JP2013137079A - Transmission with auxiliary transmission mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent a synchronization mechanism becoming out-of-synchronization regarding a transmission with an auxiliary transmission mechanism.SOLUTION: A transmission with an auxiliary transmission mechanism includes: an auxiliary speed-change shaft 43 that is provided in a select direction and rotated according to the operation of an operation lever; an auxiliary gear shift lever 45 that is freely rotatably supported to the auxiliary speed-change shaft 43; an elastic member 71 that connects the auxiliary speed-change shaft 43 with the auxiliary gear shift lever 45; a main speed-change shaft 44 that is provided in a select direction; a main gear shift lever 47 that is provided extending from the main speed-change shaft 44 and moved in the select direction by the operation of the operation lever; a shift shaft 42 that is provided extending in a shift direction and connected to a shift block 51; a protruding part 46 that is protrudingly provided to the auxiliary speed-change shaft 43; a protruding part 48 that is protrudingly provided to the main speed-change shaft 44; and a connecting member 49 whose one end is freely rotatably connected to the protruding part 46 and whose the other end is freely rotatably connected to the protruding part 48.

Description

  The present invention relates to a transmission with a subtransmission mechanism, and more particularly to a transmission with a subtransmission mechanism that simultaneously shifts a main transmission mechanism and a subtransmission mechanism.

  In a transmission with a sub-transmission mechanism that includes a sub-transmission mechanism in addition to the main transmission mechanism, a separate operation mechanism is required for each transmission mechanism. In order to obtain an optimum gear ratio according to the traveling state of the vehicle, the operation mechanism of the main transmission mechanism and the operation mechanism of the subtransmission mechanism must be operated simultaneously, which is very troublesome for the driver. For this reason, it is generally not used to switch the auxiliary transmission mechanism while the vehicle is running. In order to improve the operability of such a transmission with a sub-transmission mechanism, the operation of the sub-transmission mechanism is known as a switch type that uses an actuator such as electricity, pneumatic pressure, or hydraulic pressure (for example, patent document) 1).

JP-A-9-72417

  As shown in FIG. 9 (a), the general synchronous transmission coupling is as follows. (1) The sleeve spline teeth 90 and block ring dog teeth 91 come into contact with each other in the axial direction from the neutral position of the sleeve. A synchronization start position, (2) a dog facing position where the spline teeth 90 and the dog teeth 92 of the transmission gear contact, (3) a dog engagement start position where the spline teeth 90 and the dog teeth 92 of the transmission gear start meshing, and (4) The process is performed through detent-fixed steps in which the spline teeth 90 and the dog teeth 92 are completely meshed. In such a synchronous coupling, a synchronization failure may be caused in the synchro mechanism particularly when it is affected by a disturbance between the synchronization start position and the dog meshing start position (see arrow A in FIG. 9B).

  By the way, as shown in FIG. 9B, when the main transmission mechanism and the sub-transmission mechanism are simultaneously shifted, the sleeve on the sub-transmission mechanism side starts moving from the neutral position before the sleeve on the main transmission mechanism side. In this transmission mechanism, the sub-transmission mechanism side synchro mechanism reaches the synchronization start position before the main transmission mechanism-side synchro mechanism. For this reason, if the sync mechanism on the main transmission mechanism reaches the synchronization start position while the sync mechanism on the side of the sub transmission mechanism is at the dog meshing start position from the synchronization start position, these sync mechanisms interfere with each other and There is a possibility of causing synchronization loss in the synchro mechanism.

  The present invention has been made in view of the above points, and an object of the present invention is to synchronize the synchronization mechanism that can be caused when the main transmission mechanism and the auxiliary transmission mechanism are simultaneously operated in a transmission with an auxiliary transmission mechanism. The purpose is to effectively prevent collapse.

  In order to achieve the above object, a transmission with a subtransmission mechanism according to the present invention is a transmission with a subtransmission mechanism that simultaneously shifts the main transmission mechanism and the subtransmission mechanism by operating the operation lever in the select direction and the shift direction. A sub-transmission shaft that extends in the select direction on the sub-transmission mechanism side and rotates in response to an operation of the operation lever in the shift direction, and an upper end portion of the sub-transmission shaft is rotatable. A sub-shifting shift lever that is supported and extends downward, an elastic member that connects the sub-shifting shaft and the sub-shifting shift lever, and a sub-shifting gear disposed below the sub-shifting shaft. A sub-shifting shift block that engages with the lower end of the shift lever, a rotatable main transmission shaft provided extending in the select direction on the main transmission mechanism side, and the main transmission shaft. A main transmission shift lever that extends in the direction and moves in the selection direction when the operation lever is operated in the selection direction, and is arranged in parallel in the selection direction below the main transmission shaft, and A plurality of main transmission shift blocks that engage with the lower end of the shift lever, a first protrusion that protrudes from the auxiliary transmission shaft, and a second protrusion that protrudes from the main transmission shaft; A connecting member having one end rotatably connected to the first projecting portion and the other end rotatably connected to the second projecting portion, and operating the sub-shift by operating the operating lever in a shift direction. Regardless of the direction of rotation of the main shaft, the rotational force transmitted to the main transmission shaft through the connecting member is converted into one direction by the connecting member, so that the main transmission shift lever is moved in one direction. The sub-transmission shaft rotational force is transmitted via the elastic member so that the sub-transmission mechanism-side sync mechanism and the main transmission mechanism-side sync mechanism start synchronous coupling simultaneously. It is transmitted to the shift lever for use.

  Further, a flange is formed on the auxiliary transmission shaft located between the main transmission shift lever and the first projecting portion, and the elastic member has one end fixed to the flange and the other end connected to the other end. The elastic lever may be a spring.

  Of the plurality of main transmission shift blocks, the main transmission shift block not corresponding to the movement direction of the main transmission shift fork to which the corresponding gear corresponds corresponds to a rod fixed to the main transmission shift block, one end May be connected to the shift shaft via a reversing mechanism having a rotatable reversing lever hinged to the rod and having the other end hinged to the shift shaft.

  In addition, the first protrusion is inclined at a predetermined angle toward the main transmission shaft from the auxiliary transmission shaft upward, and the second protrusion is upward from the main transmission shaft. The connecting member is inclined at a predetermined angle on the side of the auxiliary transmission shaft, and one end of the connecting member is hinged to the upper end of the first projecting portion and the other end is hinged to the upper end of the second projecting portion. Also good.

  In addition, the guide member further includes a guide member that guides the connecting member so as to be horizontally movable in the shift direction, the first protrusion is provided on one end surface of the sub-transmission shaft adjacent to the periphery, and the second protrusion is The main transmission shaft is provided at one end surface adjacent to the periphery, and the connecting member is formed with a guide groove at one end for guiding the first protrusion in the vertical direction and at the other end with the second protrusion. A hole through which the part is rotatably inserted may be formed.

  According to the transmission with a subtransmission mechanism of the present invention, it is possible to effectively prevent synchronization loss of the synchro mechanism that may be caused when the main transmission mechanism and the subtransmission mechanism are simultaneously shifted.

It is a skeleton figure which shows the transmission with an auxiliary transmission mechanism which concerns on one Embodiment of this invention. It is a typical perspective view which shows the shift operation apparatus of the transmission with an auxiliary transmission mechanism which concerns on one Embodiment of this invention. It is the typical whole block diagram which looked at the transmission mechanism of the transmission with an auxiliary transmission mechanism which concerns on one Embodiment of this invention from the top. It is the typical detailed block diagram which looked at the principal part of the transmission mechanism of the transmission with an auxiliary transmission mechanism which concerns on one Embodiment of this invention. It is the typical detailed block diagram which looked at the principal part of the transmission mechanism of the transmission with an auxiliary transmission mechanism which concerns on one Embodiment of this invention from the front. It is the typical detailed block diagram which looked at the principal part of the transmission mechanism of the transmission with an auxiliary transmission mechanism which concerns on one Embodiment of this invention from upper direction. In the transmission with a subtransmission mechanism according to an embodiment of the present invention, each of the steps of synchronous coupling when the subtransmission mechanism and the main transmission mechanism are simultaneously operated to shift. It is the typical detailed block diagram which looked at the principal part of the transmission mechanism of the transmission with an auxiliary transmission mechanism which concerns on other embodiment from the side. (A) is a figure explaining the synchronous coupling | bonding of a general synchronizing mechanism, (b) is each of the synchronous coupling | bonding at the time of shifting operation of a subtransmission mechanism and a main transmission mechanism simultaneously in the transmission with the conventional subtransmission mechanism. It is a figure which shows a process.

  Hereinafter, based on FIGS. 1-7, the transmission with an auxiliary transmission mechanism which concerns on one Embodiment of this invention is demonstrated. The same parts are denoted by the same reference numerals, and their names and functions are also the same. Therefore, detailed description thereof will not be repeated.

  As shown in FIG. 1, a transmission with a sub-transmission mechanism (hereinafter simply referred to as a transmission) 10 according to the present embodiment is provided with a splitter-type sub-transmission mechanism 11 disposed on the input side and on the output side. The main transmission mechanism 12 is provided.

  An input shaft 13 to which an engine output (not shown) is transmitted is disposed on the auxiliary transmission mechanism 11 side. A main shaft 14 is disposed coaxially with the input shaft 13 on the main transmission mechanism 12 side. Further, the auxiliary transmission mechanism 11 and the main transmission mechanism 12 are provided with a counter shaft 15 parallel to the input shaft 13 and the main shaft 14.

  A splitter low speed gear 20 is provided on the input shaft 13 so as to be relatively rotatable. Further, on the main shaft 14, a splitter high speed gear 21, a main third speed gear 22, a main second speed gear 23, a main first speed gear 24, and a main reverse gear 25 are relatively rotated in order from the input side (left side in FIG. 1). It is provided as possible. The counter shaft 15 includes a counter low-speed gear 30 that meshes with the splitter low-speed gear 20, a counter high-speed gear 31 that meshes with the splitter high-speed gear 21, a counter third-speed gear 32 that meshes with the main third-speed gear 22, and a main second-speed gear. A counter second gear 33 that meshes with the main gear 23, a counter first gear 34 that meshes with the main first gear 24, and a counter reverse gear 36 that meshes with the main reverse gear 25 and the idler gear 35 are fixed. That is, the transmission 10 according to the present embodiment has six forward speeds (first speed L to third speed H) and two reverse speeds by selectively switching the splitter gears 20 and 21 and selectively switching the main gears 22 to 25. (Reverse L, reverse H) speed change is possible.

  Next, the shift operation device 80 of this embodiment will be described based on FIG.

  The shift operation device 80 includes a plurality of H-type gates 81 and an operation lever 82 that can move the H-type gates 81 so that the sub-transmission mechanism 11 and the main transmission mechanism 12 can be operated simultaneously. . A select path 83 is provided in the select direction of the H-shaped gate 81, and a neutral position N corresponding to the neutral mode is set at the center thereof. Further, four shift paths 84 to 87 orthogonal to the select path 83 are provided in the shift direction of the H-type gate 81. Further, shift positions corresponding to the above-described six forward speeds (1st speed L to 3rd speed H) and 2nd reverse speeds (reverse L, reverse H) are set at the ends of these four shift paths 84 to 87, respectively. Has been. That is, the shift operation device 80 of the present embodiment is connected to the shift mechanism of the subtransmission mechanism 11 when the operation lever 82 is operated in the shift direction, while the selection mechanism of the main transmission mechanism 12 is operated when the operation lever 82 is operated in the select direction. It is configured to be connected to.

  Next, based on FIGS. 3-7, the transmission mechanism 40 of this embodiment is demonstrated.

  As shown in FIG. 3, the speed change mechanism 40 of the present embodiment includes a first shift shaft 41 extending in the shift direction, a second shift shaft 42 extending in parallel with the first shift shaft 41, and a sub-speed change. A splitter shift shaft 43 extending in the select direction on the mechanism 11 side, a main shift shaft 44 extending in the select direction on the main transmission mechanism 12 side, and a splitter shift lever 45 provided on the splitter shift shaft 43. A splitter link arm 46 provided on the splitter shift shaft 43, a main shift lever 47 provided on the main shift shaft 44, a main link arm 48 provided on the main shift shaft 44, A link member 49 for connecting the splitter link arm 46 and the main link arm 48. The splitter shift block 50 disposed below the splitter shift shaft 43 and a plurality (four in this embodiment) of main shift blocks 51 to 54 arranged in parallel in the select direction below the main shift shaft 44. A splitter shift fork 55 provided on the first shift shaft 41 so as to be movable in the axial direction, a main R / 1-speed shift fork 57 fixed to the second shift shaft 42, and the first shift shaft 41. Fixed main 2/3 speed shift fork 58, main R / 1 speed connection mechanism 60, main 2/3 speed connection mechanism (not shown), and annular flange formed on splitter shift shaft 43 70, and a spring 71 interposed between the splitter shift lever 45 and the annular flange 70. That.

  As shown in FIG. 4, the splitter shift lever 45 extends downward from the splitter shift shaft 43, and its lower end engages with a recess formed in the center of the splitter shift block 50. . Further, a hole 45a through which the splitter shift shaft 43 is rotatably inserted through a bearing 72 is formed at the upper end of the splitter shift lever 45 (see FIG. 5).

  An annular flange 70 is formed on the splitter shift shaft 43 positioned between the splitter shift lever 45 and the splitter link arm 46. Further, between the annular flange 70 and the splitter shift lever 45, one end portion is fixed to the side surface of the annular flange 70 and the other end portion is used as an elastic member fixed to the side surface of the splitter shift lever 45. A spring 71 is interposed.

  That is, when the shift mechanism of the auxiliary transmission mechanism 11 is shifted (see arrow X in FIG. 3) by the operation of the operation lever 82 (see FIG. 2) in the shift direction and the splitter shift shaft 43 rotates, the splitter shift is performed. The lever 45 is rotated by the rotational force transmitted through the flange 70 and the spring 71. Accordingly, the splitter shift block 50 is configured to move in the left-right direction (see arrows X and Y in FIG. 4) in accordance with the operation of the operation lever 82 in the shift direction.

  The splitter link arm 46 extends from the splitter shift shaft 43 upward at an angle with a predetermined angle toward the main shift shaft 44 (right side in FIG. 4). The lower end portion of the splitter link arm 46 is fixed to the splitter shift shaft 43, while the upper end portion is hingedly connected to one end portion (left end in FIG. 4) of the link member 49.

  The main shift lever 47 extends downward from the main shift shaft 44 and has a lower end engaged with a recess formed in the center of the main shift blocks 51 to 54. The upper end of the main shift lever 47 is spline-fitted to the main shift shaft 44 and rotates integrally with the main shift shaft 44 while moving the main shift shaft 44 in the axial direction (select direction). It is configured to be possible. That is, when the selection mechanism of the main transmission mechanism 12 is selected (see arrow Y in FIG. 3) by the operation of the operation lever 82 (see FIG. 2) in the select direction, the main shift lever 47 is moved to the main shift shaft. 44 is moved in the select direction. As a result, the lower end portion of the main shift lever 47 engages with the concave portions of the main shift blocks 51 to 54 corresponding to the selected arbitrary shift position.

  The main link arm 48 extends from the main shift shaft 44 at an angle with a predetermined angle toward the splitter shift shaft 43 side (left side in FIG. 4). The lower end portion of the main link arm 48 is fixed to the main shift shaft 44, and the upper end portion is hinged to the other end portion (the right end in FIG. 4) of the link member 49 so as to be rotatable.

  That is, in the speed change mechanism 40 according to the present embodiment, one end of the link member 49 is hinged to the splitter link arm 46 and the other end is rotatably connected to the main link arm 48. This is a four-bar linkage mechanism having two hinge connection portions and the shaft center of the main shift shaft 44 as rotation fulcrums. Thus, the left and right rotational forces (see arrows C and D in FIG. 4) transmitted from the splitter shift shaft 43 to the link member 49 via the splitter link arm 46 are rotated in the left direction by the link member 49. Force (see arrow E in FIG. 4). As a result, the splitter shift block 50 is moved in both the left and right directions (see arrows X and Y in FIG. 4) according to the operation of the operation lever 82 in the shift direction, while the main shift blocks 51 to 54 are moved in the right direction. It is moved only in one direction (see arrow Y in FIG. 4).

  Next, the main R / 1-speed connection mechanism 60 according to this embodiment will be described with reference to FIG.

  The main R / 1 speed connecting mechanism 60 includes a connecting member 61 for connecting and fixing the main reverse shift block 51 and the second shift shaft 42, a rod 62 fixed to the main first speed shift block 52, and a central portion. And a reversing lever 63 that can rotate around the fulcrum. The reversing lever 63 has one end hinged to the rod 62 and the other end hinged to the second shift shaft 42.

  That is, the rightward moving force (see arrow A in FIG. 6) of the main reverse shift block 51 is directly transmitted to the second shift shaft 42 via the connection member 61, while the main first speed shift is performed. The moving force of the block 52 in the right direction (see arrow A in FIG. 6) is reversed to the moving force in the left direction (see arrow B in FIG. 6) by the rotation operation of the reversing lever 63 and applied to the second shift shaft 42. Communicated. As a result, when the main reverse shift block 51 moves in the right direction, the main R / 1 speed shift fork 57 moves to the right side of the main reverse gear shift fork 57 (see FIG. When the main first-speed shift block 52 moves to the right, the main 1 disposed on the left side of the main R / 1-speed shift fork 57 is rotated by the reversing lever 63. It is configured to move toward the speed gear 24 (see FIG. 1).

  In the main 2/3 speed connecting mechanism (not shown), the connecting member 61 connects and fixes the main 2 speed shift block 53 and the first shift shaft 41, and the reversing lever 63 is the main 3 speed shift block. The main R / 1 speed connecting mechanism 60 is configured in substantially the same manner except that it is hingedly connected to the rod 62 fixed to 54 and the first shift shaft 41. Therefore, detailed description and illustration of the main 2/3 speed connection mechanism are omitted.

  Next, the speed change operation of the transmission 10 according to the present embodiment will be described.

  First, the reverse L shifting operation will be described. When the operation lever 82 shown in FIG. 2 is operated in the select direction from the neutral position N to the orthogonal point to the shift path 84 in the select path 83, the main shift lever 47 is moved by the select operation of the select mechanism. Move up in the select direction. As a result, the lower end portion of the main shift lever 47 is engaged with the concave portion of the main reverse shift block 51.

  In this state, when the operation lever 82 is operated in the shift direction to the position of the reverse L through the shift path 84, the splitter shift shaft 43 is rotated clockwise, that is, clockwise (arrow A in FIG. 4). ). Further, the rotational force of the splitter shift shaft 43 is transmitted through the annular flange 70 and the spring 71, and the splitter shift lever 45 is similarly rotated clockwise (see arrow A in FIG. 4). As a result, the splitter shift fork 55 moves to the left with the splitter shift block 50 toward the splitter low-speed gear 20 (see FIG. 1). (See point A in FIG. 7). The contact state of the synchronizing mechanism of the splitter low-speed gear 20 is maintained until the operation lever 82 reaches a predetermined operation angle (see point B in FIG. 7) due to the bending deformation of the spring 71.

  On the other hand, the clockwise (clockwise) rotational force of the splitter shift shaft 43 is converted into a counterclockwise (counterclockwise) rotational force by the link member 49 constituting a part of the four-bar linkage mechanism. The shift lever 47 is rotated counterclockwise, that is, counterclockwise (see arrow F in FIG. 4). As a result, the main R / 1 speed shift fork 57 moves to the right in the direction of the main reverse gear 25 (see FIG. 1) together with the main reverse shift block 51, and the corresponding sleeve (not shown) is not shown. The spline teeth and the dog teeth of the block ring are brought into contact (see point B in FIG. 7).

  When the synchronization mechanism of the main reverse gear 25 reaches the synchronization start position, the synchronization mechanism of the main reverse gear 25 and the synchronization of the splitter low-speed gear 20 maintained at the synchronization start position (contact state) due to the bending deformation of the spring 71. The mechanism simultaneously starts an operation for engaging the spline teeth of the sleeve with the dog teeth of the block ring, that is, synchronous coupling of the synchro mechanism (see points B to C in FIG. 7).

  Next, the reverse H shift operation will be described. When the operation lever 82 shown in FIG. 2 is operated in the select direction from the neutral position N to the orthogonal point to the shift path 84 in the select path 83, the main shift lever 47 is moved by the select operation of the select mechanism. Move up in the select direction. As a result, the lower end portion of the main shift lever 47 is engaged with the concave portion of the main reverse shift block 51.

  In this state, when the operating lever 82 is operated in the shift direction to the position of the backward movement H through the shift path 84, the shift shaft 43 for the splitter is rotated counterclockwise, that is, counterclockwise (indicated by the arrow in FIG. 4). (See B). Further, the rotational force of the splitter shift shaft 43 is transmitted through the annular flange 70 and the spring 71, and the splitter shift lever 45 is similarly rotated counterclockwise (see arrow B in FIG. 4). As a result, the splitter shift fork 55 moves to the right with the splitter shift block 50 toward the splitter high-speed gear 21 (see FIG. 1). (See point A in FIG. 7). The contact state of the synchronization mechanism of the splitter high speed gear 21 is maintained until the operation lever 82 reaches a predetermined operation angle (see point B in FIG. 7) due to the bending deformation of the spring 71.

  On the other hand, the counterclockwise (counterclockwise) rotational force of the splitter shift shaft 43 is transmitted via a link member 49 that forms a part of the four-bar linkage mechanism, and the main shift lever 47 is counterclockwise. That is, it is rotated counterclockwise (see arrow F in FIG. 4). As a result, the main R / 1 speed shift fork 57 moves to the right in the direction of the main reverse gear 25 (see FIG. 1) together with the main reverse shift block 51, and the corresponding sleeve (not shown) is not shown. The spline teeth and the dog teeth of the block ring are brought into contact (see point B in FIG. 7).

  When the synchronization mechanism of the main reverse gear 25 reaches the synchronization start position, the synchronization mechanism of the main reverse gear 25 and the synchronization of the splitter high-speed gear 21 that has been maintained at the synchronization start position (contact state) due to the bending deformation of the spring 71. The mechanism simultaneously starts an operation for engaging the spline teeth of the sleeve with the dog teeth of the block ring, that is, synchronous coupling of the synchro mechanism (see points B to C in FIG. 7).

  That is, according to the transmission 10 of the present embodiment, regardless of whether the operation lever 82 of the shift operation device 80 is operated in the shift direction 84 in the reverse L or reverse H direction on the shift path 84, The rotational force transmitted to the shift shaft 44 is converted into a counterclockwise (counterclockwise) rotational force by the link member 49. As a result, regardless of the shift direction of the operation lever 82, the main R / 1-speed shift fork 57 is connected to the main reverse gear 25 together with the main reverse shift block 51 and the second shift shaft 42 (see FIG. 1). ) To be surely moved in the right direction.

  Further, in the synchronization mechanism on the auxiliary transmission mechanism 11 side, the contact state (synchronization start position) between the spline teeth of the sleeve and the dog teeth of the block ring is caused by the bending deformation of the spring 71 and the synchronization mechanism on the main transmission mechanism 12 side. This is maintained until the synchronization start position is reached. Thus, even if the sleeve on the auxiliary transmission mechanism 11 side starts moving from the neutral position before the sleeve on the main transmission mechanism 12 side, the synchronization mechanism on the auxiliary transmission mechanism 11 side and the synchronization mechanism on the main transmission mechanism 12 side Are configured to initiate synchronous coupling simultaneously.

  Next, the shifting operation of the first speed L will be described. When the operation lever 82 shown in FIG. 2 is operated in the select direction from the neutral position N to the orthogonal point to the shift path 85 in the select path 83, the main shift lever 47 is moved by the select operation of the select mechanism. Move up in the select direction. As a result, the lower end portion of the main shift lever 47 is engaged with the concave portion of the main first speed shift block 52.

  In this state, when the operation lever 82 is operated in the shift direction to the position of the first speed L through the shift path 85, the shift shaft 43 for the splitter is rotated clockwise, that is, clockwise (arrow in FIG. 4). (See A). Further, the rotational force of the splitter shift shaft 43 is transmitted through the annular flange 70 and the spring 71, and the splitter shift lever 45 is similarly rotated clockwise (see arrow A in FIG. 4). As a result, the splitter shift fork 55 moves to the left with the splitter shift block 50 toward the splitter low-speed gear 20 (see FIG. 1). (See point A in FIG. 7). The contact state of the synchronizing mechanism of the splitter low-speed gear 20 is maintained until the operation lever 82 reaches a predetermined operation angle (see point B in FIG. 7) due to the bending deformation of the spring 71.

  On the other hand, the clockwise (clockwise) rotational force of the splitter shift shaft 43 is converted into a counterclockwise (counterclockwise) rotational force by the link member 49 constituting a part of the four-bar linkage mechanism. The shift lever 47 is rotated counterclockwise (see arrow F in FIG. 4), and the main first speed shift block 52 is moved rightward. Then, the rightward moving force of the main first speed shift block 52 is converted to the leftward by the rotating operation of the reversing lever 63 and transmitted to the second shift shaft 42. As a result, the main R / 1st speed shift fork 57 moves to the left toward the main first speed gear 24 (see FIG. 1) together with the second shift shaft 42, and the corresponding sleeve (not shown) is not shown. The spline teeth and the dog teeth of the block ring are brought into contact (see point B in FIG. 7).

  When the synchronization mechanism of the main first speed gear 24 reaches the synchronization start position, the synchronization mechanism of the main first speed gear 24 and the splitter low speed gear 20 maintained at the synchronization start position (contact state) by the bending deformation of the spring 71. The synchronous mechanism of the sleeve simultaneously starts the operation for the spline teeth of the sleeve to mesh with the dog teeth of the block ring, that is, synchronous coupling of the synchronous mechanism (see points B to C in FIG. 7).

  Next, the shifting operation of the first speed H will be described. When the operation lever 82 shown in FIG. 2 is operated in the select direction from the neutral position N to the orthogonal point to the shift path 85 in the select path 83, the main shift lever 47 is moved by the select operation of the select mechanism. Move up in the select direction. As a result, the lower end portion of the main shift lever 47 is engaged with the concave portion of the main first speed shift block 52.

  In this state, when the operating lever 82 is operated in the shift direction to the position of the first speed H through the shift path 85, the shift shaft 43 for the splitter is rotated counterclockwise, that is, counterclockwise (in FIG. 4). (See arrow B). Further, the rotational force of the splitter shift shaft 43 is transmitted through the annular flange 70 and the spring 71, and the splitter shift lever 45 is similarly rotated counterclockwise (see arrow B in FIG. 4). As a result, the splitter shift fork 55 moves to the right with the splitter shift block 50 toward the splitter high-speed gear 21 (see FIG. 1). (See point A in FIG. 7). The contact state of the synchronization mechanism of the splitter high speed gear 21 is maintained until the operation lever 82 reaches a predetermined operation angle (see point B in FIG. 7) due to the bending deformation of the spring 71.

  On the other hand, the counterclockwise (counterclockwise) rotational force of the splitter shift shaft 43 is transmitted via a link member 49 that forms a part of the four-bar linkage mechanism, and the main shift lever 47 rotates counterclockwise ( 4) and the main first speed shift block 52 is moved in the right direction. Then, the rightward moving force of the main first speed shift block 52 is converted to the leftward by the rotating operation of the reversing lever 63 and transmitted to the second shift shaft 42. As a result, the main R / 1st speed shift fork 57 moves to the left toward the main first speed gear 24 (see FIG. 1) together with the second shift shaft 42, and the corresponding sleeve (not shown) is not shown. The spline teeth and the dog teeth of the block ring are brought into contact (see point B in FIG. 7).

  When the synchronization mechanism of the main first-speed gear 24 is in the synchronization start position, the synchronization mechanism of the main first-speed gear 24 and the splitter high-speed gear 21 that has been maintained at the synchronization start position (contact state) by the bending deformation of the spring 71. The sync mechanism of the sleeve simultaneously starts the operation for the spline teeth of the sleeve to mesh with the dog teeth of the block ring, that is, the synchronization of the synchro mechanism simultaneously (see points B to C in FIG. 7).

  That is, according to the transmission 10 of the present embodiment, regardless of whether the operation lever 82 of the shift operation device 80 is operated on the shift path 85 in the shift direction of the first speed L or the first speed H, the shift shaft 43 for the splitter The rotational force transmitted to the main shift shaft 44 is converted into a counterclockwise (counterclockwise) rotational force by the link member 49. Further, the rightward moving force transmitted to the main first speed shift block 52 is converted to the left by the rotation of the reversing lever 63 and transmitted to the second shift shaft 42. Thus, regardless of the shift direction of the operation lever 82, the main R / 1st speed shift fork 57 moves leftward toward the main first speed gear 24 (see FIG. 1) together with the second shift shaft 42. It is configured to be surely moved.

  The speed change operation of the second speed and the second speed (second speed L / H) is substantially the same as the second speed of the reverse speed (reverse speed L / H), and the speed change operation of the third speed and the second speed (third speed L / H) is It operates in substantially the same manner as the first speed and second speed (first speed L / H). Therefore, the detailed description of the shifting operation for the second speed and the second speed (second speed L / H) and the third speed and the second speed (third speed L / H) is omitted.

  As described above in detail, according to the transmission 10 of the present embodiment, the synchronization mechanisms on the auxiliary transmission mechanism 11 side and the main transmission mechanism 12 side are configured such that synchronous coupling is simultaneously started by the bending deformation of the spring 71. Has been.

  Therefore, it is possible to effectively prevent synchronization loss of the synchro mechanism that may be caused when the subtransmission mechanism 11 and the main transmission mechanism 12 are simultaneously shifted.

  Further, according to the transmission 10 of the present embodiment, the shift between the auxiliary transmission mechanism 11 and the main transmission mechanism 12 can be simultaneously performed only by operating the operation lever 82 of the shift operation device 80 in the select direction and the shift direction. it can.

  Accordingly, it is not necessary to separately provide a shift operation device corresponding to the main transmission mechanism and the sub-transmission mechanism as in the conventional device, and the sub-transmission mechanism 11 and the main transmission mechanism 12 can be obtained by operating only one operation lever 82. Simultaneous shifting is possible, improving the operability of the driver and effectively shortening the shifting time.

  Further, since it is not necessary to switch the operation of the subtransmission mechanism 11 using an actuator such as an electric, pneumatic, or hydraulic actuator, it is possible to effectively suppress a decrease in reliability and an increase in cost due to the mounting of the actuator. Can do.

  In addition, this invention is not limited to the above-mentioned embodiment, In the range which does not deviate from the meaning of this invention, it can change suitably and can implement.

  For example, as shown in FIG. 8, the splitter link arm 46 is provided as a cylindrical projection 46a on one end surface of the splitter shift shaft 43 adjacent to the periphery, and the main link arm 48 is provided with a cylindrical projection. 48a may be provided on one end face of the main shift shaft 44 adjacent to the periphery. In this case, a guide member 90 that guides the link member 49 so as to be horizontally movable in the shift direction is provided, and a guide groove 49a that guides the protrusion 46a in the vertical direction is formed at one end of the link member 49 and at the other end. What is necessary is just to form the hole 49b which penetrates the protrusion part 48a rotatably.

  Further, the elastic member is not limited to the spring 71, and a plate spring, rubber, or the like may be applied as long as it is bent and deformed.

  Further, the transmission 10 is not limited to 6 forward speeds (1st speed L to 3rd speed H), but is 4 forward speeds (1st speed L to 2nd speed H), 8 forward speeds (1st speed L to 4th speed H), or The present invention can be widely applied to transmissions having more stages.

  Further, the transmission 10 is not limited to a manual transmission, and can be applied to a mechanical manual transmission (AMT) in which a shift operation and a selection operation are automated by an actuator or the like.

DESCRIPTION OF SYMBOLS 10 Transmission 11 Sub transmission mechanism 12 Main transmission mechanism 41 1st shift shaft 42 2nd shift shaft 43 Shift shaft for splitters (Sub transmission shaft)
44 Main shift shaft (Main transmission shaft)
45 Shift lever for splitter (shift lever for auxiliary transmission)
46 Link arm for splitter (first protrusion)
47 Shift lever for main (shift lever for main transmission)
48 Main link arm (second protrusion)
49 Link member
50 Shift block for splitter (shift block for auxiliary transmission)
51-54 Main shift block (shift block for main transmission)
60 Main R / 1-speed connection mechanism 63 Reverse lever 82 Operation lever 70 Annular flange (flange)
71 Spring (elastic member)

Claims (6)

A transmission with a sub-transmission mechanism that simultaneously shifts the main transmission mechanism and the sub-transmission mechanism by operating the operation lever in the select direction and the shift direction,
A sub-transmission shaft that extends in the select direction on the sub-transmission mechanism side and rotates in response to an operation in the shift direction of the operation lever, and an upper end portion of the sub-transmission shaft is rotatably supported. A sub-shifting shift lever extending downward, an elastic member connecting the sub-shifting shaft and the sub-shifting shift lever, and the sub-shifting shift lever disposed below the sub-shifting shaft. A sub-shifting shift block that engages with the lower end of the main transmission mechanism, a rotatable main transmission shaft that extends in the select direction on the main transmission mechanism side, and extends downward from the main transmission shaft. A shift lever for main speed change that is provided and moves in the select direction by operation of the operation lever in the select direction, and is arranged in parallel in the select direction below the main speed change shaft. A plurality of main transmission shift blocks that engage with a lower end portion of the main transmission shift lever, a first protruding portion that protrudes from the auxiliary transmission shaft, and a second protrusion that protrudes from the main transmission shaft. A protrusion, and a connecting member having one end rotatably connected to the first protrusion and the other end rotatably connected to the second protrusion.
Regardless of which direction the auxiliary transmission shaft is rotated in the shift direction of the operating lever, the rotational force transmitted to the main transmission shaft via the connecting member is unidirectionally driven by the connecting member. Converted to rotate the main shift lever in only one direction,
The rotational force of the auxiliary transmission shaft is applied to the auxiliary transmission shift lever via the elastic member so that the synchronous mechanism on the auxiliary transmission mechanism side and the synchronizing mechanism on the main transmission mechanism side simultaneously start synchronous coupling. A transmission with a sub-transmission mechanism that is transmitted. A flange is formed on the auxiliary transmission shaft located between the main transmission shift lever and the first protrusion,
2. The transmission with a subtransmission mechanism according to claim 1, wherein one end portion of the elastic member is fixed to the flange and the other end portion is fixed to the main shift shift lever.   The transmission with a subtransmission mechanism according to claim 1 or 2, wherein the elastic member is a spring.   Among the plurality of main transmission shift blocks, the main transmission shift block that does not correspond to the movement direction of the main transmission shift fork to which the corresponding gear corresponds corresponds to the rod fixed to the main transmission shift block and one end of the rod. 4. The auxiliary shaft according to claim 1, wherein the sub shaft is connected to the shift shaft via a reversing mechanism having a rotatable reversing lever hinged to the rod and having the other end hinged to the shift shaft. A transmission with a transmission mechanism. The first protrusion is provided to be inclined at a predetermined angle toward the main transmission shaft from the auxiliary transmission shaft upward.
The second projecting portion is provided to be inclined at a predetermined angle toward the auxiliary transmission shaft from the main transmission shaft upward.
5. The speed change with a subtransmission mechanism according to claim 1, wherein one end of the connecting member is hinge-connected to an upper end of the first projecting portion and the other end is hinge-connected to an upper end of the second projecting portion. Machine. A guide member for guiding the connecting member so as to be horizontally movable in the shift direction;
The first projecting portion is provided on one end surface of the auxiliary transmission shaft adjacent to the periphery,
The second protrusion is provided adjacent to a peripheral edge on one end surface of the main transmission shaft.
The connecting member is formed with a guide groove for guiding the first protrusion in the vertical direction at one end and a hole for rotatably inserting the second protrusion at the other end. A transmission with a subtransmission mechanism according to any one of the above.