Actuating device for a manual transmission

Abstract

Actuating device (1) for a transmission (2), comprising at least one piston (3) and a shift sleeve (4), wherein the piston (3) is fixedly connected to the shift sleeve (4), characterized in that the actuating device (1) has at least one housing (12) with an inner circumferential surface (13), wherein the shift sleeve (4) with the piston (3) is arranged in the housing (12), wherein the piston (3) with the inner circumferential surface (13) and a partition (16) extending inwards from the inner circumferential surface (13) along a radial direction (14) to a first end (15) forms an annular first pressure chamber (18) extending along a circumferential direction (17) and an annular second pressure chamber (19) extending along the circumferential direction (17).

Description

[0001] The present invention relates to an actuating device for a manual transmission, in particular for a manual transmission of a motor vehicle. The actuating device is intended to enable selection of different gear ratios of the manual transmission.

[0002] WO 2015 / 117610 A1 discloses actuating devices for operating manual transmissions in which shift sleeves are actuated by shift forks. The shift forks are supported by guide rods, and the shift forks are actuated by shift drums or hydraulic pistons.

[0003] A relevant actuating device for a manual transmission is also known from DE 10 2006 049 280 A1.

[0004] The hydraulic pistons can be provided in the rotating part of the actuating device, where they are then hydraulically connected via rotary unions.

[0005] The existing actuation devices require a lot of installation space, at the very least. Furthermore, mechanical effort may be required to support the protruding shift forks with the guide rods. The hydraulic rotary unions can lead to friction losses.

[0006] Based on this, the present invention is based on the object of at least partially alleviating the problems known from the prior art and, in particular, of providing an actuating device for a manual transmission which has a compact design.

[0007] This object is achieved with an actuating device according to the features of independent claim 1. Further advantageous embodiments of the invention are specified in the dependent claims. The features listed individually in the dependent claims can be combined with one another in a technologically expedient manner and can define further embodiments of the invention. Furthermore, the features specified in the claims are further specified and explained in the description, with further preferred embodiments of the invention being presented.

[0008] An actuating device for a manual transmission is proposed, comprising at least one piston and a shift sleeve, wherein the piston is fixedly connected (in particular rotationally fixed or exclusively jointly displaceable) to the shift sleeve.

[0009] In particular, the piston and the shift sleeve are designed as a single piece (single-piece, integrally connected). In particular, the piston and shift sleeve are designed as multiple parts, at least for arrangement in an operating position relative to a housing, and are only connected to each other after they have been arranged in the housing.

[0010] In particular, the actuating device has a rotational axis, wherein at least the at least one piston and the shift sleeve are arranged coaxially to one another and to the rotational axis.

[0011] In particular, it is provided that the at least one piston (the pistons) of the actuating device are arranged coaxially to the shift sleeve, wherein the cylinder, piston and shift sleeve form a unit.

[0012] The cylinder, in which the piston is arranged to be displaceable, in particular along an axial direction (parallel to the axis of rotation), is formed in particular by a housing (connected to a motor vehicle, in particular a fixed one).

[0013] The piston can rotate with the shift sleeve and the cylinder can be arranged (stationary).

[0014] Seals can be provided between a rotating part and a stationary part which have only low (or even no) frictional moments without pressure, but seal when pressure is applied (actuating pressure).

[0015] In particular, a sliding sleeve structure and a transmission are further proposed, comprising the described actuating device and / or a corresponding sliding sleeve structure.

[0016] The actuation takes place here in particular via at least one integrated piston, which is pressurized with pressurized fluid via stationary (fixed) supply lines.

[0017] This involves direct actuation of the pistons or the sliding sleeve by the hydraulic forces directly via the piston(s).

[0018] Moving parts of the piston can be connected to the actual sliding sleeve and sealed against housing parts / against fixed parts via seals.

[0019] Furthermore, the seals can have a gap between the differently rotating areas in the force-free state, which minimizes friction and thus wear or power loss.

[0020] Actuating the piston by applying pressure closes the gap. A slight fluid flow prior to closing may be tolerated.

[0021] In particular, the shift sleeve is connected to a synchronizer body in a rotationally fixed manner and can be displaced via the piston at least between a first switching position and a second switching position (along the axial direction), wherein the synchronizer body can be connected in a rotationally fixed manner via the shift sleeve in the first switching position to a first switching toothing and in the second switching position, if necessary, to a second switching toothing.

[0022] In particular, a neutral position (along the axial direction) is provided between the first shift position and the second shift position. In particular, in the neutral position, the shift sleeve is not rotationally connected to either the first shift toothing or the second shift toothing (but only to the synchronizer hub).

[0023] In particular, the actuating device additionally comprises at least one synchronizer body. In particular, the synchronizer body is or can be connected to a transmission shaft in a rotationally fixed manner, so that the transmission shaft can be connected to the first gearshift toothing or to the second gearshift toothing via the synchronizer body and the shift sleeve.

[0024] In particular, each gearshift toothing is connected to a shaft in a rotationally fixed manner. This preferably allows torque transmitted via the transmission shaft to be transferred to an (output) shaft via the synchronizer hub, shift sleeve, and gearshift toothing.

[0025] Preferably, the shift sleeve is rotatably connected to a first intermediate gear at least before reaching the first shift position, wherein the first intermediate gear is frictionally connected to the first shift toothing via a further displacement of the shift sleeve, so that a torque can be transmitted frictionally.

[0026] Preferably, the shift sleeve is rotatably connected to a second intermediate gear at least before reaching the second shift position, wherein the second intermediate gear is frictionally connected to the second shift toothing via a further displacement of the shift sleeve.

[0027] The speed of the shift gearing and the synchronizer hub can be synchronized via an intermediate gear. The intermediate gear can be connected to the shift sleeve in a rotationally fixed manner, particularly via a toothing. In particular, the intermediate gear can be connected to the shift gearing via a friction surface, so that the speeds of the shift sleeve or intermediate gear on the one hand and the shift gearing on the other hand can be synchronized before a rotationally fixed connection between the shift sleeve and the respective shift gearing is created in a first or second shift position. In particular, further displacement of the shift sleeve into the first or second shift position is prevented by a lock as long as a speed difference still exists between the shift sleeve and the respective shift gearing.

[0028] According to the invention, the actuating device has at least one housing with an inner circumferential surface, wherein the shift sleeve with the piston is arranged in the housing, wherein the piston with the inner circumferential surface and a partition wall extending from the inner circumferential surface along the radial direction inwards to a first end forms an annular first pressure chamber extending along a circumferential direction and an annular second pressure chamber extending along the circumferential direction.

[0029] In particular, each pressure chamber is defined radially outwardly by the housing and radially by the partition or the shift sleeve. In the radial direction inwardly, the pressure chambers are also defined by the shift sleeve.

[0030] In particular, the first pressure chamber and the second pressure chamber are delimited by walls, whereby the walls can have different rotational speeds from one another. The walls, together with the seals (first, second, third seal), form the pressure chambers. Each pressure chamber is delimited, in particular, at least by the inner circumferential surface of the housing, the partition wall, and the shift sleeve. The inner circumferential surface, partition wall, and shift sleeve form the walls of each pressure chamber. In particular, the piston or shift sleeve rotates relative to the (stationary) housing with the partition wall.

[0031] In particular, the piston or the shift sleeve is designed in several parts and is assembled for arrangement in the housing only after the piston or the shift sleeve has been arranged opposite the partition wall to form the one-piece piston or the one-piece shift sleeve.

[0032] Preferably, the first pressure chamber is connectable to a first pressure line via the housing, and the second pressure chamber is connectable to a second pressure line via the housing. In particular, a first fluid channel on a first side of the partition wall and a second fluid channel on a second side of the partition wall each extend along the circumferential direction through the housing around the pressure chambers.

[0033] In particular, the first fluid channel is connected to the first pressure chamber via first openings and the second fluid channel is connected to the second pressure chamber via second openings.

[0034] In particular, the first openings and the second openings are each arranged (immediately) adjacent to the partition wall in the inner peripheral surface of the housing. In particular, the housing has fixed supply lines for the first and second pressure lines.

[0035] In particular, at least one pressure chamber can be sealed by at least one seal, whereby the at least one seal seals the at least one pressure chamber in a fluid-tight manner only when the at least one pressure chamber is subjected to an actuating pressure. The actuating pressure is, in particular, higher than a pressure prevailing in the adjacent pressure chamber. In particular, these two pressures differ by at least 5%, preferably by at least 10% (based on the higher pressure).

[0036] In particular, the other pressure chamber (e.g., the first) can also be sealed via the (first) seal arranged therein when one (second) pressure chamber is subjected to an actuating pressure. If one (second) pressure chamber is subjected to the actuating pressure, the volume of the (second) pressure chamber will increase; in particular, the volume of the (first) pressure chamber will decrease in the same way. The fluid must then flow out through the (first) openings.

[0037] The pressure in the (first) pressure chamber is then also increased (e.g. compared to the surroundings), in particular by at least 10% higher than the ambient pressure).

[0038] The first pressure chamber can be sealed by at least one first seal and the second pressure chamber by at least one second seal, wherein, upon actuation of an actuating pressure in each case and displacement of the piston toward a switching position in the other pressure chamber, end-position damping for the piston is realized by the at least one seal assigned to this pressure chamber. In particular, the end-position damping is realized in that, shortly before reaching, for example, the first switching position, the second seal in the second pressure chamber at least partially closes the second openings, so that the fluid to be displaced from the second pressure chamber can flow out through the second openings only more slowly.

[0039] In particular, the first pressure chamber and the second pressure chamber can be sealed against each other in a fluid-tight manner via a third seal arranged at the first end, wherein the third seal seals the pressure chambers against each other in a fluid-tight manner only when at least one pressure chamber is subjected to an actuating pressure.

[0040] A method for actuating a manual transmission with an actuating device (in particular with the one already described) is further described, wherein the actuating device comprises at least one piston and a shift sleeve rigidly connected to the piston, as well as a synchronizer body rigidly connected to the shift sleeve. The method comprises at least the following step: a) Displacing the piston and thus the shift sleeve between at least a first shift position and a second shift position by applying an actuating pressure to the piston; wherein the synchronizer body is connected in a rotationally fixed manner via the shift sleeve to a first shift toothing in the first shift position and to a second shift toothing in the second shift position.

[0041] The statements regarding the actuating device apply equally to the method and vice versa.

[0042] In particular, a transmission arrangement is proposed, comprising at least a transmission with a plurality of gear ratios and an actuating device, in particular the actuating device already described, via which the individual gear ratios can be selected. In particular, an actuator is also provided, via which the pressure chambers of the actuating device can be pressurized with a pressurized fluid.

[0043] Furthermore, a motor vehicle with the transmission arrangement already described is proposed, at least further comprising a drive unit and the transmission arrangement with a plurality of switchable gear ratios, wherein the drive unit and transmission can be connected in a torque-transmitting manner.

[0044] The following features are also suggested: 1. Actuating device for manual transmission, comprising at least one piston and a shift sleeve, wherein the piston is fixedly connected to the shift sleeve. 2. Actuating device according to feature 1, characterized in that the piston is an integral component of the shift sleeve (piston and shift sleeve are in particular designed as one piece, in one piece or with a material fit). 3. Actuating device according to one of the preceding features, characterized in that two piston chambers (pressure chambers) are formed by the shift sleeve and a radial outer surface (inner circumferential surface), preferably a housing component (housing). 4. Actuating device according to one of the preceding features, characterized in that the fluid supply into a piston chamber (pressure chamber) is realized via openings in the cylinder housing (on the inner peripheral surface or on the housing). 5. Sliding sleeve structure for engaging a gear in a transmission, characterized in that the actuation takes place via at least one integrated piston which is pressurized with pressurized fluid via stationary supply lines. 6. Motor vehicle transmission comprising an actuating device according to one of features 1 to 4 and a sliding sleeve structure according to feature 5.

[0045] As a precaution, it should be noted that the numerals used here ("first", "second",...) primarily serve (only) to distinguish between several similar objects, quantities, or processes, and therefore do not necessarily specify any interdependence and / or sequence of these objects, quantities, or processes. Should a dependence and / or sequence be required, this is explicitly stated here or will be obvious to the person skilled in the art upon studying the specifically described embodiment.

[0046] The invention and the technical environment are explained in more detail below with reference to the figures. It should be noted that the invention is not intended to be limited by the exemplary embodiments shown. In particular, unless explicitly stated otherwise, it is also possible to extract partial aspects of the facts explained in the figures and combine them with other components and findings from the present description and / or figures. In particular, it should be noted that the figures and in particular the illustrated proportions are only schematic. The same reference numerals denote the same objects, so that explanations from other figures can be used as a supplement if necessary. They show: Fig. 1: an actuating device in a side view in section; Fig. 2: a manual transmission with an actuating device in a perspective view; Fig. 3: the actuating device according to Fig. 1 and Fig. 2 in a perspective view in section; Fig. 4: the actuating device according to Fig. 1 to 3 in a neutral position in a side view in section; Fig. 5: the actuating device according to Fig. 4 after pressurisation of the first pressure chamber; Fig. 6: the actuating device according to Fig. 5 in the first switching position; Fig. 7: the actuating device according to Fig. 6 in the first switching position, no actuating pressure; Fig. 8: the actuating device according to Fig. 7 in the first switching position, pressurization of the second pressure chamber; Fig. 9: the actuating device according to Fig. 8, neutral position reached; and Fig. 10: a detail of the actuating device according to Fig. 2 in a side view in section.

[0047] Fig. 1 shows an actuating device 1 in a side view in section. Fig. 2 shows a manual transmission 2 with an actuating device 1 in a perspective view. Fig. 3 shows the actuating device 1 according to Fig. 1 and Fig. 2 in a perspective view in section. The Fig. 1 to 3 are described together below.

[0048] The actuating device 1 for a manual transmission 2 comprises a piston 3 and a shift sleeve 4, wherein the piston 3 is fixedly connected to the shift sleeve 4. In the present case, the piston 3 and the shift sleeve 4 are designed as a single piece. In particular, the piston 3 and the shift sleeve 4 are designed as multiple parts, at least for arrangement in an operating position relative to a housing 12, and are only connected to one another after arrangement in the housing 12. In particular, the actuating device 1 has a rotation axis 35, wherein the piston 3 and the shift sleeve 4 are arranged coaxially to one another and to the rotation axis 35.

[0049] The actuation takes place via an integrated piston 3, which is supplied with pressurized fluid via stationary (fixed) supply lines 34.

[0050] The shift sleeve 4 is connected to a synchronizer body 5 in a rotationally fixed manner and is switched via the piston 3 between a first switching position 6 (see Fig. 6) and a second switching position 7 (switch positions 6, 7 are in Fig. 1, the arrows indicate the displacement of the piston 3 and the shift sleeve 4 relative to the housing 12) along the axial direction 26, wherein the synchronizer body 5 is rotatably connected via the shift sleeve 4 in the first switching position 6 to a first switching toothing 8 and in the second switching position 7 to a second switching toothing 9.

[0051] In the present case, the piston 3 is arranged in a neutral position 27 (along the axial direction 26) between the first shift position 6 and the second shift position 7. In the neutral position 27, the shift sleeve 4 is not rotationally connected to either the first shift toothing 8 or the second shift toothing 9 (but exclusively to the synchronizer body 5).

[0052] The actuating device 1 comprises a synchronizer body 5. The synchronizer body 5 is connected or can be connected in a rotationally fixed manner to a transmission shaft (via the internal toothing shown), so that the transmission shaft can be connected in a rotationally fixed manner to the first switching toothing 8 or to the second switching toothing 9 via the synchronizer body 5 and the shift sleeve 4.

[0053] The shift sleeve 4 can be connected in a rotationally fixed manner to a first intermediate gear 10 before reaching the first shift position 6, wherein the first intermediate gear 10 can be frictionally connected to the first shift toothing 8 via a further displacement of the shift sleeve 4.

[0054] The shift sleeve 4 can be connected in a rotationally fixed manner to a second intermediate gear 11 before reaching the second shift position 7, wherein the second intermediate gear 11 can be frictionally connected to the second shift toothing 9 via a further displacement of the shift sleeve 4.

[0055] The actuating device 1 further comprises a housing 12 with an inner circumferential surface 13, wherein the shift sleeve 4 with the piston 3 is arranged in the housing 12, wherein the piston 3 with the inner circumferential surface 13 and a partition wall 16 extending from the inner circumferential surface 13 along the radial direction 14 inwards to a first end 15 forms an annular first pressure chamber 18 extending along a circumferential direction 17 and an annular second pressure chamber 19 extending along the circumferential direction 17.

[0056] Each pressure chamber 18, 19 is delimited in the radial direction 14 on the outside by the housing 12 and along the radial direction 14 by the partition 16 or by the shift sleeve 4. In the radial direction 14 on the inside, the pressure chambers 18, 19 are also delimited by the shift sleeve 4.

[0057] The first pressure chamber 18 and the second pressure chamber 19 are delimited by walls (first piston wall 38, second piston wall 39, partition wall 16, inner circumferential surface 13, and shift sleeve 4 or piston 3), whereby the walls can have different rotational speeds. In particular, the inner circumferential surface 13 of the housing 12, together with the partition wall 16, can be operated at a different rotational speed than the other walls. The walls, together with the seals 22, 23, 25, form the pressure chambers 18, 19. Each pressure chamber 18, 19 is delimited by the inner circumferential surface 13 of the housing 12, the partition wall 16, and the shift sleeve 4 or piston 3. The inner circumferential surface 13, the partition wall 16, and the shift sleeve 4 or piston 3 form the walls of each pressure chamber 18, 19.

[0058] The first seal 22 is arranged on a first piston wall 38 which extends along the radial direction 14 and forms a wall of the first pressure chamber 18.

[0059] The second seal 23 is arranged on a second piston wall 39 which extends along the radial direction 14 and forms a wall of the second pressure chamber 18.

[0060] The first pressure chamber 18 is connectable via the housing 12 to a first pressure line 20, and the second pressure chamber 19 is connectable via the housing 12 to a second pressure line 21. A first fluid channel 28 on a first side 30 of the partition wall 16 and a second fluid channel 29 on a second side 31 of the partition wall 16 each extend along the circumferential direction 17 through the housing 12 around the pressure chambers 18, 19.

[0061] The first fluid channel 28 is connected to the first pressure chamber 18 via first openings 32 and the second fluid channel 29 is connected to the second pressure chamber 19 via second openings 33.

[0062] The first openings 32 and the second openings 33 are each arranged directly adjacent to the partition wall 16 in the inner peripheral surface 13 of the housing 12. The housing 12 has supply lines 34 for the first and second pressure lines 20, 21 fixedly arranged on the housing 12.

[0063] The first pressure chamber 18 can be sealed by a first seal 22 and the second pressure chamber 19 by a second seal 23, wherein when an actuating pressure 24 is applied to one of the pressure chambers 18, 19 and the piston 3 is displaced towards a switching position 6, 7, in the other pressure chamber 19, 18, end position damping for the piston 3 is realized by the seal 22, 23 assigned to this pressure chamber 19, 18. The end position damping is realized in that shortly before reaching, for example, the first switching position 6, the second seal 23 in the second pressure chamber 19 at least partially closes the second openings 33, so that the fluid to be displaced from the second pressure chamber 19 can flow out only more slowly via the second openings 33 (see Fig. 6).

[0064] Furthermore, the first pressure chamber 18 and the second pressure chamber 19 can be sealed fluid-tight against each other via a third seal 25 arranged at the first end 15, wherein the third seal 25 only seals the pressure chambers 18, 19 fluid-tight against each other when at least one pressure chamber 18, 19 is subjected to an actuating pressure 24.

[0065] Actuation occurs by means of a piston 3 on a circular ring (e.g. around the shift sleeve 4). The working volume of the piston 3 is enclosed by a radially inner boundary surface which is axially displaceable and firmly connected to the shift sleeve 4, a radially outer boundary surface (inner peripheral surface 13) which is fixed in an upright position, and two or more circular disks which limit the working volume in the axial direction 26 and are alternately firmly connected to the outer boundary surface or the inner boundary surface. Depending on the number of circular disks, one or more separate working volumes result. Preferably, there are three circular disks, which form two separate working volumes (pressure chambers 18, 19), with each working volume being used for movement in one direction. Preferably, the shift sleeve 4 and the radially inner boundary surface are a single component.

[0066] In the Fig. 1 circular discs are shown: • Piston wall left (connected to the radially inner boundary surface; here the left boundary wall of the shift sleeve 4 for the second pressure chamber 19) • (middle) partition wall 16 (connected to the radially outer boundary surface, i.e. the inner circumferential surface 13 of the housing 12) • Piston wall on the right (connected to the radially inner boundary surface; here the right boundary wall of the switching sleeve 4 for the first pressure chamber 18).

[0067] The piston wall on the left is firmly connected to the radially inner boundary surface. The seal on the left (second seal 23) seals the gap to the radially outer boundary surface (left; inner peripheral surface 13).

[0068] The (middle) partition 16 is firmly connected to the radially outer boundary surface (inner circumferential surface 13) and separates the working volume on the left (second pressure chamber 19) from the working volume on the right (first pressure chamber 18). The middle seal (third seal 25) seals the gap to the radially inner boundary surface.

[0069] The piston wall on the right is firmly connected to the radially inner boundary surface. The seal on the right (first seal 22) seals the gap to the radially outer boundary surface (right; inner circumferential surface 13).

[0070] The seals 22, 23, and 25 are designed so that, without pressure, they form a gap (radially and axially) with the corresponding circular discs, thus minimizing friction at different rotational speeds of the disc and the radial boundary surfaces. Only when a fluid or gas is forced into the corresponding working volume (pressure chamber 18, 19) do the affected seals 22, 23, and 25 contact the circular discs due to the resulting pressure difference (acting in the axial direction 26) and seal the corresponding gap.

[0071] In the illustrated design, the working fluid flows into the working volumes (pressure chambers 18, 19) on the right and left via the distribution channels (fluid channels 28, 29) on the right and left and the connecting bores (openings 32, 33) on the right and left. The distribution channels on the right and left are each supplied via connecting lines (pressure lines 20, 21) connected to supply lines 34.

[0072] In Fig. 2, the synchronizer body 5 with the internal gearing (for a positive, torque-resistant connection to the shaft) and the second shift gearing 9 are visible. Furthermore, one of the supply lines 34 to the distribution channels (fluid channels 28, 29) is visible, as is the housing 12 with the distribution channels.

[0073] The housing 12 is fixed to the gear housing by means of fastening elements 37, so that the axial actuating forces as well as the torque due to friction are supported.

[0074] The supply lines 34 on the left and right are connected to the distribution channels (fluid channels 28, 29 on the left and right, respectively). The distribution channels are connected to the working volumes (pressure chambers 18, 19) via the connecting holes (openings 32, 33) on the left and right, respectively. The distribution channels, together with the large number of connecting holes, ensure a large cross-sectional area for the supply of the working fluid.

[0075] The synchronizer hub 5 is connected to the shaft (not shown) in a rotationally fixed manner, e.g., by means of internal gearing. The clutch bodies (left and right) (shifting gears 8, 9) are each rotationally fixedly connected to the gears to be shifted or to other shafts (preferably hollow shafts; not shown here).

[0076] When the shift sleeve 4 is actuated in the axial direction 26 by means of the actuator, the shift sleeve 4 first presses the friction surfaces of the synchronization together, and further axial movement of the shift sleeve 4 is prevented by a lock (not shown). When a synchronous speed is reached between the synchronizer body 5 and one of the clutch bodies (shift teeth 8, 9), the lock releases further axial movement of the shift sleeve 4. The shift sleeve 4 is further displaced axially by the actuation until the shift sleeve 4 reaches a positive connection with the shift teeth 8, 9 (in the circumferential direction 17), whereby a positive torque transmission between the synchronizer body 5 and the clutch body (shift teeth 8, 9) is ensured.

[0077] The housing 12 is fastened to the fixed or gear housing by means of fastening elements, so that the axial actuating forces as well as the torque due to friction are supported.

[0078] Fig. 4 shows the actuating device 1 according to Fig. 1 to 3 in a neutral position 27 in a side view in section. The statements of the Fig. Reference is made to paragraphs 1 to 3.

[0079] Here, there is no actuation pressure 24, or the same pressure exists in both pressure chambers 18, 19. The seals 22, 23, 25 are each arranged at a distance from the walls with which they would form a sealing surface if an actuation pressure 24 were present. The partition wall 16 is arranged centrally with the shift sleeve 4. The shift sleeve 4 is only connected to the synchronizer body 5 in a rotationally fixed manner.

[0080] In Fig. 4, the actuator is in the central rest position without pressure. The three seals 22, 23, 25 (left, center, and right) are spaced axially from the annular discs 26, so that several gaps (left, center, and right) are present between the seals 22, 23, and 25.

[0081] Fig. 5 shows the actuating device 1 according to Fig. 4 after pressurization of the first pressure chamber 18. The statements of the Fig. Reference is made to paragraphs 1 to 3.

[0082] Here, the first pressure chamber 18 is pressurized with a pressurized fluid and an actuating pressure 24. The first seal 22 and the third seal 25 each rest against the designated wall to form the sealing surface.

[0083] Fig. Figure 5 shows the beginning of an actuation to the right. A working fluid is pressed through the distribution channel on the right (first fluid channel 28) via the connecting holes on the right (first openings 32) into the piston volume on the right (first pressure chamber 18). Initially, a portion of the medium flows through the gaps, but an overpressure nevertheless builds up in the piston volume (first pressure chamber 18). This overpressure presses both the center seal (third seal 25) and the right seal (first seal 22) against the (middle) partition wall 16 and against the piston wall on the right (sliding sleeve 4), respectively, so that the gaps (center and right) consist of Fig. 4 will be closed. In Fig. 5 the columns are already closed.

[0084] Fig. 6 shows the actuating device 1 according to Fig. 5 in the first switching position 6. Refer to the statements of Fig. Reference is made to paragraphs 1 to 3.

[0085] The shift sleeve 4 or piston 3 is now completely shifted to the right. The shift sleeve 4 is connected in a rotationally fixed manner to the first intermediate gear 10 and the first shift toothing 8.

[0086] Fig. Figure 6 shows the situation immediately after reaching the right end position (first switching position 6). Due to the displacement movement to the right, the seal on the left (second seal 23) has contacted the piston wall on the left (switching sleeve 4) and has been axially displaced by the piston wall on the left.

[0087] If necessary, the seal on the left (second seal 23) closes the connecting holes on the left (second openings 33), slightly impeding the flow of the working fluid from the piston volume on the left (second pressure chamber 19) into the distribution channel on the left (second fluid channel 29). This allows for end-of-stroke cushioning if required.

[0088] Fig. 7 shows the actuating device 1 according to Fig. 6 in the first switching position 6, without actuating pressure 24. Refer to the Fig. Reference is made to paragraphs 1 to 3.

[0089] Here, there is no actuating pressure 24, or the same pressure exists in both pressure chambers 18, 19. The seals 22, 23, 25 are each arranged at a distance from the walls with which they would form a sealing surface if an actuating pressure 24 were present.

[0090] Fig. Figure 7 shows the situation in the depressurized state in the right rest position (first switching position 6, no actuation pressure 24). Due to axial wobbling and other effects, axial clearances arise again between the seals 22, 23, 25 (left, right, center) and the piston walls 38, 39 (shift sleeve 4) as well as the (center) partition wall 16. This can cause gaps to arise again between the seals 22, 23, 25 and the annular discs.

[0091] Fig. 8 shows the actuating device 1 according to Fig. 7 in the first switching position 6, pressurization of the second pressure chamber 19. Refer to the statements of the Fig. Reference is made to paragraphs 1 to 3.

[0092] Here, the second pressure chamber 19 is pressurized with a pressurized fluid and an actuating pressure 24. The second seal 23 and the third seal 25 each rest against the designated wall to form the sealing surface.

[0093] Fig. Figure 8 shows the beginning of an actuation back to the center position (neutral position 27). The piston volume on the left (second pressure chamber 19) is filled with working fluid via the distribution channel on the left (second fluid channel 29) and the connecting holes on the left (second openings 33). This creates an overpressure in the left piston volume, which presses the seals on the left and center (second seal 23 and third seal 25) against the piston wall on the left and the (center) separating web (separating wall 16), respectively, so that the gaps close and the seals 23, 25 seal the piston volume on the left. In the illustration of the Fig. This is already the case in 8. Due to the pressure in the piston volume on the left, the actuator moves axially to the left together with the shift sleeve 4.

[0094] Fig. 9 shows the actuating device 1 according to Fig. 8, neutral position 27 reached. Refer to the comments on Fig. 4 is referred to.

[0095] In contrast to Fig. 4, the seals 22, 23, 25 still form the sealing surfaces with the respective walls.

[0096] Fig. Figure 9 shows the situation when the center rest position (neutral position 27) is reached. Due to the shifting movement to the left, the seal on the right (first seal 22) has pressed against the piston wall on the right and has been axially shifted by the piston wall on the right.

[0097] After removing the working pressure (actuating pressure 24), the seals 22, 23, 25) can again assume a distance position in the axial direction 26 and the state as in Fig. 4 reached again.

[0098] A movement to the left is similar to the steps above from Fig. 4 to Fig. 9 with page numbers reversed.

[0099] Fig. 10 shows a detail of the actuating device 1 according to Fig. 2 in a side view in section.

[0100] The seal on the right (first seal 22) preferably consists of at least two parts to simplify assembly. This is especially useful for hard seals that can only be deformed to a limited extent for assembly.

[0101] For example, the seal on the right consists of the actual seal and a clamp 36, which ensures that the seal 22 can form an axial gap with the piston wall, but the width of the gap is limited. During assembly, the clamp 36 hooks its fingers behind a bead of the seal.

[0102] For assembly reasons, the middle seal (third seal 25) is preferably also mounted from two individual parts around the (middle) partition wall 16. List of reference symbols 1 actuating device 2 manual transmissions 3 pistons 4 Shift sleeve 5 synchronizer bodies 6 first switching position 7 second switching position 8 first gear teeth 9 second gear teeth 10 first intermediate gear 11 second intermediate gear 12 housings 13 Inner peripheral surface 14 radial direction 15 first end 16 Partition wall 17 Circumferential direction 18 first printing room 19 second printing room 20 first pressure line 21 second pressure line 22 first seal 23 second seal 24 actuation pressure 25 third seal 26 axial direction 27 Neutral position 28 first fluid channel 29 second fluid channel 30 first page 31 second page 32 first opening 33 second opening 34 supply line 35 axis of rotation 36 bracket 37 Fastening element 38 first piston wall 39 second piston wall

Claims

[1] Actuating device (1) for a manual transmission (2), comprising at least one piston (3) and a shift sleeve (4), wherein the piston (3) is firmly connected to the shift sleeve (4), characterized by in that the actuating device (1) has at least one housing (12) with an inner circumferential surface (13), wherein the shift sleeve (4) with the piston (3) is arranged in the housing (12), wherein the piston (3) with the inner circumferential surface (13) and a partition wall (16) extending from the inner circumferential surface (13) along a radial direction (14) inwards to a first end (15) forms an annular first pressure chamber (18) extending along a circumferential direction (17) and an annular second pressure chamber (19) extending along the circumferential direction (17). [2] Actuating device (1) according to claim 1, wherein the piston (3) and the shift sleeve (4) are designed in one piece. [3] Actuating device (1) according to one of the preceding claims, wherein the shift sleeve (4) is connected in a rotationally fixed manner to a synchronizer body (5) and is displaceable via the piston (3) at least between a first switching position (6) and a second switching position (7), wherein the synchronizer body (5) is rotatably connected to a first switching toothing (8) via the shift sleeve (4) at least in the first switching position (6). [4] Actuating device (1) according to one of claims 1 to 3, wherein the first pressure chamber (18) and the second pressure chamber (19) are delimited by walls, wherein the walls can have different rotational speeds from one another. [5] Actuating device (1) according to one of the preceding claims, wherein the first pressure chamber (18) is connectable to a first pressure line (20) via the housing (12) and the second pressure chamber (19) is connectable to a second pressure line (21) via the housing (12). [6] Actuating device (1) according to one of the preceding claims 1 to 5, wherein at least one pressure chamber (18, 19) can be sealed by means of at least one seal (22, 23), wherein the at least one seal (22, 23) seals the at least one pressure chamber (18, 19) in a fluid-tight manner only when the at least one pressure chamber (18, 19) is subjected to an actuating pressure (24). [7] Actuating device (1) according to one of the preceding claims, wherein the first pressure chamber (18) can be sealed by at least one first seal (22) and the second pressure chamber (19) can be sealed by at least one second seal (23), wherein when the respective one pressure chamber (18, 19) is subjected to an actuating pressure (24) and the piston (3) is displaced towards a switching position (6, 7) in the respective other pressure chamber (19, 18), an end position damping for the piston (3) is realized by the at least one seal (23, 22) assigned to this pressure chamber (19, 18). [8] Actuating device (1) according to one of the preceding claims, wherein the first pressure chamber (18) and the second pressure chamber (19) can be sealed fluid-tightly against one another via a third seal (25) arranged at the first end (15), wherein the third seal (25) only seals the pressure chambers (18, 19) fluid-tightly against one another when at least one pressure chamber (18, 19) is subjected to an actuating pressure (24).

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