results in an increase in the switching force and therefore with the dynamics of the overall system.

Furthermore, a sealing point is saved, whereby the inner System friction is reduced and efficiency is increased becomes.

FIG. 6 shows a further alternative embodiment, in which the annular piston 46 is provided with a hollow cylindrical outer part 100 and a hollow cylindrical inner part 102 . A sealing of the pressure chambers A, B against one another takes place by means of a single O-ring receptacle 92 at one end of the outer part 100 and by a single O-ring receptacle 94 at the opposite end on the inner part 102 .

In Fig. 7, a further alternative embodiment is shown in which the axial reaction force is not introduced into the housing 32 via the rear housing bearing of the roller drive. Rather, the piston rod 44 is designed as a tie rod. For this purpose, the piston rod 44 passes through the closed end of the shift drum 30 . The sealing takes place by means of a device 123 between these two elements. Axial bearings 122 are provided on the inside of the end of the shift drum 30 and on the outside. The end of the piston rod 44 projecting from the outer axial bearing 122 is designed as a radial bearing 124 .

In this way, the rear storage in the housing 32 can be made significantly easier. In contrast to the design of the actuator 110 from FIG. 5, however, the additional seal 123 is required.

Fig. 8 shows a schematic split seal, as an alternative to the seal between the annular piston 46 and the cylinder of suitable piston / cylinder assembly. Such a gap seal is also used for valve spools. Here, z. B. sealing washers 126 made of hard-coded aluminum or plastic.

In addition to the shown modifications of the preferred On events of actuators 26 , 70 , 110 in FIGS . 1, 4 and 5, the following modifications are also possible.

In addition to the pin connection 74 , other alternative connections can also be realized between the cylinder sleeve 72 and the piston rod 44 . For example, the piston rod 44 can be provided with a screw attachment which passes through a bore in the cylinder sleeve 72 and onto which a nut is screwed for securing against heel.

In general, it is possible to interchange the position of the spiral groove 50 and the axial groove 52 , that is to say to provide a spiral groove on the outer circumference of the annular piston 46 and an axial groove on the inner circumference. The ring piston does not rotate here. The pivotal movement of the shift drum is then forced by the outer coupling pin and the outer helical groove. However, the stroke required for certain pivoting angle 58 is longer in this alternative embodiment.

In this case, since the annular piston 46 is not designed to be rotatable, an anti-rotation lock between the cylinder sleeve and the piston rod can also be realized in that two parallel piston rods are provided. In this case, both piston rods can be used to guide the oil, provided that they are hollow. One piston rod can supply the pressure chamber A and the other piston rod the pressure chamber B.

The arrangement of the spiral groove or spiral groove 50 and the resultant arrangement of the axial groove 52 can prove to be more favorable, depending on the operating pressure, the friction conditions and the roller diameter, inside or outside. In the embodiments shown, the arrangement of the helical groove 50 on the inside has advantages over the arrangement on the outside. Because the resulting switching forces are significantly higher in the arrangement used and the moments of loss considerably lower compared to an arrangement of the spiral groove outside.

It is understood that instead of the radial feed of oil by means of the oil guide ring 86 , as shown in Fig. 4, ei ne axial feed can take place via the end face. It is particularly conceivable that the piston rod 44 is not continuously hollow but is equipped with two opposite blind holes, one of which serves to supply the pressure chamber A and the other to supply the pressure chamber B.

In the two-part design of the annular piston 46 , the two parts can be pressed together and, if necessary, additionally screwed. The screw heads can then be used to secure the minimum pressure chamber volume and as end stops.

By arranging the seals at the opposite ends of the annular piston 46 and correspondingly designing the spiral groove 50 and the axial groove 52 , the annular piston 46 can be preassembled and installed as an assembly on the piston rod 44 .

The integration of the piston / cylinder assembly 42 in the shift drum 30, the entire shift drum 30 can be mounted as before assembled and tested structural unit or cartridge in the transmission 10th

The fact that the swivel drive 42 is designed as a hydraulic actuator leads to the following advantages. In principle, hydraulic drives are characterized by good time behavior, low power-to-weight ratio and their small space requirements. This means gain in dynamics due to the elimination of a reduction, high actuating forces and a reduction in weight.

Due to the small space requirement, the drive can be integrated into the shift drum 30 in a longitudinal piston manner.

By pre-assembling in cartridge design, the swivel drive 42 can be easily installed by inserting it into the gear 10 .

Due to the robust solution of translating into rotary movements by means of simple coupling devices based on grooves and pins, the manufacturing disadvantages of threads are avoided. Furthermore, the hydraulic devices which are often installed anyway in an automatable transmission can be used. If an external hydraulic supply unit with memory is provided, the drive of the pump ( FIG. 1) can be made smaller (lighter) than an electric motor for the shift drum 30 that is comparable in terms of dynamics and shifting force. The degrees of freedom offered by the hydraulics make it possible to optimally adapt to the task at hand, without having any impact on the environment. The hydraulics also enable a high integrated power transmission. The electronic control units can be easily integrated electrically, there is no mixture of electromagnetic valves and electric motors.

If the swivel drive 42 is used for actuating tasks in an H manual transmission with two degrees of freedom, one can do without lever kinematics (tolerance, parts). A highly integrated design can also be realized.

In particular, if two shift drums are used instead of one shift drum, the advantage of the hydraulic swivel drive 42 over electromotive systems is high.

The rotary actuator is compared to a solution with a rotary lobe based on a linear piston / cylinder arrangement sealing technology much less expensive. They are higher fer tolerances possible. Due to the comparatively low Pressing the sealing elements becomes high efficiency achieved.

An actuator for a transmission according to the second aspect of the invention is generally designated by 200 in FIG. 9.

The actuator 200 serves to linearly move and twist a shift rod, not specified, in a linear manner. The direction of linear movements is generally shown at S in FIG. 9, the direction of rotary movements at W '.

The linear movement is used to switch the clutch couplings of the transmission, similar to the switching movements S by means of a shift lever which is guided in an H-shifting gate, as is also indicated in Fig. 9. The rotary movements, which are denoted by W 'in Fig. 9, correspond to Wählbleun gene W for selecting alleys of the H-shift gate.

The actuator 200 includes a housing 202 . The housing 202 contains a ring section 204 and a first and a second cylinder half 206 , 208 . The two cylinder halves 206 , 208 are provided at the two axial ends of the ring section 204 .

An outer cylinder space 210 is formed by the cylinder halves 206 , 208 and the ring portion 204 , in which a selector piston 212 is arranged.

The selector piston 212 is arranged in a starting position centrally inside half of the cylinder space 210 , so that a partial cylinder space is formed at both axia len ends. A seal plate 214 is provided for each seal between the partial cylinder spaces and the selector piston 212 .

The selector piston 212 is, as shown in more detail in FIGS . 10 and 11, provided on its outer circumference with two outer Diago nalnuten 216 , fen approximately helical from one axial end to the other axial end of the selector piston 212 . A shoulder 217 is provided approximately in the middle, in the area of which the diagonal grooves 217 each run approximately in the axial direction.

On the ring portion 204 of the housing 202 , two stationary guide pins 218 are provided which protrude into the outer cylinder space 210 , in such a way that they engage in the diagonal grooves 216 lying opposite.

In this connection it should be noted that Fig. 9 does not show a flat section through the actuator, but is cut in the lower half by a different plane than in the upper half.

The engagement of the guide pin 218 in the diagonal groove 216 is shown in the lower half of FIG. 9.

On the inner circumference, the selector piston 212 is provided with two axial grooves 220 lying opposite one another. In the axial grooves 220 engage outside ßnasen 224 of a coupling ring 222 , which is shown schematically in Fig. 14 in plan view.

The coupling ring 222 is fixed between the two cylinder halves 206 , 208 in an axially non-displaceable but rotatable manner.

While the outer lugs 224 protrude from the outer peripheries of the cylinder halves 206 , 208 , inner lugs of the coupling ring 222 protrude from the inner circumference of the cylinder halves 206 , 208 .

Inside the cylinder halves 206 , 208 an inner cylin derraum 228 is provided, in which a switching piston 232 is axially displaceable and rotatably mounted ver. The sealing between the cylinder halves 206 , 208 and the switching piston 232 and thus the inner cylinder space 228 is carried out via two O-rings 230 .

The switching piston 232 has a central section 234 of greater thickness. The middle section 234 is generally against the inner circumference of the cylinder halves 206 , 208 . At the transitions between the middle section 234 and the thinner Endab sections of the switching piston 232 , respective sealing plates 236 are provided. Through the seal plate 236 228 two opposite part cylinders are divided space of the inner cylinder chamber.

The switching piston 232 , as can also be seen in particular in FIGS. 12 and 13, is provided on its outer circumference with two opposite axial grooves 238 . The inner lugs 226 of the coupling ring 222 engage in these axial grooves 238 .

The partial cylinder spaces of the outer cylinder chamber 210 are each weils supplied via hydraulic fluid supply 240 with hydraulic fluid. Accordingly, the opposite Teilzylin derraumen of the inner cylinder chamber 228 via hydraulic fluid lines 242 can be supplied with hydraulic fluid.

The operation of the actuator 200 is as follows.

From the basic position shown in FIG. 9, a selection movement W 'can be initiated by introducing hydraulic fluid (via one of the lines 240 ) into one of the two sub-cylinder spaces of the outer cylinder space 210 . As a result, the selector piston 212 is axially offset. Since the housing-fixed guide pins 218 engage in the diagonal grooves 216 , the selector piston 212 is simultaneously rotated during this axial movement. The rotary movement is converted into a rotary movement of the switching piston 232 by means of the coupling pin. This process corresponds to a selection movement W with an H-guided shift lever.

Switching movements S are carried out by supplying hydraulic fluid into one of the partial cylinder spaces of the inner cylinder space 228 (via one of the lines 242 ). This results in an axial offset of the switching piston 232 , corresponding to a switching movement S. The rotational position of the pistons 212 , 232 is not influenced, since the inner lugs 226 slide in the outer axial groove of the central section 234 of the switching piston 232 .

It can be seen that from the middle position shown in FIG. 9, which corresponds to the position of a gear lever in the alley for the third / fourth gear, both selection movements to one side (e.g. to the alley of the first and second gears) ) as well as to the other side (e.g. to the alley of the fifth / sixth gear).

Correspondingly, from the middle position shown in FIG. 9, both a switching movement within an aisle can take place in one direction and the other, B. for engaging the first or second gear.

The first and the second aspect of the invention have in common that an element is provided for implementing a translation-rotation conversion, which is provided with a helical or diagonal groove as well as with an axial groove. In the case of actuator 200 , this is selector piston 212 . In the case of the actuator 26 , the actuator 70 and the actuator 110 , this is the annular piston 46 .

A transmission is therefore also regarded as a separate invention provide with a hydraulic actuator that one Annular piston with at least one axially and at least one has a helical groove.  

In general, the second aspect of the invention, ie when using such an actuator on an H- Manual transmission, achieve a particularly compact design. Fer ner compared to the actuator that from DE 196 15 267 C1 is known, an advantage that the shift shaft has no transverse force is exposed.

The actuator 200 can be realized in a cartridge design. The total number of parts is particularly low.

As part of a hybrid solution, it is also possible to realize the rotary movement of the coupling ring 222 by means of an electromotive selection angle drive.

Due to the heel 217 in the diagonal groove 216 , stable selection angles are possible in an alley (in particular in the alley for the third or fourth gear).

It is understood that much of the features and advantages which be in detail with respect to the first aspect of the invention have also been written on the second aspect of the inven apply without this being discussed in detail here. Ent speaking passages describing the first aspect of the Invention can also be read on the second aspect.

Claims (25)

1. Automated transmission ( 10 ) for motor vehicles, with a plurality of gears, which clutches ( 18 ) are assigned to engage and disengage the same, with at least one clutch ( 18 ) for engaging and disengaging at least one gear by means of an actuator ( 26 ; 70 ; 110 ) can be actuated, the actuator ( 26 ; 70 ; 110 ) having a shift drum ( 30 ) with at least one circumferential track ( 38 ), the course of which actuates the clutch ( 18 ) when the shift drum ( 30 ) rotates is, and where the actuator ( 26 ; 70 ; 110 ) has a fluid mechanical rotary drive ( 42 ) for the shift drum ( 30 ), characterized in that the rotary drive ( 42 ) has a linear piston / cylinder arrangement ( 42 ), the lifting axis (31) is aligned parallel to the axis of rotation (31) of the shift drum (30). In that the rotary drive (42) is 2. The transmission of claim 1, characterized in that a hydraulic pivot drive (42). 3. Gearbox according to claim 1 or 2, characterized in that the rotary drive ( 42 ) in the shift drum ( 30 ) is inte grated. 4. Transmission according to one of claims 1-3, characterized in that the piston / cylinder arrangement ( 42 ) has a Kop pelvorrichtung ( 50-56 ), the lifting movements of the piston / cylinder arrangement ( 42 ) in rotary movements of the shift drum ( 30th ) implements. 5. Transmission according to claim 4, characterized in that the coupling device ( 50-56 ) has a helical profile ( 50 ) with a pitch angle ( 59 ) in the range from 10 ° to 80 °, in particular from 30 ° to 50 °. 6. Transmission according to claim 4 or 5, characterized in that the coupling device ( 50-56 ) limits the rotatability of the shift drum ( 30 ). 7. Transmission according to one of claims 1-6, characterized in that the piston / cylinder arrangement ( 42 ) has an annular piston ( 46 ). 8. Transmission according to claim 7, characterized in that the annular piston ( 46 ) is axially movably mounted on a rotationally fixed piston rod ( 44 ). 9. Transmission according to claim 8, characterized in that the piston rod ( 44 ) has a hollow channel ( 84 ) for fluid conduction. 10. Transmission according to one of claims 7-9, characterized in that the annular piston ( 46 ) on the piston rod ( 44 ) by means of a first coupling device ( 50 , 54 ) is rotatably supported to a limited extent. 11. Transmission according to claim 10, characterized in that the first coupling device ( 50 , 54 ) is designed such that an axial stroke of the annular piston ( 46 ) on the piston rod ( 44 ) a rotational movement of the annular piston ( 46 ) with respect to the piston rod ( 44 ) induced, and vice versa. 12. Transmission according to claim 11, characterized in that the first coupling device ( 50 , 54 ) has a helical profile ( 50 ) with a pitch angle ( 59 ) in the range from 10 ° to 80 °, in particular from 30 ° to 50 °. 13. Transmission according to claim 11 or 12, characterized in that the annular piston ( 46 ) by means of a second coupling device ( 52 , 56 ) rotatably coupled to the shift drum ( 30 ) GE. 14. Transmission according to one of claims 4-13, characterized in that the coupling device (s) ( 50-56 ) each have a coupling pin ( 54 , 56 ) which engages in a corresponding coupling groove ( 50 , 52 ). 15. Transmission according to one of claims 1-14, characterized in that the piston / cylinder arrangement ( 42 ) has a cylinder ( 72 ) with an opening ( 73 ) and a piston ( 46 ) through the opening ( 73 ) is coupled to the shift drum ( 30 ). 16. Transmission according to claim 15, characterized in that the cylinder ( 72 ) is rigidly connected to a piston rod ( 44 ) on which the piston ( 46 ) is mounted. 17. Transmission according to claim 15 or 16, characterized in that the cylinder ( 72 ) is formed in two parts. 18. Transmission according to one of claims 1-14, characterized in that the shift drum forms the cylinder ( 30 ) of the piston / cylinder arrangement ( 42 ). 19. Transmission according to one of claims 7-18, characterized in that the annular piston ( 46 ) is formed in two parts. 20. Transmission according to one of claims 3-19, characterized in that the piston / cylinder arrangement ( 42 ) is pre-assembled in the manner of a cartridge in the shift drum ( 30 ). 21.Automatizable transmission for motor vehicles, with a plurality of gears, to which at least two shift clutches are assigned for engaging and disengaging the same, which can be selected separately, the shift clutches being actuatable by means of an actuator device ( 200 ), the actuator device ( 200 ) selects one of the clutches by means of a first movement (W ') and actuates the respectively selected clutch by means of a second movement (S), the directions of the first and second movements (W', S) being approximately perpendicular to one another, wherein the actuator device ( 200 ) has a first linear piston / cylinder arrangement ( 204 , 206 , 208 , 212 ) for executing first movements (W ') and a second linear piston / cylinder arrangement ( 206 , 208 , 234 ) for executing of second movements (S), and wherein a translational rotation converter ( 218 , 216 , 220 , 222 , 238 ) is provided such that a linear displacement of the piston ( 212 ) of the first piston / cylinder arrangement ( 204 , 206 , 208 , 212 ) is converted into a rotary movement (W ') of the piston ( 234 ) of the second piston / cylinder arrangement ( 206 , 208 , 234 ), characterized in that
the first linear piston / cylinder arrangement ( 204 , 206 , 208 , 212 ) is arranged parallel to the second linear piston / cylinder arrangement ( 206 , 208 , 234 ) and
that the translational rotation converter ( 218 , 216 , 220 , 222 , 238 ) has at least one helical profile ( 216 ). 22. Transmission according to claim 21, characterized in that the piston ( 212 ) of the first piston / cylinder arrangement ( 204 , 206 , 208 , 212 ) has an outer groove ( 216 ) and an inner groove ( 220 ), one of which ( 216 ) is designed as a screw groove ( 216 ). 23. Transmission according to claim 21 or 22, characterized in that the helical profile ( 216 ) has a shoulder in order to enable a stable selection angle at this point. 24. Transmission according to one of claims 21-23, characterized in that the second piston / cylinder arrangement ( 206 , 208 , 234 ) is arranged concentrically within the first piston / cylinder arrangement ( 204 , 206 , 208 , 212 ). 25. Transmission according to one of claims 21-24, characterized in that the rotation-translation converter ( 218 , 216 , 220 , 222 , 238 ) has a coupling ring ( 222 ), the axial position of which is fixed and which is in respective grooves ( 220 , 238 ) the piston ( 212 , 234 ) of the piston / cylinder assemblies engages.