JPWO2014208214A1 - Shift mechanism of multi-disc transmission - Google Patents

Abstract

The shift mechanism (140) operates the select lever (141) for selecting the operation mode, the reverse idle gear (113a), and the select lever (141) to change the operation mode to the reverse mode and the parking mode. When the position of the reverse idle gear (113a) is set to the first gear position that meshes with the input-side reverse gear (113i) and the output-side reverse gear (113o) and the neutral mode and the drive mode are set, the reverse idle gear (113a) And a gear positioning mechanism for setting the position of the second gear position not to mesh with the input-side reverse gear (113i) and the output-side reverse gear (113o).

Description

  The present invention relates to a shift mechanism for a multi-disc transmission.

  In JP2010-53995A, a primary disk provided on the input shaft and a secondary disk provided on the output shaft are partially overlapped to provide a disk overlap area, and both disks are sandwiched between a pair of pressing rollers in this area. A multi-disc transmission that transmits the rotation of an input shaft to an output shaft by bringing them into contact is disclosed.

  In a multi-disc transmission, a shift is realized by changing a position where a pair of pressing rollers sandwich both discs. That is, if the position between the two disks is close to the input shaft, the gear ratio changes to the low side (large gear ratio side), and if close to the output shaft, the gear ratio changes to the high side (low gear ratio side). .

  In a multi-disc transmission, an input shaft is configured by meshing an input-side reverse gear provided on an input shaft and an output-side reverse gear provided on an output shaft with a reverse idle gear provided on a counter shaft so as to be free to rotate. The reverse state in which the rotation of the disk is reversed and transmitted to the output shaft can be realized. From this state, when both disks are sandwiched between the pressing rollers, the path for transmitting the rotation is the path through the gear train and the path through the disk. Since the rotation direction of each path is opposite, a parking state where the output gear does not rotate can be realized.

  Thus, in order to prevent the gear from meshing in the neutral mode or drive mode while allowing the reverse idle gear to mesh with the reverse gear in the two operation modes, the reverse gear is set to the position corresponding to the position of the select lever. Connect the manual lever of the position sensor and the striking rod so that the gear moves in conjunction with the reverse idle gear so that the reverse idle gear meshes with the reverse gear when the transmission mode is the parking mode and the reverse mode. It is conceivable to increase the gear width (see FIG. 7).

  However, in the above structure, the reverse idle gear width increases, so the range of movement of the reverse idle gear when moved so as not to mesh with the reverse gear increases, and the mode is switched between neutral mode and drive mode. Since the reverse idle gear moves, the movable range of the reverse idle gear is further increased. For this reason, there existed a problem that a transmission enlarged.

  The present invention has been made in view of such technical problems, and an object of the present invention is to provide a shift mechanism capable of suppressing the size of a multi-disc transmission.

  According to an aspect of the present invention, a primary disk provided on an input shaft to which rotation of a drive source is input, and a secondary disk provided on an output shaft and partially overlapping with the primary disk are connected to the input shaft. A shift mechanism of a multi-disc transmission for transmitting the rotation of the input shaft to the output shaft by being sandwiched between a pair of pressing rollers movably provided between the output shaft and the multi-disc transmission. A select lever for selecting an operation mode of the machine, an input side reverse gear provided on the input shaft, and an output provided on the output shaft provided so as to be freely slidable on the counter shaft and slidable in the axial direction. A reverse idle gear in which the reverse rotation state in which the rotation of the input shaft is reversed and transmitted to the output shaft is achieved by meshing with the reverse gear on the side, and the select lever When the operation mode is changed to the reverse mode and the parking mode, the position of the reverse idle gear is set to the first gear position that meshes with the input side reverse gear and the output side reverse gear. And a gear positioning mechanism for setting the position of the reverse idle gear to a second gear position that does not mesh with the input-side reverse gear and the output-side reverse gear when the drive mode is set. A mechanism is provided.

FIG. 1 is an overall schematic diagram of a multi-disc transmission according to a first embodiment of the present invention. FIG. 2 is a diagram illustrating the relationship between the primary disk, the secondary disk, and the pressing roller. FIG. 3A is a diagram illustrating a reverse state of the shift mechanism according to the first embodiment of the present invention. FIG. 3B is a diagram illustrating a parking state of the shift mechanism according to the first embodiment of the present invention. FIG. 3C is a diagram illustrating a neutral state of the shift mechanism according to the first embodiment of the present invention. FIG. 3D is a diagram illustrating a drive state of the shift mechanism according to the first embodiment of the present invention. FIG. 4 is a diagram illustrating a reverse state of the shift mechanism according to the second embodiment of the present invention. FIG. 5A is a diagram illustrating a reverse state of the shift mechanism according to the third embodiment of the present invention. FIG. 5B is a diagram illustrating a parking state of the shift mechanism according to the third embodiment of the present invention. FIG. 5C is a diagram illustrating a neutral state of the shift mechanism according to the third embodiment of the present invention. FIG. 5D is a diagram illustrating a drive state of the shift mechanism according to the third embodiment of the present invention. FIG. 6 is a diagram illustrating a reverse state of the shift mechanism according to the fourth embodiment of the present invention. FIG. 7 is a diagram showing a comparative example of the present invention.

<First Embodiment>
Hereinafter, a first embodiment of the present invention will be described with reference to the accompanying drawings.

  FIG. 1 is an overall schematic diagram of a multi-disc transmission (hereinafter referred to as “transmission”) 1 according to a first embodiment of the present invention.

  The transmission 1 is a transmission that is provided between an engine 10 serving as a power source and a differential gear (not shown), shifts rotation input from the engine 10, and outputs the output gear 20 to the differential gear. As described below, the transmission 1 includes a transmission case 30, a clutch 40, an input shaft 50, an output shaft 60, a primary disk 70, a secondary disk 80, a pair of pressing rollers 90, and a pressing force. A mechanism 100, a direct coupling mechanism 110, a composite cam mechanism 120, a step motor 130, and a shift mechanism 140 are provided.

  The input shaft 50 is provided coaxially with the engine 10, and the output shaft 60 is provided parallel to the input shaft 50. Each of the input shaft 50 and the output shaft 60 is rotatably supported by the transmission case 30.

  The clutch 40 is a diaphragm type dry clutch. In a state where the release lever 41 is not pushed to the engine 10 side, the clutch disc 43 is pushed against the flywheel 44 by the diaphragm spring 42 and the clutch 40 is fastened. On the other hand, when the release lever 41 is pushed to the engine 10 side, the release bearing 45 is pushed to the engine 10 side, the diaphragm spring 42 is pushed and shrunk, the clutch disc 43 is separated from the flywheel 44, and the clutch 40 is released. .

  The primary disk 70 is composed of a plurality of circular disks and is fixed to the input shaft 50. Similarly, the secondary disk 80 is composed of a plurality of circular disks and is fixed to the output shaft 60. The primary disk 70 and the secondary disk 80 are arranged alternately so that a region where the disks 70 and 80 partially overlap is formed (see FIG. 2).

  The pressing roller 90 is rotatably held by the holding portion 92 via a bearing 91 and is disposed on both sides with the primary disk 70 and the secondary disk 80 interposed therebetween.

  The pressing roller 90 can be moved in a direction perpendicular to the disk surface by a pressing mechanism 100 described later. When a pressing force is applied to the primary disk 70 and the secondary disk 80 from the pressing roller 90 by the pressing mechanism 100, the primary disk 70 and the secondary disk 80 are elastically deformed and contacted, and the rotation of the input shaft 50 causes the primary disk 70 and the secondary disk 80 to rotate. It is transmitted to the output shaft 60 via 80.

  Further, as shown in FIG. 2, the pressing roller 90 can be moved along a shaft connecting line O connecting the input shaft 50 and the output shaft 60 by the composite cam mechanism 120 described later, whereby the primary disk 70 is moved. By changing the contact position between the secondary disk 80 and the secondary disk 80, the gear ratio of the transmission 1 can be changed to stepless or stepped. Specifically, when the contact position between the primary disk 70 and the secondary disk 80 is changed to the input shaft 50 side, the transmission ratio of the transmission 1 is changed to the Low side (large transmission ratio side), and conversely, the output shaft 60 side When changed to, the transmission ratio of the transmission 1 is changed to the High side (the transmission ratio small side).

  The pressing mechanism 100 includes a rotation shaft 101 fixed to the transmission case 30, a pair of clamp arms 102 and 103 that are swingably connected to the rotation shaft 101, and a pair of clamp arms 102 and 103. And a pressing force adjusting mechanism 104 provided on the end side.

  The pressing force adjusting mechanism 104 is attached to the arc-shaped rail 105 fixed to one clamp arm 102 and the other clamp arm 103 so as to be rotatable, and a roller 106 provided at an end is engaged with the arc-shaped rail 105. It is comprised with the rotation engaging part 107 to join. A force in the rotation center direction is always applied to the roller 106 by a spring 108, and the rotation engagement portion 107 can be rotated by a step motor (not shown).

  When the rotation engagement portion 107 is rotated counterclockwise from the state shown in the drawing, the component perpendicular to the disk surface of the urging force of the spring 108 increases, and the force with which the pair of clamp arms 102 and 103 press the pressing roller 90 is increased. And the pressing force acting on the primary disk 70 and the secondary disk 80 from the pressing roller 90 increases. In order to reduce or prevent the pressing force acting on the primary disk 70 and the secondary disk 80 from the pressing roller 90, the rotation engaging portion 107 may be rotated clockwise.

  The direct coupling mechanism 110 is a mechanism that transmits the rotation of the input shaft 50 to the output shaft 60 through a gear train, and includes a low gear train 111 and a high gear train 112 as forward gear trains, and a reverse gear train 113 as a reverse gear train. With.

  The low gear train 111 has more teeth than the input side low gear 111i and the input side low gear 111i provided so as to be freely rotatable on the input shaft 50, meshes with the input side low gear 111i, and is fixed to the output shaft 60. It is comprised with the output side low gear 111o. A spline 111s is formed at the end of the input side low gear 111i.

  The high gear train 112 has a smaller number of teeth than the input high gear 112i and the input high gear 112i provided on the input shaft 50 so as to be free-wheeling, meshes with the input high gear 112i, and is fixed to the output shaft 60. It is comprised with the output side High gear 112o. A spline 112s is formed at the end of the input side high gear 112i.

  A hub 114 and a sleeve 115 are disposed between the input-side low gear 111i and the input-side high gear 112i. The hub 114 is fixed to the input shaft 50, and splines 114s are formed on the outer peripheral surface. The sleeve 115 has splines 115s formed on the inner peripheral surface.

  In the illustrated state, the spline 115s of the sleeve 115 is fitted only to the spline 114s of the hub 114, and is not fitted to the spline 111s of the input side low gear 111i and the spline 112s of the input side high gear 112i. In this state, the rotation of the input shaft 50 is not directly transmitted to the output shaft 60 through either the low gear train 111 or the high gear train 112.

  When the sleeve 115 is slid to the input-side low gear 111i side from the non-directly connected state and the spline 115s of the sleeve 115 is fitted to both the spline 111s of the input-side low gear 111i and the spline 114s of the hub 114, the input-side low gear 111i. Is engaged with the input shaft 50 so as not to rotate relative to the input shaft 50, and the rotation of the input shaft 50 is transmitted to the output shaft 60 via the Low gear train 111.

  Conversely, when the sleeve 115 is slid from the non-directly connected state to the input side high gear 112i side and the spline 115s of the sleeve 115 is fitted to both the spline 112s of the input side high gear 112i and the spline 114s of the hub 114, the input side The high gear 112i is engaged with the input shaft 50 so as not to rotate relative to the input shaft 50, and the rotation of the input shaft 50 is transmitted to the output shaft 60 via the high gear train 112.

  The sleeve 115 is slid by converting the rotation of the step motor 130 into a linear motion by the composite cam mechanism 120 and transmitting the linear motion to the sleeve 115. This will be described later.

  The reverse gear train 113 includes a counter shaft 113c provided in parallel to the input shaft 50 and the output shaft 60, a reverse idle gear 113a provided on the counter shaft 113c so as to be free to rotate and slidable in the axial direction, and the input shaft 50. The input side reverse gear 113i fixed to the output shaft 60 and the output side reverse gear 113o fixed to the output shaft 60 are provided.

  When the driver operates the select lever 141 of the shift mechanism 140, the reverse idle gear 113a slides between a position where it does not mesh with the input side reverse gear 113i and the output side reverse gear 113o and a position where it meshes. The shift mechanism 140 will be described later.

  When the reverse idle gear 113a is engaged with the input-side reverse gear 113i and the output-side reverse gear 113o, the reverse gear train 113 reverses the rotation of the input shaft 50 and transmits it to the output shaft 60.

  Further, in this state, when a pressing force is applied from the pressing roller 90 to the primary disk 70 and the secondary disk 80, the path for transmitting rotation is the path between the path via the reverse gear train 113 and the path via the disks 70 and 80. Since there are two systems and the directions of rotation of the respective paths are opposite, the output shaft 60 is in a parking state in which it does not rotate.

The composite cam mechanism 120 is a single actuator (step motor 130) and has the following three functions:
A function of engaging / disengaging the clutch 40 A function of switching between a friction transmission state in which the rotation of the engine 10 is transmitted through the primary disk 70 and the secondary disk 80 and a direct connection state in which the rotation is transmitted through the direct connection mechanism 110 This is a cam mechanism that realizes a function of changing the gear ratio of the transmission 1 by displacing 90 along the shaft coupling line O.

  The composite cam mechanism 120 includes a feed screw 121, a slide nut 122, a first cam 123, a first rod 124, a second cam 125, and a second rod 126.

  The feed screw 121 is connected to the rotation shaft of the step motor 130 and is driven to rotate by the step motor 130.

  The slide nut 122 is screwed to the feed screw 121 and is displaced in the feed direction of the feed screw 121 when the step motor 130 is driven to rotate.

  The first cam 123 is a cam that is provided on the engine 10 side of the slide nut 122 and has a cam surface on the engine 10 side, and a roller 124r provided at the end of the first rod 124 is in contact with the cam surface. . The first rod 124 is passed through a through hole formed in the transmission case 30, and an end located on the opposite side of the roller 124 r is in contact with the release lever 41 of the clutch 40.

  When the step motor 130 is driven to rotate and the first cam 123 is displaced together with the slide nut 122 and the first rod 124 is pushed toward the engine 10 by the cam crest of the first cam 123, the release lever 41 is pushed toward the engine 10 side. Then, the clutch 40 is released. On the contrary, when the cam crest of the first cam 123 is lowered, the first rod 124 is returned to the transmission 1 side, and the release lever 41 is returned to the transmission side by the force of the diaphragm spring 42, the clutch 40 is engaged. To do.

  The second cam 125 is provided on the direct coupling mechanism 110 side of the slide nut 122. The second cam 125 is a positive cam that has a cam groove extending in the feed direction of the feed screw 121 while meandering, and a roller 126r provided at the end of the second rod 126 engages with the cam groove. The end of the second rod 126 located on the opposite side of the roller 126r is connected to the sleeve 115 of the direct coupling mechanism 110.

  When the step motor 130 is driven to rotate and the second cam 125 is displaced together with the slide nut 122, the rotation of the step motor 130 is converted into a linear motion of the second rod 126, which is transmitted to the sleeve 115 of the direct coupling mechanism 110. 115 slides. Thereby, the direct connection mechanism 110 can be switched between a low direct connection state, a non-direct connection state, and a high direct connection state.

  The second rod 126 has notches formed in the second rod 126 corresponding to each state so that the direct coupling mechanism 110 can stably hold the low direct connection state, the non-direct connection state, and the high direct connection state. A positioning mechanism 127 composed of a ball plunger is provided.

  The holding portion 92 of the pressing roller 90 is provided with a latch mechanism 93. When the slide nut 122 is displaced to a position where it comes into contact with the holding portion 92 of the pressing roller 90, the latch mechanism 93 causes the slide nut 122 and the holding portion to move. 92 are connected. Accordingly, when the step motor 130 is driven to rotate, the pressing roller 90 is displaced along the axis connecting line O, and the step motor 130 can function as a speed change actuator.

  In this state, by applying a pressing force from the pressing roller 90 to the primary disk 70 and the secondary disk 80, a friction transmission state in which the rotation of the input shaft 50 is transmitted to the output shaft 60 via the primary disk 70 and the secondary disk 80. Is realized. The pressing force applied from the pressing roller 90 to the primary disk 70 and the secondary disk 80 is adjusted by the pressing force adjusting mechanism 104 according to the required torque capacity.

  The transmission 1 according to the present embodiment can switch the parking mode, the reverse mode, the neutral mode, and the drive mode by the shift mechanism 140. Hereinafter, the details of the shift mechanism 140 will be described with reference to the drawings showing the states of the respective modes.

  FIG. 3A is a diagram illustrating a reverse state of the shift mechanism 140 according to the first embodiment of the present invention.

  The shift mechanism 140 includes a select lever 141, a position sensor 142, and a gear positioning mechanism 200.

  The select lever 141 is rotatably supported on the rotation shaft 143. The transmission 1 can switch the above four operation modes by the driver operating the select lever 141.

  The gear positioning mechanism 200 includes a slide block 144 and a striking rod 145.

  The slide block 144 is slidably supported by the slide shaft 146 and is disposed on the opposite side of the operation portion 141a of the select lever 141 with the rotation shaft 143 sandwiched in a direction in which the slide block 144 can move in the operation direction of the select lever 141. The A first stopper 147 and a second stopper 148 that restrict the movement of the slide block 144 are provided at both ends of the slide shaft 146, respectively.

  The slide block 144 and the select lever 141 are connected by a spring 149. The mounting position of the spring 149 on the select lever 141 side is provided on the side opposite to the operation portion 141a with the rotating shaft 143 interposed therebetween. In the reverse state where the select lever 141 is in the reverse mode position, as shown in FIG. The slide block 144 is held at a position in contact with the first stopper 147 by the tension of the spring 149.

  The striking rod 145 is provided so as to be parallel to the counter shaft 113c and movable in the axial direction, and a bracket 150 is attached to an end on the position sensor 142 side. The bracket 150 and the slide block 144 are connected by a connecting member 151, so that when the slide block 144 moves, the striking rod 145 moves in the axial direction in conjunction with it.

  The striking rod 145 is connected to the reverse idle gear 113a by a bracket 152 attached to the opposite side of the bracket 150, and when the striking rod 145 moves in the axial direction, the reverse idle gear 113a also moves in the axial direction in conjunction with it. To do. Accordingly, the reverse idle gear 113a is held at a position where it is engaged with the reverse gears 113i and 113o as shown in FIG. 3A in the reverse state where the select lever 141 is in the reverse mode position.

  The striking rod 145 has a notch formed in the striking rod 145 and a ball plunger corresponding to each mode of the transmission 1 so that the position of the reverse idle gear 113a can be stably held. Is provided.

  The position sensor 142 is a sensor that detects the mode of the transmission 1 selected by the select lever 141. The position sensor 142 includes a manual lever 154 that is rotatably supported on the rotation shaft 153. The end of the manual lever 154 opposite to the rotating shaft 153 is connected to the end of the select lever 141 via the connecting member 155, and when the select lever 141 is operated, the manual lever 154 is also moved in conjunction. The position sensor 142 detects the mode of the transmission 1 selected by the select lever 141 from the position of the manual lever 154.

  FIG. 3B is a diagram illustrating a parking state of the shift mechanism 140 according to the first embodiment of the present invention.

  When the selector lever 141 is operated to switch the mode of the transmission 1 from the reverse mode to the parking mode, the select lever 141 rotates about the rotation shaft 143, so that the mounting position of the spring 149 on the select lever 141 side is reached. However, it moves to the first stopper 147 side.

  Here, as shown in FIG. 3A, since the slide block 144 is already in contact with the first stopper 147 in the reverse state, the slide block 144 does not move any further. Therefore, the striking rod 145 connected to the slide block 144 does not move, and the reverse idle gear 113a is also held at a position where it engages with the reverse gears 113i and 113o, as shown in FIG. 3B.

  Even when the mode of the transmission 1 is switched from the parking mode to the reverse mode, the slide block 144 does not move, so that the reverse idle gear 113a is held at a position where it engages with the reverse gears 113i and 113o.

  FIG. 3C is a diagram illustrating a neutral state of the shift mechanism 140 according to the first embodiment of the present invention.

  When the mode of the transmission 1 is switched from the reverse mode to the neutral mode by operating the select lever 141, the select lever 141 rotates about the rotation shaft 143, so that the mounting position of the spring 149 on the select lever 141 side However, it moves to the 2nd stopper 148 side.

  As a result, the slide block 144 moves to a position where it comes into contact with the second stopper 148 due to the tension of the spring 149.

  When the slide block 144 moves from a position where it comes into contact with the first stopper 147 to a position where it comes into contact with the second stopper 148, the striking rod 145 also moves in conjunction with it. As a result, as shown in FIG. 3C, the reverse idle gear 113a also moves to a position where it does not mesh with the reverse gears 113i, 113o, and the shift mechanism 140 enters the neutral state.

  Even when the mode of the transmission 1 is switched from the neutral mode to the reverse mode, the slide block 144 moves and the striking rod 145 moves in conjunction with it. As a result, the reverse idle gear 113a also moves to a position where it engages with the reverse gears 113i, 113o, and the shift mechanism 140 is in the reverse state.

  FIG. 3D is a diagram illustrating a drive state of the shift mechanism 140 according to the first embodiment of the present invention.

  When the selector lever 141 is operated to switch the mode of the transmission 1 from the neutral mode to the drive mode, the select lever 141 rotates about the rotation shaft 143, so that the spring 149 mounting position on the select lever 141 side is installed. However, it moves to the 2nd stopper 148 side.

  Here, as shown in FIG. 3C, the slide block 144 is already in contact with the second stopper 148 in the neutral state, and therefore does not move any further. Therefore, the striking rod 145 connected to the slide block 144 does not move, and the reverse idle gear 113a is also held at the same position as in the neutral state as shown in FIG. 3D.

  Even when the mode of the transmission 1 is switched from the drive mode to the neutral mode, the slide block 144 does not move, so that the reverse idle gear 113a is held at the same position as in the neutral state.

  Next, the effect of this embodiment is demonstrated.

  In the multi-disc transmission 1, as described above, when the reverse idle gear 113a is engaged with the input-side reverse gear 113i and the output-side reverse gear 113o, the rotation of the input shaft 50 is reversed and transmitted to the output shaft 60. In this state, when a pressing force is applied from the pressing roller 90 to the primary disk 70 and the secondary disk 80, the path for transmitting the rotation passes through the reverse gear train 113 and the disks 70 and 80. Since there are two systems with the paths and the rotation directions of the paths are opposite, the output shaft 60 is in a parking state in which it does not rotate.

  Accordingly, in the multi-disc transmission 1, the reverse idle gear 113a is engaged with the reverse gears 113i and 113o in the reverse mode and the parking mode, and the reverse idle gear 113a is engaged with the reverse gears 113i and 113o in the neutral mode and the drive mode. It is necessary not to.

  In order to realize this, for example, as in the shift mechanism shown in FIG. 7, the manual lever of the position sensor and the striking rod are moved so that the reverse gear moves in conjunction with the position of the select lever. It is conceivable to increase the width W of the reverse idle gear so that the reverse idle gear meshes with the reverse gear when the transmission is in the reverse mode and the parking mode.

  However, in the above-described structure, the reverse idle gear width W is increased, so that the movable range of the reverse idle gear is increased when the reverse idle gear is moved so as not to mesh with the reverse gear. Also, when the neutral mode and the drive mode are switched, the reverse idle gear moves in conjunction with each other, so that the movable range of the reverse idle gear is further increased. For this reason, there exists a problem that a transmission will enlarge.

  In contrast, in the shift mechanism 140 according to the present embodiment, the reverse idle gear 113a does not move when switching between the reverse mode and the parking mode. Therefore, even if the width of the reverse idle gear 113a is reduced, the reverse idle gear 113a does not move. The gear 113a can be kept engaged with the reverse gears 113i and 113o, and the movable range of the reverse idle gear 113a when moved so as not to mesh with the reverse gears 113i and 113o can be reduced. Also, when the neutral mode and the drive mode are switched, the reverse idle gear 113a does not move, so that the movable range of the reverse idle gear 113a can be reduced. Therefore, the size of the transmission 1 can be suppressed.

Second Embodiment
Subsequently, a second embodiment of the present invention will be described.

  FIG. 4 is a diagram illustrating a reverse state of the shift mechanism 140 according to the second embodiment of the present invention. In addition, the same code | symbol is attached | subjected to the structure same as 1st Embodiment.

  As shown in FIG. 4, the second embodiment is different from the first embodiment in that the gear positioning mechanism 200 includes a cam 170 instead of the slide block 144. Hereinafter, the difference from the first embodiment will be mainly described.

  The cam 170 is slidably supported by the slide shaft 146 and is disposed on the opposite side of the operation portion 141 a of the select lever 141 with the rotation shaft 143 sandwiched in a direction in which the cam 170 can move in the operation direction of the select lever 141. . A first stopper 147 and a second stopper 148 that restrict the movement of the cam 170 are attached to both ends of the slide shaft 146, respectively.

  The cam 170 is engaged with a roller 171 attached to the select lever 141 by a cam groove 170a formed on the surface of the select lever 141 on the rotating shaft 143 side, and the reverse state in which the select lever 141 is in the reverse mode position. Then, as shown in FIG. 4, the first stopper 147 and the roller 171 hold the first stopper 147 at a position where the first stopper 147 abuts.

  The cam 170 is connected to a bracket 150 attached to the striking rod 145 by a connecting member 151. When the cam 170 moves, the striking rod 145 moves in conjunction with the cam 170.

  When the selector lever 141 is operated and the mode of the transmission 1 is switched from the reverse mode to the parking mode, the selector lever 141 rotates about the rotation shaft 143, so that the roller 171 moves to the first stopper 147 side. To do.

  Since the shape of the portion of the cam groove 170a in contact with the roller 171 at this time is formed so as to coincide with the locus drawn by the outer diameter of the roller 171, the cam 170 is not pushed and moved by the roller 171. . Therefore, the cam 170 is held by the first stopper 147 and the roller 171 while maintaining the position in contact with the first stopper 147.

  When the selector lever 141 is operated to change the mode of the transmission 1 from the reverse mode to the neutral mode, the selector lever 141 rotates about the rotation shaft 143, so that the roller 171 moves to the second stopper 148 side. Do

  As a result, the cam 170 moves to the second stopper 148 side in conjunction with the movement of the roller 171, and in the neutral state where the select lever 141 is in the neutral mode position, the cam 170 comes into contact with the second stopper 148. 2 is held by the stopper 148 and the roller 171.

  When the selector lever 141 is operated and the mode of the transmission 1 is switched from the neutral mode to the drive mode, the selector lever 141 rotates about the rotation shaft 143, so that the roller 171 moves to the second stopper 148 side. To do.

  Since the shape of the portion of the cam groove 170a in contact with the roller 171 at this time is formed so as to coincide with the locus drawn by the outer diameter of the roller 171, the cam 170 is not pushed and moved by the roller 171. . Accordingly, the cam 170 is held by the second stopper 148 and the roller 171 while maintaining the position in contact with the second stopper 148.

  According to this embodiment, the same effect as that of the first embodiment can be obtained.

<Third Embodiment>
Subsequently, a third embodiment of the present invention will be described.

  FIG. 5A is a diagram illustrating a reverse state of the shift mechanism 140 according to the third embodiment of the present invention. In addition, the same code | symbol is attached | subjected to the structure same as 1st Embodiment.

  As shown in FIG. 5A, the third embodiment is different from the first embodiment in that the gear positioning mechanism 200 does not include the slide block 144 and the manual lever 172 of the position sensor 142 and the striking rod 145 are connected. To do. Hereinafter, the difference from the first embodiment will be mainly described.

  The bracket 150 of the striking rod 145 and the end of the manual lever 172 on the striking rod 145 side are connected by a spring 173, so that when the manual lever 172 moves, the striking rod 145 also moves in the axial direction. Moving.

  Further, a first stopper 174 and a second stopper 175 that restrict the movement of the striking rod 145 by contacting the bracket 150 are provided on both sides of the bracket 150, respectively.

  In the state where the select lever 141 is in the reverse mode position, that is, in the reverse state where the manual lever 172 is in the reverse mode position, the striking rod 145 has the bracket 150 in the first position due to the tension of the spring 173 as shown in FIG. It is held at a position where it comes into contact with the stopper 174. Further, the reverse idle gear 113a connected to the striking rod 145 is held at a position where it engages with the reverse gears 113i and 113o.

  FIG. 5B is a diagram illustrating a parking state of the shift mechanism 140 according to the third embodiment of the present invention.

  When the select lever 141 is operated to change the mode of the transmission 1 from the reverse mode to the parking mode, the manual lever 172 moves in conjunction with the operation of the select lever 141. Then, when the manual lever 172 rotates about the rotation shaft 153, the attachment position of the spring 173 on the manual lever 172 side moves to the first stopper 174 side.

  Here, as shown in FIG. 5A, the striking rod 145 is in a position where the bracket 150 is already in contact with the first stopper 174 in the reverse state, and does not move any further. Therefore, the reverse idle gear 113a connected to the striking rod 145 also does not move and is held in a position where it engages with the reverse gears 113i and 113o as shown in FIG. 5B.

  FIG. 5C is a diagram illustrating a neutral state of the shift mechanism according to the third embodiment of the present invention.

  When the selector lever 141 is operated to change the mode of the transmission 1 from the reverse mode to the neutral mode, the manual lever 172 moves in conjunction with the operation of the select lever 141. Then, when the manual lever 172 rotates about the rotation shaft 153, the attachment position of the spring 173 on the manual lever 172 side moves to the second stopper 175 side.

  As a result, the striking rod 145 moves to a position where the bracket 150 comes into contact with the second stopper 175, and in conjunction with the movement of the striking rod 145, the reverse idle gear 113a also has a reverse gear 113i, It moves to a position where it does not mesh with 113o, and the shift mechanism 140 enters a neutral state.

  FIG. 5D is a diagram illustrating a drive state of the shift mechanism 140 according to the third embodiment of the present invention.

  When the select lever 141 is operated to switch the mode of the transmission 1 from the neutral mode to the drive mode, the manual lever 172 moves in conjunction with the operation of the select lever 141. Then, when the manual lever 172 rotates about the rotation shaft 153, the attachment position of the spring 173 on the manual lever 172 side moves to the second stopper 175 side.

  Here, as shown in FIG. 5C, the striking rod 145 is in a position where the bracket 150 is already in contact with the second stopper 175 in the neutral state, and does not move any further. Therefore, the reverse idle gear 113a connected to the striking rod 145 also does not move and is held at the same position as in the neutral state.

  According to this embodiment, the same effect as that of the first embodiment can be obtained.

<Fourth embodiment>
Subsequently, a fourth embodiment of the present invention will be described.

  FIG. 6 is a diagram illustrating a reverse state of the shift mechanism 140 according to the fourth embodiment of the present invention. In addition, the same code | symbol is attached | subjected to the structure same as 3rd Embodiment.

  As shown in FIG. 6, the fourth embodiment is different from the third embodiment in that a manual lever 172 of the position sensor 142 and a striking rod 145 are connected by a cam 176. Hereinafter, the difference from the third embodiment will be mainly described.

  A cam 176 is attached to the end of the striking rod 145 on the position sensor 142 side. The cam 176 is engaged with a roller 177 attached to the manual lever 172 by a cam groove 176 a formed on the surface of the manual lever 172 on the rotating shaft 153 side. Thus, when the manual lever 172 moves, the striking rod 145 moves in the axial direction in conjunction with the movement.

  Further, on both sides of the cam 176, a first stopper 174 and a second stopper 175 are provided for restricting the movement of the striking rod 145 by contacting the cam 176, respectively.

  In the state where the select lever 141 is in the reverse mode position, that is, in the reverse state where the manual lever 172 is in the reverse mode position, the cam 176 contacts the first stopper 174 in the striking rod 145 as shown in FIG. In position, it is held by the first stopper 174 and the roller 177.

  When the select lever 141 is operated to change the mode of the transmission 1 from the reverse mode to the parking mode, the manual lever 172 moves in conjunction with the operation of the select lever 141. Then, the manual lever 172 rotates about the rotation shaft 153, so that the roller 177 moves to the first stopper 174 side.

  The shape of the portion of the cam groove 176a that contacts the roller 177 at this time is formed so as to coincide with the locus drawn by the outer diameter of the roller 177, and the cam 176 is not moved by being pushed by the roller 177. Therefore, the striking rod 145 does not move to the first stopper 174 side, and is held by the first stopper 174 and the roller 177 while keeping the position where the cam 176 contacts the first stopper 174.

  When the selector lever 141 is operated to change the mode of the transmission 1 from the reverse mode to the neutral mode, the manual lever 172 moves in conjunction with the operation of the select lever 141. Then, the manual lever 172 rotates about the rotation shaft 153, so that the roller 177 moves to the second stopper 175 side.

  As a result, the striking rod 145 moves to the second stopper 175 side in conjunction with the movement of the roller 177, and is held by the second stopper 175 and the roller 177 at a position where the cam 176 contacts the second stopper 175. .

  When the select lever 141 is operated to switch the mode of the transmission 1 from the neutral mode to the drive mode, the manual lever 172 moves in conjunction with the operation of the select lever 141. Then, the manual lever 172 rotates about the rotation shaft 153, so that the roller 177 moves to the second stopper 175 side.

  The shape of the portion of the cam groove 176a that contacts the roller 177 at this time is formed so as to coincide with the locus drawn by the outer diameter of the roller 177, and the cam 176 is not moved by being pushed by the roller 177. Therefore, the striking rod 145 does not move to the second stopper 175 side, and is held by the second stopper 175 and the roller 177 while keeping the position where the cam 176 contacts the second stopper 175.

  According to this embodiment, the same effect as that of the first embodiment can be obtained.

  The embodiment of the present invention has been described above, but the above embodiment is merely one example of application of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. is not.

  For example, in the first embodiment, the select lever 141 and the slide block 144 are connected by the spring 149, and in the third embodiment, the manual lever 172 and the bracket 150 are connected by the spring 173. The elastic body may be used.

  This application claims the priority based on Japanese Patent Application No. 2013-132942 for which it applied to Japan Patent Office on June 25, 2013, All the content of this application is integrated in this specification by reference.

Claims (7)

A primary disk provided on the input shaft to which rotation of the drive source is input and a secondary disk provided on the output shaft and partially overlapping with the primary disk can be moved between the input shaft and the output shaft. A shift mechanism of a multi-disc transmission for contacting the rotation of the input shaft to the output shaft by being sandwiched between a pair of pressing rollers provided in
A select lever for selecting an operation mode of the multi-disc transmission;
The input shaft is provided so as to be free to rotate on the counter shaft and slidable in the axial direction, and meshes with an input side reverse gear provided on the input shaft and an output side reverse gear provided on the output shaft. A reverse idle gear that realizes a reverse state in which the rotation of the shaft is reversed and transmitted to the output shaft;
When the select lever is operated to change the operation mode to the reverse mode and the parking mode, the position of the reverse idle gear is set to the first gear position that meshes with the input-side reverse gear and the output-side reverse gear, A gear positioning mechanism for setting the position of the reverse idle gear to a second gear position that does not mesh with the input-side reverse gear and the output-side reverse gear when in the neutral mode and the drive mode;
A shift mechanism of a multi-disc transmission comprising: A shift mechanism for a multi-disc transmission according to claim 1,
The gear positioning mechanism is
A movable member that moves in conjunction with the operation of the select lever;
A first stopper for controlling movement of the movable member when the select lever is operated to change the operation mode from the reverse mode to the parking mode;
A second stopper for restricting the movement of the movable member when the select lever is operated to change the operation mode from the neutral mode to the drive mode;
A connecting member that is connected to the movable member and the reverse idle gear, moves in conjunction with the movement of the movable member, and moves the reverse idle gear to the first gear position or the second gear position;
A shift mechanism of a multi-disc transmission comprising: A shift mechanism for a multi-disc transmission according to claim 2,
The movable member is provided so as to be movable in the operation direction of the select lever, is connected to the select lever via an elastic member, and is moved by the elastic force of the elastic member in conjunction with the operation of the select lever. Because
The connecting member is a rod provided parallel to the counter shaft and movable in the axial direction, one side connected to the slide block, and the other side connected to the reverse idle gear.
Shift mechanism for multi-disc transmission. A shift mechanism for a multi-disc transmission according to claim 2,
The movable member is a cam that is movably provided in the operation direction of the select lever, engages with the select lever, and moves in conjunction with the operation of the select lever,
The connecting member is a rod provided in parallel with the counter shaft and movable in the axial direction, one side connected to the cam, and the other side connected to the reverse idle gear.
Shift mechanism for multi-disc transmission. A shift mechanism for a multi-disc transmission according to claim 1,
A manual lever that moves in conjunction with the operation of the select lever and that specifies the operation mode selected by the select lever based on the moved position,
The gear positioning mechanism is
A connecting member that is connected to the manual lever and the reverse idle gear, moves in conjunction with the movement of the manual lever, and moves the reverse idle gear;
A first stopper for controlling the movement of the connecting member and holding the reverse idle gear at the first gear position when the select lever is operated to change the operation mode from the reverse mode to the parking mode. When,
A second stopper for controlling the movement of the movable member and holding the reverse idle gear at the second gear position when the select lever is operated to change the operation mode from the neutral mode to the drive mode. When,
A shift mechanism of a multi-disc transmission comprising: A shift mechanism for a multi-disc transmission according to claim 5,
The connecting member is provided in parallel with the counter shaft and movable in the axial direction, one side is connected to the manual lever via an elastic member, the other side is connected to the reverse idle gear, The rod is moved by the elastic force of the elastic member in conjunction with the movement, and is a rod that moves the reverse idle gear.
Shift mechanism for multi-disc transmission. A shift mechanism for a multi-disc transmission according to claim 5,
The connecting member is provided parallel to the counter shaft and movable in the axial direction. The connecting member is engaged with the manual lever by a cam provided on one side, and the other side is connected to the reverse idle gear. A rod that moves in conjunction with the movement of the lever and moves the reverse idle gear.
Shift mechanism for multi-disc transmission.

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