JP2022146837A - Meshing clutch mechanism, frictional clutch mechanism, and two-level shift device - Google Patents

Abstract

To provide a meshing clutch mechanism capable of preventing torque from being interrupted during gear change and capable of transmitting coast torque during a low-speed stage, a frictional clutch mechanism, and a two-level shift device.SOLUTION: In a meshing clutch mechanism, a meshing clutch has a lock function at a low-speed stage and a frictional clutch transmits torque at a high-speed stage. Both the high-speed stage and the low-speed stage can transmit coast torque, and seamless gear change is possible up and down. Torque transmission in both directions of drive and coast is possible and, when used for an electric vehicle, for example, reverse torque transmission is possible in backward driving and in an energy regeneration mode. Moreover, with a one-way clutch function, torque is not interrupted during gear change to the high-speed stage, and smooth gear change is possible. When used at the high-speed stage, the meshing clutch is used for the low-speed stage, so that loss due to drag torque of the frictional clutch does not occur, which improves efficiency.SELECTED DRAWING: Figure 32

Description

TECHNICAL FIELD The present invention relates to dog clutch mechanisms, friction clutch mechanisms, and two-speed transmissions.

A conventional two-speed transmission has been proposed in which a planetary gear unit as disclosed in Japanese Patent Application Laid-Open No. 2002-300002 is characterized by reducing the rotational speed of a motor or maintaining it at a constant speed. However, there is a problem that the torque is cut off because the gear once passes through the neutral when shifting to a high gear.
In addition, as shown in Patent Document 2, there has been proposed a device for increasing the power consumption efficiency and reducing the shift shock perceivable by the driver by allocating the low-speed stage and the high-speed stage by de-energizing and energizing electromagnetic coils. there is However, in this device, in order to prevent double engagement, it is necessary to provide a neutral in which both the low-speed and high-speed clutches are not engaged. There was a problem that torque could not be transmitted.

JP 2016-017632 A Japanese Patent No. 6545921

The problems to be solved are that the torque is interrupted at the time of shifting and that the coast torque cannot be transmitted at the low speed stage.

The present invention relates to the invention of a variable speed clutch mechanism for shifting a two-speed transmission, in which the low speed stage is free-coupled by a mesh clutch and the high speed stage is loosely coupled by a friction clutch, and a planetary gear or a biaxial gear utilizing the variable speed clutch mechanism. 2-speed transmission. The shape of the dog clutch of the low-speed stage is a first and a second dog clutch facing each other with a height H from the tooth bottom to the tooth tip, and the drive torque transmitting tooth flank of the first dog clutch is parallel to the rotation axis. Alternatively, the second dog clutch is slightly inclined in the direction in which the second dog clutch is pulled in by the meshing torque, and an inclined surface is provided that connects the tooth bottom of the first dog clutch and the point of height X from the tooth bottom of the drive tooth surface, When the second dog clutch meshes with the drive tooth surface of the first dog clutch from the slope, it is lifted by X from the tooth bottom. The second dog clutch has a shape that rises to a predetermined height X from the tooth bottom of the first dog clutch. Note that X is a positive number including 0.
Further, the coast tooth flank of the first dog clutch extends from the tooth bottom to the position X-ΔX, parallel to the rotation axis, in the direction in which the second dog clutch is engaged by engagement torque, or in the second dog clutch at the friction angle or less. It has a tooth flank in the direction in which the clutch disengages, and the tooth flank has a shape inclined in the range of 45 to 80 degrees with respect to the rotation axis from the position of X-ΔX to the tip. Note that ΔX includes negative values.

The drive tooth flank of the second dog clutch has an angle with respect to the rotation axis that matches the tooth flank on the tip side of X from the tooth bottom of the first dog clutch, and the coast tooth flank is X from the tooth bottom of the first dog clutch. The tooth flank of -ΔX or less and the shape having the same angle with respect to the axis of rotation.

Furthermore, in the low-speed stage, the elastic body presses the second dog clutch in the direction of meshing with the first dog clutch, and the drive torque causes the second dog clutch to rise by ΔX from the tooth bottom of the first dog clutch due to the slope effect. The dog clutch is pressed against the tooth bottom of the first dog clutch when the meshing surface moves due to the application of coast torque, and the second dog clutch has a tooth surface of X-ΔX or less from the tooth bottom of the first dog clutch. to engage. Therefore, the first and second dog clutches can transmit not only drive torque but also coast torque.

When shifting to a high-speed stage, the shift mechanism that moves the second dog clutch maintains the second dog clutch at a position X above the tooth bottom of the first dog clutch by drive torque, and the second dog clutch 5 coasts. To prevent a second dog clutch from moving in the tooth bottom direction of a first dog clutch even if it moves in the direction.

At the same time or a little later than the operation of the shift mechanism, the high-speed gear friction clutch is engaged. When the high-speed friction clutch starts to be engaged, the torque applied to the first and second dog clutches decreases in the drive torque direction and shifts to coast torque. At this time, due to the action of the shift mechanism, the second dog clutch disengages further from the tooth bottom in the meshing direction from the position of X. The first dog clutch comes into contact with a slope inclined between 45 degrees and 80 degrees with respect to the first rotation axis, which is a slope from the tooth bottom to the tooth tip from X-ΔX. By the action of the slope, the second dog clutch is urged in the disengagement direction with respect to the first dog clutch, and the engagement of the first and second dog clutches is released. Then, the transmission of drive torque shifts to the friction clutch of the high-speed stage. Therefore, torque is transmitted from both the dog clutch and the friction clutch to the non-driving body when shifting from the low speed stage to the high speed stage, and the torque is transmitted smoothly without interruption when shifting from the dog clutch to the friction clutch.

Further, if the shift mechanism quickly drives the second dog clutch, the second dog clutch can be disengaged directly without coming into contact with the coast tooth flank of the first dog clutch.

Furthermore, when the friction clutch of the high-speed stage starts to be engaged and the meshing surface pressure of the drive tooth surfaces of the first and second dog clutches decreases or becomes zero, the shift mechanism is driven in order to quickly release the meshing of the dog clutch. A member that couples with the actuator and a member that drives the second dog clutch are coupled with an elastic body, and during upshifting, the member that couples with the actuator is moved to the high speed stage when the drive tooth surface of the dog clutch is still engaged. position, the elastic body is deformed to accumulate potential energy, the coupling force of the high-speed stage friction clutch increases, and when the surface pressure on the drive tooth surface of the dog clutch decreases or disappears, the elastic body instantly It is also possible to employ a mechanism in which the member for driving the second dog clutch is driven by the potential energy of the body member, and the meshing of the first and second dog clutches is instantaneously released.

The two-speed transmission of the present invention uses a dog clutch mechanism having the above-mentioned special function for the low speed stage of a planetary gear train or a two-shaft gear train, and a friction clutch mechanism for the high speed stage. , a two-speed transmission capable of shifting without interrupting drive torque during shifting.

The present invention enables torque transmission in both directions of driving and coasting when the gear is in a low speed stage. In addition, the one-way clutch function prevents torque loss when shifting to high speed gears and enables smooth shifting. Furthermore, when used in a high-speed stage, since a dog clutch is used in a low-speed stage, loss due to drag torque of the friction clutch does not occur and efficiency increases.

4 is a main cross-sectional view of the first dog clutch mechanism; FIG. FIG. 4 is a cross-sectional view of teeth of the first and second dog clutches meshing in a positive torque direction; FIG. 4 is a cross-sectional view of a state in which the first and second dog clutches are engaged in the direction of negative torque; FIG. 5 is a cross-sectional view when the first and second dog clutches are disengaged; FIG. 4 is a main cross-sectional view of a second dog clutch mechanism; FIG. 4 is a main cross-sectional view of a third dog clutch mechanism; FIG. 11 is a main cross-sectional view of a fourth dog clutch mechanism; 4 is a cross-sectional view of the first shift mechanism; FIG. It is a sectional view of a second shift mechanism. FIG. 11 is a main cross-sectional view of a fifth dog clutch mechanism; FIG. 11 is a main cross-sectional view of a sixth dog clutch mechanism; It is a sectional view of a third shift mechanism. It is a sectional view of a third shift mechanism. FIG. 4 is a cross-sectional view of the third shift mechanism during shifting operation; It is a cross-sectional view of the third shift mechanism after shifting. FIG. 11 is a main cross-sectional view of a fourth shift mechanism; FIG. 11 is a main cross-sectional view of a seventh dog clutch mechanism; FIG. 11 is a main cross-sectional view of an eighth dog clutch mechanism; It is a sectional view of a fifth shift mechanism. It is a sectional view of a fifth shift mechanism. FIG. 11 is a cross-sectional view of the fifth shift mechanism during shifting operation; FIG. 11 is a cross-sectional view of the fifth shift mechanism after shifting; FIG. 11 is a cross-sectional view of a sixth shift mechanism; FIG. 11 is a main cross-sectional view of a ninth dog clutch mechanism; FIG. 11 is a main cross-sectional view of a tenth dog clutch mechanism; FIG. 11 is a main cross-sectional view of an eleventh dog clutch mechanism; FIG. 11 is a main cross-sectional view of a twelfth dog clutch mechanism; FIG. 21 is a main cross-sectional view of a thirteenth dog clutch mechanism; FIG. 21 is a main cross-sectional view of a fourteenth dog clutch mechanism; FIG. 20 is a main cross-sectional view of a fifteenth dog clutch mechanism; FIG. 21 is a main cross-sectional view of a sixteenth dog clutch mechanism; It is a main cross-sectional view of a third A two-speed transmission. FIG. 3 is a main cross-sectional view of a third B two-speed transmission; Fig. 2 is a main cross-sectional view of the first A two-speed transmission; FIG. 4 is a main cross-sectional view of the first B two-speed transmission; It is a main cross-sectional view of a fifth two-speed transmission. FIG. 11 is a main cross-sectional view of a sixth two-speed transmission;

01a shown in FIG. 1 is a main sectional view of the first dog clutch mechanism. Reference numerals 3 and 5 shown in FIG. 2 denote the shapes of the teeth of the first and second dog clutches (hereinafter referred to as dog clutches), showing the shape and the state in which both mesh in the direction of positive torque (hereinafter referred to as drive torque). . FIG. 3 shows a state in which the first and second dog clutches 3 and 5 are meshed in the direction of negative torque (hereinafter referred to as coast torque). FIG. 4 shows a view when the first and second dog clutches 3, 5 are disengaged. 01b shown in FIG. 5 is the second dog clutch mechanism, 01c shown in FIG. 6 is the third dog clutch mechanism, and 01d shown in FIG. 7 is the main sectional view of the fourth dog clutch mechanism.
07a shown in FIG. 8 is a first shift mechanism, and 07b shown in FIG. 9 is a second shift mechanism. 1, 3, 4, and 5 is a dog clutch that takes charge of the low speed stage of the two-speed transmission.

Reference numeral 09 shown in the first dog clutch mechanism 01a of FIG. A second rotating body is shown. 9b denotes a second hub fixed to the torque transmission shaft 1 or integrally processed. 13b is fixed to the second hub 9b in the rotational direction and slidably engaged in the axial direction, and the second dog clutch 5 and the outer peripheral portion are means to be pulsated in the axial direction by the first shift mechanism 07a. A second sleeve with a two-sleeve peripheral groove 11b is shown. 03 denotes a first pressing means for urging the second dog clutch 5 in the meshing direction of the first dog clutch 3 . Reference numeral 15 denotes one or a plurality of slanted grooves 15 provided on the inner diameter of the second sleeve 13b, and 19 denotes holes 17 corresponding to the slanted grooves 15 provided on the second hub 9b and elastic members engaging the holes 17. a body 19 and 21 a transmission member for transmitting the pressing force of the elastic body 19 to the slope groove 15 . When the transmission member 21 presses the slope groove 15 in the radial direction, the slope effect presses the second sleeve 13b toward the first dog clutch 3 . In addition, 05 in FIG. 6 is the second pressing means. The second pressing means 05 includes a second elastic body 33 for applying an axial thrust to the second sleeve 13b, a ring plate 35 for transmitting the axial thrust of the second elastic body 33 to the second hub 9b, and the ring plate 35 to the second hub 9b. It consists of a stopper ring 37 fastened to 9b.

FIG. 2 shows the tooth profiles of the first dog clutch 3 and the second dog clutch 5, and the state in which the dog clutches are meshed with positive torque (hereinafter referred to as drive torque). 4 shows a state in which the first and second dog clutches 3 and 5 are disengaged.
The first drive torque transmission tooth flank 23 on the side of the first dog clutch 3 that transmits the drive torque has a tooth flank 29 from a point A at a distance of X from the tooth bottom 25 to the tooth top 27, which is second with respect to the rotation axis. It has a meshing surface parallel to the angle of the direction in which the dog clutch 5 is meshed or the axis of rotation, and a slope 31 connects the point A to the tooth bottom 25 . The first coast torque transmission tooth flank 39 of the first dog clutch 3 extends from point B at a distance of X-ΔX from the tooth bottom 25 to the tooth bottom 25 in a direction or axis in which the second dog clutch 5 is pulled in with respect to the rotation axis. , or has a tooth surface 41 having an angle equal to or less than the friction angle that disengages the second dog clutch 5, and the surface from point B to the tooth tip 27 is inclined from 45 degrees to 80 degrees with respect to the rotation axis. It has a tooth flank 43 with a single bevel or a compound bevel.

8, 07a is a first shift mechanism, 45 is a rotary actuator, 47 is a first rotary actuator shaft driven by the rotary actuator 45, 49 is an arm fixed to the first rotary actuator shaft 47, and 51 is attached to the arm 49. It is a sleeve moving member that is fastened and engaged with the second sleeve outer peripheral groove 11b. Rotation of the rotary actuator 45 causes the sleeve moving member 51 to move in an arc, axially moving the second sleeve 13b, and driving the first and second dog clutches 3, 5 to engage and disengage.
07b shown in FIG. 9 is a second shift mechanism, 53 is a linear motion actuator, 55 is a shift rod driven by the linear motion actuator 53, 57 is engaged with the second sleeve outer peripheral groove 11b and fastened to the shift rod 55, The second shift mechanism 07b is a shift fork that is moved in the axial direction by the direct acting actuator 53 to engage and disengage the first dog clutch 3 and the second dog clutch 5. The second shift mechanism 07b is composed of the above members.
The rotary or linear actuators 45, 53 can be electric, hydraulic, pneumatic, electromagnetic solenoid, manual, or the like.
Between the portions 58 and 60 of the sleeve moving member 51 and the shift fork 57 that engage with the second sleeve outer circumferential groove 11b and the second sleeve outer circumferential groove 11b, there is a gap Y that is the same as or slightly larger than the aforementioned X. When the first and second dog clutches 3 and 5 are engaged with drive torque, the gap Y is in the engagement and disengagement direction of the second dog clutch 5, and when engaged with coast torque, the first dog clutch 3 side. The rotary actuator 45 is controlled to a position resulting in .

FIG. 5 is a main sectional view of the second dog clutch mechanism 01b, in which the shift mechanism of the first dog clutch mechanism 01a is changed from the first shift mechanism 07a to the second shift mechanism 07b. FIG. 6 is a main sectional view of the third dog clutch mechanism 01c, in which the second sleeve pressing means of the first dog clutch mechanism 01a is changed from the first pressing means 03 to the second pressing means 05. As shown in FIG. FIG. 7 is a main sectional view of the fourth dog clutch mechanism 01d, in which the first shift mechanism 07a of the first dog clutch mechanism 01a is changed to the second shift mechanism 07b, and the pressing means of the second sleeve 13b is replaced with the first pressing mechanism. This is a dog clutch mechanism in which the means 03 is changed to the second pressing means 05.

When the first dog clutch 3 and the second dog clutch 5 are meshed by the drive torque, the second drive torque transmission tooth surface 23b of the second dog clutch 5 is aligned with the slope 31 of the first dog clutch 3 as shown in FIG. is lifted by X from the tooth bottom 25. At this time, the gap Y is formed in the opposite direction of the first dog clutch 3 . When the two dog clutches are engaged with the coast torque, as shown in FIG. , the second coast torque transmission tooth flank 39b of the second dog clutch 5 meshes with the tooth flank 41 below point B of X-ΔX from the tooth bottom of the first coast torque transmission tooth flank 39 of the first dog clutch 3, Transmits coast torque. At this time, the clearance Y shifts to the first dog clutch 3 side.
In this manner, the dog clutch mechanism can transmit torque in both the drive and coast directions.

At the time of shifting to the high-speed stage, when the driving torque starts to transfer to the friction clutch of the high-speed stage, which will be described later, the first and second drive torque transmission tooth flanks 23, 23b of the first dog clutch 3 and the second dog clutch 5 are shifted. The transmission torque decreases and eventually becomes 0, and the engagement shifts to the first and second coast torque transmission tooth flanks 39 and 39b, and the internal circulation torque is generated by the double meshing of the high speed stage and the low speed stage, and the dog clutch meshing portion. generates coast torque.
In the present invention, the first shift mechanism 07a or the second shift mechanism 07b is moved in the engagement and disengagement direction when the gap Y is on the opposite side of the first dog clutch 3 immediately before or at the same time as the shift to the high speed stage. drive to shift the clearance Y to the first dog clutch 3 side. Therefore, even if the drive torque of the second dog clutch 5 is lost, the second dog clutch tooth tip 59 is separated from the tooth root 25 of the first dog clutch by X by the first or second shift mechanism 07a, 07b. Even if the axial position is maintained, the axial thrust of the sleeve pressing member is blocked by the first and second shift mechanisms 07a and 07b. Since the friction is lost, the first or second shift mechanism 07a, 07b can easily move the second sleeve 13b from the first dog clutch 3 in the disengaging direction by ΔY. That is, the second dog clutch tooth tip 59 is lifted from the tooth bottom 25 of the first dog clutch 3 by X+ΔY.

As shown in FIG. 4, the first coast torque transmission tooth flank 39 of the first dog clutch 3 forms a slope 31b inclined from 45 degrees to 80 degrees with respect to the rotation axis from the point B to the tooth tip 27. As shown in FIG. Therefore, by setting ΔY to be larger than ΔX, the second coast torque transmission tooth surface 39b of the second dog clutch 5 contacts the slope 31b. Therefore, before the coast torque between the first and second dog clutches 3 and 5 increases due to the slope effect of the slope 31b, that is, before the internal circulation torque increases due to the double meshing of the high-speed stage and the low-speed stage, the second dog clutch 5 generates an axial movement in the direction of disengagement from the first dog clutch 3, and furthermore, the first or second shift mechanism 07a, 07b is driven in the direction of engagement and disengagement of the dog clutch, so that the second dog clutch 5 is disengaged from the first dog clutch 3. It is possible to smoothly disengage from the engagement with.

As described above, according to the dog clutch of this embodiment, torque can be transmitted in both the drive and coast directions during normal operation at a low speed. The meshing of the second dog clutch 5 can be released smoothly without increasing the internal circulation torque due to the double meshing of the high-speed stage and the low-speed stage.

01e shown in FIG. 10 is a main sectional view of the fifth dog clutch mechanism, 01f shown in FIG. 11 is a main sectional view of the sixth dog clutch mechanism, 07c shown in FIG. 12 is the third shift mechanism, and FIGS. A sectional view of the shift mechanism 07c, 07d shown in FIG. 16 indicates the fourth shift mechanism.

The fifth dog clutch mechanism 01e shown in FIG. 10 is a dog clutch mechanism in which the shift mechanism of the fourth dog clutch mechanism 01d is changed from the second shift mechanism 07b to the third shift mechanism 07c.
07c shown in FIG. 12 is a diagram of the third shift mechanism. 65a is a first rotary arm coupled to the second rotary actuator shaft 47b, 65b is a second rotary arm rotatably and slidably supported by the second rotary actuator shaft 47b, and has an axial drive means 69 for the second sleeve 13b; A reference numeral 61 denotes a third elastic body, for example, a spiral spring.
When the second rotating arm 65b drives the second sleeve 13b away from the first dog clutch 3, the first rotating arm 65a drives the second rotating arm 65b via the third elastic body 61, engaging the dog clutch. In the matching direction, the first rotating arm 65a directly drives the second rotating arm 65b without the third elastic body 61 intervening.

FIG. 13 is a cross-sectional view of the third shift mechanism 07c. A second rotating arm 65b is sandwiched between the first rotating arm 65a and the rotating actuator 45 and is engaged with the second rotating actuator shaft 47b so as to be slidable in the rotating direction. The first rotating arm 65a is fastened and fixed to the second rotating actuator shaft 47b, and supports a third elastic body 61, for example, a helical spring. The first rotating arm 65a is provided with a first pin 73 for driving the first end portion 71 of the third elastic body 61 and a second pin 75 for directly driving the second rotating arm 65b. A third pin 79 driven by the second end portion 77 of the third elastic body 61 is provided on the second rotating arm 65b at a position that does not interfere with the first rotating arm 65a. The first end 71 of the third elastic body 61 is in contact with the first pin 73 and the second end 77 is in contact only with the third pin 79 . When the third elastic body 61 is assembled, the third pin 79 is rotated clockwise with a predetermined torque T in a state in which the first end 71 is moved leftward in the drawing with respect to the second end 77 . One pin 73 is assembled at an angle that generates torque in a counterclockwise twisting direction. The reaction torque T is absorbed in the left direction in the figure by the first pin 73, and the first end 71 moves in the right direction in the figure. The second pin 75 in contact with the two-rotating arm 65b fixes the second rotating arm 65b at a predetermined rotational position with torque T with respect to the first rotating arm 65a. T is set to overcome the pressing forces of the first and second pressing means 03, 05 that press the second sleeve 13b and the first sleeve 13a, which will be described later.

A position where the rotary actuator 45 disengages the second sleeve 13b in a state where the first dog clutch 3 and the second dog clutch 5 are engaged in the drive torque direction and the second sleeve 13b does not move in the disengagement direction due to the friction torque of the tooth surfaces. 14, the first rotating arm 65a rotates, deforming the third elastic body 61 and moving the first pin 73 to a predetermined position shown in FIG. The predetermined position is the position when the first and second dog clutches 3, 5 are disengaged.
In the state of FIG. 14, potential energy is accumulated between the first end 71 and the second end 77 of the third elastic body 61, and the first end 71 engages the third pin 79 of the second rotating arm 65b to engage the second dog clutch. The torque T+TΔ for rotating in the detachment direction of 5 is continuously applied. In this state, when the engagement torque between the first dog clutch 3 and the second dog clutch 5 disappears, the potential energy of the third elastic body 61 causes the second rotating arm 65b to move the second sleeve 13b to the first and second dog clutches 3 at once. , 5 are disengaged, and the relative positions of the first rotating arm 65a and the second rotating arm 65b return to the original state before the operation of the rotary actuator 45, and assume the position shown in FIG.

When shifting the second dog clutch 5 from the disengaged position to the position where it meshes with the first dog clutch 3, the rotary actuator 45 is rotated in the opposite direction to that when disengaged. At this time, the second pin 75 attached to the first rotating arm 65a directly drives the second rotating arm 65b to move the second sleeve 13b to the initial engagement position.

01f shown in FIG. 11 is a main sectional view of the sixth dog clutch mechanism 01d, which is a clutch mechanism in which the shift mechanism is changed from the second shift mechanism 07b to the fourth shift mechanism 07d shown in FIG. .
FIG. 16 shows a main sectional view of the fourth shift mechanism 07d. 53 is a linear motion actuator, and 55b is a second shift rod driven by the linear motion actuator 53 . A second shift fork 57b is slidably engaged with the second shift rod 55b. An elastic stopper 83 is fastened to the second shift rod 55b with a fastening member 81. As shown in FIG. A second shift fork stopper 85 is fastened to the second shift rod 55b.

When the first and second dog clutches 3 and 5 are engaged in a driving torque transmission state, the second shift fork 57b engages the outer circumference of the second shift rod 55b as shown in FIG. The first end portion 87 of the second shift fork 57b is pressed by the preload P stronger than the pressing force of the first and second pressing means 03, 05, and the end portion 91 of the second shift fork 57b is in contact with the shift fork stopper 85. The second end 89 of the second elastic body 33 contacts the elastic stopper 83, and the second shift fork 57b and the second shift rod 55b are engaged so as not to cause relative movement with a force equal to or less than the preload P. there is
The second elastic body 33 in this state receives a predetermined preload and presses the end portion 91 of the second shift fork 55 b against the shift fork stopper 85 .

When the first and second dog clutches 3 and 5 are engaged with each other by receiving the drive torque, the second shift fork 57b moves only by the gap Y even if the linear actuator 53 drives the second shift rod 55b in the disengagement direction. . However, since the second elastic body 33 is interposed between the second shift fork 57b and the second shift rod 55b, the second shift rod 55b is positioned at a predetermined position where the first dog clutch 3 and the second dog clutch 5 are disengaged. , while compressing and deforming the second elastic body 33 . Assuming that the thrust increase due to the deformation of the second elastic body 33 is ΔP, a force of P+ΔP acts between the second shift fork 57b and the second sleeve 13b.
In this state, when the transmission torque between the first dog clutch 3 and the second dog clutch 5 disappears, the frictional force on the drive tooth flanks of the first and second dog clutches 3 and 5 decreases. The stored potential energy quickly drives the second shift fork 57b to a predetermined position where the second dog clutch 5 disengages from the first dog clutch 3, and the first and second dog clutches 3, 5 are quickly engaged. To be released. On the other hand, when the second dog clutch 5 is shifted in the direction of meshing with the first dog clutch 3, the second shift fork stopper 85 moves the second shift fork 57b to a predetermined position where the first and second dog clutches 3, 5 mesh. drive directly to

By using an elastic body for the third and fourth shift mechanisms 07c and 07d, it is possible to advance the driving start timing of the third and fourth shift mechanisms 07c and 07d when shifting to a high speed stage. Since the engagement of the dog clutch 5 is accelerated by the elastic body in the disengagement direction while the engagement of the dog clutch 5 shifts from the first drive torque transmission tooth surface 23 to the first coast torque transmission tooth surface 39 of the first dog clutch 3, the second dog clutch 5 Since the second coast torque transmission tooth flank 39b of the first dog clutch contacts a portion closer to the tooth tip 27 than the first coast torque transmission tooth flank 39 of the first dog clutch, the engagement and disengagement is ensured, and the value of ΔX is increased. It is possible to improve the meshing contact area of the coast tooth surface and improve durability.

01g shown in FIG. 17 is a main sectional view of the seventh dog clutch of this embodiment, 01h shown in FIG. 18 is a main sectional view of the eighth dog clutch mechanism, 07e shown in FIG. 19 is the fifth shift mechanism, and FIGS. , 22 shows a sectional view of the fifth shift mechanism in a predetermined state. 07f shown in FIG. 23 is a sectional view of the sixth shift mechanism.

A seventh dog clutch mechanism 01g shown in FIG. 17 is obtained by changing the shift mechanism of the fifth dog clutch mechanism 01e from the third shift mechanism 07c to a fifth shift mechanism 07e shown in FIG.
A fifth shift mechanism 07e shown in FIG. 19 has a fourth elastic body 95, for example, a helical spring, for shifting the first and second dog clutches 3 and 5 in both disengagement and meshing directions in relation to the third shift mechanism 07c. It has an intervening structure. A second elastic body holding member 97 holding a fourth elastic body 95 is fastened and fixed to a third rotary actuator shaft 93 of the rotary actuator 45 , and a third rotary actuator shaft is provided between the rotary actuator 45 and the second elastic body holding member 97 . A fourth pin 101 is provided on the second elastic body holding member 97, and the third rotary actuator shaft 93 of the fourth pin 101 of the third rotary arm 99 A fifth pin 103 is provided in the outer diameter direction, a third end portion 105 and a fourth end portion 107 extending substantially radially in the outer diameter direction are provided at both ends of the fourth elastic body 95, and the ends cross each other , the fourth pin 101 and the fifth pin 103 are engaged with each other and held by the second elastic holding member 97 .

FIG. 20 shows the state when the fifth shift mechanism 07e is in a positional relationship in which the tip 59 of the second dog clutch 5 is in contact with the bottom 25 of the first dog clutch 3. As shown in FIG. Therefore, when the first and second dog clutches 3 and 5 are engaged with the coast torque, the fifth shift mechanism 07e assumes the position shown in FIG. When the engagement torque of the first and second dog clutches 3, 5 shifts in the driving direction, the second dog clutch 5 is lifted by X from the tooth bottom 25 of the first dog clutch as described above with reference to FIG. At this time, the third rotating arm 99 rotates as the second dog clutch 5 moves, but the third rotating actuator shaft 93 coupled to the rotating actuator 45 is fixed by the check mechanism or the rotating actuator 45 so as not to rotate. back.
Therefore, the third rotating arm 99 and the fourth pin 101 also do not move, and the third rotating arm 99 biases the third end portion 105 of the fourth elastic body 95 with the fifth pin 103, causing the fourth elastic body 95 to bend. while rotating by a predetermined angle corresponding to the X. When the coast torque is applied to the first and second dog clutches 3 and 5 again, the tip 59 of the second dog clutch 5 is separated from the first dog clutch tooth bottom slope 31, and the fourth elastic body 95 returns to its flexure. As a result, the fourth elastic body 95 is returned to the initial position shown in FIG. 20, and the second dog clutch tooth addendum 59 moves to a position in contact with the tooth bottom 25 of the first dog clutch. In other embodiments, the second sleeve outer peripheral groove 11b shown in FIG. 19 and the shift tip member 109 engaged with the groove are engaged with a gap Y, but in this embodiment, the gap is not necessary. , the shift tip member 109 and the second sleeve outer circumferential groove 11b are engaged with a minimum clearance necessary for smooth sliding. That is, the fourth elastic body 95 of the fifth shift mechanism 07e replaces the functions of the first and second pressing means 03,05. Accordingly, a dog clutch mechanism using this shift mechanism basically does not require the first or second pressing means 03, 05.

The eighth dog clutch mechanism 01h shown in FIG. 18 replaces the fifth shift mechanism 07e of the seventh dog clutch mechanism 01g with the sixth shift mechanism 07f shown in FIG. The sixth shift mechanism 07f of FIG. 23 is slidably engaged with the outer circumference of the third shift rod 55c, and preloads a fifth elastic body 111 that is similarly engaged with the outer circumference of the third shift rod 55c. A first piston 113 and a second piston 115 are provided, and first and second fastening members 123 and 125 are fastened to the third shift rod 55c on opposite surfaces of the pistons 113 and 115 in contact with the fifth elastic body 111. The first and second pistons 113 and 115 are structured so that they do not separate from each other due to the elastic body 111 . The third shift fork 57c is slidably engaged with the outer peripheral portions of the first and second pistons 113, 115 and has a cylindrical portion 117 that wraps the fifth elastic body 111. First and second pistons 113 and 115 have a first stopper member 119 and a second stopper member 121 which are in contact with the surface opposite to the surface in contact with the fifth elastic body 111 and which are fastened to the inner diameter of the cylindrical portion 117 of the third shift fork.

When the first dog clutch 3 and the second dog clutch 5 are meshed by the drive torque, even if the direct-acting actuator 53 is driven in the disengagement direction of both dog clutches for shifting to the high-speed stage, both dog clutches are not meshed. They do not change their relative position due to the frictional force created by the torque.
Therefore, the position of the third shift fork 57c interlocking with the second dog clutch 5 does not change, and the third shift rod 55c moves the first shift fork 57c to a predetermined position in the direction in which the first and second dog clutches 3, 5 are disengaged. Together with the piston 113, the fifth elastic body 111 moves while being compressed toward the second fastening member 125 at the end of the cylindrical portion 117 of the third shift fork 57c. Therefore, the third shift fork 57c receives the axial thrust in the disengagement direction of the first and second dog clutches 3 and 5 by the fifth elastic body 111. As shown in FIG. When the driving torque starts to transfer to the torque transmission means of the high-speed stage, the engagement torque between the first dog clutch 3 and the second dog clutch 5 decreases as described above, and the frictional force on the tooth flanks also decreases. When the frictional force is less than the pressing force applied to the third shift fork 57c by the fifth elastic body 111, the third shift fork 57c moves to the disengaged position of the first and second dog clutches 3, 5 together with the second sleeve 13b. move quickly to In this state, the first and second pistons 113 and 115 are connected to the first and second fastening members 123 and 125 provided on the third shift rod 55c and the first and second fastening members 123 and 125 provided on the cylindrical end of the third shift fork 57c. 1. Return to the position where the second stopper members 119 and 121 are contacted.

When the first dog clutch 3 and the second dog clutch 5 are engaged from the disengaged position, the direct-acting actuator 53 moves the third shift rod 55c to a position where the tooth tip 59 of the second dog clutch contacts the tooth bottom 25 of the first dog clutch. up to or slightly beyond that position and lock in that position. As described above, when the first and second dog clutches 3 and 5 are meshed with the drive torque, the tip 59 of the second dog clutch is lifted by X from the bottom 25 of the first dog clutch. Accordingly, the third shift fork 57c is also moved by X in the direction in which the first and second dog clutches 3 and 5 are disengaged by the first and second fastening members 119 and 121 while deforming the fifth elastic body 111 . When the drive torque shifts from the drive torque to the coast torque other than when shifting to a high-speed stage, the fifth elastic body 111 drives the first and second fastening members 119 and 121, and the third shift fork 57c moves to the second gear. The dog clutch tooth tip 59 is pressed against the tooth bottom of the first dog clutch 25. - 特許庁

In this embodiment, even when the first and second dog clutches 3 and 5 are engaged, the rotary and direct acting actuators 45 and 53 move to the predetermined positions as in the third embodiment. While deforming the elastic bodies 61, 95, 111, the third rotary actuator shaft 93 or the third shift rod 55c can be driven to a predetermined shift position. Therefore, the second dog clutch 5 can be quickly disengaged from the first dog clutch 3 irrespective of the speed of the actuator when shifting to the high-speed stage. Therefore, X of the first dog clutch 3 can be reduced and ΔX can be increased, thereby improving the durability of the meshing tooth flanks. Furthermore, the first and second pressing means 03, 05 for pressing the second sleeve 13b are not required, thereby simplifying the structure.

01i shown in FIG. 24 is a main sectional view of the ninth dog clutch mechanism, 01j shown in FIG. 25 is the tenth dog clutch, 01k shown in FIG. 26 is the eleventh dog clutch mechanism, and 01l shown in FIG. 27 is the twelfth dog clutch. 4 is a main cross-sectional view of the clutch mechanism; FIG.
This embodiment is an embodiment of the invention in which the second rotating body 7b and the second hub 9b of the first embodiment are replaced with the first rotating body 7a and the first hub 9a.
In the ninth, tenth, eleventh, and twelfth dog clutch mechanisms 01i, 01j, 01k, and 01l, a first rotor 7a having a first dog clutch 3 and a first boss 2a is the first boss 2a, The bearing 4 and first and second bearing fastening members 6a and 6b are fixed and engaged with the inner diameter portion of a first hub 9a, which will be described later, so as to rotate freely and axially.

The first hub 9 a is fixed to the case 09 with a fastening member 8 or made integrally with the case 09 . The shift mechanism of the ninth dog clutch mechanism 01i shown in FIG. The shift mechanism of the dog clutch mechanism 01j is the second shift mechanism 07b, and the pressing means of the first sleeve 13a is the first pressing means 03. As shown in FIG. The eleventh dog clutch mechanism 01k shown in FIG. 26 is obtained by replacing the pressing means of the first sleeve 13a from the first pressing means 03 to the second pressing means 05 in the ninth dog clutch mechanism 01i, as shown in FIG. The twelfth dog clutch mechanism 01l is obtained by replacing the sleeve pressing means of the tenth dog clutch mechanism 01j from the first pressing means 03 to the second pressing means 05. As shown in FIG.

The difference between this embodiment and the first embodiment is that the first sleeve 13a having the second dog clutch 5 and the first hub 9a engaging the first sleeve 13a do not rotate. The first sleeve 13a does not rotate as described above, and the first hub 9a is fixed to the case 09 and does not move in the axial direction.

In this embodiment, since the first sleeve 13a does not rotate, there is no sliding between the first sleeve 13a, the first and second shift mechanisms 07a, 07b, and the second pressing means 05, and there is no frictional wear and durability. Excellent.

01m and 01n shown in FIGS. 28 and 29 are main sectional views of the thirteenth and fourteenth dog clutch mechanisms.
The thirteenth dog clutch mechanism 01m is a dog clutch mechanism in which the first shift mechanism 07a of the ninth dog clutch mechanism 01i is replaced with a third shift mechanism 07c, and the first pressing means 03 is replaced with a second pressing means 05. , The fourteenth dog clutch mechanism 01n is a dog clutch mechanism in which the second shift mechanism 07b of the tenth dog clutch mechanism 01j is replaced with the fourth shift mechanism 07d, and the first pressing means 03 is replaced with the second pressing means 05. be.

This embodiment has the same effects as those described in the second and fourth embodiments.

01o and 01p shown in FIGS. 30 and 31 are main sectional views of the fifteenth and sixteenth dog clutch mechanisms of this embodiment.
The fifteenth dog clutch mechanism 01o is a dog clutch mechanism having a structure in which the first shift mechanism 07a of the ninth dog clutch mechanism 01i is replaced with a fifth shift mechanism 07e and the first and second pressing means 03 and 05 are removed. The sixteenth dog clutch mechanism 01p is a dog clutch mechanism in which the second shift mechanism 07b of the tenth dog clutch mechanism 01j is replaced with the sixth shift mechanism 07f and the first and second pressing means 03 and 05 are removed. . Along with the change of the shift mechanism, as described in the third embodiment, the first sleeve outer peripheral groove 11a in contact with the fifth and sixth shift mechanisms 07e and 07f has no play.

The effects of this embodiment are similar to the effects described in the third and fourth embodiments.

023 and 025 shown in FIGS. 32 and 33 are main sectional views of the third A and B two-speed transmission, which is the present embodiment of the two-speed transmission.
The third A and B two-speed transmissions 023 and 025 are driven by a driving member 127 such as an electric motor or a CVT, and a low-speed drive gear 131a and a high-speed drive gear 131b are engaged with a drive shaft 129 rotatably supported by the case 09. A low-speed driven gear 135a and a high-speed drive gear 131b are engaged with a driven shaft 133 which has an external member driving means 141 for driving an external member 139 such as a differential and is rotatably supported by the case 09. It is a two-speed transmission of a two-row gear mechanism consisting of a low-speed gear train 011 and a high-speed gear train 013 with which a high-speed driven gear 135b is engaged.

A third A two-speed transmission 023 shown in FIG. 32 has a first dog clutch 3 that meshes with a low-speed drive gear 131a fastened to a drive shaft 129. A low-speed driven gear 135a is rotatably engaged with the driven shaft 133, is engaged at a predetermined position by a stopper 137 and the second hub 9b.
A spline 143 is provided so that the second sleeve 13b, which is fixedly fastened or integrally processed to the driven shaft 133 and has the second dog clutch 5 on its outer peripheral portion, is fixed to the second hub 9b in the axial direction and in the rotational direction. are engaged by means such as The first dog clutch 3 and the second dog clutch 5 are connected and disconnected by the third shift mechanism 07c shown in FIGS. 10 and 12 described above. The third B two-speed transmission 025 shown in FIG. 33 switches the first and second dog clutches 3 and 5 from the fourth shift mechanism 07d shown in FIGS.

A high-speed drive gear 131b fixedly fastened to the drive shaft 129 is meshed with the gear, and engaged with a bearing 136 on one side of the case 09 so as to be rotatable and axially positioned. Means 151 for supporting the outer diameter portion 149 of the first friction member 147a in the rotational direction by sandwiching the bearing 145 with respect to the high-speed driven gear 135b, and the axial thrust applied to the first and second friction members 147a and 147b of the elastic body 153, which will be described later. A second clutch housing 033 having means 155 for receiving pressure is fastened. Further, the inner diameter portion of the second boss 2b rotatably supports the driven shaft 133 with a bearing 157. As shown in FIG. The driven shaft 133 is provided with a second friction clutch hub 035b having means 159 for engaging the second friction member 147b in the rotational direction on the outer diameter portion at a position where the inner diameter and the axial direction of the second clutch housing 033 overlap. has been concluded.

A first friction member 147a is engaged with the second clutch housing 033, and a second friction member 147b is engaged with the second friction clutch hub 035b by contacting the first friction member 147a on one side or both sides thereof.
A pressing force adjusting member 161 for adjusting the pressing force applied to the first and second friction members 147a and 147b is in contact with the first or second friction members 147a and 147b. and transmits the pressing force to the first and second friction members 147a and 147b. The pressing force adjusting member 161 has a central hole 167 through which a second friction clutch actuator shaft 165 (to be described later) passes through and a bearing contact portion 169 at the center portion. A bearing 163 is engaged to receive axial thrust in a force reducing direction, and a release flange 171 fastened to a second friction clutch actuator shaft 165 passing through the central hole 167 is in contact with the bearing 163 . A fastening member 152 is fastened to the inner diameter portion of the second clutch housing 033 and receives the reaction force of the elastic body 153 .

The second friction clutch actuator 173 that drives the second friction clutch actuator shaft 165 is a linear actuator that drives the second friction clutch actuator shaft 165 axially.
In a state where the axial force of the second friction clutch actuator 173 is not applied to the bearing 163, the first and second friction members 147a and 147b are engaged by the axial thrust of the elastic body 153, and the high-speed driven gear 135b is engaged. and the driven shaft 133 rotate integrally.
When the second friction clutch actuator 173 is driven and the release flange 171 applies an axial force to the pressing force adjusting member 161 via the bearing 171 in a direction that inhibits the pressing force of the friction member of the elastic body 153, the first and second friction The friction coupling between members 147a and 147b is released and the torque coupling between high speed driven gear 135b and driven shaft 133 is released.
The second friction clutch actuator 173 may use an electric motor, electromagnetic solenoid, hydraulic pressure, pneumatic pressure, or the like.

When the first and second dog clutches 3 and 5 are in mesh, the torque transmitted to the low-speed driven gear 135a is transmitted to the driven shaft 133, and a low-speed state is established in which an external member 139 such as a differential is driven. .
In this state, when the low-speed drive and driven gears 131a and 135a are transmitting the drive torque, the second dog clutch 5 engages with the first dog clutch 3 while floating by X as described above. In this state, even if the fifth shift mechanism 07e is operated to a position where the first and second dog clutches 3 and 5 are disengaged from engagement, the second dog clutch 5 does not move due to the frictional force due to the engagement torque and remains in the engagement position. to maintain However, the deformation of the fourth elastic body 95 causes the rotary actuator 45 of the fifth shift mechanism 07e to rotate to the disengaged position. In this state, by driving the second friction clutch actuator 173, the second friction clutch mechanism 017 starts to engage and start transmitting torque while slipping. When the transmission torque of the second friction clutch mechanism 017 reaches a predetermined torque, the engagement of the second dog clutch 5 moves in the direction of the first coast torque transmission tooth surface 39 of the first dog clutch 3 and the fourth elastic body 95 As a result, the second coast torque transmission tooth surface 39b of the second dog clutch 5 moves to the slope 31b starting at a position X-ΔX away from the tooth root 25 of the coast tooth surface 25 of the first dog clutch 3. Contact. Therefore, due to the slope effect of the slope 31b and the force of the fourth elastic body 95 of the fifth shift mechanism 07e, the first and second dog clutches 3, 5 are disengaged smoothly and quickly. Then, the entire driving torque is transferred to the high-speed gear train 013 by the second friction clutch 017, and the switching from the low-speed stage to the high-speed stage is smoothly completed.

It is important that the driving torque is not interrupted during acceleration or rapid downshifting when climbing a slope, ie, kickdown. In the case of such a downshift, the second friction clutch actuator 173 is operated to loosen the transmission torque capacity of the second friction clutch mechanism 017 until a minute slip occurs, and the second friction clutch actuator 173 is driven in this state. Stop, while maintaining the torque transmission of the second friction clutch mechanism 017, the input rotation is increased until the first dog clutch 3 slightly exceeds the rotation of the second dog clutch 5, and in this state, the linear or rotary actuator of the shift mechanism is operated. 45 and 53 are operated, and the second sleeve 13b is driven by the shift mechanism to a predetermined position where the second dog clutch 5 and the first dog clutch 3 are meshed. At the same time, the second friction clutch actuator 173 is operated to release the second friction clutch mechanism 017 . Through this series of operations, it is possible to shift down without interrupting the driving torque. When the third A and B two-speed transmissions 023 and 025 of the present embodiment are used for an electric vehicle, the slight slip of the second friction clutch mechanism 017 and the rotation seat difference between the first and second dog clutches 3 and 5 are can be detected by comparing the rotation of the driving member 127, which is an example of an electric motor, with the vehicle speed.
During normal downshifting, the second friction clutch mechanism 017 is first completely disengaged, the rotation of the first dog clutch 3 is slightly increased more than the rotation of the second dog clutch 5, and the third shift mechanism 07c shifts to the first gear. The first and second dog clutches 3 and 5 should be meshed.

The third B two-speed transmission 025 shown in FIG. This is an example in which the first pressing means 03 is used. Other structures, functions, and operations are the same as those of the third A two-speed transmission 023.

The example shown in FIGS. 32 and 33 of this embodiment is an example using the third and fourth shift mechanisms 07c and 07d as the shift mechanism. A sixth shift mechanism 07a, 07b, 07e, 07f may be used.
Further, the second sleeve pressing means is unnecessary when the fifth and sixth shift mechanisms 07e and 07f are used as described above, and when other shift mechanisms are used, the first and second pressing means 03 are used. , 05 may be used.

In this embodiment, it is possible to seamlessly shift to both high speed and low speed gears without interrupting the drive torque, and it is possible to transmit coast torque to both high speed and low speed gears. is possible, and when used for CVT, engine braking can be used.

This embodiment is an example in which the seventeenth or eighteenth dog clutch mechanisms 01q, 01r and the second friction clutch mechanism 017 are arranged on the driven shaft 133. The seventeenth or eighteenth dog clutch mechanism 01q, 01r, the second dog clutch mechanism 017,
(1) The aforementioned layout in which the seventeenth or eighteenth dog clutch mechanism 01q, 01r and the second friction clutch mechanism 017 are provided on the driven shaft 133.
(2) A layout in which the seventeenth or eighteenth dog clutch mechanism 01q, 01r is provided on the driven shaft 133 and the second friction clutch mechanism 017 is provided on the drive shaft 129;
(3) A layout in which the second friction clutch mechanism 017 is provided on the driven shaft 133 and the seventeenth or eighteenth dog clutch mechanism 01q, 01r is provided on the drive shaft 129;
(4) A layout in which the seventeenth or eighteenth dog clutch mechanism 01q, 01r and the second friction clutch mechanism 017 are provided on the drive shaft 129;
As described above, four combinations are possible for the layout of the two-speed transmission in this embodiment.

019 shown in FIG. 34 is the first A two-speed transmission, and 021 shown in FIG. 35 is a main sectional view of two two-speed transmissions of the first B two-speed transmission.
In the first A two-speed transmission 019, the first rotating body 7a of the fourth embodiment is the internal gear 7c, and the internal gear 7c engages the internal gear 175 and the outer diameter portion 149 of the first friction member 147a. The first clutch housing 031 has a first boss 2a and a first dog clutch 3 which are rotatably and axially fixedly engaged with the inner diameter of the first hub 9a by means of a bearing 4 . A first planet pinion 179 meshing with the internal gear 7c and rotatably engaged with a first planet carrier 177, which will be described later, a support means 181 for rotatably supporting the first planet pinion 179, and an external member for driving the external member 139. The driving means 141 has a means 185 for engaging the inner diameter portion 183 of the second friction member 147b, and is rotatably engaged with the outer circumference of the first sun gear shaft 187 and the inner diameter of the first boss 2a to be described later by means of bearings 191 and 193. A driving force transmission composed of a first planet carrier 177 that engages with the first planet carrier 177 and a first sun gear 189 that receives power from a driving member 127 such as a motor, CVT, etc., is rotatably engaged with the case 09, and meshes with the first planet pinion 179. have elements.

The transmission means of the first A two-speed transmission 019 shown in FIG. 34 has a fifteenth dog clutch mechanism 01o and a first friction clutch mechanism 015 shown in FIG. The transmission means of the first B two-speed transmission 021 shown in FIG.
In the first friction clutch mechanism 015, the outer diameter portion 149 of the first friction member 147a is axially freely engaged with the first clutch housing 031 provided on the internal gear 7c only in the rotational direction. , and the inner diameter portion 199 of the second friction member 147b is engaged with the outer diameter portion 197 of the first friction clutch hub 035a of the first planet carrier 177 in the rotational direction. Further, a pressing force adjusting member 195 is provided in the inner diameter portion 201 of the first clutch housing to be in contact with the first or second friction members 147a and 147b to adjust the pressing force applied to the members. Alternatively, the elastic body 153 is in contact with the surface opposite to the surface in contact with the second friction members 147a, 147b, and applies a pressing force to the first and second friction members 147a, 147b via the pressing force adjusting member 195.
A reaction force adjusting member 207 that contacts the elastic body 153 and receives its reaction force is fastened to the inner diameter portion 201 of the first clutch housing by a fastening member 203 , and transmits the reaction force of the elastic body 153 to the first clutch housing 031 . The pressing force applied to the first and second friction members 147 a and 147 b by the elastic body 153 is received by the pressing force receiver 205 provided in the first clutch housing 031 .

The pressing force adjusting member 195 has a sleeve 209 passing through the central hole of the reaction force adjusting member 207 at its central portion, and the sleeve 209 is slidably engaged with the outer diameter of the planet carrier cylindrical portion 211 . A predetermined axial gap is provided between the pressing force adjusting member 195 and the reaction force adjusting member 207 .
Furthermore, a pair of opposed differential gear sets 037 having different numbers of teeth are engaged with the outer periphery of the sleeve 209 via bearings 217 , which mesh with the pinion 215 of the first friction clutch actuator 213 . The first gear 225 of the differential gear set 037 is in contact with the reaction force adjusting member 207 via a bearing 219, and a plurality of cam grooves having gradients in the depth direction on the circumference are formed on both opposing surfaces of the differential gear set 037. 221, and rolling elements 223 corresponding to the number of cam grooves are engaged with the cam grooves 221, and the relative rotation of the differential gear set 037 changes the distance between the first and second gears 225 and 227. It's becoming A combination of the cam grooves 221 and the rolling elements 223 is a torque cam mechanism 039 . A bearing 231 is interposed between the second gear 227 facing the first gear 225 and the stopper ring 229 , and the stopper ring 229 is fastened to the sleeve 209 by a fastening member 233 .

When the pinion 215 is driven by the first friction clutch actuator 213 to drive the differential gear set 037 meshing with the pinion 215, the first gear 225 and the second gear 227 have different numbers of teeth, thereby causing relative rotation. If the relative rotation is in the direction in which the mutual distance is widened by the action of the torque cam mechanism 039, the axial thrust in the widening direction applies thrust to the bearings 219 and 231, and the pressing force adjusting member 195 pushes the elastic body 153 into the reaction force adjusting member. 207 to reduce or eliminate the friction torque acting on the first and second friction members 147a and 147b.
When the first friction clutch actuator 213 is driven in the opposite direction, the elastic body 153 presses the first and second friction members 147a and 147b without being blocked by the pressing force adjusting member 195, and the friction clutch is engaged. .

When the first dog clutch 3 and the second dog clutch 5 of the first A two-speed transmission 019 shown in FIG. 34 are in mesh with each other, the internal gear 7c is stopped. , the first planet pinion 179 meshes with the internal gear 7c and revolves together with the first planet carrier 177 at an angular velocity equal to or less than half the angular velocity of the first sun gear 189 while rotating. An external member drive means 141 provided on the first planet carrier 177 drives the external member 139 at a speed slower than the input speed of the first sun gear 189 . Therefore, this state is the low speed stage of the transmission.

As described above, when the first and second dog clutches 3 and 5 are transmitting drive torque, the second dog clutch 5 is lifted by X with respect to the first dog clutch 3 .
From this state, the rotary or direct acting actuators 45, 53 of the fifteenth or sixteenth dog clutch mechanisms 01o, 01p are moved to the first dog clutch while the second dog clutch 5 deflects the third or fourth elastic bodies 61, 95. Even if it is driven to a predetermined position where it disengages from the clutch 3, the first and second dog clutches 3 and 5 remain at that position due to the frictional force of meshing. However, as described above, the action of the third elastic body 61 allows the rotary actuator 45 to rotate to a predetermined position and hold that position.
When the first friction clutch actuator 213 is driven from this state and engagement of the first friction clutch mechanism 015 is started, the meshing forces of the first and second dog clutches 3 and 5 are gradually reduced, and the reduced torque is Shifting to the first friction clutch mechanism 015, the friction force on the tooth surface of the dog clutch becomes smaller and disappears. When the transmission torque is transferred to the first friction clutch mechanism 015, the first sun gear 189 and the first planet carrier 177 rotate together, and the two-speed transmission shifts to the high speed stage.

Shifting from a high speed stage to a low speed stage is performed by the first friction clutch mechanism 015, the fifteenth or sixteenth dog clutch mechanism 01o, 01p and the drive member 127, for example an electric motor, as described in the seventh embodiment. It is performed by cooperation of rotation control of.
The shift to the low speed stage is the same as in the seventh embodiment. In this embodiment, a differential gear, a torque cam, and an elastic body are used. In addition to directly pressing the friction clutch with a torque cam, the present friction clutch may also press the friction clutch using hydraulic pressure, pneumatic pressure, or electromagnetic force.

In this embodiment, two-speed transmission is possible on one shaft, and the first clutch housing 031 can be easily set to the internal gear 7c, so that the mechanism becomes compact. Although this embodiment uses the fifteenth and sixteenth dog clutch mechanisms 01o and 01p, the ninth, tenth, eleventh, twelve, thirteenth and fourteenth dog clutch mechanisms 01i, 01j and 01k are used. , 01l, 01m, 01n may be used.

027 shown in FIG. 36 is the fifth two-speed transmission, and 029 shown in FIG. 37 is the main sectional view of the sixth two-speed transmission.
09 is a case, 241 is a second sun gear shaft rotatably engaged with the case 09 and a second planet carrier 235 described later, and has a power input member 237 and a second sun gear 239. 245 is the outer circumference of the second sun gear shaft 241. a third sun gear 243 having a larger pitch diameter than the second sun gear 239, an external member driving means 141, and a first friction clutch hub 035a. A second planet pinion integrally having a third gear 257 meshing with the second sun gear 239 and a fourth gear 259 meshing with the third sun gear 243 and having a pitch diameter smaller than that of the third gear 257; The second planet carrier is rotatably fixed and supported in the axial direction by bearings 4 to the support shaft 249 that rotatably supports the second planet pinion 247, the first clutch housing 031, and the inner diameter portion 251 of the first hub 9a. be. Reference numeral 139 denotes an external member such as a differential.
01e is a fifth dog clutch mechanism having a function of coupling and releasing between the second planet carrier 235 and the first hub 9a. 015 is the first friction clutch mechanism having the function of releasing the frictional connection between the third sun gear shaft 245 and the second planet carrier 235 .

When the first dog clutch 3 and the second dog clutch 5 are engaged, the second planet carrier 235 is stopped. When the second sun gear 239 drives the third gear 257 of the second planet pinion 247 in this state, the fourth gear 259 also rotates at the same angular velocity as the third gear 257 . However, since the pitch diameter of the fourth gear 259 is smaller than that of the third gear 257 , the peripheral speed on the pitch circle is smaller than that of the third gear 257 . Also, the pitch circle diameter of the third sun gear 243 meshing with the fourth gear 259 is larger than the pitch circle diameter of the second sun gear 239 . Torque is transmitted in the order of the second sun gear 239 , the third gear 257 , the fourth gear 259 and the third sun gear 243 , so the angular velocity of the third sun gear 243 is smaller than the angular velocity of the second sun gear 239 . Therefore, when the first dog clutch 3 and the second dog clutch 5 are engaged, the transmission is in the low speed stage.

On the other hand, when the engagement between the first dog clutch 3 and the second dog clutch 5 is released and the first friction clutch mechanism 015 is engaged, the angular velocities of the second planet carrier 235 and the third sun gear shaft 245 become equal. Therefore, the angular velocities of the second sun gear shaft 241 and the third sun gear shaft 245 are also equal, and the rotation of the third sun gear shaft 245 is not decelerated and becomes the same as that of the second sun gear shaft 241, which is the input member. Therefore, this state is the high speed stage of the fifth and sixth two-speed transmissions 027 and 030 .

Shifting from the low speed stage to the high speed stage and from the high speed stage to the low speed stage is the same as in the eighth embodiment. In the case of the eighth embodiment, the speed reduction ratio of the low-speed stage must be larger than 2, but in the case of the present embodiment, the speed reduction ratio can be implemented in a wide range including 2, and the range of selection of the speed reduction ratio is widened.

1 Torque transmission shaft 2a First boss 2b Second boss 3 First dog clutch 4 Bearing 5 Second dog clutch 7a First rotor 7b Second rotor 7c Internal gear 9a First hub 9b Second hub 13a First sleeve 13b Second sleeve 45 Rotary actuator 53 Linear actuator 61 Third elastic body 65a First rotary arm 65b Second rotary arm 95 Fourth elastic body 99 Third rotary arm 129 Drive shaft 131a Low speed drive gear 131b High speed drive gear 133 Driven shaft 135a low speed driven gear 135b high speed driven gear 147a first friction member 147b second friction member 173 second friction clutch actuator 177 first planet carrier 179 first planet pinion 187 first sun gear shaft 189 first sun gear 213 first friction clutch actuator 225 First gear 227 Second gear 235 Second planet carrier 239 Second sun gear 241 Second sun gear shaft 243 Third sun gear 245 Third sun gear shaft 247 Second planet pinion 257 Third gear 259 Fourth gear 03 First pressing Means 05 Second pressing means 07a First shift mechanism 07b Second shift mechanism 07c Third shift mechanism 07d Fourth shift mechanism 07e Fifth shift mechanism 07f Sixth shift mechanism 09 Case 015 First friction clutch mechanism 017 Second friction clutch mechanism 037 Differential gear set 039 Torque cam mechanism

Claims (11)

A first rotating body rotatably supported by a case, which will be described later, and a first dog clutch provided on the first rotating body, where H is the distance from the tooth root to the tooth tip, and the first dog clutch, which will be described later, A point A where X<H is defined on the tooth surface on the side that transmits positive torque (drive torque) to the second dog clutch, and the tooth surface from point A to the tooth tip H is parallel to the rotation axis or the second clutch. An inclined surface is provided that is inclined in the retracting direction and connects the tooth bottom from the point A, and the tooth surface that transmits negative torque (coast torque) to the second dog clutch of the first dog clutch extends from the tooth bottom to X-Δ Parallel to the axis of rotation or in the direction of pulling in or disengaging the second meshing clutch up to a distance of X, slightly inclined below the friction angle, and from the above X-ΔX to the tip of the tooth H is 45 with respect to the above-mentioned rotation axis. a first dog clutch composed of slopes inclined at an angle of 80 degrees or more, and a drive side tooth flank of the drive tooth flank of the first dog clutch at the same angle from X to tip H of the drive tooth flank of the first dog clutch with respect to the rotation axis. The coast tooth flank has the same angle as the tooth flank from the bottom of the coast tooth flank of the first dog clutch to X-ΔX, and this portion has a tooth profile that contacts each other without a gap, and the inner diameter portion will be described later. Means for receiving thrust in the meshing direction with the first dog clutch by pressing means (to be described later), and shift mechanism (to be described later). A second dog clutch having a means for giving and receiving an axial movement force, a pressing means for applying an axial force to the second dog clutch in a meshing direction with the first dog clutch, and a means for moving the second dog clutch in the axial direction. a shift mechanism that engages and disengages the first dog clutch; an actuator that drives the shift mechanism; a first hub fixed or made integrally with a case, which will be described later, with a fastening member or the like, and whose inner diameter portion engages a bearing that rotatably supports the first rotating body; the first rotating body; A dog clutch mechanism consisting of a case for mounting first and second dog clutches, a first hub, a shift mechanism, an actuator, etc. The first rotating body of claim 1 is a second rotating body rotatably engaged with the outer periphery of a drive shaft or torque transmission shaft rotatably attached to a case, wherein the first hub of claim 1 is: A dog clutch mechanism, comprising: a second hub fastened to or integrally formed with the drive shaft or the torque transmission shaft. The shift mechanism of claims 1 and 2 is composed of a member for driving the second dog clutch and a shift member driven by an actuator, and the members are fixedly fastened or integrally molded so as not to cause relative movement between them, 3. The dog clutch mechanism of claims 1 and 2, wherein a second dog clutch is driven in engagement and disengagement directions with said first dog clutch. 4. A member for driving the second dog clutch according to claim 3 is engaged with a member driven by the actuator so as to be slidable in an axial direction or a swinging direction, and the member driven by the actuator is connected to the second dog clutch. 3. The dog clutch mechanism according to claim 1, wherein the dog clutch is driven only in the direction of disengagement from said first dog clutch through an elastic body, and is driven in the direction of engagement without the elastic body. A member for driving the second dog clutch is driven by the member driven by the actuator in both directions of engagement and disengagement with the first dog clutch via an elastic body. dog clutch mechanism. A dog clutch mechanism according to claims 1 and 2, wherein the means for pressing the second dog clutch in the direction of the first dog clutch and the elastic body of claim 5 are the same member. A drive shaft having means for receiving the output of a driving member such as a motor and rotatably supported by a case with bearings, etc., a low-speed drive gear and a high-speed drive gear rotatably or fixed to the drive shaft, and an external member and a driven shaft rotatably supported by bearings or the like in a case; A two-row gear mechanism consisting of a high-speed driven gear meshing with a drive gear, wherein one of the low-speed drive gear or the low-speed driven gear of the low-speed gear train is fixed to its support shaft, and the other low-speed gear is fixed to its support shaft one high speed gear of the high speed gear train is fixed to the support shaft of the high speed gear and the other high speed gear is rotatably engaged with a support shaft of said gear, and torque is transmitted and released between another high speed gear and the shaft with which said gear is engaged by a friction clutch mechanism. A two-speed transmission, wherein the dog clutch mechanism of claim 7 is the dog clutch of claims 2-6. A high-speed drive gear or a high-speed drive gear in which the friction clutch mechanism of claim 7 is rotatably engaged with the drive shaft or the driven shaft, the drive shaft or the driven shaft passes through the inner diameter portion, and the second boss is supported in the case by bearings. A second clutch having a driven gear, a means for engaging a first friction member with the inner diameter portion of the second boss that is fastened with the bearing interposed on the opposite side of the gear, and a means for receiving the pressing force of the friction member. a housing, and means for engaging a second friction member on an outer diameter portion of the clutch housing at an inner diameter axial position for rotatably engaging the high-speed drive gear or the high-speed driven gear, and a center of the gear. a second friction clutch hub fastened to the drive shaft or the driven shaft penetrating through a portion; a pressing force adjusting member for adjusting the pressing force applied to the first and second friction members; and applying the pressing force to the member. a fastening member that transmits the reaction force of the elastic body to the second clutch housing; a bearing that applies an axial force to the pressing force adjusting member in a direction of reducing the pressing force of the friction member of the elastic body; A second friction clutch mechanism comprising a second friction clutch actuator shaft for applying said axial force to a bearing and a second friction clutch actuator for driving said second friction clutch actuator shaft. The first rotating body of claim 1 is an internal gear described later, and the internal gear engages the internal gear and the outer diameter portion of the first friction member, and the pressing force of the first and second friction members is a first boss rotatably and axially fixedly engaged with the inner diameter of the first hub by a bearing; a first dog clutch; a first planet pinion that meshes with, a first sun gear shaft that receives power from a driving member such as a motor, means for rotatably supporting the first planet pinion, external member driving means for driving an external member, and the a first planet carrier having means for engaging the inner diameter of the second friction member and rotatably engaging the outer circumference of the first sun gear and the inner diameter of the first boss with bearings; and the first sun gear meshing with the first planet pinion, the first dog clutch, the second dog clutch engaging with the first hub, etc. and a first friction clutch mechanism for coupling and disengaging torque between said internal gear and said first planet carrier. The first rotating body of claim 1 is a second planet carrier, which will be described later, which has means for being driven by a driving member such as a motor, and is rotatably supported by a case and the inner diameter of the second planet carrier, which will be described later, by bearings. a second sun gear shaft having a second sun gear; a third sun gear rotatably engaged with the outer periphery of the second sun gear shaft and having a larger pitch diameter than the second sun gear; external member driving means and second friction a third sun gear shaft having a first friction clutch hub with which the inner peripheral portion of the member engages; a third gear meshing with the second sun gear; and a third gear meshing with the third sun gear and having a smaller pitch diameter than the third gear. It has a second planet pinion integrally having four gears, a support shaft that rotatably supports the first dog clutch, the first clutch housing, and the second planet pinion, and rotates with a bearing on the inner diameter of the first hub. A dog clutch according to claims 1, 3 to 6, further comprising: a second planet carrier fixed and supported in the axial direction; a second dog clutch engaged with the first dog clutch and the outer peripheral portion of the first hub; mechanism and a friction clutch mechanism for coupling and disengaging torque between said third sun gear shaft and said second planet carrier.

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