CLAW-TYPE GEARSHIFT AND METHOD OF SHIFTING A CLAW-TYPE GEARSHIFT

Abstract

A claw-type gearshift has a sliding sleeve which is adapted to be axially displaced on a hub body and a clutch body of a speed change gear. The hub body has at least one thrust piece arranged thereon which includes a friction surface that cooperates with a mating friction surface on the clutch body, the at least one thrust piece being displaceable in the circumferential direction between a release position and two locking positions that are located on either side of the release position. A first locking structure on the at least one thrust piece cooperates with a second locking structure on the internal toothing of the sliding sleeve. The locking structures are configured such that in each of the locking positions, the locking structures rest against each other such that a further axial movement of the sliding sleeve is blocked. For shifting a gear, a difference in speed between the clutch body and the hub body is reduced.

Claims

1. A claw-type gearshift, comprising: a sliding sleeve which is adapted to be axially displaced on a hub body and includes an internal toothing having a multitude of sliding sleeve teeth, and a clutch body of a speed change gear, which includes an external toothing which has a multitude of clutch body teeth and is adapted to engage with the internal toothing of the sliding sleeve, wherein arranged at the hub body is at least one thrust piece which is coupled to the sliding sleeve and includes a friction surface that cooperates with a mating friction surface on the clutch body, wherein the at least one thrust piece is displaceable in relation to the hub body in the circumferential direction by a certain degree between a release position and two locking positions, the locking positions being located on either side of the release position in the circumferential direction, and wherein the at least one thrust piece includes a first locking structure which cooperates with a second locking structure on the internal toothing of the sliding sleeve, and the locking structures are configured such that in each of the locking positions, the locking structures rest against each other such that a further axial movement of the sliding sleeve is blocked.

2. The claw-type gearshift according to claim 1, wherein the first locking structure on the at least one thrust piece includes two axially limited and oppositely oriented recesses that are open in the circumferential direction, and the second locking structure on the internal toothing of the sliding sleeve is formed by radial tooth extensions, wherein in each of the locking positions a respective tooth extension engages in one of the recesses.

3. The claw-type gearshift according to claim 2, wherein the tooth extensions are provided to limit a shifting travel toward the clutch body.

4. The claw-type gearshift according to claim 1, wherein the at least one thrust piece is received in a retainer in the hub body, the retainer being made so large that it allows a displacement of the at least one thrust piece in the circumferential direction into both locking positions.

5. The claw-type gearshift according to claim 1, wherein the friction surface is formed on a lower surface of the at least one thrust piece and the mating friction surface is formed on a conical surface of the clutch body.

6. The claw-type gearshift according to claim 1, wherein the sliding sleeve teeth and the clutch body teeth are formed without engagement slopes.

7. The claw-type gearshift according to claim 1, wherein the claw-type gearshift is for a manual transmission.

8. A method of shifting a claw-type gearshift having a sliding sleeve which is adapted to be axially displaced on a hub body and a clutch body of a speed change gear, which is adapted to move into engagement with the sliding sleeve, wherein arranged on the hub body is at least one thrust piece which is adapted to be deflected axially and in the circumferential direction and which includes a friction surface adapted to come into contact with a mating friction surface on the clutch body, comprising: reducing a difference in speed between the clutch body and the hub body; applying a shifting force and deflecting the sliding sleeve in the axial direction toward the speed change gear to be shifted, causing the at least one thrust piece to be deflected axially and the friction surface of the at least one thrust piece to come into contact with the mating friction surface of the clutch body; displacing the at least one thrust piece in the circumferential direction to one of the locking positions by the frictional connection with the clutch body, wherein a further axial movement of the sliding sleeve is prevented by engagement of the first locking structure on the at least one thrust piece with the second locking structure on the sliding sleeve; returning the at least one thrust piece to the release position in the circumferential direction by the frictional connection when a change in direction of the relative rotational speed of the clutch body and the hub body takes place; and engaging the internal toothing of the sliding sleeve with the external toothing of the clutch body.

9. The method according to claim 8, wherein the at least one thrust piece blocks an axial further movement of the sliding sleeve irrespective of the acting shift force, and a relative rotation between the hub body and the clutch body, which allows the internal toothing of the sliding sleeve to engage in the external toothing of the clutch body, is achieved by a speed difference between the sliding sleeve and the clutch body that builds up after the rotational speed crossing.

10. The method according to claim 8, wherein a locking block of the at least one thrust piece is displaced radially inwards when, in the release position, the sliding sleeve is engaged in the clutch body.

11. The method according to claim 8, wherein the adaption of the speeds of the hub body and the clutch body is effected by a device separate from the at least one thrust piece.

12. The method according to claim 8, wherein the internal toothing of the sliding sleeve has a multitude of sliding sleeve teeth, and the external toothing of the clutch body has a multitude of clutch body teeth, wherein arranged at the hub body is at least one thrust piece which is coupled to the sliding sleeve and includes a friction surface that cooperates with a mating friction surface on the clutch body, wherein the at least one thrust piece is displaceable in relation to the hub body in the circumferential direction by a certain degree between a release position and two locking positions, the locking positions being located on either side of the release position in the circumferential direction, and wherein the at least one thrust piece includes a first locking structure which cooperates with a second locking structure on the internal toothing of the sliding sleeve, and the locking structures are configured such that in each of the locking positions, the locking structures rest against each other such that a further axial movement of the sliding sleeve is blocked.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0028] FIG. 1 shows a schematic exploded view of a claw-type gearshift according to the disclosure for carrying out a method according to the disclosure;

[0029] FIG. 2 shows a schematic partly sectional view of the claw-type gearshift of FIG. 1;

[0030] FIGS. 3 and 4 show schematic perspective views of the locking structures on the thrust piece and on the sliding sleeve;

[0031] FIGS. 5 and 6 show schematic views of the claw-type gearshift from FIG. 1 in a neutral position, the thrust piece being in its release position;

[0032] FIGS. 7 and 8 show schematic views of the claw-type gearshift from FIG. 1 in a locked position, with the thrust piece in one of its locking positions; and

[0033] FIGS. 9 and 10 show schematic views of the claw-type gearshift from FIG. 1 in a docking position, in which the thrust piece is in the release position and the sliding sleeve is in engagement with the clutch body.

DETAILED DESCRIPTION

[0034] For the sake of clarity, where components are shown more than once in the drawings, not all of them are provided with reference numbers.

[0035] The claw-type gearshift 10 illustrated in the figures, which is designed here for a manual transmission of a motor vehicle, serves to optionally connect a rotatable shaft to a speed change gear (not shown) for joint rotation therewith. The shaft carries a hub body 12, which is connected to said shaft for joint rotation therewith, while a clutch body 14 is permanently attached to the speed change gear for joint rotation therewith.

[0036] The hub body 12 includes an external toothing 16 that is permanently in engagement with an internal toothing 18 of a sliding sleeve 20 that surrounds the hub body 12 in the circumferential direction U.

[0037] The sliding sleeve 20 is displaceable in the axial direction A by a certain degree to either side of the hub body 12, with the toothings 16, 18 remaining in engagement with each other at all times. The sliding sleeve 20 is axially displaceable so far that the internal toothing 18 comes to engage with an external toothing 22 of the clutch body 14.

[0038] As is illustrated in FIG. 1, generally two speed change gears, each with a clutch body 14, are arranged on either side of the hub body 12 so that two gears can be shifted by the axial movement of the sliding sleeve 20.

[0039] In a circumferential surface of the hub body 12, a plurality of thrust pieces 23, in this case three, are arranged so as to be evenly distributed over the circumference, which are each accommodated in a radial retainer 24 and which are movable to a certain degree in both directions both in the axial direction A and in the circumferential direction U.

[0040] Accommodated in each of the thrust pieces 23 is a so-called locking block 26, which can be pressed into the thrust piece 23 in the radial direction r against a spring tension. With respect to the movement in the axial direction A, the thrust pieces 23 cooperate with the sliding sleeve 20 in a known manner. In a neutral position, the locking blocks 26 each engage in a latching groove 28 on the inside of the sliding sleeve 20, so that the thrust pieces 23 are deflected axially when the sliding sleeve 20 is displaced (see FIGS. 7 and 8). When the internal toothing 18 of the sliding sleeve 20 engages the external toothing 22 of the clutch body 14, the locking blocks 26 are pressed into the respective thrust piece 23 so that the sliding sleeve 20 can slide thereover (see FIGS. 9 and 10).

[0041] In this example, all three thrust pieces 23 are of identical structure.

[0042] On the surface that fits into the external toothing 16 of the hub body 12, each of the thrust pieces 23 has a first locking structure 30 that cooperates with a second locking structure 32 on the internal toothing 18 of the sliding sleeve 20 to block an axial movement of the sliding sleeve 20 in the locked position of the claw clutch 10.

[0043] The first locking structure 30 is formed here by two opposing recesses 34 which are open in the circumferential direction U and are each bounded axially by a web 38. The sides of the webs 38 that face the recess 34 extend in the circumferential direction U.

[0044] The second locking structure 32 here consists of a respective tooth extension 39 on each of the sliding sleeve teeth 36 that are adjacent to the tooth having the latching groove 28 (see FIG. 4). Each tooth extension 39 projects radially beyond the rest of the sliding sleeve tooth 36. The axial length of the recesses 34 is coordinated with the axial length of the tooth extensions 39 such that the latter can fully lie in the recess 34 in the axial direction A.

[0045] In the circumferential direction U, the recesses 34 are each spaced apart from the next sliding sleeve tooth 36 by half a tooth spacing of the sliding sleeve toothing 18 in the neutral position of the claw clutch 10.

[0046] The tooth extensions 39 perform a dual function here, in that they also serve as a stop in a known manner to specify the depth of engagement between the sliding sleeve toothing 18 and the clutch body toothing 22 and thus to limit the shifting travel of the sliding sleeve 20.

[0047] At its axial edges, each thrust piece 23 includes a friction surface 42, which here is arranged on the lower side of the thrust piece 23.

[0048] The friction surfaces 42 are part of a conical surface which is adapted in shape to a conical surface on the respective clutch body 14, on which a mating friction surface 44 is formed (see, for example, FIGS. 1 and 2).

[0049] The retainer 24 in which the thrust piece 23 is received in the hub body 12 is configured such that the respective thrust piece 23 has sufficient clearance in the axial direction A that it can be displaced to the clutch bodies 14 so far in both directions until the friction surface 42 moves into frictional contact with the mating friction surface 44.

[0050] In the circumferential direction U, the clearance for movement of the thrust piece 23 in the retainer 24 between two side surfaces 46, which delimit the retainer 24 in the circumferential direction U, is larger and selected such that the thrust piece 23 can move from a central neutral position in either direction by an angular distance of α/2 between two sliding sleeve teeth 36. This distance is dimensioned such that the tooth extensions 39 can engage in and completely leave the recesses 34 again (see, for example, FIGS. 6, 8 and 10).

[0051] In this way, the thrust pieces 23 can move from a central release position, in which none of the tooth extensions 39 engages in a recess 34, to two opposite locking positions, in which a respective one of the tooth extensions 39 is located in one of the recesses 34.

[0052] The toothings 18, 22 of the sliding sleeve 20 and the clutch body 14 include dimensions that are matched to each other so that the sliding sleeve teeth 36 can engage between the clutch body teeth 40.

[0053] Both the sliding sleeve teeth 36 and the clutch body teeth 40 are formed completely without engagement slopes.

[0054] Referring to FIGS. 5 to 10, the operation of the claw-type gearshift 10 will now be described.

[0055] FIGS. 5 and 6 show the claw-type gearshift 10 in a neutral position.

[0056] The sliding sleeve 20 inclusive of the thrust pieces 23 and the clutch body 14 are axially spaced apart from each other and do not touch. The sliding sleeve 20 is positioned centrally between the two clutch bodies 14. The sliding sleeve teeth 36 are located in the gaps of the toothing 22 in the circumferential direction U. The tooth extensions 39 are located outside the recesses 34.

[0057] For shifting a gear, the speeds of the hub body 12 and the clutch body 14, which is to be coupled to the sliding sleeve 20, are first largely equalized by a device 48 for speed adaption (shown schematically in FIG. 2). The device 48 may, for example, be coupled to an electric motor of the vehicle and does not comprise the thrust pieces 23.

[0058] Only when this substantial speed adaption has been effected is an axial shifting force F applied, to the right in the Figures. The sliding sleeve 20 is displaced a short distance in the axial direction A, deflecting the locking blocks 26 in the process, which in turn entrain the thrust pieces 23 in the axial direction A until the friction surface 42 on the thrust piece 23 moves into frictional contact with the mating friction surface 44 on the clutch body 14 of the speed change gear to be shifted.

[0059] Since the hub body 12 and the clutch body 14 rotate at different speeds, the thrust pieces 23 are entrained in the circumferential direction U by the frictional forces between the friction surface 42 and the mating friction surface 44. In the process, the thrust pieces 23 flip from the central release position into one of the two locking positions. The rotation of the thrust pieces 23 is limited by the side surfaces 46 of the retainer 24 in the hub body 12.

[0060] The relative movement of the thrust pieces 23 in relation to the internal toothing 18 of the sliding sleeve 20 causes the tooth extension 39 of one of the sliding sleeve teeth 36 to move into the recess 34 on both sides of the sliding sleeve tooth 36 which includes the latching groove 28.

[0061] The sliding sleeve 20 is therefore prevented from further axial movement by the webs 38 axially bounding the recess 34.

[0062] The claw-type gearshift 10 is now in its locked position, in which the sliding sleeve 20 cannot move further toward the clutch body 14 in the axial direction A.

[0063] It is not intended that the sliding sleeve 20 can actively rotate the thrust pieces 23 back to their release position. The sides of the webs 38 facing the recess 34 are oriented such that the sliding sleeve teeth 36 cannot generate a sufficient force component in the circumferential direction U to result in a rotation of the thrust piece 23. When the thrust pieces 23 are in one of the locking positions, the sliding sleeve 20 is prevented from moving axially further to the associated clutch body 14, irrespective of the axial shifting force F applied.

[0064] The thrust pieces 23 here do not perform the task of speed adaption between the hub body 12 and the clutch body 14, which is effected practically exclusively by the device 48.

[0065] The device 48 further acts to adapt the speeds of the hub body 12 and the clutch body 14. In this process, after a short period of time, a rotational speed crossing will occur, that is, a change in direction of the relative rotational speed of the hub body 12 and the clutch body 14.

[0066] This change in the direction of rotation causes the thrust pieces 23 to flip back to the release position in the circumferential direction U, resulting in the docking position shown in FIGS. 9 and 10. The tooth extensions 39 are located next to the recesses 34 in the circumferential direction U.

[0067] The sliding sleeve 20 can now be moved further in the axial direction A, with its internal toothing 18 engaging with the external toothing 22 of the clutch body 14.

[0068] The rotational speed crossing is also always associated with the build-up of a new, small difference in speed between the hub body 12 and the clutch body 14. This ensures that the sliding sleeve 20 and the clutch body 14 automatically move to a position in which the sliding sleeve teeth 36 meet the gaps in the external toothing 22 of the clutch body 14, even if there should be a tooth-on-tooth position at the first contact.

[0069] The thrust pieces 23 are not involved in this process.

[0070] While having a compact axial type of construction, the claw-type gearshift 10 allows a low-noise and low-wear shifting, since the movement of the sliding sleeve 20 is blocked as a result of the circumferential displacement of the thrust pieces 23 until a rotational speed crossing has taken place. However, the thrust pieces 23 are not made use of for speed adaption here.