JP2017061954A - Power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a power transmission device capable of smoothly and promptly performing power separating action or power switching action.SOLUTION: A power transmission device 4 is equipped with an idling gear 41 which is provided idly rotatably provided on a rotary shaft 3 and is adjacent to a clutch hub 42 on the rotary shaft, is equipped with a first gear 41b; and a sleeve 43 which is engaged with the clutch hub so as to move in an axis direction CL of the rotary shaft, and can reciprocate between an engaging position S engaged with a spline teeth of the idling gear and a neutral position N disengaged from the spline teeth of the idling gear. A thrust transmission member 44 reciprocating a sleeve in the axial direction is equipped with a first extending portion 44c provided with a first engaging portion 44e engaged with an engaged portion 43b of the sleeve, a second extending portion 44d which is engaged with the engaged portion of the sleeve, and is provided with a second engaging portion 44f separated from the first engaging portion by a predetermined angle about an axis, and a base portion 44b connected with base end portions of the first and second extending portions.SELECTED DRAWING: Figure 1

Description

  The present invention relates to an apparatus for transmitting power from a driving source to a driven part.

  2. Description of the Related Art Conventionally, a power transmission device that can transmit or block power from a driving source to a driving wheel as a driven part is used in a vehicle power train or the like. For example, a power transmission device is used when it is necessary to stop rotation of a rotation shaft that is a transmission destination of rotation or torque while maintaining rotation of an output shaft from a drive source such as an engine or an electric motor. Further, when the vehicle is driven by driving the engine, a power transmission device that cuts off the transmission of power to the electric motor is used so that the electric motor does not become rotational resistance.

  Patent Document 1 describes a so-called dog clutch 56 as a power transmission device. A hub is integrally formed on the outer peripheral surface of the motor output shaft MOS on the transmission side (Patent Document 1: right side in FIG. 7). Spline teeth are formed on the outer peripheral surface of the hub, and an annular sleeve 71 in which inner teeth that engage with the spline teeth are formed is fitted on the spline teeth. The sleeve 71 is slidable in the axial direction with respect to the hub. A motor output gear 54 is provided adjacent to the transmission side of the hub. The motor output gear 54 is provided so as to be rotatable relative to the motor output shaft MOS on the same axis. A cylindrical protrusion is integrally formed on the hub side surface of the motor output gear 54, and spline teeth that engage with the inner teeth of the sleeve 71 are formed on the outer peripheral surface of the cylindrical protrusion.

  An outer circumferential groove is provided on the outer circumferential surface of the sleeve 71, and the tip of the shift fork 73 is engaged with the outer circumferential groove. The shift fork 73 is fixed to a shift rod 72 slidably provided on the transmission case in a direction along the axial direction of the motor output shaft MOS. The shift fork 73 moves in a direction along the rotational axis direction of the motor output shaft MOS, and moves the sleeve 71 between the hub and the motor output gear 54. When the sleeve 71 is positioned at a position straddling both the spline teeth of the hub and the spline teeth of the motor output gear 54, the motor output shaft MOS and the motor output gear 54 are integrally rotated to transmit power. .

JP 2005-106266 A

However, in the power transmission device disclosed in Patent Document 1, the shift fork 73 that moves the sleeve 71 is provided on another axis that is located away from the rotation axis of the motor output shaft MOS provided with the sleeve 71. It is fixed to the shift rod 72. Then, the shift fork 73 is engaged with one portion of the outer peripheral groove of the sleeve 71, and the sleeve 71 is moved in the direction along the rotation axis of the motor output shaft MOS. Therefore, a force biased from the shift fork 73 acts on the sleeve 71. The slight inclination of the shift rod 72 caused by such a biased force and the backlash of the sliding portion that slides the shift rod 72 and the transmission case affect the power switching operation that should be smooth, so that the power can be switched quickly. There was a problem of causing trouble.
And in order to operate a shift rod smoothly, it was necessary to generate a big thrust, and there existed a problem that the necessity of aiming at the enlargement of an actuator and the increase in the energization current in an electric actuator occurred.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a power transmission device capable of smoothly and quickly performing an operation of separating power and an operation of switching power.

  In order to solve the above-mentioned problem, the structural feature of the invention according to claim 1 is that in the power transmission device, the case, the rotating shaft rotatably supported by the case, and the rotating shaft are integrally rotated. A clutch hub provided, an idler gear provided adjacent to the clutch hub on the rotary shaft and free to rotate on the rotary shaft, and having spline teeth coaxially; and formed in an annular shape, the clutch hub And a meshing position that meshes with the spline teeth of the idler gear and the spline of the idler gear, and is meshed with the clutch hub so as to be movable along the axial direction of the rotary shaft. A sleeve capable of reciprocating between a tooth and a disengaged neutral position; and a thrust transmission member for reciprocating the sleeve along the axial direction. The thrust transmission member includes a first engagement portion that engages with an engaged portion of the sleeve so as to be circumferentially slidable, and is continuous with the first engagement portion from the first engagement portion in the axial direction. A first extending portion extending along an engagement portion that engages with an engaged portion of the sleeve so as to be able to slide in the circumferential direction, and is about the axis with respect to the first engaging portion. A second engaging portion that is separated by a predetermined angle; a second extending portion that is continuous with the second engaging portion and extends from the second engaging portion along the axial direction; and the first and second portions And a base portion to which the base end portion of the extending portion is connected.

  According to this, when the sleeve is reciprocated along the axial direction, the sleeve is engaged by the first engaging portion, the first engaging portion, and the second engaging portion separated by a predetermined angle around the axis. The When the thrust transmission member reciprocates, the base end portion of the first extension portion and the base end portion of the second extension portion are connected by the base portion, so that the first engagement portion continuous with the first extension portion And the second engaging portion continuous with the second extending portion move simultaneously. Therefore, the sleeve engaged by the first engagement portion and the second engagement portion can move between the clutch hub and the idler gear in a state where no thrust bias occurs. In this way, the sleeve moves without causing inclination or backlash, so that smooth and quick disconnection and connection of power transmission can be performed.

1 is a schematic view showing a first embodiment of a power disconnecting device according to the present invention in cross section. It is a top view which shows a thrust transmission member. It is a front view which shows a thrust transmission member. It is a schematic diagram showing a second embodiment of the power disconnecting device in cross section. It is the schematic which shows 3rd embodiment of a power disconnecting apparatus in a cross section. It is the schematic which shows 4th embodiment of a power disconnection apparatus in a cross section. It is the schematic which shows 5th embodiment of a power disconnection apparatus in a cross section.

(First embodiment)
Hereinafter, a first embodiment in which a power transmission device according to the present invention is applied to a speed increasing device 1 will be described with reference to the drawings. FIG. 1 is a schematic diagram showing the speed increasing device 1 in a cross-sectional view.
The speed increasing device 1 includes a case 2, an input shaft 3, a power disconnecting device 4 as a power transmission device, an output shaft 6, and an actuator 7. Moreover, the input shaft 3 in this embodiment is a rotating shaft according to the present invention.

  The case 2 is formed of, for example, an aluminum alloy or the like, and has a gear chamber main body 21 that is formed in a substantially cylindrical shape, a first wall 22 that closes one end of the gear chamber main body 21, and the gear chamber main body 21 in the left-right direction. A second wall 23 is provided. A storage chamber 24 in which a base portion of a thrust transmission member, which will be described later, is stored is provided at a lower portion of the first wall 22 on the outer side (left side in FIG. 1) so as to protrude to the outside of the first wall 22. The storage chamber 24 includes a cylindrical first storage space 25 extending in the horizontal direction, and a square cylindrical second storage space 26 provided on the gear chamber main body 21 side continuously to the first storage space 25. Have. In the first housing space 25, a base portion 44b of a thrust transmission member 44 described later is housed. The second accommodating space 26 accommodates base end portions of a first extending portion 44c and a second extending portion 44d, which will be described later, continuing from the base portion 44b. A pair of guide holes 26a through which the first extension portion 44c and the second extension portion 44d pass are formed in the first wall 22 facing the second accommodation space 26 in the horizontal direction. On the outer wall 27 side (left wall side in FIG. 1) of the first housing space 25, a connecting hole 27 a that connects a motor output shaft 7 a of the actuator 7 described later and a thrust transmission member 44 is provided.

  The input shaft 3 is rotatably supported by the case 2 below the gear chamber body 21. That is, one end (the left end in FIG. 1) of the input shaft 3 is rotatably attached to the first wall 22 via the first bearing 22a. The other end (right end in FIG. 1) of the input shaft 3 is rotatably attached to the second wall 23 via a second bearing 23a.

  The output shaft 6 is rotatably supported by the case 2 at the upper part of the gear chamber main body 21. That is, one end (the left end in FIG. 1) of the output shaft 6 is rotatably attached to the first wall 22 via the third bearing 22b. The other end (right end in FIG. 1) of the output shaft 6 is rotatably attached to the second wall 23 via a fourth bearing 23b.

An intermediate shaft 8 is provided between the input shaft 3 and the output shaft 6. The intermediate shaft 8 is rotatably supported on the case 2. That is, one end (the left end in FIG. 1) of the intermediate shaft 8 is rotatably attached to the first wall 22 via the fifth bearing 22c. The other end (right end in FIG. 1) of the intermediate shaft 8 is rotatably attached to the second wall 23 via a sixth bearing 23c.
The input shaft 3 is provided so that, for example, a driving force of an engine (not shown) can be input via a clutch (not shown).
The input shaft 3 is provided with an idle gear 41 described later. A helical gear 41 a is formed on the outer peripheral surface of the idle gear 41.

  A first intermediate gear 8 a is provided on the outer peripheral surface of the intermediate shaft 8. A helical gear that meshes with a helical gear 41a formed on the outer peripheral surface of the idle gear 41 is formed on the outer peripheral surface of the first intermediate gear 8a. The first intermediate gear 8a is provided to rotate integrally with the intermediate shaft 8. The number of teeth of the helical gear of the first intermediate gear 8 a is smaller than the number of teeth of the helical gear 41 a of the idle gear 41. On the outer peripheral surface of the intermediate shaft 8, a second intermediate gear 8b is provided adjacent to the first intermediate gear 8a. The second intermediate gear 8b is provided to rotate integrally with the intermediate shaft 8. A helical gear is formed on the outer peripheral surface of the second intermediate gear 8b. The number of teeth of the helical gear of the second intermediate gear 8b is larger than the number of teeth of the helical gear of the first intermediate gear 8a.

  An output gear 6 a is provided on the outer peripheral surface of the output shaft 6. A helical gear that meshes with the helical gear of the second intermediate gear 8b is formed on the outer peripheral surface of the output gear 6a. The number of teeth of the helical gear of the output gear 6a is smaller than that of the helical gear of the second intermediate gear 8b.

  The power separation device 4 includes an idle gear 41, a clutch hub 42, a sleeve 43, and a thrust transmission member 44. An idle gear 41 is attached to the outer peripheral surface of the input shaft 3 via a needle bearing (not shown) so as to be freely rotatable (relatively rotatable). As described above, the helical gear 41 a is formed on the outer peripheral surface of the idle gear 41. The surface of the idle gear 41 on the first wall 22 side is provided with a cylindrical protrusion that protrudes toward the first wall 22 and is formed around the input shaft 3, and spline teeth 41 b are provided around the cylindrical protrusion. It is installed.

  Further, on the outer peripheral surface of the input shaft 3, on the first wall 22 side of the idle gear 41, a clutch hub 42 is provided side by side so as to be adjacent to the idle gear 41. The clutch hub 42 is formed in an annular shape and is provided to rotate integrally with the input shaft 3 by spline fitting or press-fitting. Spline external teeth 42 a are formed on the outer peripheral surface of the clutch hub 42.

  The sleeve 43 is formed in an annular shape, and an outer peripheral groove 43a as an engaged portion is formed on the outer peripheral surface. Spline inner teeth 43 b that engage with the spline outer teeth 42 a of the clutch hub 42 are formed on the inner peripheral surface of the sleeve 43. Due to the engagement between the spline inner teeth 43 b of the sleeve 43 and the spline outer teeth 42 a of the clutch hub 42, the sleeve 43 is fitted to the clutch hub 42 so as to be movable in the direction of the axis CL of the input shaft 3. The sleeve 43 is movable between a meshing position S where the spline inner teeth 43b mesh with the spline teeth 41b of the idler gear 41 and a neutral position N where the spline inner teeth 43b disengages from the spline teeth 41b of the idler gear 41. It is configured.

  As shown in FIGS. 2 and 3, the thrust transmission member 44 includes a columnar connecting member 44a, a disc-shaped base 44b, a first extending portion 44c, a second extending portion 44d, a first engaging portion 44e, and A second engagement portion 44f is provided.

  One end of the connecting member 44 a is connected to the motor output shaft 7 a of the actuator 7 by a joint (not shown), and moves integrally with the motor output shaft 7 a of the actuator 7. The other end of the connecting member 44a is fixed to the center of the base 44b by caulking or welding, for example. The base portion 44b is made of, for example, iron, and the base end portions of the first extension portion 44c and the second extension portion 44d are integrally fixed to the outer peripheral end of the base portion 44b. The first extending portion 44c includes a first parallel portion 44c1 extending in a direction parallel to the axis 44b1 of the base portion 44b, an extending portion 44c2 extending in the outer diameter direction continuously to the first parallel portion 44c1, and an extension. A second parallel portion 44c3 extending in a direction parallel to the axis 44b1 of the base portion 44b and extending away from the base portion 44b is provided continuously to the portion 44c2. The shape of the second extending portion 44d is the same as that of the first extending portion 44c, and similarly includes a first parallel portion 44d1, an extended portion 44d2, and a second parallel portion 44d3. The first extending portion 44c includes a first engaging portion 44e at the tip of the second parallel portion 44c3.

  The first engaging portion 44e is made of, for example, a low friction / wear resistant resin and is formed in a substantially rectangular parallelepiped shape. The first engaging portion 44 e has a proximal end portion fixed to the first extending portion 44 c and a distal end portion provided to face the outer peripheral surface of the sleeve 43. A contact portion 44e1 having a circular curved surface along the outer peripheral groove 43a of the sleeve 43 is formed at the tip of the first engagement portion 44e. The first engaging portion 44e engages with the outer circumferential groove 43a of the sleeve 43 so as to be slidable in the circumferential direction, and restricts the movement of the sleeve 43 along the axis CL direction. The second engaging portion 44f is formed in the same manner as the first engaging portion 44e and has a similar contact portion 44f1. The second engaging portion 44f is provided 180 degrees (predetermined angle) around the axis 44b1 of the base portion 44b with respect to the first engaging portion 44e.

  In the present embodiment, when the thrust transmission member 44 is housed in the housing chamber 24 and assembled to the actuator 7, the shaft center of the motor output shaft 7 a and the shaft center 44 b 1 of the base portion 44 b are connected to the axis CL of the input shaft 3. It is arranged coaxially. The first extending portion 44c and the second extending portion 44d are arranged symmetrically across the input shaft 3 and extend parallel to the direction of the axis CL. The first engaging portion 44e and the second engaging portion 44f are positions in which the outer circumferential groove 43a of the sleeve 43 is symmetric about the axis CL of the input shaft 3 and are 180 degrees apart from each other around the axis CL. Are engaged.

As the actuator 7 for reciprocating the thrust transmission member 44, for example, a linear motor described in Japanese Patent Application Laid-Open No. 2008-259413 can be used. In this linear motor, a plurality of coils are juxtaposed along the axial direction of the motor output shaft to form a cylindrical core, and a plurality of N-pole magnets are attached to the motor output shaft passing through the through hole of the core. It is configured by alternately arranging S-pole magnets. By controlling energization to each coil, the motor output shaft 7a can be reciprocated and positioned at an arbitrary position.
A position sensor 5 is provided at an opening end portion of the connection hole 27a of the outer wall 27 facing the first accommodation space 25 so that the stroke position of the motor output shaft 7a can be detected. As the position sensor 5, for example, various position sensors such as an optical position sensor and a linear encoder can be used. The detected stroke position is transmitted to a control device (not shown). The actuator 7 is connected to a power source via a control circuit such as a switching element, and the stroke is controlled by the control device.

(Operation)
Next, the operation of the power disconnecting device 4 of the first embodiment configured as described above will be described below with reference to FIG.
The control device (not shown) positions the motor output shaft 7a of the actuator 7 at the retracted end. As a result, the thrust transmission member 44 positions the sleeve 43 at the neutral position N. The input shaft 3 is rotated by a driving force from an engine (not shown) as a power source. The idle gear 41 is in a state where the rotation is stopped.

The control device drives the actuator 7 to advance the motor output shaft 7a. The thrust transmission member 44 moves to the second wall 23 side along the axis line CL direction. The outer peripheral groove 43a of the sleeve 43 is engaged at a symmetrical position with the axis CL between the first engaging portion 44e and the second engaging portion 44f. Therefore, the first engaging portion 44e and the second engaging portion 44f move simultaneously, so that the thrust for moving the sleeve 43 does not become biased. The sleeve 43 can move smoothly and quickly from the neutral position N to the meshing position S.
Therefore, in order to operate the sleeve 43 smoothly, it is not necessary to generate a large thrust in the actuator 7, and it is not necessary to increase the size of the actuator 7 or increase the energization current in the actuator 7.
The position of the sleeve 43 that moves from the neutral position N to the meshing position S is detected by a position sensor 5 that detects the stroke position of the motor output shaft 7 a of the actuator 7. The control device controls the advance amount of the motor output shaft 7 a based on the stroke position of the motor output shaft 7 a corresponding to the position of the sleeve 43.

When the spline inner teeth 43b of the sleeve 43 mesh with the spline teeth 41b of the idle gear 41 at the meshing position S, the idle gear 41 starts to rotate.
In the gear configuration of the present embodiment, the number of teeth of the helical gear on the input shaft side is larger than the number of teeth of the helical gear on the output shaft side to be meshed. Rotate. Further, in the intermediate shaft 8, since the second intermediate gear 8b on the output shaft side has a larger number of teeth and the gear diameter is larger than that of the first intermediate gear 8a on the input shaft side, the first intermediate gear 8a and the second intermediate gear 8b Are integrally rotated to produce the same effect as that on the output shaft side is increased.
As described above, the speed increasing device 1 of the first embodiment can increase the rotation input from the engine to the input shaft 3 and output it from the output shaft 6.

  As is clear from the above description, the power disconnecting device 4 of the first embodiment is provided so as to rotate integrally with the case 2, the input shaft 3 rotatably supported by the case 2, and the input shaft 3. The clutch hub 42, the input shaft 3 adjacent to the clutch hub 42 and provided in the input shaft 3 for free rotation, and the spline gear 41b coaxially provided with the spline teeth 41b are formed in an annular shape. Of the idle gear 41 and the meshing position S meshed with the spline teeth 41b of the idle gear 41 and meshed with the clutch hub 42 so as to be movable along the axis CL direction of the input shaft 3. A sleeve 43 capable of reciprocating between the spline teeth 41b and the disengaged neutral position N; and a thrust transmission member 44 for reciprocating the sleeve 43 along the direction of the axis CL. Thus, the thrust transmission member 44 is engaged with the outer peripheral groove 43a of the sleeve 43 so as to be slidable in the circumferential direction, and the first engagement portion 44e is connected to the first engagement portion 44e. A first extending portion 44c extending along the axis CL direction, and an engaging portion that engages with the outer circumferential groove 43a of the sleeve 43 so as to be capable of sliding in the circumferential direction, with respect to the first engaging portion 44e. A second engagement portion 44f that is separated by a predetermined angle around the axis CL, and a second extension portion 44d that is continuous with the second engagement portion 44f and extends from the second engagement portion 44f along the axis CL direction. , And a base portion 44b to which the base end portions of the first and second extending portions 44c and 44d are connected.

  According to this, when the sleeve 43 is reciprocated along the axis CL direction by the thrust transmission member 44, the sleeve 43 is separated from the first engagement portion 44e and the first engagement portion 44e by a predetermined angle around the axis CL. Engaged with the second engagement portion 44f. When the thrust transmission member 44 reciprocates, the base end portion of the first extension portion 44c and the base end portion of the second extension portion 44d are connected by the base portion 44b, so that the first extension portion 44c continues. The first engaging portion 44e and the second engaging portion 44f in which the second extending portion 44d is continuous move simultaneously. Therefore, the sleeve 43 engaged by the first engagement portion 44e and the second engagement portion 44f can move between the clutch hub 42 and the idler gear 41 in a state where no thrust bias occurs. . As described above, the sleeve 43 moves without causing inclination or backlash, so that the power transmission can be disconnected and connected smoothly and quickly. Therefore, in order to operate the sleeve 43 smoothly, it is not necessary to generate a large thrust in the actuator 7, and it is not necessary to increase the size of the actuator 7 or increase the energization current to the actuator 7.

Further, the power separating device 4 includes an actuator 7 that reciprocates the thrust transmission member 44 between the meshing position S and the neutral position N.
According to this, the thrust generated in the actuator 7 is transmitted to the sleeve 43 without deviation through the first engagement portion 44e and the second engagement portion 44f. Since the sleeve 43 moves without causing inclination or backlash, the power can be disconnected and connected smoothly and quickly.

In the first embodiment, the second engagement portion 44f is set to an angular position that is 180 degrees apart about the axis CL of the input shaft 3 with respect to the first engagement portion 44e. As long as the rigidity of the one extending portion and the second extending portion is high, the first engaging portion and the second engaging portion need only be able to move at the same time, and may not be symmetrical across the rotation axis. For example, the first engagement portion and the second engagement portion may have an angular position separated by 160 degrees.
In addition, although the axis of the motor output shaft 7a of the actuator 7 and the axis 44b1 of the base 44b coincide with the axis CL of the input shaft 3, the present invention is not limited to this. For example, the axis is connected to the motor output shaft 7a. The connecting member 44a may be connected to a position shifted from the axis 44b1 of the base 44b. In this case, the first extension part, the second extension part, and the base part have high rigidity, and the thrust from the motor output shaft 7a is transmitted to the first engagement part and the second engagement part without deviation. Anything is acceptable.
In addition, the engagement portion that engages the sleeve 43 is not limited to the two positions of the first engagement portion and the second engagement portion. For example, the engagement portions are engaged at three angular positions 120 degrees apart from each other. A part may be provided.
Further, an input shaft connected to a power source such as an engine and an output shaft connected to the driven part may be provided in reverse. As a result, the reduction gear can be configured using the power disconnecting device.

Further, the connecting member 44a is connected to the actuator 7. However, the present invention is not limited to this. For example, the connecting member is connected to the manual shift operating mechanism, and the thrust transmission member is reciprocated by manual operation instead of the actuator. It may function as a power disconnecting device.
Although the actuator 7 is an electric linear actuator, the present invention is not limited to this. For example, a hydraulic actuator may be used.
Further, the engaged portion of the sleeve 43 is the outer peripheral groove 43a, but is not limited to this, and may be a protrusion formed over the outer periphery of the sleeve, for example. In this case, the first engaging portion and the second engaging portion may each have a groove portion that supports the side surface of the protrusion from both sides.

(Second embodiment)
Next, a second embodiment in which the power disconnecting device (power transmission device) according to the present invention is applied to the speed increasing device 101 will be described with reference to FIG.
The power disconnecting device 104 in the speed increasing device 101 of the second embodiment is provided with a coil spring 144a1 as an elastic member around a connecting member 144a provided in the first accommodation space 25 of the accommodation chamber 24. However, it differs from the first embodiment.
The coil spring 144a1 is disposed in a compressed state between the surface of the outer wall 27 facing the first housing space 25 and the surface of the base portion 44b facing the first housing space 25. Since other configurations are the same as those of the first embodiment, the same reference numerals are given and description thereof is omitted.

  The power separating device 104 according to the second embodiment urges the sleeve 43 toward the meshing position S by moving the thrust transmission member 44 by the urging force of the coil spring 144a1. The thrust transmission member 44 positions the sleeve 43 at the meshing position S by abutting a contact member 262 provided at a position where the extended portions 44c2 and 44d2 face the second accommodation space 26 of the first wall 22. Yes. When the actuator 7 is driven, the actuator 7 generates a thrust stronger than the biasing force of the coil spring 144a1 in the direction opposite to the biasing force, moves the thrust transmission member 44, and positions the sleeve 43 at the neutral position N. At that time, the thrust transmission member 44 positions the sleeve 43 at the neutral position N by abutting a contact member 261 provided at a position where the extended portions 44c2 and 44d2 face the second housing space 26 of the outer wall 27. Stop.

The power disconnecting device 104 of the second embodiment constitutes a power disconnecting device as a normal close. Moreover, since the actuator 7 only needs to move the thrust transmission member 44 in one direction, the low-cost actuator 7 can be used. Further, the power separation device 104 having a very simple structure can be obtained without requiring a position sensor or complicated control.
Other functions and effects are the same as those of the first embodiment, and a description thereof will be omitted.
As is clear from the above description, the power disconnecting device 104 according to the present embodiment includes the coil spring 144a1 that biases the sleeve 43 toward the meshing position S.

According to this, the thrust applied to the thrust transmission member 44 may be generated in one direction, and a simple and low-cost apparatus can be obtained without requiring a complicated mechanism for reciprocating. Moreover, as the power disconnection device 104, a normal closed state can be formed by setting the direction in which the urging force of the coil spring 144a1 is generated to a normal state, and safety and functionality can be improved.
Although the coil spring 144a1 is applied as the elastic member that biases the thrust transmission member 44, the present invention is not limited to this, and for example, rubber or a leaf spring may be applied.

(Third embodiment)
Next, a third embodiment in which the power separation device (power transmission device) according to the present invention is applied to the speed increasing device 201 will be described with reference to FIG.
The power disconnecting device 204 in the speed increasing device 201 of the third embodiment is the first embodiment in that the detent mechanism 205 is disposed in the connecting member 244a provided in the first accommodation space 25 of the accommodation chamber 24. Is different.

The detent mechanism 205 includes positioning grooves 205a and 205b, a steel ball 205d that is urged by a spring and fits in the positioning grooves 205a and 205b, and a support rod 205c that incorporates a spring and supports the steel ball 205d so as to be biased. I have.
The positioning grooves 205a and 205b are provided above the outer peripheral surface of the connecting member 244a along the axial direction of the connecting member 244a. The positioning grooves 205a and 205b have a first positioning groove 205a for stopping the thrust transmission member 44 at a position corresponding to the meshing position S of the sleeve 43, and a thrust transmission member 44 at a position corresponding to the neutral position N of the sleeve 43. And a second positioning groove 205b to be stopped. The support rod 205c protrudes from the top wall 27b facing the first accommodation space 25 toward the connecting member 244a.
Since the other configuration is the same as that of the first embodiment, the same reference numerals are given and description thereof is omitted.
As is clear from the above description, the power disconnecting device 204 of the third embodiment includes a detent mechanism 205 that holds the sleeve 43 at either the meshing position S or the neutral position N via the thrust transmission member 44. It is that.

According to this, since the thrust transmission member 44 can hold the sleeve 43 at the meshing position S or the neutral position N by the detent mechanism 205, the sleeve 43 can be positioned reliably and quickly. Further, the thrust transmission member 44 does not need to continuously generate the thrust generated for positioning at the meshing position S or the neutral position N. Thereby, the power disconnection device 204 can reduce the running cost.
Other functions and effects are the same as those of the first embodiment, and thus description thereof is omitted.

(Fourth embodiment)
Next, a fourth embodiment in which a power disconnecting device (power transmission device) according to the present invention is applied to a speed increasing device 301 will be described with reference to FIG.
In the speed increasing device 301 in the fourth embodiment, the intermediate shaft 308 is provided with a power separation device 304 as a power transmission device, and a coil spring 344b that biases the thrust transmission member 44 moves the sleeve 43 to the neutral position N. , The gears of the input shaft 303, the output shaft 306, and the intermediate shaft 308 constituting the speed increasing device 301 are different, and in these respects, the first embodiment is different from the first embodiment. Is different. In the present embodiment, the intermediate shaft 308 corresponds to the rotation shaft.

The differences from the first embodiment will be described below.
The input shaft 303 is provided with an input gear 303a, and a helical gear is formed on the outer peripheral surface of the input gear 303a. The input gear 303a is provided to rotate integrally with the input shaft 303.
An intermediate gear 308 a is provided on the outer peripheral surface of the intermediate shaft 308. A helical gear that meshes with a helical gear formed on the outer peripheral surface of the input gear 303a is formed on the outer peripheral surface of the intermediate gear 308a. The intermediate gear 308a is provided to rotate integrally with the intermediate shaft 308. The number of teeth of the helical gear of the intermediate gear 308a is smaller than the number of teeth of the helical gear of the input gear 303a.

  An idle gear 341 is provided on the outer peripheral surface of the intermediate shaft 308 adjacent to the intermediate gear 308a. The idle gear 341 is attached to the intermediate shaft 308 so as to be idle (relatively rotatable) via a needle bearing (not shown). A helical gear 41 a is formed on the outer peripheral surface of the idle gear 341. The number of teeth of the helical gear 41a of the idle gear 341 is larger than the number of teeth of the intermediate gear 308a. Other configurations of the idle gear 341 in the fourth embodiment are the same as those of the idle gear 41 of the first embodiment.

An output gear 306 a is provided on the outer peripheral surface of the output shaft 306. A helical gear that meshes with the helical gear 341a of the idle gear 341 is formed on the outer peripheral surface of the output gear 306a. The number of teeth of the helical gear of the output gear 306a is smaller than the number of teeth of the helical gear 341a of the idle gear 341.
Further, in the power separating device 304 of the fourth embodiment, the coil spring 344b is compressed between the surface of the base portion 44b facing the second housing space side 26 and the first wall 22 facing the second housing space 26. It is arranged in a state.
Since other configurations are the same as those of the first embodiment, the same reference numerals are given and description thereof is omitted.

  The power separation device 304 of the fourth embodiment biases the sleeve 43 toward the neutral position N via the thrust transmission member 44 by the biasing force of the coil spring 344b. The thrust transmission member 44 positions the sleeve 43 at the neutral position N by abutting against the abutting member 261 provided at the position where the extended portions 44c2 and 44d2 face the second accommodating space 26 of the outer wall 27. When the actuator 7 is driven, the actuator 7 generates a thrust stronger than the biasing force of the coil spring 344b in the direction opposite to the biasing force, moves the thrust transmission member 44, and positions the sleeve 43 at the meshing position S. At this time, the extended portions 44 c 2 and 44 d 2 abut on the abutting member 262 provided at a position facing the second accommodation space 26 of the first wall 22.

  The power disconnecting device 304 of the fourth embodiment constitutes a power disconnecting device as a normally open. Moreover, since the actuator 7 only needs to move the thrust transmission member 44 in one direction, a simple and low-cost actuator can be used. Further, the power separation device 304 having a very simple structure can be obtained without requiring a position sensor or complicated control.

(Fifth embodiment)
Next, a fourth embodiment in which a power separation device (power transmission device) according to the present invention is applied to a transmission 401 will be described with reference to FIG.
The power disconnecting device in the fifth embodiment includes two power disconnecting devices 404 and 405, a first power disconnecting device 404 and a second power disconnecting device 405, and the position of the sleeve 43 in the two power disconnecting devices 404 and 405 is determined. By alternately switching, the transmission 401 that outputs the rotation of the input shaft 403 at a different number of rotations at the output shaft 406 is configured. Further, the gears of the input shaft 403, the output shaft 406, and the intermediate shaft constituting the transmission 401 are different, and the intermediate shaft has two shafts, a first intermediate shaft 408 and a second intermediate shaft 409. These points are different from the first embodiment.

The differences from the first embodiment will be described below.
The input shaft 403 is rotatably supported by the case 2 at the middle position of the gear chamber main body 21. That is, one end (the left end in FIG. 7) of the input shaft 403 is rotatably attached to the first wall 22 via the fifth bearing 22c. The other end (right end in FIG. 7) of the input shaft 403 is rotatably attached to the second wall 23 via a sixth bearing 23c.

  The output shaft 406 is rotatably supported by the case 2 at the lower part of the gear chamber body 21. That is, one end (the left end in FIG. 7) of the output shaft 406 is rotatably attached to the first wall 22 via the seventh bearing 22d. The other end (right end in FIG. 7) of the output shaft 406 is rotatably attached to the second wall 23 via an eighth bearing 23d.

  A first intermediate shaft 408 is provided between the input shaft 403 and the output shaft 406. The first intermediate shaft 408 is rotatably supported by the case 2. That is, one end of the first intermediate shaft 408 (left end in FIG. 7) is rotatably attached to the first wall 22 via the ninth bearing 22e. The other end (right end in FIG. 7) of the first intermediate shaft 408 is rotatably attached to the second wall 23 via a tenth bearing 23e.

  A second intermediate shaft 409 is provided above the input shaft 403. The second intermediate shaft 409 is rotatably supported by the case 2. That is, one end (left end in FIG. 7) of the second intermediate shaft 409 is rotatably attached to the first wall 22 via the eleventh bearing 22f. The other end (the right end in FIG. 7) of the second intermediate shaft 409 is rotatably attached to the second wall 23 via a twelfth bearing 23f. In the present embodiment, the first intermediate shaft 408 and the second intermediate shaft 409 correspond to the rotation shaft.

  A first input gear 403a and a first idle gear 403b are provided on the outer peripheral surface of the input shaft 403. The first input gear 403a is provided to rotate integrally with the input shaft 403. The first idle gear 403b is provided on the input shaft 403 so as to be idle. Helical gears are formed on the outer peripheral surfaces of the first input gear 403a and the first idle gear 403b, respectively.

  On the outer peripheral surface of the first intermediate shaft 408 provided between the input shaft 403 and the output shaft 406, the second idler gear 441 is rotatable (relatively rotatable) via a needle bearing (not shown). Is attached. A helical gear 441 a that meshes with a helical gear formed on the outer peripheral surface of the first input gear 403 a is formed on the outer peripheral surface of the second idle gear 441. The number of teeth of the helical gear 441a of the second idle gear 441 is larger than the number of teeth of the helical gear of the first input gear 403a. The second idle gear 441 constitutes a part of the first power disconnecting device 404. Other configurations of the second idle gear 441 are the same as those of the idle gear 41.

  A first intermediate gear 408 a is provided on the first intermediate shaft 408 adjacent to the second idle gear 441. The first intermediate gear 408a is provided to rotate integrally with the first intermediate shaft 408. A helical gear is formed on the outer peripheral surface of the first intermediate gear 408a. The number of teeth of the helical gear of the first intermediate gear 408a is smaller than the number of teeth of the helical gear of the second idler gear 441. The first intermediate shaft 408 is provided with a third idle gear 408b on the opposite side of the second idle gear 441 across the first intermediate gear 408a. The third idle gear 408b is provided on the first intermediate shaft 408 so as to be idle. A helical gear is formed on the outer peripheral surface of the third idle gear 408b.

  A first output gear 406 a and a second output gear 406 b are provided on the outer peripheral surface of the output shaft 406. The first output gear 406a and the second output gear 406b are provided to rotate integrally with the output shaft 406. A helical gear that meshes with the helical gear of the first intermediate gear 408a is formed on the outer peripheral surface of the first output gear 406a. The number of teeth of the helical gear of the first output gear 406a is larger than the number of teeth of the helical gear of the first intermediate gear 408a. A helical gear is also formed on the outer peripheral surface of the second output gear 406b.

A second intermediate shaft 409 is provided on the opposite side of the first intermediate shaft 408 across the input shaft 403. A fourth idle gear 442 is attached to the outer peripheral surface of the second intermediate shaft 409 via a needle bearing (not shown) so as to be freely rotatable (relatively rotatable). A helical gear 442a that meshes with the helical gear of the first input gear 403a is formed on the outer peripheral surface of the fourth idler gear 442. The number of teeth of the helical gear 442a of the fourth idler gear 442 is larger than the number of teeth of the helical gear of the first input gear 403a. The fourth idle gear 442 constitutes a part of the second power separation device 405. Other configurations of the fourth idle gear 442 are the same as those of the idle gear 41.
A second intermediate gear 409 a is provided on the outer peripheral surface of the second intermediate shaft 409 adjacent to the fourth idle gear 442. The second intermediate gear 409a is provided to rotate integrally with the second intermediate shaft 409. A helical gear is formed on the outer peripheral surface of the second intermediate gear 409a. The number of teeth of the helical gear of the second intermediate gear 409a is smaller than the number of teeth of the helical gear 442a of the fourth idler gear 442.

The helical gear of the second intermediate gear 409a meshes with the helical gear of the first idler gear 403b provided on the input shaft 403. The number of teeth of the helical gear of the second intermediate gear 409a is slightly larger than the number of teeth of the helical gear of the first idle gear 403b. The helical gear of the first idle gear 403b meshes with the helical gear of the third idle gear 408b provided on the first intermediate shaft 408. The number of teeth of the helical gear of the first idle gear 403b is slightly larger than the number of teeth of the helical gear of the third idle gear 408b. The helical gear of the third idle gear 408b meshes with the helical gear of the second output gear 406b provided on the output shaft 406. The number of teeth of the helical gear of the third idle gear 408b is larger than the number of teeth of the helical gear of the second output gear 406b.
The actuators 7 of the first power disconnecting device 404 and the second power disconnecting device 405 are connected to a power supply (not shown) via a control circuit such as a switching element. The stroke position of the motor output shaft 7a of the actuator 7 is detected by the position sensor 5, and the detected stroke position is transmitted as position data to a control device (not shown). The control device controls the sleeve 43 in the first power disconnecting device 404 and the second power disconnecting device 405 so that the sleeves 43 are positioned at positions opposite to each other in the meshing position S and the neutral position N. Two power disconnecting devices 404 and 405 function as the transmission 401.
Since other configurations are the same as those of the first embodiment, the same reference numerals are given and description thereof is omitted.

(Operation)
Next, the operation of the power disconnecting device in the fifth embodiment will be described with reference to FIG. The control device (not shown) drives the actuator 7 to position the sleeve 43 at the meshing position S in the first power disconnecting device 404. In the second power disconnecting device 405, the sleeve 43 is positioned at the neutral position N.

  The input shaft 403 is rotated by a driving force from an engine (not shown) as a power source, and the first input gear 403a rotates integrally with the input shaft 403. The first idle gear 403b is idle with respect to the input shaft 403.

  The first input gear 403a meshes with the helical gear 441a of the second idle gear 441 and the helical gear 442a of the fourth idle gear 442. Since the fourth idle gear 442 is not engaged with the sleeve 43, it is idle with respect to the second intermediate shaft 409. The second idle gear 441 is engaged with the sleeve 43 at the meshing position S and rotates the first intermediate shaft 408. The first intermediate gear 408 a is rotated by the first intermediate shaft 408, and the first output gear 406 a meshed with the first intermediate gear 408 a is rotated together with the output shaft 406.

In this case, the gear configuration of the present embodiment is such that the number of teeth of the helical gear on the input shaft side is smaller than the number of teeth of the helical gear on the output shaft side to be meshed, so that the gear on the output shaft side is always in comparison with the gear on the input shaft side. Rotates at a reduced speed. Further, in the first intermediate shaft 408, the number of teeth of the helical gear 441a of the second idler gear 441 on the input shaft side is larger than the number of teeth of the first intermediate gear 408a on the output shaft side. When the first intermediate gear 408a and the first intermediate gear 408a rotate together, the same effect as that obtained when the output shaft is decelerated is produced.
In this case, the rotation input from the engine to the input shaft 403 can be decelerated and output from the output shaft 406.

Next, the control device drives the actuator 7 to position the sleeve 43 at the neutral position N in the first power disconnecting device 404 and to position the sleeve 43 at the meshing position S in the second power disconnecting device 405.
In this case, the rotation of the input shaft 403 is the first input gear 403a, the fourth idler gear 442, the second intermediate gear 409a, the first idler gear 403b, the third idler gear 408b, and the second output gear 406b. , The output shaft 406 is rotated. In this gear configuration, the gear is configured to increase the speed from the second intermediate gear 409a to the second output gear 406b.

  Therefore, in the first power disconnecting device 404, the output shaft 406 is rotated at a faster rotational speed than when the second idle gear 441 is engaged with the sleeve 43, and the power input to the input shaft 403 is output to the output shaft. 406 is output. In other words, the transmission 401 can be configured by switching the first power disconnecting device 404 and the second power disconnecting device 405 alternately to different sleeve positions (engagement position S, neutral position N).

  Thus, even when the two power disconnecting devices 404 and 405 are operated in synchronism, the sleeve 43 has a uniform force that is not biased from the first engaging portion 44e and the second engaging portion 44f. The power to move at the same time works. As a result, the sleeve 43 can smoothly and quickly move between the meshing position S and the neutral position N, and the power of the transmission 401 can be reliably switched.

In the above-described embodiment, the transmission 401 is configured by using two power disconnecting devices 404 and 405 having sleeves at two moving positions of the neutral position N and the meshing position S. However, it is not limited to this. For example, the transmission may be configured by a single power disconnect device in which the sleeve has a neutral position and two meshing positions. That is, a clutch hub fixed to the outer periphery of the rotating shaft, a sleeve fitted to the clutch hub, adjacent to one side of the clutch hub, adjacent to the first idler gear rotating freely with the rotating shaft, and adjacent to the other side of the clutch hub Further, a second idler gear that freely rotates with the rotation shaft may be provided.
In this case, the first extending portion and the second extending portion of the thrust transmission member that moves the sleeve are arranged so as to extend beyond the outer periphery of the first idle gear and the outer periphery of the second idle gear, respectively. What is necessary is just to set it as the structure engaged so that the sleeve which exists between idle gears may be pinched | interposed.

  The present invention is not limited to the embodiment described above and shown in the drawings, and can be implemented with appropriate modifications within a range not departing from the gist.

  2 ... Case, 3 ... Input shaft (rotary shaft), 4 ... Power disconnecting device (power transmission device), 41 ... Free gear, 41b ... Spline teeth, 42 ... Clutch Hub, 43 ... sleeve, 43a ... outer peripheral groove (engaged portion), 44 ... thrust transmission member, 44b ... base, 44c ... first extension, 44d ... first Two extending portions, 44e ... first engaging portion, 44f ... second engaging portion, 7 ... actuator, 104 ... power disconnecting device (power transmission device), 144a1 ... coil spring (Elastic member), 204... Power separation device (power transmission device), 205... Detent mechanism, 303... Input shaft (rotary shaft), 304 .. power separation device (power transmission device), 341 ... Swivel gear, 344b ... Coil spring (elastic member) 403 ... input shaft, 404 ... first power disconnecting device, 405 ... second power disconnecting device, CL ... axis, N ... neutral position, S ... meshing position.

Claims (4)

Case and
A rotating shaft rotatably supported by the case;
A clutch hub provided to rotate integrally with the rotating shaft;
An idler gear provided adjacent to the clutch hub on the rotary shaft and free to rotate on the rotary shaft, and having spline teeth coaxially;
Engagement that is formed in an annular shape, rotates integrally with the clutch hub, meshes with the clutch hub so as to be movable along the axial direction of the rotation shaft, and meshes with the spline teeth of the idler gear A sleeve capable of reciprocating between a position and the spline teeth of the idle gear and a disengaged neutral position;
A thrust transmission member that reciprocates the sleeve along the axial direction, and
The thrust transmission member is
A first engaging portion that engages with an engaged portion of the sleeve so as to be able to slide in the circumferential direction;
A first extending portion that is continuous with the first engaging portion and extends from the first engaging portion along the axial direction;
An engaging portion that engages with an engaged portion of the sleeve so as to be capable of sliding in a circumferential direction, and a second engaging portion that is separated from the first engaging portion by a predetermined angle around the axis;
A second extending portion that is continuous with the second engaging portion and extends from the second engaging portion along the axial direction;
And a base portion to which base end portions of the first and second extending portions are connected.   The power transmission device according to claim 1, further comprising an actuator that reciprocates the thrust transmission member between the meshing position and the neutral position.   The power transmission device according to claim 1, further comprising an elastic member that urges the sleeve toward one of the meshing position and the neutral position.   The power transmission device according to any one of claims 1 to 3, further comprising a detent mechanism that holds the thrust transmission member at either the meshing position or the neutral position.

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