JP6935808B2 - Shift mechanism and transmission - Google Patents

Description

The present disclosure relates to a shift mechanism and a transmission.

Conventionally, as a shift mechanism, there is a barrel type speed change mechanism described in Patent Document 1. This barrel-type speed change mechanism includes a barrel having a cam groove formed on the outer peripheral surface and an actuator that rotationally drives the barrel, and shifts gears by moving a shift fork along the cam groove by rotating the barrel. This barrel type transmission mechanism selectively switches between transmission and disconnection of rotational power between transmission gears adjacent to each other on the same axis by using a dog clutch including a dog and a dog sleeve.

Japanese Unexamined Patent Publication No. 2009-180342

In a vehicle equipped with the barrel type transmission mechanism, if the vehicle is stopped without downshifting, the vehicle will stop while maintaining the gear stage, and as the next process, the operation of returning the gear stage to neutral is performed. Alternatively, it is necessary to shift to the first gear in preparation for starting. Against this background, in the barrel type transmission mechanism, the fork shaft (shift fork) is moved along the cam groove of the shift barrel to shift gears, so that shifts must be performed one step at a time during downshifts and upshifts. Therefore, it is difficult to quickly and easily perform the desired shift.

Therefore, an object of the present disclosure is to provide a shift mechanism and a transmission which can reliably perform jump shift, that is, shift to a gear stage farther than one gear, and have excellent shift operability.

In order to solve the above problems, the shift mechanism according to the present disclosure includes a rotating member, two or more transmission members, and a plurality of gears, and the transmission member is movable in the axial direction to the rotating member. Each of the transmission member and the gear has a dog tooth, and when the dog tooth of the transmission member and the dog tooth of the gear mesh with each other, the transmission member and the gear are engaged with each other. Power is transmitted between the gears to rotatably support the transmission member, and the transmission member is moved in the axial direction so that the transmission member can be moved by the dog teeth of the transmission member of the gear. Two or more translational members that are selectively positioned at an engaging position that meshes with the dog tooth and an open position where the dog tooth of the transmission member is located at an axially spaced distance from the dog tooth of the gear. When the barrel rotates, the barrel is rotatable and has a cam groove on the outer peripheral side in which the pin of the translation member is housed, and the width of the cam groove in the axial direction is changed. A groove that selectively realizes a first state in which the translation member and the transmission member move in the axial direction and a second state in which the translation member and the transmission member do not move in the axial direction when the barrel rotates. It further includes a width variation mechanism.

Further, the transmission according to the present disclosure includes a shift mechanism according to the present disclosure, a counter gear that meshes with each of the gears, and a rotating shaft that executes power transmission between the counter gears.

According to these disclosures, the groove width variation mechanism can vary the axial width of the cam groove, and in the second state, the pin does not come into contact with the side surface of the cam groove and the movement of the pin is the cam groove. It is possible to realize a free state that is not regulated on the side. Therefore, by rotating the barrel to the desired shift position in the second state and then selecting the first state, the desired gear stage can be executed without passing through the intervening gear stages, and the jump shift is surely and smoothly performed. Can be executed.

Further, in the shift mechanism of the present disclosure, the barrel may have a cam groove in which two or more of the pins are housed.

According to the above configuration, the number of cam grooves provided in the barrel can be reduced. Therefore, the barrel can be made compact, and the shift mechanism can be made compact.

According to the shift mechanism and the transmission according to the present disclosure, it is possible to reliably execute a jump shift, that is, a shift to a gear stage separated from one gear, and to improve the operability of the shift.

It is a front view which shows the main part of the transmission which concerns on one Embodiment of this disclosure. It is a front view corresponding to FIG. 1 in the state which the groove width variation mechanism realizes the 1st state. It is a figure explaining the movement in the cam groove of the 1st and 2nd pins when a barrel rotates in a 1st state. It is a figure explaining the position in the cam groove of the 1st and 2nd pins when a barrel rotates in a 2nd state. It is a front view explaining the shift mechanism of the modification. It is a front view explaining the shift mechanism of another modification.

Hereinafter, embodiments according to the present disclosure will be described in detail with reference to the accompanying drawings. When a plurality of embodiments and modifications are included in the following, it is assumed from the beginning that a new embodiment is constructed by appropriately combining the characteristic portions thereof. Further, in the following examples, the same components are designated by the same reference numerals in the drawings, and duplicate description will be omitted. In addition, the plurality of drawings include schematic views, and the dimensional ratios such as length, width, and height of each member do not always match between different drawings. Further, in the following description, a transmission capable of performing 4-speed shifting will be described as an example, but as is clear from the following description, the transmission may be capable of shifting to 5-speed or higher. , Reverse may be feasible. Execution of reverse can be easily realized by engaging the gear on the input side and the gear on the output side via a relay gear instead of directly engaging the gear. Further, among the components described below, the components not described in the independent claims indicating the highest level concept are arbitrary components and are not essential components.

FIG. 1 is a front view showing a main part of the transmission 1 according to the embodiment of the present disclosure. As shown in FIG. 1, the transmission 1 includes a shift mechanism 10, first to fourth counter gears 81 to 84, and an input shaft 85 as an example of a rotating shaft. Further, the shift mechanism 10 has an output shaft 15 as a rotating member, a barrel 20, a first fork 25, a second fork 30, a first dog ring 35, a second dog ring 40, and a groove width fluctuation mechanism 45. The first and second doglings 35,40 constitute two or more transmission members, and the first and second forks 25,30 constitute two or more translational members.

The barrel 20 has a barrel body 21, a cylindrical first cam groove defining member 22, and a cylindrical second cam groove defining member 23. The central axis of the barrel body 21 extends in a direction substantially parallel to the axial direction of the output shaft 15. Further, the barrel body 21 is spline-fitted with the inner peripheral surfaces of the first and second cam groove defining members 22 and 23, respectively, and the barrels of the first and second cam groove defining members 22 and 23 are respectively. It is movable relative to the main body 21 in the axial direction. The first and second cam groove defining members 22, 23 need only be movable relative to the barrel body 21, and the barrels of the first and second cam groove defining members 22, 23, respectively. The main body 21 may be engaged by serration fitting, key fitting, or the like instead of spline fitting.

The first cam groove defining member 22 and the second cam groove defining member 23 are arranged at intervals in the axial direction of the barrel body 21. A single cam groove 38 is formed between the first cam groove defining member 22 and the second cam groove defining member 23. An actuator (not shown) having an electric motor or the like as a drive source is connected to the barrel main body 21, and the barrel main body 21 is rotated by rotational power applied from the actuator.

The first fork 25 has a first fork shaft 26 and a first shift fork 27. The first fork shaft 26 extends along the axial direction of the barrel body 21, and the first shift fork 27 is fixed to the first fork shaft 26 in the radial direction from the first fork shaft 26 to the first fork shaft 26. Extends to. The first shift fork 27 includes a pair of holding portions 27a. A first shift head (not shown) is integrally attached to the first fork shaft 26, and a first pin (29 in FIGS. 3 and 4) provided at the tip of the first shift head is shown. ) Is fitted in the cam groove 38.

The second fork 30 has a second fork shaft 31 and a second shift fork 32. The second fork shaft 31 extends along the axial direction of the barrel body 21, and the second shift fork 32 is fixed to the second fork shaft 31 in the radial direction from the second fork shaft 31 to the second fork shaft 31. Extends to. The second shift fork 32 includes a pair of holding portions 32a. A second shift head 33 is integrally attached to the second fork shaft 31, and a second pin 34 provided at the tip of the second shift head 33 is spaced from the first pin 29 in the cam groove 38. It is fitted in the left state.

The first dog ring 35 is an annular member and is fitted on the output shaft 15. The first dog ring 35 is spline-fitted, serrated-fitted, or key-fitted with the output shaft 15, rotates synchronously with the output shaft 15, and is movable relative to the output shaft 15 in the axial direction. .. A groove is provided on the outer peripheral surface of the first dog ring 35. The inner portions of the pair of holding portions 27a of the first shift fork 27 are fitted into the grooves of the first dog ring 35, and hold the first dog ring 35 rotatably.

A first dog tooth 35a is formed at one end of the first dog ring 35 in the axial direction. Further, a first gear 50 is arranged on one side of the first dog ring 35 in the axial direction. The 1st gear 50 is fixed to the output shaft 15 via a bearing, for example, and is rotatably fixed to the output shaft 15 by this. The first gear 50 has a first dog tooth 50a at the other end in the axial direction. The 1st speed dog tooth 50a meshes with the 1st dog tooth 35a when the 1st dog ring 35 moves relative to one side in the axial direction with respect to the output shaft 15, and the 1st speed dog tooth 50a becomes the 1st dog tooth 35a. When meshed, the first dog ring 35 can rotate synchronously with the first gear 50.

Further, a second dog tooth 35b is formed at an end portion of the first dog ring 35 on the other side in the axial direction. Further, a third gear 52 is arranged on the other side of the first dog ring 35 in the axial direction. The third gear 52 is fixed to the output shaft 15 via a bearing, for example, and is rotatably fixed to the output shaft 15 by this. The third-speed gear 52 has a third-speed dog tooth 52a at one end in the axial direction. The 3rd speed dog tooth 52a meshes with the 2nd dog tooth 35b when the 1st dog ring 35 moves relative to the other side in the axial direction with respect to the output shaft 15, and the 3rd speed dog tooth 52a becomes the 2nd dog tooth 35b. When meshed, the first dog ring 35 can rotate synchronously with the third gear 52.

The second dog ring 40 is an annular member and is fitted on the output shaft 15. The second dog ring 40 is spline-fitted, serrated-fitted, or key-fitted with the output shaft 15, rotates synchronously with the output shaft 15, and is movable relative to the output shaft 15 in the axial direction. .. A groove is provided on the outer peripheral surface of the second dog ring 40. The inner portions of the pair of holding portions 32a of the second shift fork 32 are fitted into the grooves of the second dog ring 40, and hold the second dog ring 40 rotatably.

A third dog tooth 40a is formed at one end of the second dog ring 40 in the axial direction. A second gear 51 is arranged on one side of the second dog ring 40 in the axial direction. The second gear 51 is rotatably fixed to the output shaft 15 on the other side of the third gear 52 in the axial direction with a distance from the third gear 52. The second gear 51 is fixed to the output shaft 15 via a bearing, for example. The second gear 51 has a second dog tooth 51a at the other end in the axial direction. The second-speed dog tooth 51a meshes with the third dog tooth 40a when the second dog ring 40 moves relative to one side in the axial direction with respect to the output shaft 15, and the second-speed dog tooth 51a becomes the third dog tooth 40a. When meshed, the second dog ring 40 can rotate synchronously with the second gear 51.

Further, a fourth dog tooth 40b is formed at the other end of the second dog ring 40 in the axial direction. Further, a fourth gear 53 is arranged on the other side of the second dog ring 40 in the axial direction. The 4-speed gear 53 is fixed to the output shaft 15 via a bearing, for example, and is rotatably fixed to the output shaft 15 by this. The 4-speed gear 53 has a 4-speed dog tooth 53a at one end in the axial direction. The 4-speed dog tooth 53a meshes with the 4th dog tooth 40b when the 2nd dog ring 40 moves relative to the other side in the axial direction with respect to the output shaft 15, and the 4-speed dog tooth 53a becomes the 4th dog tooth 40b. When meshed, the second dog ring 40 can rotate synchronously with the fourth gear 53.

The groove width fluctuation mechanism 45 moves the first and second cam groove defining members 22, 23 in the axial direction on the principle of a ball screw. Specifically, each of the first and second cam groove defining members 22 and 23 has annular grooves 22a and 23a extending in the circumferential direction, and the groove width fluctuation mechanism 45 includes a motor 46 as an actuator and a first nut. 47 and a second nut 48 are included.

The first nut 47 has a female screw that is screwed into a male screw 46b provided on the rotating shaft 46a of the motor 46, and a protruding portion 47a that fits into the annular groove 22a. The protruding portion 47a of the first nut 47 is fixed to, for example, the first cam groove defining member 22, and the first nut 47 does not rotate with respect to the rotation shaft 46a. Further, the second nut 48 has a female screw screwed into the male screw 46b provided on the rotating shaft 46a of the motor 46, and a protruding portion 48a fitted into the annular groove 23a. The protruding portion 48a of the second nut 48 is fixed to, for example, the second cam groove defining member 23, and the second nut 48 does not rotate with respect to the rotation shaft 46a.

As shown in FIG. 1, the outer diameter and the number of teeth of each gear 50 to 53 are the largest in the 1st gear 50, and are the 2nd gear 51, the 3rd gear 52, the 4th gear 53, and the high speed gear. Therefore, it is gradually getting smaller. Further, the first counter gear 81 meshes with the first gear 50, the second counter gear 82 meshes with the second gear 51, and the third counter gear 83 meshes with the third gear 52. A fourth counter gear 84 meshes with the fourth gear 53. The fourth counter gear 84 has the largest outer diameter and number of teeth of each counter gear 81 to 84, and is a counter gear that meshes with the third counter gear 83, the second counter gear 82, the first counter gear 81, and the low speed gear. It gradually becomes smaller as it becomes. Each of the counter gears 81 to 84 is fitted and fixed to the input shaft 85. The input shaft 85 extends substantially parallel to the output shaft 15.

The shift of the transmission 1 is executed by using an operation unit that allows the driver to select a jump shift. For example, a push switch can be mentioned as such an operation unit, and by selecting a desired switch, it may be possible to select a jump shift or a shift of up or down one step at a time. Alternatively, such an operation unit can be realized by a shift lever and a push button. For example, by pressing the push button provided on the upper part of the shift lever, a jump shift can be selected, but the push button is not pressed. At that time, a shift that goes up or down one step at a time may be selected.

The control signal input by the operation unit is input to the ECU (Electronic Control Unit). The ECU controls an actuator such as a motor that rotates the barrel body 21 and a motor 46 based on the control signal to realize a desired shift.

The vehicle equipped with the transmission of the present disclosure may have an operation unit for increasing or decreasing the speed change step by step at a position different from the operation unit for selecting jump shift. Further, such an operation unit may include a paddle switch provided on the steering wheel, and the paddle switch may include an upshift switch and a downshift switch. Then, each time the upshift switch and the downshift switch are operated, the shift may be increased or decreased by one step.

Next, the operation of the transmission 1 will be described with reference to FIGS. 2 to 4 as an example of performing a shift from neutral to 3rd speed. First, it is assumed that the driver selects an operation of sequentially increasing the gears one step at a time from neutral to the third speed by using the operation unit. Then, the ECU controls the motor 46 in order to realize the first state. Then, under the control, the rotation shaft 46a of the motor 46 rotates in the direction indicated by the arrow C in FIG. 2, and the first and second cam groove defining members 22, 23 are moved from the first and second nuts 47, 48. Receives forces in the direction of approaching each other. Then, in the first and second cam groove defining members 22, 23, the width of the cam groove 38 is slightly larger than the diameter of the first and second pins 29, 34, and the cam groove 38 is formed by the rotation of the barrel body 21. Move to a position where the movement of the first and second pins 29,34 can be regulated.

After that, an actuator such as a motor that rotates the barrel body 21 operates to rotate the barrel body 21 in the direction indicated by the arrow D in FIG. FIG. 3 is a diagram illustrating the movement of the first and second pins 29, 34 in the cam groove 38 due to the rotation of the barrel body 21. In the initial state shown in FIG. 3A, the first and second pins 29 and 34 are both present in the neutral position. When the first pin 29 is in the neutral position, the first dogling 35 is axially spaced on both the first and third gears 52 and the second pin 34 is in neutral. When present in position, the second dogling 40 is axially spaced into both the second gear 51 and the fourth gear 53. After that, when the barrel body 21 rotates, as shown in FIG. 3B, the second pin 34 exists in the neutral position, while the first pin 29 moves from the neutral position to the right side on the paper surface.

Then, referring to FIG. 2, the first fork 25 on the right side of the paper moves to the right side as the first pin 29 moves to the right side, so that the first doggling 35 moves to the right side and the first dog ring 35 moves to the right side. The first dog tooth 35a of the dog ring 35 meshes with the first dog tooth 50a of the first gear 50. As a result, the rotational power of the input shaft 85 is transmitted to the output shaft 15 via the first counter gear 81, the first gear 50, and the first dog ring 35, and the shift to the first gear is executed.

After that, when the barrel body 21 is further rotated, the first and second pins 29 and 34 are in the neutral position shown in FIG. 3 (c) due to the regulation on the side surface of the cam groove 38, and then in FIG. 3 (d). It becomes the 2nd speed position shown in. In the second speed position, the first pin 29 is located in the neutral position, while the second pin 34 moves to the right. By moving the second pin 34 to the right side, the second fork 30 shown in FIG. 2 moves to the right side of the paper surface, and as a result, the third dog tooth 40a of the second dog ring 40 is moved to the second speed of the second gear 51. It meshes with the dog tooth 51a. By the meshing of the dog teeth, the rotational power of the input shaft 85 is transmitted to the output shaft 15 via the second counter gear 82, the second gear 51, and the second dog ring 40, and the shift to the second gear is executed. ..

After that, when the barrel is further rotated, the first and second pins 29, 34 are in the neutral position shown in FIG. 3 (e) due to the regulation on the side surface of the cam groove 38, and then are shown in FIG. 3 (f). It will be in the 3rd speed position. In the 3rd speed position, the 2nd pin 34 is located in the neutral position, while the 1st pin 29 moves to the left side on the paper surface. By moving the first pin 29 to the left side, the first fork 25 shown in FIG. 2 moves to the left side of the paper surface, and as a result, the second dog teeth 35b of the first dog ring 35 move to the third speed of the third gear 52. It meshes with the dog tooth 52a. By the meshing of the dog teeth, the rotational power of the input shaft 85 is transmitted to the output shaft 15 via the third counter gear 83, the third gear 52, and the first dog ring 35, and the shift to the third gear is executed. ..

On the other hand, assuming that the user selects a jump shift from the 1st speed to the 3rd speed using the operation unit, the ECU controls the motor 46 to realize the second state. Then, under the control, the rotation shaft 46a of the motor 46 rotates in the direction indicated by the arrow A in FIG. 1, and the first and second cam groove defining members 22, 23 are moved from the first and second nuts 47, 48. Receives forces in directions away from each other. Then, as shown in FIG. 1, the first and second cam groove defining members 22, 23 move to a position where the cam groove 38 cannot regulate the movements of the first and second pins 29, 34 due to the rotation of the barrel body 21. do. The operation is shown in FIGS. 4A and 4B. In FIG. 4A, as in FIG. 3B, the second pin 34 is present at the neutral position, while the first pin 29 is present at the position where the first speed is realized. Further, in the state shown in FIG. 4B, the width of the cam groove 38 is widened, and the movements of the first and second pins 29, 34 cannot be regulated by the side surface of the cam groove 38.

Subsequently, the position of the barrel body 21 shown in FIG. 4C, that is, the first state is temporarily selected by the control of the actuator by the ECU that rotates the barrel body 21 in the direction shown by the arrow B in FIG. If so, it will rotate to the position where the 3rd speed is realized. After that, the ECU actually controls the motor 46 to realize the first state. Then, under the control, the rotation shaft 46a of the motor 46 rotates in the direction indicated by the arrow C in FIG. 2, and the first and second cam groove defining members 22, 23 have the widths of the first and second cam grooves 38. Slightly larger than the diameter of the 2 pins 29,34, the rotation of the barrel body 21 moves the cam groove 38 to a position where the movements of the 1st and 2nd pins 29,34 can be regulated. Under the control of this ECU, as shown in FIG. 4D, the first pin 29 moves to the left side by the force from the side surface of the cam groove 38, so that the third speed is executed. With such control, a jump shift from the 1st speed to the 3rd speed without passing through the 2nd speed is executed.

As described above, the shift mechanism 10 according to the present disclosure includes an output shaft (rotating member) 15, first and second doglings (two or more transmission members) 35,40, and four gears (plurality of gears) 50 to 53. To be equipped. Further, each of the first and second doglings 35 and 40 is engaged with the output shaft 15 so as to rotate synchronously in a state of being movable in the axial direction of the output shaft 15. Further, the first and second dog rings 35, 40 and the gears 50 to 53 have dog teeth 35a, 35b, 40a, 40b, 50a, 51a, 52a, 53a. Further, when the dog teeth 35a, 35b, 40a, 40b of the first and second dog rings 35, 40 and the dog teeth 50a, 51a, 52a, 53a of the gears 50 to 53 mesh with each other, the first and second dog rings 35, Power is transmitted between 40 and each of the gears 50 to 53. Further, the shift mechanism 10 rotatably supports the first and second doglings 35 and 40, and moves the first and second doglings 35 and 40 in the axial direction to move the first and second doglings 35 and 40 in the axial direction. The 40 is engaged with the dog teeth 35a, 35b, 40a, 40b meshing with the dog teeth 50a, 51a, 52a, 53a of the gears 50 to 53, and the dog teeth 35a, 35b of the first and second dog rings 35,40. , 40a, 40b are selectively positioned in open positions positioned axially spaced apart from the dog teeth 50a, 51a, 52a, 53a of the gears 50 to 53, the first and second forks 25,30 ( Two or more translational members). Further, the shift mechanism 10 includes a barrel body 21 that is rotatable and has a cam groove 38 on the outer peripheral side in which the pins 29, 34 of the first and second forks 25, 30 are accommodated. Further, the shift mechanism 10 changes the width of the cam groove 38 in the axial direction so that when the barrel body 21 rotates, the first and second forks 25, 30 and the first and second dog rings 35, 40 are shafts. A first state in which the barrel body 21 moves in the direction and a second state in which the first and second forks 25, 30 and the first and second dog rings 35, 40 do not move in the axial direction when the barrel body 21 rotates are selectively selected. The groove width fluctuation mechanism 45 to be realized is provided. Further, the transmission 1 according to the present disclosure is an input shaft (rotation) that executes power transmission between the shift mechanism 10, counter gears 81 to 84 that mesh with the gears 50 to 53, and counter gears 81 to 84. Axis) 85 and.

Therefore, the groove width fluctuation mechanism 45 can change the axial width of the cam groove 38, and in the second state, the pins 29, 34 do not come into contact with the side surface of the cam groove 38, and the movement of the pins 29, 34 However, it is possible to realize a free state in which the side surface of the cam groove 38 is not regulated. Therefore, after rotating the barrel body 21 to a desired shift position in the free state (second state), the desired gear stage can be freely selected by selecting the first state, and the jump shift is surely and smoothly performed. Can be executed.

Further, in the shift mechanism 10, the barrel body 21 may have a cam groove 38 in which two or more pins 29, 34 are housed.

According to the above configuration, the number of cam grooves 38 provided in the barrel body 21 can be reduced. Therefore, the barrel body 21 can be compactly configured, and the shift mechanism 10 can be compactly formed.

The present disclosure is not limited to the above-described embodiment and its modifications, and various improvements and changes can be made within the scope of the claims of the present application and the equivalent scope thereof.

For example, in the above embodiment, the case where the barrel main body 21 has only one cam groove 38 has been described, but the barrel may have a plurality of cam grooves. Further, the case where the barrel main body 21 has a cam groove 38 in which two pins 29 and 34 are fitted has been described, but the barrel has a cam groove in which only one pin is fitted. May be good. Alternatively, the barrel may have a cam groove in which three or more pins are fitted, in which case the desired jump shift can be easily performed in a 6-speed or higher transmission. Needless to say, a 6-speed or higher transmission has 6 or higher gears.

Further, the jump shift from the 1st speed to the 3rd speed has been described. However, when N is a natural number and M is a natural number 2 or more away from N, a jump shift from N speed to M speed or a jump shift from M speed to N speed may be executed. Further, when N is a natural number, a jump shift from reverse to N speed without passing through neutral may be executed.

Further, the case where the rotating member in which the first and second dog rings 35 and 40 rotate synchronously is the output shaft 15 has been described. However, the rotating member in which the first and second doglings rotate synchronously may be an input shaft. In this case, when the power of the input shaft is transmitted to the gear having the largest number of teeth shown in FIG. 1, the fourth speed is executed, and when the power of the input shaft is transmitted to the gear shown by 51. 3rd gear is executed. Further, when the power of the input shaft is transmitted to the gear shown by 52 in FIG. 1, the second speed is executed, and when the power of the input shaft is transmitted to the gear shown by 53, the first speed is executed.

Further, a case where the groove width fluctuation mechanism 45 moves the first and second cam groove defining members 22 and 23 in the axial direction toward each other or in the direction away from each other by using the principle of the ball screw has been described. However, the translation member may use other actuators to move the first and second cam groove defining members in the axial direction of the rotating member in a direction approaching each other or in a direction away from each other.

Specifically, as shown in FIG. 5, the groove width fluctuation mechanism 145 may include two linear solenoids 170 and 180. Further, the protruding portion 175a of the force applying member 175 fixed to the telescopic shaft 170a of one of the linear motion solenoid 170 may be fitted and fixed in the annular groove 22a of the first cam groove defining member 22. Further, the protruding portion 185a of the force applying member 185 fixed to the telescopic shaft 180a of the other linear motion solenoid 180 may be fitted and fixed in the annular groove 23a of the first cam groove defining member 23. Then, by controlling the expansion and contraction of the expansion and contraction shafts 170a and 180a of the linear solenoids 170 and 180 in the directions indicated by the arrows E and F by the ECU, the movement of the first and second cam groove defining members 22 and 23 in the axial direction is realized. You may.

As in this modification, when the linear motion solenoids 170 and 180 are used to move the first and second cam groove defining members 22 and 23 by expanding and contracting the expansion and contraction shafts 170a and 180a, the first and second cam grooves are moved. It is easy to increase the moving speed of the defining members 22 and 23, and it is easy to improve the responsiveness of the first and second cam groove defining members 22 and 23. Therefore, it is possible to realize a smooth jump shift with better responsiveness.

Alternatively, as shown in FIG. 6, the groove width fluctuation mechanism 245 may include a barrel 260 having the first and second cam grooves 255a and 255b, and an actuator 280 such as a motor for rotating the barrel 260. Further, the protruding portion 222a of the first cam groove defining member 222 may be fitted into the first cam groove 255a, and the protruding portion 223a of the second cam groove defining member 223 may be fitted into the second cam groove 255b. Then, the barrel 260 may be rotated in the direction indicated by the arrow G by the actuator 280 to rotate the first and second cam groove defining members 222 and 223 in the axial direction.

Alternatively, as the groove width fluctuation mechanism, the first and second cam groove defining members may be moved in the axial direction by using a hydraulic cylinder, a rack and pinion mechanism, or the like, and any other known mechanism capable of realizing linear movement may be used. The first and second cam groove defining members may be used to move the first and second cam groove defining members in the axial direction.

1 transmission, 10 shift mechanism, 15 output shaft (rotating member), 20 barrel, 25 1st fork, 29 1st fork pin, 30 2nd fork, 34 2nd fork pin, 35 1st doggling, 35a 1st 1 Dogling 1st Dog Tooth, 35b 1st Dogling 2nd Dog Tooth, 38 Cam Groove, 40 2nd Dogling, 40a 2nd Dogling 3rd Dog Tooth, 40b 2nd Dogling 4th Dog Tooth, 45,145 , 245 Groove width fluctuation mechanism, 50 1st gear, 50a 1st gear, 51 2nd gear, 51a 2nd dog tooth, 52 3rd gear, 52a 3rd gear, 53 4th gear, 53a 4th dog tooth , 81 1st counter gear, 82 2nd counter gear, 83 3rd counter gear, 84 4th counter gear, 85 Input shaft (rotary shaft), 170,180 Linear solenoid.

Claims (3)

With rotating members
With two or more transmission members
With multiple gears,
The transmission member is engaged with the rotating member so as to rotate synchronously in a state of being movable in the axial direction.
Each of the transmission member and the gear has a dog tooth, and when the dog tooth of the transmission member and the dog tooth of the gear mesh with each other, power is transmitted between the transmission member and the gear.
By rotatably supporting the transmission member and moving the transmission member in the axial direction, the transmission member is provided with an engaging position in which the dog teeth of the transmission member mesh with the dog teeth of the gear. Two or more translational members that selectively position the dog teeth of the transmission member in open positions located at intervals in the axial direction with respect to the dog teeth of the gear.
A barrel that is rotatable and has a cam groove on the outer peripheral side that accommodates the pins of the translation member.
By varying the axial width of the cam groove, the translation member and the transmission member move in the axial direction when the barrel rotates, and the translation occurs when the barrel rotates. A groove width fluctuation mechanism that selectively realizes a second state in which the member and the transmission member do not move in the axial direction, and
A shift mechanism further equipped with. The shift mechanism according to claim 1, wherein the barrel has the cam groove in which two or more of the pins are housed. The shift mechanism according to claim 1 or 2,
A counter gear that meshes with each of the gears
A rotating shaft that transmits power to and from the counter gear,
A transmission equipped with.

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