WO2018092521A1

WO2018092521A1 - Shift guide structure

Info

Publication number: WO2018092521A1
Application number: PCT/JP2017/038220
Authority: WO
Inventors: 祐樹羽原; 直紀佐治; 貴広吉田
Original assignee: アイシン・エーアイ株式会社
Priority date: 2016-11-17
Filing date: 2017-10-23
Publication date: 2018-05-24

Abstract

A shift guide structure that comprises, for example: a guide pin that is provided on a case or on a shift-and-select shaft that is supported by the case so as to be capable of moving in the axial and circumferential directions; and a guide plate that is provided on the other of the case and the shift-and-select shaft and is provided with a pathway that guides the guide pin between a plurality of positions that correspond to gear steps. The shift guide structure is configured such that a first movement range that is the movement range of the guide pin with respect to the pathway of the guide plate is entirely within a second movement range that, as established by a selection mechanism that includes an inner lever, an interlock, and a shift head, is the movement range of the guide pin with respect to the location in which the guide plate has been provided.

Description

Shift guide structure

The present invention relates to a shift guide structure.

Conventionally, in a stepped transmission such as manual transmission (MT) or automated manual transmission (AMT), a guide pin provided on one of the shift and select shaft and the case and a guide pin provided on the other correspond to the gear stage There is known a shift guide structure provided with a guide plate provided with a path for guiding between a plurality of positions (Patent Document 1).

Patent No. 4587066

In the above-described conventional configuration, the movement range of the guide pin is partially limited by the selection mechanism including the inner lever, the interlock, and the shift head. As an example, in a configuration in which the movement range of the guide pin determined by the selection mechanism is partially narrower than the movement range of the guide pin determined by the path of the guide plate, A guide pin that has moved away from the edge may move along the edge of the path. In such a case, there is a possibility that the guide pin may follow a moving path so as to bend, and the smooth movement of the guide pin and thus the shift lever may be hindered.

Therefore, one of the problems of the present invention is to obtain, for example, a shift guide structure in which the guide pin and hence the shift lever can move more smoothly.

The shift guide structure of the present invention includes, for example, a shift and select shaft axially and circumferentially movably supported by the case, a guide pin provided on one of the cases, the shift and select shaft, and the case A guide plate provided on the other side and provided with a path for guiding the guide pin between the plurality of positions corresponding to the gear, and the first direction and the first direction according to the movement of the shift and select shaft An inner lever selectively movable between a second direction different from the direction and a selection mechanism for switching the gear according to the movement of the inner lever, in the path of the guide plate The entire area of the first movement range in which the guide pin can move is determined by the selection mechanism. Configured to be included within a second range of movement possible.

According to the present invention, for example, since the second movement range by the selection mechanism covers the entire area of the first movement range by the shift guide structure, the guide pin can move from the second movement range to the first movement range There is no bending of the moving path due to the transition to Therefore, the guide pin and hence the shift lever can be moved more smoothly.

Further, in the shift guide structure, the guide plate is provided separately from the base wall provided with the opening forming the path, the mounting wall protruding from the base wall, and the mounting wall, and the base wall is provided from the base wall And a protruding reinforcing wall. According to such a configuration, for example, the rigidity and the strength of the guide plate are enhanced by the reinforcing wall, so that the deformation of the guide plate due to the abutment of the guide pin is suppressed.

In the shift guide structure, the reinforcing wall is one of two, and the two reinforcing walls are parallel to each other and have different axial lengths of the shift and select shaft. According to such a configuration, for example, the guide plate can be reinforced more efficiently.

Further, in the shift guide structure, the width along the shift direction of the insertion portion of the guide pin in the path is larger than the width along the selection direction of the insertion portion. According to such a configuration, for example, the guide plate can be configured to be smaller in the select direction, and deformation of the guide pin due to contact with the guide plate in the shift direction can be suppressed.

Further, in the shift guide structure, the guide plate includes an opening that constitutes the path, and a surface that faces the opening and that restricts the movement of the inner lever in the first direction by contact with the guide pin. And was provided. According to such a configuration, for example, the movement of the inner lever in the first direction can be restricted by the guide plate and the guide pin. Therefore, according to the shift guide structure, for example, the number of parts can be reduced as compared with the configuration in which the movement of the inner lever in the first direction is restricted by the inner lever, interlock and case, and the guide pin Variations in the movement range of the

Further, in the shift guide structure, the mounting wall protrudes from the base wall in a direction away from the shift and select shaft. According to such a configuration, for example, since the guide plate can be brought close to the shift and select shaft, the shift guide structure can be miniaturized.

FIG. 1 is an exemplary and schematic perspective view of the shift guide structure of the embodiment. FIG. 2 is an exemplary and schematic front view seen from the axial direction of the shift guide structure of the embodiment. FIG. 3 is an exemplary and schematic front view of an opening as a path provided in the guide plate of the shift guide structure of the embodiment. FIG. 4 is an exemplary and schematic perspective view of a guide pin included in the shift guide structure of the embodiment. FIG. 5 is an exemplary and schematic front view of a guide pin included in the shift guide structure of the embodiment as viewed from the axial direction of the guide pin. FIG. 6 is an exemplary and schematic plan view of the selection mechanism of the embodiment. FIG. 7 is an exemplary and schematic front view of the selection mechanism of the embodiment. FIG. 8 is an exemplary and schematic plan view of the selection mechanism of the embodiment, showing that a fourth gear is selected. FIG. 9 is an exemplary and schematic plan view of the selection mechanism of the embodiment, showing a state in the middle of transition from the fourth speed to the fifth speed. FIG. 10 is an exemplary and schematic plan view of the selection mechanism of the embodiment, showing that the fifth gear is selected. FIG. 11 is an exemplary and schematic view showing a movement locus of the guide pin in the guide plate of the embodiment and a movement locus in a portion provided with the guide plate of the guide pin determined by the selection mechanism.

In the following, exemplary embodiments of the present invention are disclosed. The configurations of the embodiments shown below, and the operations, results, and effects provided by the configurations are examples. The present invention can also be realized with configurations other than the configurations disclosed in the following embodiments. Further, according to the present invention, it is possible to obtain at least one of various effects and derivative effects obtained by the configuration.

(Embodiment)
FIG. 1 is a perspective view of a shift guide structure 1 of a stepped transmission, and FIG. 2 is a front view of the shift guide structure 1 seen from the axial direction. In the following, the axial direction of the rotation center Ax of the shift and select shaft 10 is simply referred to as the axial direction, the circumferential direction of the rotation center Ax is simply referred to as the circumferential direction, and the radial direction of the rotation center Ax is simply the diameter It is called a direction.

As shown in FIG. 1, the shift guide structure 1 includes a shift and select shaft 10, a guide pin 20, and a guide plate 30.

The shift and select shaft 10 is supported by the case 40 (FIG. 2) so as to be movable in the axial direction (Se direction) and in the circumferential direction (C direction). The shift and select shaft 10 operates in conjunction with the operation of a shift lever (not shown). Various known mechanisms and configurations can be applied as a transmission mechanism that transmits the operation of the shift lever to the shift and select shaft 10 to move the shift and select shaft 10.

As shown in FIGS. 1 and 2, in the present embodiment, the guide pin 20 is fixed to the shift and select shaft 10 and the guide plate 30 is fixed to the case 40. The shift guide structure 1 is configured such that the guide pin 20 and the guide plate 30 move relative to each other in accordance with axial and circumferential movement of the shift and select shaft 10. Therefore, although not shown, the shift guide structure may be a structure in which the guide pin 20 is fixed to the case 40 and the guide plate 30 is fixed to the shift and select shaft 10.

The guide pins 20 project radially outward from the outer peripheral surface of the shift and select shaft 10. The guide pin 20 is fixed to the shift and select shaft 10. Therefore, the guide pin 20 moves in the axial direction and the circumferential direction in conjunction with the movement of the shift and select shaft 10 in the axial direction and the circumferential direction.

As shown in FIG. 2, the guide plate 30 is fixed to the case 40. The guide plate 30 has a flat base wall 31. The base wall 31 extends along the direction orthogonal to the radial direction and along the axial direction. The base wall 31 has

surfaces

31a and 31b. The surface 31 a faces the shift and select shaft 10. The surface 31 b is provided on the opposite side of the surface 31 a.

As shown in FIG. 1, the base wall 31 is provided with an opening 32 that constitutes a path along which the guide pin 20 moves. The opening 32 penetrates the

surfaces

31a and 31b. The guide pin 20 is inserted into the opening 32.

FIG. 3 is a front view of the opening 32. FIG. The opening 32 includes a slit forming the select path 32 a and a slit forming the shift path 32 b. The select path 32a guides the guide pin 20 in the select direction (Se direction). The shift path 32 b guides the guide pin 20 in the shift direction (Sh direction). A plurality of shift paths 32b parallel to and spaced from each other are orthogonal to one select path 32a extending in the select direction. One select path 32a extends so as to be bridged between central portions of the plurality of shift paths 32b. The two end portions of the shift path 32b are gates G1 to G6 and GR of each shift speed.

Further, as shown in FIG. 3, the guide plate 30 has an inner circumferential surface 31 c surrounding the opening 32. The inner circumferential surface 31 c has a plurality of surfaces 31 d to 31 i facing the opening 32. A pair of surfaces 31 d is provided for each shift path 32 b. The pair of surfaces 31 d are provided to be spaced apart from each other in the select direction (Se direction), and extend in the shift direction (Sh direction). Each surface 31 d faces the selection direction (Se direction) as the first direction. The surface 31 d is a plane. A shift path 32b is provided between the pair of surfaces 31d. The ends on the gates G1 to G6 and GR side of the pair of surfaces 31d are connected by a surface 31e. The surface 31e is a curved surface. The

surfaces

31 f and 31 g are both end surfaces in the select direction (Se direction) on the inner peripheral surface 31 c. The surface 31f and the surface 31g are spaced apart from each other in the select direction (Se direction) and extend in the shift direction (Sh direction). The surface 31 f and the surface 31 g each include a surface 31 d. The surface 31 f and the surface 31 g face in the select direction (Se direction). A select path 32a is provided between the surface 31f and the surface 31g. The surface 31 h is connected to the end of the surface 31 f opposite to the gate GR, and extends in the select direction (Se direction). The surface 31i is connected to the surface 31d, and is inclined with respect to the selection direction (Se direction) and the shift direction (Sh direction). The surface 31i is also referred to as an oblique portion.

The

surfaces

31 d, 31 f, 31 g limit the movement of the inner lever 50 (FIG. 6) in the select direction (Se direction) by contact with the guide pin 20.

In the present embodiment, the guide pin 20 moves in the selection direction (Se direction) in conjunction with the axial movement of the shift and select shaft 10. Further, the guide pin 20 moves in the shift direction (Sh direction) in conjunction with the movement of the shift and select shaft 10 in the circumferential direction (C direction). However, the shift and select shaft 10 and the shift guide structure 1 may be configured such that the axial direction corresponds to the shift direction and the circumferential direction corresponds to the select direction.

Selection mechanism 100 (see FIGS. 6 and 7) selectively moves

fork shafts

712, 734, 756 and 7R corresponding to the axial and circumferential positions (posture) of shift and select shaft 10, thereby The transmission gear (gear) is switched. In the position and posture of the shift and select shaft 10 corresponding to the state where the guide pin 20 is positioned at the gate G1, the transmission is shifted through the first gear (gear set). Similarly, in the position and posture of shift and select shaft 10 corresponding to the state where guide pin 20 is positioned at gates G2 to G6, the transmission has second to sixth speeds corresponding to gates G2 to G6, respectively. It will be in the state which changes gears via a gear stage. Further, in the position and posture of the shift and select shaft 10 corresponding to the state where the guide pin 20 is positioned at the gate GR, the transmission is shifted through the reverse gear.

As shown in FIGS. 1 and 2, in addition to the base wall 31, the guide plate 30 has two reinforcing

walls

33 and 34 and a mounting wall 35. Reinforcing

walls

33 and 34 protrude from the end of base wall 31 in the shift direction (Sh direction) at a substantially constant height in the direction intersecting with base wall 31 and extend along the select direction (Se direction). ing. The two reinforcing

walls

33, 34 are parallel to one another. The reinforcing

walls

33 and 34 can increase the rigidity of the guide plate 30. The reinforcing

walls

33 and 34 are provided separately from the mounting wall 35 for attachment to the case 40. The mounting wall 35 protrudes from the base wall 31 in a direction away from the shift and select shaft 10. Specifically, the mounting wall 35 projects from the end of the surface 31 b of the base wall 31 in the selection direction (Se direction) in a direction away from the shift and select shaft 10. The mounting wall 35 is provided with an opening 35a through which a fixing tool (not shown) such as a bolt passes. The mounting wall 35 also contributes to the improvement of the rigidity of the guide plate 30. Thus, with such a configuration, the rigidity of the guide plate 30 can be further improved by the reinforcing

walls

33 and 34 and the mounting wall 35. In the embodiment in which the guide plate 30 is fixed to the shift and select shaft 10, the mounting wall 35 is attached to the shift and select shaft 10.

Also, as shown in FIG. 1, the lengths of the two reinforcing

walls

33, 34 are different. The two reinforcing

walls

33 and 34 and the peripheral parts are compared with the configuration in which the positions and the lengths of the two reinforcing

walls

33 and 34 are the same because the position and the length of the two reinforcing

walls

33 and 34 are different. Has the advantage of being easy to avoid interference with That is, according to such a configuration, there is an advantage that the degree of freedom of the layout of the peripheral parts and the guide plate 30 is increased. That is, the guide plate 30 can be reinforced more efficiently by such two reinforcing

walls

33 and 34. The reinforcing wall 33 protrudes from the side adjacent to the four gates G1, G3, G5 and GR, and the reinforcing wall 34 protrudes from the side adjacent to the three gates G2, G4 and G6. Thus, the base wall 31 can be reinforced more effectively by making the reinforcing wall 33 facing more gates G1, G3, G5, GR longer.

Further, as shown in FIG. 2, the reinforcing wall 33, the base wall 31 and the reinforcing wall 34 surround the outer periphery of the shift and select shaft 10 in a U-shape. In other words, the reinforcing

walls

33 and 34 project from the base wall 31 in the direction approaching the shift and select shaft 10. With such a configuration, the configuration including the shift and select shaft 10 and the shift guide structure 1 is prevented from being enlarged in the radial direction.

In the configuration as described above, the guide pin 20 moves between the plurality of gates G1 to G6, GR in the opening 32 in accordance with the shift operation by the driver or the actuator. When the guide pin 20 moves in the opening 32 (path), the outer periphery of the guide pin 20 contacts the edge of the base wall 31 facing the opening 32, that is, the inner peripheral surface 31c.

In this case, it is not preferable that the guide pin 20 is deformed by the contact with the inner circumferential surface 31c. However, if the guide pin 20 is made thicker as a countermeasure, there is a possibility that it may contribute to the increase in size of the guide plate 30 and hence the shift guide structure 1.

Also, if there is a sudden change in shape, such as a protrusion or a corner, on the outer periphery of the guide pin 20, for example, the rapid change in shape abuts against the inner circumferential surface 31c facing the opening 32. The smooth movement of the guide pin 20 between G6 and GR may be hindered. Such inhibition of the smooth movement of the guide pin 20 is particularly effective when the guide pin 20 moves from the gate G4 to the gate G5 as shown in FIG. It is easy to occur when moving.

Therefore, the guide pin 20 is configured to be unlikely to cause the above-described inconvenience. 4 is a perspective view of the guide pin 20, FIG. 5 is a sectional view taken along the line VV of FIG. 4 of the guide pin 20, and more specifically, orthogonal to the longitudinal direction of the insertion portion 22, ie orthogonal to the radial direction. It is sectional drawing along.

As apparent from FIG. 4, the cross section of the insertion portion 22 shown in FIG. 5 is constant in a section of a predetermined length along the longitudinal direction of the guide pin 20 (the radial direction of the shift and select shaft 10). That is, the outer peripheral surface of the insertion portion 22 is a ruled surface having generatrix parallel to the longitudinal direction of the guide pin 20.

As shown in FIGS. 4 and 5, the guide pin 20 has a cylindrical portion 21 and an insertion portion 22. The cylindrical portion 21 includes a joint with the shift and select shaft 10. The insertion portion 22 includes the tip 20 a of the guide pin 20. The tip 20 a of the guide pin 20 is also the tip of the insertion portion 22. The insertion portion 22 is thinner than the cylindrical portion 21 and is inserted into the opening 32. The tip 20 a is accommodated in the opening 32. That is, the tip 20 a does not protrude from the opening 32.

Thus, according to the present embodiment, by making the cylindrical portion 21 thicker than the insertion portion 22, the rigidity and strength of the guide pin 20 can be further enhanced as compared with the case where the cylindrical portion 21 is not provided. Furthermore, since the insertion portion 22 is thinner than the cylindrical portion 21, the shift guide structure 1 can be configured more compactly than when the insertion portion 22 has the same thickness as the cylindrical portion 21. In the present embodiment, the insertion portion 22 is provided at the tip of the guide pin 20, but the insertion portion 22 may be provided at an intermediate position in the longitudinal direction of the guide pin 20.

Further, as shown in FIG. 5, the outer peripheral edge 22a of the cross section of the insertion portion 22 includes two parallel straight portions 22b and two projecting portions 22d connecting the end portions 22c of the two straight portions 22b. Including. As shown in FIG. 5, the distance between the two straight portions 22b, that is, the width Ws in the short direction of the outer peripheral edge 22a is smaller than the width W1 in the longitudinal direction of the outer peripheral edge 22a. Here, as is apparent from FIGS. 1 and 3, the insertion portion 22 is accommodated in the opening 32 in a posture that is long in the shift direction (Sh direction). That is, the width Ws in the short direction along the select direction (Se direction) of the insertion portion 22 is smaller than the width Wl in the longitudinal direction along the shift direction. The center line CL of the cross section of the insertion portion 22 is shown in FIG. The center line CL is parallel to the two straight line portions 22 b and located midway between the two straight line portions 22 b.

According to the present embodiment, the gap between the plurality of shift paths 32b can be narrowed in the guide plate 30 by the shape and attitude of the insertion portion 22 as described above, so that the shift guide structure 1 can be made more compact. Can. In addition, since the insertion portion 22 has a long cross section in the shift direction, when the insertion portion 22 moves to each of the gates G1 to G6, GR and strikes the inner peripheral surface 31c facing the opening 32, The rigidity and strength of the guide pin 20 with respect to the force input from the circumferential surface 31 c to the guide pin 20 in the shift direction can be further increased.

Further, as shown in FIG. 5, in the present embodiment, the protruding portion 22 d is a semicircle, and the radius R thereof is half the width Ws in the short direction. Accordingly, the outer peripheral edge 22a is generally oval. That is, the outer peripheral edge 22a has a parallel portion (two straight portions 22b) and two semicircles (protruding portions 22d) located at both ends of the parallel portion and having a diameter between the parallel portions. There is.

As described above, according to the present embodiment, the outer peripheral edge 22a of the cross section of the insertion portion 22 has an oval shape, so that there is an advantage that manufacturing and inspection can be performed more easily or more accurately.

In addition, as shown in FIG. 5, in the present embodiment, it can be said that the protruding portion 22 d includes one semicircular curved portion. Further, as is apparent from FIG. 5, the radius R of the protruding portion 22d, that is, the curvature radius of the curved portion, is smaller than the radius of the cylindrical portion 21 (1⁄2 of the outer diameter D).

Thus, according to the present embodiment, the radius R of the projecting portion 22 d (the radius of curvature of the curved portion) is smaller than the radius of the cylindrical portion 21, so the radius R of the projecting portion 22 d is the same as the radius of the cylindrical portion 21. In this case, the shape change at the end 22c between the straight portion 22b and the protruding portion 22d is more gradual than in the case where Therefore, the outer peripheral edge 22 a is less likely to be caught with the inner peripheral surface 31 c facing the opening 32. Thus, the guide pin 20 can move more smoothly in the opening 32.

Also, as shown in FIG. 5, the outer peripheral edge 22a is smooth as a whole. That is, the straight portion 22b and the protruding portion 22d are smoothly continuous, and the protruding portion 22d is smoothly continuous throughout the protruding portion 22d. Here, “smoothly continuous” means, for example, a function at each point x when the outer peripheral edge 22a is represented by a function y = f (x) of a variable x in the Sh direction and a variable y in the Se direction. We show that y = f (x) is continuous and the function y = f (x) is differentiable by x.

As described above, according to the present embodiment, the outer peripheral edge 22 a is smooth as a whole, so that the outer peripheral edge 22 a is unlikely to be caught with the inner peripheral surface 31 c facing the opening 32. Thus, the guide pin 20 can move more smoothly in the opening 32.

6 is a plan view of the selection mechanism 100, and FIG. 7 is a front view of the selection mechanism 100. As shown in FIG. As shown in FIGS. 6 and 7, the selection mechanism 100 has an inner lever 50, interlocks 61 and 62, and shift heads 812, 834, 856 and 8R. The selection mechanism 100 selectively operates the

fork shafts

712, 734, 756, and 7R according to the operation of the inner lever 50 to switch the gear of the transmission via a shift fork or the like (not shown).

The inner lever 50 is shown in FIG. 7 according to the select direction (Se direction) as the first direction and the circumferential movement (rotation) of the shift and select shaft 10 in conjunction with the shift and select shaft 10. It moves in the shift guide direction (Shg direction) as the second direction. As shown in FIG. 7, the inner lever 50 projects, for example, radially outward from the shift and select shaft 10.

The

interlocks

61 and 62 follow the inner lever 50 and move in the select direction. However, the interlock 61 does not move in the shift direction.

The shift heads 812, 834, 856, 8R move in the shift direction together with the

corresponding fork shafts

712, 734, 756, 7R in accordance with the movement of the inner lever 50 in the shift guide direction (Shg direction). However, the shift heads 812 834 856 8R do not move in the select direction.

In this embodiment, as an example, each of the shift heads 812, 834, 856, 8R has the arms 8a on both sides in the shift direction, and the inner lever 50 and the

interlocks

61, 62 are provided in the recess 8b between the arms 8a. And is accommodated so as to be movable in the select direction.

In such a configuration, the inner lever 50 moves in the select direction according to the axial movement of the shift and select shaft 10, and between the arms 8a of the shift heads 812, 834, 856, 8R (recessed portion Located at 8b).

Further, in response to the circumferential movement (rotation) of the shift and select shaft 10, the inner lever 50 moves in the shift guide direction (Shg direction), thereby being adjacent to the inner lever 50, that is, in the recess 8b. The shift head accommodating the inner lever 50 moves in the shift direction.

8 to 10 are operation diagrams of the selection mechanism 100 according to the embodiment, in which the gear is switched from the fourth gear to the fifth gear. In FIG. 8, the shift head 834 is positioned at the position where the fourth gear is operated (the lower position in FIG. 8) by the inner lever 50 positioned at the position Pi4. As shown in FIG. 9, when the inner lever 50 is positioned at the position Pii between the two shift heads 834 and 856, the

interlocks

61 and 62 restrict the movement of the shift heads 834 and 856 in the shift direction. Ru. Further, in FIG. 10, the shift head 856 is positioned at the position where the fifth gear is operated (upper position in FIG. 10) by the inner lever 50 positioned at the position Pi5.

FIG. 11 shows a second movement range Ts in which the guide pin 20 determined by the selection mechanism 100 can move and a first movement range Tg in which the guide pin 20 determined by the shift guide structure 1 can move. It is a schematic diagram shown. The first movement range Tg and the second movement range Ts are, for example, ranges in which the axial center (center) of the guide pin 20 can move in the opening 32 of the guide plate 30. That is, the second movement range Ts is determined based on the gap between each component of the selection mechanism 100, the movement range of each component, the dimensional tolerance of each component, and the like. The first movement range Tg is determined by the guide pin 20 and the opening 32.

As apparent from FIG. 11, in the present embodiment, the second movement range Ts includes the first movement range Tg. That is, in the present embodiment, the movement range of the guide pin 20 is determined by the inner circumferential surface 31 c facing the opening 32. Thus, for example, the guide pin 20 can move along the inner circumferential surface 31c.

Here, assuming that there is a region where the second movement range Ts is positioned inside the first movement range Tg (hereinafter referred to as a reverse region), the guide pin 20 is in the inside in the reverse region. It does not contact the circumferential surface 31c. Therefore, the guide pin 20 moving away from the inner circumferential surface 31c and moving in the reverse rotation area sometimes moves along the inner circumferential surface 31c. In this case, the movement such that the guide pin 20 is bent The path will be followed, and the smooth movement of the guide pin 20 and hence the shift lever may be impeded.

In this respect, according to the present embodiment, since the second movement range Ts includes the first movement range Tg, bending of the movement path does not occur as described above. Therefore, the guide pin 20 and thus the shift lever can be moved more smoothly.

Further, as described above, according to the present embodiment, the reinforcing

walls

33 and 34 can suppress the deformation of the guide plate 30 due to the contact with the guide pin 20. Further, according to the present embodiment, the guide plate 30 can be reinforced more efficiently by the two reinforcing

walls

33 and 34 having different lengths.

Also, as described above, according to the present embodiment, the width Wl along the shift direction of the insertion portion 22 of the guide pin 20 is larger than the width Ws along the select direction. Therefore, the guide plate 30 can be configured to be smaller in the select direction, and deformation of the guide pin 20 due to the guide plate 30 in the shift direction can be suppressed.

As described above, in the present embodiment, the guide plate 30 faces the opening 32 and is a surface that limits the movement of the inner lever 50 in the selection direction (Se direction, first direction) by contact with the guide pin 20. 31d, 31f, 31g are provided. According to such a configuration, for example, the movement of the inner lever 50 in the selection direction (Se direction) can be restricted by the guide plate 30 and the guide pin 20. Therefore, according to the present embodiment, for example, the number of parts can be reduced compared to the configuration in which the movement of the inner lever 50 in the selection direction (Se direction) is limited by the inner lever, interlock and case. And the dispersion | variation in the movement range of the guide pin 20 can be reduced.

Further, in the present embodiment, the mounting wall 35 protrudes from the base wall 31 in a direction away from the shift and select shaft 10. According to the present embodiment, for example, since the guide plate 30 can be brought close to the shift and select shaft 10, the shift guide structure 1 can be miniaturized.

Further, in the present embodiment, the guide pin 20 has the distal end portion 20a included in the insertion portion 22, and the guide plate 30 is provided with the opening 32 in which the distal end portion 20a is accommodated. According to such a configuration, for example, since the tip 20a of the guide pin 20 does not protrude from the opening 32, the axial length of the guide pin 20 is longer than the configuration in which the tip of the guide pin protrudes from the opening Can be shortened. Therefore, since the load input to the guide pin 20 can be reduced, the durability of the guide pin 20 can be improved.

As mentioned above, although the embodiment of the present invention was illustrated, the above-mentioned embodiment is an example, and limiting the scope of the invention is not intended. The embodiment can be implemented in various other forms, and various omissions, substitutions, combinations, and changes can be made without departing from the scope of the invention. Further, specifications (structure, type, direction, shape, size, length, width, height, number, arrangement, position, etc.) of each configuration and shape can be appropriately changed and implemented. For example, the configuration of the selection mechanism is not limited to those disclosed in the above embodiments.

DESCRIPTION OF SYMBOLS 1 ... Shift guide structure, 10 ... Shift and selection shaft, 20 ... Guide pin, 22 ... Insertion part, 30 ... Guide plate, 31 ... Base wall, 31d, 31f, 31g ... Surface, 32 ... Opening part (path | route), 35 ... mounting wall, 40 ... case, 50 ... inner lever, 61, 62 ... interlock, 100 ... selection mechanism, 812, 834, 856, 8 R ... shift head, Tg ... first movement range, Ts ... second movement range.

Claims

A shift and select shaft axially and circumferentially movably supported by the case, and a guide pin provided to one of the cases;
A guide plate provided on the other of the shift and select shaft and the case and provided with a path for guiding the guide pin between a plurality of positions corresponding to gear stages;
An inner lever selectively movable between a first direction and a second direction different from the first direction according to the movement of the shift and select shaft;
A selection mechanism that switches the gear in accordance with the movement of the inner lever;
Equipped with
The entire range of the first movement range in which the guide pin can move in the path of the guide plate is configured to be included in the second movement range in which the guide pin can move according to the selection mechanism. Transmission shift guide structure.
The guide plate is
A base wall provided with an opening that constitutes the path;
A mounting wall projecting from the base wall;
A reinforcing wall provided separately from the mounting wall and protruding from the base wall;
The shift guide structure according to claim 1, comprising:
The reinforcing wall is one of two,
3. The shift guide structure according to claim 2, wherein the two reinforcing walls are parallel to each other and have different axial lengths of the shift and select shaft.
The shift guide structure according to claim 2 or 3, wherein the width along the shift direction of the insertion portion of the guide pin in the path is larger than the width along the select direction of the insertion portion.
The guide plate is provided with an opening that constitutes the path, and a surface that faces the opening and that restricts the movement of the inner lever in the first direction by contact with the guide pin. The shift guide structure according to any one of Items 1 to 4.
The shift guide structure according to claim 2, wherein the mounting wall protrudes from the base wall in a direction away from the shift and select shaft.