JP2001241548A - Gear ratio switching device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gear ratio switching device reducing the manufacturing cost and minimizing the size of the whole device by eliminating an expensive electromagnetic clutch and using a planetary gear device therein. SOLUTION: The gear ratio switching device 1 comprises all such members at a proximate periphery of an output shaft 4 as the sun gears 8, 12, a fixed plate 13 and a worm wheel 14, the carrier plates 15, 18, a planetary gear shaft 20 and the planetary gears 21, 22 to transmit a reduced turning speed of a driving motor 3 to the output shaft 4. Therefore, the device 1 can minimize the size of the device by eliminating the necessity of the motor turning speed reduction using a plurality of the super gears arranged in parallel to form a multi stage meshing means like prior art. Furthermore, the device 1 can connect and disconnect the output shaft 4 and the driving motor 3 by protruding or retracting a slide pin 6a of a solenoid valve 6. In this way, the device 1 can cut the cost without using the expensive electromagnetic clutch to connect or disconnect the connection between the shaft 4 and motor 3.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gear ratio switching device for switching a gear ratio of a transmission by swinging a manual plate, and more particularly, to a reduction in size of the entire device and a manufacturing cost of the entire device. The present invention relates to a gear ratio switching device capable of reducing the gear ratio.

[0002]

2. Description of the Related Art As a transmission for shifting a vehicle such as an automobile, a transmission using an automatic transmission (hereinafter, referred to as an automatic transmission) using a fluid clutch such as a torque converter has been proposed. The automatic transmission is
A gear ratio switching device driven based on a gear ratio range selected by operating a gear selector switch provided on a driving handle or the like, a manual plate (detent lever) rocked by the gear ratio switching device, and a manual A transmission mechanism for detecting the position of the plate and operating the hydraulic control circuit in accordance with the detection result to switch the magnitude of the torque output from the torque converter.

[0003] The speed ratio switching device mainly includes a drive motor for supplying a rotating torque for swinging the manual plate, and a reduction device for reducing the rotation of the drive motor and transmitting the rotation to the manual plate. In addition, the rotational torque of the drive motor is amplified by the speed reducer and transmitted to the manual plate, thereby causing the manual plate to swing.

[0004] By the way, with the recent reduction in the weight of vehicles, reductions in the size of automatic transmissions and downsizing of transmission ratio switching devices have been attempted. However, if the drive motor is reduced in size in order to reduce the size of the shift switching device, the supply torque of the drive motor is reduced, and it is necessary to reduce the speed by the reduction gear. For example, in a speed reducer used in a certain speed ratio switching device, the speed reduction ratio is set to 1/240, and in order to obtain such a large speed reduction ratio, a plurality of spur gears are arranged in parallel at multiple stages ( For example, it is necessary to reduce the rotation of the drive motor by engaging the gears.

[0005]

However, in the above-described reduction gear in which a plurality of spur gears are meshed in multiple stages, it is necessary to support a plurality of spur gears in parallel with a plurality of shafts. There has been a problem that the reduction gear is increased in size as a whole. On the other hand, in some automatic transmissions, the gear ratio can be switched by operating a gear ratio switching device by operating a gear shift switch, while the gear ratio can also be manually switched by operating a gear shift lever.

In such an automatic transmission, a shift switching lever is connected to a manual plate connected to a speed ratio switching device via a select cable. When the shift switching lever is operated, the shift switch lever is connected to the manual plate via a select cable. When the manual plate is pulled or pushed, the manual plate is swung. Therefore, when the manual plate is manually swung, it is necessary to prevent the force accompanying the swing of the manual plate from being transmitted to the drive motor via the reduction gear.

Therefore, when the drive motor stops, it is necessary to disconnect the connection between the drive motor and the reduction gear. Connection and disconnection of this drive motor and reduction gear
This can be performed by an electromagnetic clutch operated by an electromagnetic force. However, since such an electromagnetic clutch is expensive, there is a problem in that the manufacturing cost of the speed ratio switching device increases in this respect.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and provides a speed ratio switching device capable of reducing the size of the entire device and reducing the manufacturing cost of the entire device. It is intended to be.

[0009]

In order to achieve this object, a gear ratio switching device according to claim 1 includes an output shaft connected to a manual plate that is oscillated to change the gear ratio of a transmission; A drive motor that supplies a rotation torque for rotating the output shaft, a ring gear that is rotatably fitted to the output shaft and is rotated by transmitting the rotation torque of the drive motor, A first planetary gear rotatably supported at an inner position from an outer peripheral edge of the ring gear; and a second planetary gear connected to the center of rotation of the first planetary gear and having the same center of rotation as the first planetary gear. A first sun gear meshed with the first planetary gear and provided on the output shaft; and a second sun gear meshed with the second planetary gear and rotatably fitted to the output shaft. Differential reduction gear having A rotating member connected to the second sun gear of the dynamic reduction gear and having a plurality of engaging portions provided on an outer periphery thereof, and formed to be protrudable toward the rotating member; And an engaging member engaged with one of the portions to lock the rotating member.

According to the gear ratio switching device of the first aspect, when the output shaft is rotated to swing the manual plate, the engaging member is protruded toward the rotating member, and the plurality of engaging members are projected. Engaged with any of the parts. The rotation member is locked by the engagement of the engagement member, and the rotation of the second sun gear is locked. After the engagement, when the driving of the drive motor is started, the rotation torque is transmitted to the ring gear, and the ring gear is rotated. Thereby, the first and second planetary gears revolve around the output shaft, and the first and second planetary gears are revolved by this revolution.
The planetary gear is rotated while meshing with the first and second sun gears. Here, since the rotation of the second sun gear is restrained by the engaging member, only the first sun gear is rotated by the rotation of the first planetary gear, and the rotation causes the output shaft to be rotated.
As described above, when the rotation of the drive motor is reduced by the differential reduction gear and transmitted to the output shaft, the manual plate swings, and the transmission gear ratio is switched.

On the other hand, when the manual plate is manually swung directly, first, the engagement between the engaging member and the engaging portion of the rotating member is released. By this disengagement, the lock of the rotating member is released, and the second sun gear becomes rotatable. Thereafter, when the manual plate is manually swung, the output shaft is turned, and the first sun gear is turned. When the first planetary gear rotates by this rotation, the second planetary gear also rotates and the second sun gear rotates. The rotation of the second sun gear causes the rotation member to idle, but is not transmitted to the ring gear. For this reason, even if the manual plate is manually swung and the output shaft is rotated by this, the rotation is not transmitted to the drive motor.

According to a second aspect of the present invention, there is provided the speed ratio switching device according to the first aspect, further comprising a worm threaded on an outer periphery and having a threaded tooth portion connected to the drive motor. The ring gear is provided with a worm wheel having gear teeth meshable with the teeth of the worm threaded on the outer periphery and having a rotation center crossing the axial direction of the worm.

[0013] According to the speed ratio switching device of the second aspect, it operates in the same manner as the speed ratio switching device of the first aspect, and the rotational torque of the drive motor is transmitted to the worm.
The worm is rotated. The teeth of the worm are meshed with the gear teeth of the worm wheel, and the rotation of the worm causes the worm wheel to rotate. The rotation of the worm wheel causes the ring gear to rotate about the output shaft.

According to a third aspect of the present invention, there is provided the speed ratio switching device according to the first or second aspect, wherein the engagement member is disengaged when the rotation angle of the output shaft becomes a predetermined amount or more. A control device that retracts in the protruding direction to release the engagement state between the engagement member and the plurality of engagement portions of the rotation member and stops supply of rotation torque by the drive motor. I have.

According to a fourth aspect of the present invention, there is provided a speed ratio switching device according to any one of the first to third aspects.
When the drive motor is in a stop state, a control device is provided for continuously releasing the engagement state between the engagement member and the plurality of engagement portions of the rotating member.

According to the gear ratio switching device of the fifth aspect,
5. The speed change ratio switching device according to claim 1, wherein rotation of the output shaft is stopped by a detent member that restrains swinging of a manual plate, and the differential deceleration is performed. The gear is configured to make the rotation torque of the output shaft smaller than the detent force of the detent member when the engagement state between the engagement member and the plurality of engagement portions is released.

According to the speed ratio switching device of the fifth aspect,
In addition to operating in the same manner as the gear ratio switching device according to any one of claims 1 to 4, the output shaft is stopped by a detent member that restrains swinging of the manual plate. When the engagement state between the engagement member and the plurality of engagement portions is released, the rotation torque of the output shaft is made smaller than the detent force of the detent member by the differential reduction gear. Therefore, when the output shaft is rotated by a predetermined angle, the engagement state between the engagement member and the plurality of engagement portions is released, and the rotation member is turned to a rotatable state. The manual plate is locked by the locking force, and the rotation of the output shaft is stopped.

According to the gear ratio switching device of the sixth aspect,
6. The speed change ratio switching device according to claim 1, wherein the rotation of the output shaft is stopped by a detent member that restrains swinging of a manual plate, and the differential deceleration is performed. The gear is configured to make the rotation torque of the output shaft greater than the detent force of the detent member when the engagement member and the plurality of engagement portions are engaged.

According to the speed ratio switching device of the sixth aspect,
In addition to operating in the same manner as the speed ratio switching device according to any one of the first to fifth aspects, the output shaft is stopped by a detent member that restrains swinging of the manual plate. When the engagement member and the plurality of engagement portions are engaged with each other, the rotational torque of the output shaft is made larger than the locking force of the detent member by the differential reduction gear. Therefore, when the rotation of the drive motor is started and the output shaft is rotated, the rotation of the rotation member is stopped by engaging the engagement member with the plurality of engagement portions.
The lock of the manual plate by the detent member is released, and the output shaft is rotated.

[0020]

Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings. FIG. 1 is an external view of a gear ratio switching device 1 according to an embodiment of the present invention.
The speed change ratio switching device 1 is a device that amplifies a rotation (rotation) torque supplied from the drive motor 3 and switches the speed ratio of the automatic transmission 30 by rotating the output shaft 4 with the amplified rotation torque. . The gear ratio switching device 1 includes a case body 2, and a drive motor 3 for supplying a rotational torque for rotating the output shaft 4 is attached to the case body 2 by screwing or the like. A worm 17 to be described later is provided on the rotation shaft of the drive motor 3.

The case body 2 is provided with an output shaft 4 that is rotated by receiving rotation torque supplied from the drive motor 3. The output shaft 4 is connected to a manual plate 26 described later.
A shaft member that transmits a rotational torque for swinging (see FIGS. 2 and 3), and is provided so as to penetrate in a depth direction of the case body 2 (a direction perpendicular to the paper surface of FIG. 1).
Further, a valve position sensor 5 is connected to the output shaft 4.

The valve position sensor 5 detects the rotation angle of the output shaft 4 and outputs data of the detected rotation angle to a range switching control circuit C (see FIG. 3) described later. A solenoid valve 6 is attached to the side of the valve position sensor 5 by screwing or the like. The solenoid valve 6 stops the rotation of a fixed plate 13 (see FIG. 2), which will be described later, in accordance with a command (command signal) of the range switching control circuit C.
The details of the range switching control circuit C will be described later.

FIG. 2 is a cross-sectional view of the gear ratio change device 1 taken along the line II-II in FIG. 1, and shows a manual shaft (shaft) 25 connected to the output shaft 4 and a manual plate 2.
6 is shown by a two-dot chain line, and the sun gears 8, 12, the worm wheel 14, the worm 17, and the planetary gear 2
Pitch circles 1 and 22 are shown by dashed lines. Also,
The arrow X in FIG. 2 indicates the direction in which the sliding pin 6a of the solenoid valve 6 projects.

As shown in FIG. 2, the case body 2 is a housing whose inside is formed in a hollow shape, and has an outer surface (FIG. 2).
A valve position sensor 5 and a solenoid valve 6 are mounted on the left side). The solenoid valve 6 is provided with a cylindrical sliding pin 6a at the center thereof.
“a” is configured to be able to protrude toward a fixed plate 13 described later (the direction indicated by the arrow X in FIG. 2) and to be retractable toward the opposite side (the direction opposite the arrow X in FIG. 2). The fixed plate 13 described later is locked by projecting the sliding pin 6a in the direction of arrow X, and the locked state of the fixed plate 13 is released by retracting the sliding pin 6a in the direction of arrow X. is there.

The output shaft 4 is a substantially cylindrical shaft member, and both ends of the output shaft 4 in the axial direction (horizontal direction in FIG. 2) are rotatably supported by the case body 2 via bearings 7, 7. Output shaft 4
The above-mentioned valve position sensor 5 is connected to one end (the left side in FIG. 2) of the output shaft 4, and the other end side (the right side in FIG. 26 are connected. The details of the manual shaft 25 and the manual plate 26 will be described later.

At approximately the center of the output shaft 4 in the axial direction, there is provided a sun gear 8 composed of a spur gear having a plurality of gear teeth engraved on its outer periphery. The sun gear 8 has keys 8a, 8a
Thus, the output shaft 4 is integrally rotated with the rotation of the sun gear 8. Further, a cylindrical sleeve 9 is fitted on the valve position sensor 5 side (left side in FIG. 2) from the fixed position of the sun gear 8 on the output shaft 4, and this sleeve 9 is connected via a ring-shaped spacer 10. It is provided at a distance from the sun gear 8.

A bearing 11 composed of a cylindrical sliding bearing bush or the like is fitted in the inner periphery of the sleeve 9, and the output shaft 4 passes through the inner periphery of the bearing 11. The bearing 11 rotatably holds the sleeve 9 on the outer periphery of the output shaft 4.
And the sleeve 9 can be rotated separately.

At the end of the sleeve 9 on the side of the sun gear 8 (right side in FIG. 2), a sun gear 12 is integrally provided on the outer periphery, and the sun gear 12 has a plurality of gear teeth engraved on the outer periphery. It is composed of spur gears. On the other hand, a substantially disk-shaped fixing plate 13 is integrally provided on the outer periphery of the end of the sleeve 9 on the side opposite to the sun gear 12 (the left side in FIG. 2).
The fixing plate 13 is connected to the sun gear 12 via the sleeve 9.

On the outer periphery of the fixed plate 13, a plurality of substantially semicircular concave recesses 13a are formed at substantially regular angular intervals, and each of the concave recesses 13a is provided with a sliding pin protruding from the solenoid valve 6. 6a is formed so as to be engageable. Therefore, by the engagement of the sliding pin 6a with the engagement recess 13a, the rotation of the fixing plate 13 is restrained, and the rotation of the sun gear 12 is restrained.

On the outer periphery of the output shaft 4, a ring-shaped worm wheel 14 having a plurality of gear teeth 14a engraved on the outer peripheral edge is provided. A disk-shaped carrier plate 15 is fitted and fixed therein. Therefore, with the rotation of the worm wheel 14, the worm wheel 14 and the carrier plate 15 can be synchronously rotated. The carrier plate 15 is rotatably fitted to the outer periphery of the output shaft 4 via a bearing 16, and the worm wheel 14 in which the carrier plate 15 is fitted and the output shaft 4 are separately rotated by the bearing 16. You can do it.

On the other hand, on the outer peripheral edge (lower side in FIG. 2) of the worm wheel 14, the drive motor 3 side (rear side with respect to the plane of FIG. 2) is directed toward the worm wheel 14 (front side with respect to the plane of FIG. 2). An extended worm 17 is provided. The worm 17 is connected to the rotation shaft of the drive motor 3 (see FIG. 1), and is rotated by directly transmitting the rotation torque of the drive motor 3. Warm 17
A worm tooth 17a formed of a spiral single thread is engraved on the outer periphery of the worm.

Further, the worm 17 has its axial direction (perpendicular to the plane of FIG. 2) substantially perpendicular to the direction of the center of rotation of the worm wheel 14 (ie, the axis of the output shaft 4) (horizontal direction in FIG. 2). As the worm teeth 17
a is meshed with the gear teeth 14 a of the worm wheel 14. Therefore, by rotating the worm 17 by the drive motor 3, the worm wheel 14 can be rotated around the output shaft 4.

By transmitting the rotation of the drive motor 3 by the worm 17 and the worm wheel 14 in this manner, the plurality of spur gears are meshed with each other in multiple stages, and
The rotation torque of the drive motor 3 can be greatly amplified as compared with the case where the rotation of the drive motor 3 is decelerated. For example, the gear teeth 14a
The number of teeth of the worm 17 and the number of teeth of the worm tooth 17a to one, so that the worm wheel 1
4 can be reduced to 1/78. That is, the rotational torque of the drive motor 3 can be amplified 78 times and transmitted to the worm wheel 14.

A donut-shaped carrier plate 18 is fitted around the outer periphery of the sleeve 9, and the carrier plate 18 faces the carrier plate 15 at a predetermined interval. The carrier plate 18 is rotatably fitted to the outer periphery of the sleeve 9 via a bearing 19, and the carrier 19 can rotate the carrier plate 18 and the sleeve 9 separately.

The carrier plate 18 is connected to the carrier plate 15 at a predetermined distance by a planetary gear shaft 20 and a plurality of (for example, three) substantially cylindrical supports 24. Therefore, when the carrier plate 15 is rotated around the output shaft 4 with the rotation of the worm wheel 14, the carrier plate 18 is rotated in synchronization with the rotation. By the synchronous rotation of the carrier plates 15 and 18, the planetary gear shaft 20 and the support 24 revolve around the output shaft 4.

The planetary gear shaft 20 includes a pair of planetary gears 21,
The planetary gear 20 is rotatably supported by the carrier plates 15 and 18 via bearings 23 at both ends in the axial direction (left and right directions in FIG. 2). A pair of planetary gears 21 and 22 are integrally formed on the planetary gear shaft 20, and these planetary gears 21 and 22 are formed.
Is constituted by a spur gear in which a plurality of gear teeth are engraved on the outer periphery.

The gear teeth of the planet gear 21 mesh with the gear teeth of the sun gear 8, and the gear teeth of the planet gear 22 mesh with the gear teeth of the sun gear 12. Therefore, when the planetary gear shaft 20 revolves around the output shaft 4 due to the rotation of the worm wheel 14, the planetary gears 21 and 22 accompany the revolution.
Are rotated while meshing with the sun gears 8 and 12, and the rotational torque of the planetary gears 21 and 22 due to the rotation is increased by the sun gears 8 and 1.
It is transmitted to 2.

The center of the planetary gear shaft 20, which is the rotation shaft of the planetary gears 21 and 22, is oriented in substantially the same direction as the shaft center of the output shaft 4 (left and right direction in FIG. 2). Inside the outer edge (or pitch circle) (output shaft 4
Side) is located. Therefore, the worm wheel 14
It is not necessary to provide a gear train composed of a plurality of spur gears outside the outer peripheral edge of the worm wheel 14 in order to transmit the rotational torque of the worm wheel 14 to the output shaft 4. You can do it.

In addition, the sum of the pitch circle radius of the sun gear 8 and the pitch circle diameter of the planetary gear 21 is equal to the worm wheel 1
4 is smaller than the pitch circle radius (or tip circle radius),
In addition, the sum of the pitch circle radius of the sun gear 12 and the pitch circle diameter of the planetary gear 22 is substantially equal to (or smaller than the tooth tip circle radius) of the worm wheel 14. Therefore, the sun gears 8 and 12 and the planetary gears 21 and 22
Are accommodated inside the outer peripheral edge of the worm wheel 14, so that the speed ratio switching device 1 can be further downsized as a whole.

The gear ratio switching device 1 configured as described above
According to the above, the number of teeth zs1 of the sun gear 8, the number of teeth zs2 of the sun gear 12, the number of teeth zp1 of the planetary gear 21, the number of teeth zp2 of the planetary gear 22, the pitch radius rs1 of the sun gear 8, the pitch of the sun gear 12 The circle radius rs2, the pitch circle radius rp1 of the planetary gear 21, the pitch circle radius rp2 of the planetary gear 22, the pitch circle diameter ds1 of the sun gear 8, the pitch circle diameter ds2 of the sun gear 12, the pitch circle diameter dp1 of the planetary gear 21, the planet In the case of the pitch circle diameter dp2 of the gear 22, the sun gear 8, 1
2 and the reduction ratio i by the planetary gears 21 and 22 is 1 / (1-
(Zp1 / zs1) × (zs2 / zp2)) = 1 / (1
− (Rp1 / rs1) × (rs2 / rp2)) = 1 /
(1− (dp1 / ds1) × (ds2 / dp2)).

For example, the sun gears 8 and 12 and the planetary gear 2
The pitch m diameter ds1 of the sun gear 8 is approximately 27 mm, the pitch diameter ds2 of the sun gear 12 is approximately 23 mm, the pitch diameter dp1 of the planetary gear 21 is approximately 15 mm, and the planetary gears 1 and 22 are “1”. 22 pitch circle diameter dp
2 is approximately 19 mm, the reduction ratio i is approximately 3.05, and as a result, the rotation of the drive motor 3 is (1/78)
× (1 / 3.05) = 1/238 times and transmitted to the output shaft 4. That is, the rotational torque of the drive motor 3 is
The power is multiplied by 238 and transmitted to the output shaft 4.

FIG. 3 is a system configuration diagram showing an example of use of the speed ratio switching device 1. As shown in FIG. As shown in FIG. 3, the gear ratio switching device 1 includes a drive motor 3, a valve position sensor 5, and a solenoid valve 6 electrically connected to a range switching control circuit C. The range switch SW is electrically connected. The range switching control circuit C is a circuit for controlling the operation of the speed ratio switching device 1. Specifically, when the occupant operates the range switching switch SW, the rotation angle of the rotation angle detected by the valve position sensor 5 is determined. A circuit for rotating or stopping the drive motor 3 based on the data, and for rotating or stopping the rotating plate 13 by projecting or retracting the sliding pin 6a of the solenoid valve 6.

The range switch SW is connected to the automatic transmission 3
The switch is operated by an occupant to set a gear ratio of 0, and is provided with a driving handle or the like in the vehicle. By operating this range changeover switch SW, the gear ratio of the automatic transmission 30 becomes L when the vehicle moves forward.
(Low) range, 2nd (second) range or 3rd
Three types of (third) ranges, R (reverse) range when the vehicle is moving backward, N (neutral) range when the rotation transmission to the axle 32 is cut off, and P (parking) when the vehicle is parked or stopped
The setting is changed to a total of six ranges.

On the other hand, the output shaft 4 of the gear ratio switching device 1
A substantially repellent manual plate 26 is connected via a manual shaft 25. The manual plate 26 is swung in conjunction with the rotation of the output shaft 4 of the transmission ratio switching device 1,
The armature 29 of the manual valve 29 is caused by the swing.
a is pushed.

A manual shaft 25 is connected to the lower end of the manual plate 26, and the manual plate 26 is supported so as to be swingable in the left-right direction in FIG. The upper edge of the manual plate 26 is formed in a substantially arc shape, and lock recesses 26a to 26f each having a substantially semicircular concave shape are sequentially formed in the upper edge from the left end side. A cylindrical lock pin 27 provided at the tip of a detent spring 28 made of an elastic material is formed in the six lock recesses 26a to 26f so as to be engageable. In FIG. 3, the lock pin 27 is Lock recess 26
d.

The lock pin 27 is urged by the elastic force of the detent spring 28 to the lock concave portions 26a to 26f with which the lock pin 27 is engaged, and the manual plate 26 is positioned by the urging. The lock pin 27
When the rotational torque of the output shaft 4 for swinging the manual plate 26 exceeds the elastic force of the detent spring 28, the output shaft 4 is disengaged from the engaged lock concave portion 26e, and any one of the other lock concave portions 26a to 26c, 26e, and 26f. And the manual plate 26 is positioned.

The gear ratio of the automatic transmission 30 is determined according to the position at which the manual plate 26 and the lock pin 27 are engaged. Specifically, when the lock pin 27 is engaged with the lock recess 26a, the L range is set. When the lock pin 27 is engaged with the lock recess 26b, the lock pin 27 is engaged with the lock recess 26c. 3rd range, lock pin 27 is locked concave 26d
N range, when the lock pin 27 is engaged with the lock recess 26e, the R range, the lock pin 2
When the lock 7 is engaged with the lock recess 26f, the P range is set. In FIG. 3, the lock pin 27 is
In this state, the gear ratio of the automatic transmission 30 is in the N range.

A range switching lever 33 is connected to the manual plate 26 via a select cable 34. The range switching lever 33 is a lever member that is operated by an occupant to switch the gear ratio of the automatic transmission 30, and is disposed on the side of the driver's seat in the vehicle. When the range switching lever 33 is operated by the occupant, the select cable 34 is pulled or pushed, and the manual plate 26 is swung. With this swing, the gear ratio of the automatic transmission 30 is switched via the manual valve 29.

That is, by operating the range switching lever 33, the gear ratio of the automatic transmission 30 can be switched without operating the gear ratio switching device 1. For this reason,
If the range changeover switch SW, the range changeover control circuit C or the gear ratio changeover device 1 fails for some reason, the range changeover lever 33 is operated to operate the automatic transmission 3.
The gear ratio of 0 can be switched.

The end of the armature 29a of the manual valve 29 is in contact with one side surface of the manual plate 26. The manual valve 29 detects the swing position of the manual plate 26 by an armature 29a slid in the left-right direction in FIG. 3 according to the swing of the manual plate 26, and according to the detection result, the automatic transmission 30 For operating the shift valve 30d. The armature 29a is urged to one side (the left side in FIG. 3) of the manual plate 29, and is pushed rightward in FIG. 3 when the manual plate 26 is swung clockwise with respect to the paper surface in FIG. When the manual plate 26 is swung counterclockwise with respect to the paper surface of FIG. 3, the manual plate 26 is moved to the left in FIG. 3 by the urging force.

Next, the automatic transmission 30 will be described.
The automatic transmission 30 is a type of an automatic matching transmission, and is a device that changes the rotation speed of an engine output shaft 31a of a vehicle engine 31 such as an automobile and transmits the rotation speed to an axle 32 that supports driving wheels. This automatic transmission 30
Are mainly composed of a torque converter 30a and a speed change mechanism 30b.
, A differential device 30c, and a shift valve 30d.

The torque converter 30a is a device for transmitting a rotating torque by the turning force of the mission oil filled therein. The transmission of the engine oil is transmitted by the rotation of the engine output shaft 31a, and the turning is performed. It transmits the rotational torque of the engine output shaft 31a to the speed change mechanism 30b via force. The speed change mechanism 30b is a device that changes the speed of rotation transmitted from the torque converter 30a, and increases or decreases the rotational torque from the torque converter 30a by the speed change, and transmits the torque to the differential device 30d.

The transmission mechanism 30b includes, for example, a planetary gear unit composed of a plurality of gears connected to the torque converter 30a, and a clutch and a brake for changing the power transmission path of the planetary gear unit. According to the transmission mechanism 30b, the clutch and the brake are operated by the transmission shift valve 30d to switch the power transmission path of the planetary gear unit, whereby the rotation transmitted from the torque converter 30a is shifted and transmitted to the differential device 30c. . The rotation transmitted to the differential device 30d is transmitted to the axle 3 by the differential device 30c.
2 and the drive wheels of the vehicle are rotated by rotating the axle 32.

Next, with reference to FIGS. 2 and 3, a description will be given of the operation of switching the speed ratio of the automatic transmission 30 by the speed ratio switching device 1. FIG. When the gear ratio of the automatic transmission 30 is switched by the gear ratio switching device 1, first, the shift switch SW is operated to set the L range, the second range, and the like.
One of the 3rd range, N range, R range, and P range is selected. When this selection is made, first, the sliding pin 6a of the solenoid valve 6 is protruded in the direction of arrow X in FIG. This sliding pin 6
By the protrusion of a, the sliding pin 6a is engaged with any one of the engaging recesses 13a of the fixed plate 13, and the rotation of the fixed plate 13 is restrained.

Here, for example, the shift switch SW
When the L range is selected from the N range state,
The rotational drive of the drive motor 3 is started by the range switching control circuit C. When the drive motor 3 is driven to rotate, the worm 17 connected to the rotation shaft is rotated, and the worm 17 causes the worm wheel 14 to rotate around the outer periphery of the output shaft 4. The rotation of the worm wheel 14 causes the planetary gear shaft 20 to revolve around the output shaft 4. As the planetary gear shaft 20 revolves, the planetary gears 21 and 22 mesh with the sun gears 8 and 12, and output. Revolved around axis 4. When the planetary gears 21 and 22 revolve, the planetary gears 21 and 22 rotate while meshing with the sun gears 8 and 12.

The sun gear 8 is rotated by the rotation of the planetary gear 21, and the output shaft 4 is rotated by the rotation of the sun gear 8. On the other hand, the rotation of the fixed plate 13 to which the sun gear 12 is connected is restricted by the sliding pin 6 a of the solenoid valve 6.
Also, the fixed plate 13 is not rotated. Therefore, the rotational torque supplied by the drive motor 3 is amplified and transmitted to only the output shaft 4.

When the rotation of the fixed plate 13 is restrained, the rotation torque of the output shaft 4 becomes larger than the elastic force of the detent spring 28 for urging the lock pin 27, and as a result, the manual plate 26 starts to swing. Is done. For this reason,
In order to start the rotation of the output shaft 4, there is no need to separately provide a device for performing an operation of removing the lock pin 27 biased by the detent spring 28 from the lock recesses 26a to 26f of the manual plate 26. Manufacturing cost can be reduced.

When the manual plate 26 is swung by the output shaft 4, the lock pin 27 is disengaged from the lock recess 26d, and thereafter, the lock pin 27 is released from the lock recess 26c, 2.
6b and 26a are engaged in this order. On the other hand, the rotation angle of the output shaft 4 is detected by the valve position sensor 5 and output to the range switching control circuit C. The range switching control circuit C
Based on the data detected by the valve position sensor 5, it is determined whether or not the output shaft 4 has been rotated by a predetermined angle.

For example, when the gear ratio of the automatic transmission 30 is switched from the N range to the L range, the lock pin 27 engaged with the lock recess 26d is moved to the lock recess 26a.
In such a case, the manual plate 26 must be swung clockwise in FIG. 3 by the angle θ. Therefore, the range switching control circuit C detects the rotation angle of the output shaft 4 by the swing valve position sensor 5 and locks the lock pin 27 in the lock recess 26a of the manual plate 26 when the output shaft 4 is rotated by the angle θ. It is determined that it has reached and engaged.

When it is determined by the range switching control circuit C that the output shaft 4 has been rotated by a predetermined angle, the sliding pin 6a of the solenoid valve 6 is retracted in the direction indicated by the arrow X in FIG.
The locked state of the fixed plate 13 is released, and thereafter, the rotational drive of the drive motor 3 is stopped. After the drive motor 3 is stopped, when the rotation shaft of the drive motor 3 is idled by inertia force, the rotation torque of the drive motor 3 is transmitted to the worm 17 and the worm wheel 14, and is output by the planetary gear 21 and the sun gear 8. 4 while being transmitted to the fixed plate 13 by the planetary gear 22 and the sun gear 12. In such a case, since the rotational torque of the drive motor 3 is transmitted to both the output shaft 4 and the fixed plate 13, the rotational torque transmitted to the output shaft 4 decreases by the amount of the rotational torque transmitted to the fixed plate 13. Thus, the rotation of the output shaft 4 can be easily stopped with a slight braking force.

Specifically, when the fixed plate 13 is rotatable, the rotation torque of the output shaft 4 is set to be smaller than the elastic force of the detent spring 28 for urging the lock pin 27. For this reason, the output shaft 4 is
The brake is stopped by the engagement between the lock plate 26 and the lock recess 26a of the manual plate 26, and the brake is stopped. As described above, since the rotation of the output shaft 4 is stopped by the elastic force of the detent spring 28 for positioning the manual plate 26, there is no need to separately provide a brake device or the like for stopping the rotation of the output shaft 4, and accordingly, The manufacturing cost of the entire device can be reduced.

When the drive motor 3 is stopped, the drive motor 3 may run idle due to inertial force. However, before the drive motor 3 stops, the sliding pin 6 of the solenoid valve 6 is stopped.
a and the engagement between the engagement recess 13a of the fixing plate 13 and
If the fixed state of the fixed plate 13 is released, the drive motor 3
Since the rotational torque of the output shaft 4 rotated by the idle rotation does not exceed the elastic force of the detent spring 28, the rotation angle of the output shaft 4 due to the idle rotation of the drive motor 3 can be prevented.

When the drive motor 3 is stopped,
When the manual plate 26 is positioned by the engagement of the lock pin 6a and the lock pin 27, the rotation of the output shaft 4 is completely stopped. As a result, the armature 29a of the manual valve 29 depends on the swing position of the manual plate 26.
Is determined, and the shift valve 30d is operated in accordance with the position of the armature 29a. The transmission mechanism 30b is operated by the operation of the transmission shift valve 30d,
The speed ratio of the automatic transmission 30 is switched from the speed ratio in the N range to the speed ratio in the L range.

On the other hand, when the occupant manually switches the gear ratio of the automatic transmission 30, first, the occupant operates the range switching lever 33 so that the L range, the second range, and the
One of the rd range, the R range, the N range, and the P range is selected. When this selection is made, the select cable 34 is pulled or pushed by the range switching lever 33, and the manual plate 26 is rocked. For example, when the L range is selected from the N range state by the shift switching lever 33, the select cable 34 is pulled and the manual plate 26 is swung clockwise by an angle θ with respect to the plane of FIG.

When the lock pin 27 is engaged with the lock recess 26a by the swing of the manual plate 26, the manual plate 26 is positioned by the lock pin 27 engaged with the lock recess 26a. By this positioning, the position of the armature 29a of the manual valve 29 is determined, and the shift valve 30d is operated according to the position of the armature 29a. Shift valve 3
The transmission mechanism 30b is operated by the operation of 0d, and the transmission ratio of the automatic transmission 30 is switched from the transmission ratio of the N range to the transmission ratio of the L range.

Here, the range switching control circuit C is configured to keep releasing the engagement between the sliding pin 6a of the solenoid valve 6 and the engagement recess 13a of the fixed plate 13 when the drive motor 3 is stopped. Have been. Accordingly, when the drive motor 3 is stopped, the fixed plate 13 is rotatable around the outer periphery of the output shaft 4, and the sun gear 12 connected to the fixed plate 13 via the sleeve 9 is also connected to the output shaft. 4 is rotatable around its outer periphery. As described above, by keeping the sun gear 12 and the fixed plate 13 rotatable, for example, the range switching lever 33 is operated by the occupant, and the manual plate 26 is rocked. Even if a rotational torque is applied, the rotational torque is not transmitted to the drive motor 3 via the worm wheel 14 and the worm 17.

Specifically, when the manual plate 26 is manually swung and a rotational torque is directly applied to the output shaft 4, the sun gear 8 is rotated by the rotational torque, and the planetary gear 21 rotates. The planetary gear 22 is rotated by the rotation of the planetary gear 21. When the planetary gear 22 rotates, the sun gear 12 rotates around the outer periphery of the output shaft 4, and the fixed plate 13 idles around the outer periphery of the output shaft 4. In this state,
Since the planetary gear shaft 20 does not revolve around the output shaft 4, the worm wheel 14 remains stopped without being rotated. Therefore, when the manual plate 26 is manually swung, the rotational torque applied to the output shaft 4 is transmitted to the drive motor 3 and the drive motor 3 is not rotated in the reverse direction.

As described above, according to the gear ratio switching device 1 of the present embodiment, each member for reducing the rotation of the drive motor 3 and transmitting it to the output shaft 4, that is, the sun gears 8, 12, the fixed plate 13, worm wheel 14, carrier plate 15,
18. Since the planetary gear shaft 20 and the planetary gears 21 and 22 are all provided around the vicinity of the output shaft 4, there is no need to reduce the rotation of the drive motor by meshing a plurality of spur gears in parallel in multiple stages. Accordingly, the size of the entire apparatus can be reduced.

The sliding pin 6a of the solenoid valve 6
The output shaft 4 and the drive motor 3
Can be connected or disconnected, so that there is no need to connect or disconnect the output shaft 4 and the drive motor 3 using an expensive electromagnetic clutch, and the manufacturing cost of the entire apparatus can be reduced accordingly. .

Since the rotation of the driving motor 3 is greatly reduced by the worm 17 and the worm wheel 14, there is no need to reduce the rotation of the driving motor 3 by engaging a plurality of spur gears in any number of stages. The number of parts can be reduced as a whole to reduce the manufacturing cost, and the size of the entire apparatus can be reduced.

The present invention has been described based on the embodiments. However, the present invention is not limited to the above-described embodiments, and various improvements and modifications can be made without departing from the spirit of the present invention. It can be easily inferred.

For example, in this embodiment, the worm wheel 18 has been described as the ring gear, but another gear may be used as the ring gear. Specifically, a small-diameter bevel gear may be connected to the rotating shaft of the drive motor 3 and a large-diameter bevel gear meshable with the bevel gear may be used as the ring gear.

In this embodiment, the number of the worms 17 is set to one. However, the number of the worms 17 is not necessarily limited to this, and depends on the reduction ratio of the speed change ratio switching device 1 as a whole. Therefore, the number of articles may be two or more.
Further, as an example of the use of the transmission ratio switching device 1 of the present embodiment, the automatic transmission 30 capable of performing three-stage shifting when moving forward has been described. 1 may be applied.

[0074]

According to the speed ratio switching device of the first aspect, the first and second planetary gears are supported by the ring gear, the ring gear is fitted to the output shaft, and the first shaft is mounted on the output shaft.
A sun gear is provided, and a second sun gear and a rotating member are fitted. As described above, the members for reducing the rotation of the drive motor and transmitting the rotation to the output shaft, that is, the ring gear, the differential reduction gear, and the rotation member are all provided around the output shaft. As described above, there is no need to reduce the rotation of the drive motor by arranging a plurality of spur gears in parallel in a multi-stage manner, and the size of the entire apparatus can be reduced accordingly.

When the manual plate is manually swung directly, the output shaft is also rotated by the swing. The rotation of the output shaft is caused by the engagement between the engaging member and the engaging portion of the rotating member. Can be prevented from being transmitted to the drive motor by releasing the engagement state. Moreover, since the engagement or disengagement of the engagement member and the engagement portion of the rotating member is performed by projecting or retracting the engagement member, the engagement member is projected by an inexpensive device such as a solenoid valve. Or can be retracted. Therefore, there is no need to connect or disconnect the output shaft and the drive motor by using an expensive electromagnetic clutch or the like as in a conventional gear ratio switching device, thereby reducing the manufacturing cost of the entire device. There is an effect that can be.

According to the gear ratio switching device of the second aspect,
In addition to the effects achieved by the speed ratio switching device according to the first aspect, the ring gear includes a worm wheel having a rotation center crossing the axial direction of the worm rotated by the drive motor. Can be greatly reduced, and the rotational torque of the drive motor can be greatly amplified. Therefore, it is possible to greatly amplify the rotation torque of the drive motor without having to reduce the rotation of the drive motor by gearing a plurality of spur gears in parallel in multiple stages as in the conventional gear ratio switching device. There is an effect that can be.

According to the gear ratio switching device of the third aspect,
In addition to the effects achieved by the speed ratio switching device according to claim 1 or 2, the control device causes the engagement member to retreat in the anti-projection direction when the rotation angle of the output shaft becomes a predetermined amount or more, The engagement state between the engagement member and the plurality of engagement portions of the rotation member is released, and the supply of the rotation torque by the drive motor is stopped. After the drive motor is stopped, the drive motor idles due to its inertial force.
The power is transmitted to the output shaft via the planetary gear and the first sun gear, and is transmitted to the rotating member via the second planetary gear and the second sun gear.

As described above, when the idling of the drive motor is transmitted to the rotation member, the rotation torque transmitted to the output shaft is reduced accordingly, and the braking force required for stopping the rotation of the output shaft is reduced. can do. Therefore, when the rotation of the drive motor is stopped in a state where the engagement of the rotation member by the engagement member is released, the rotation of the output shaft can be easily stopped with a slight braking force. .

According to the gear ratio switching device of the fourth aspect,
In addition to the effects achieved by the speed ratio switching device according to any one of claims 1 to 3, the control device is further configured to control the engagement between the engagement member and the plurality of engagement portions of the rotating member when the drive motor is in a stopped state. Continue to release the match state. In the case where the manual plate is manually swung because some abnormality occurs and the drive motor does not operate normally, if the engaging member and the plurality of engaging portions of the rotating member are engaged, the manual plate The output shaft is rotated by the rocking motion, and the rotation is transmitted to the drive motor, and the drive motor may be broken. Therefore, when the drive motor is in the stopped state, by continuing to release the engagement state between the engagement member and the plurality of engagement portions of the rotating member, an abnormality occurs and the manual plate is manually swung. However, since the force associated with the swing is not transmitted to the drive motor, there is an effect that the failure of the drive motor can be prevented.

According to the speed ratio switching device of the fifth aspect,
In addition to the effects achieved by the speed ratio switching device according to any one of claims 1 to 4, the rotational torque of the output shaft can be changed by the differential reduction gear by the engagement state between the engagement member and the plurality of engagement portions. Since the locking force of the detent member is reduced in the released state, the rotation of the output shaft can be stopped by the detent member that locks the manual plate. Therefore, it is not necessary to separately provide a brake device or the like for stopping the rotation of the output shaft, and accordingly, there is an effect that the manufacturing cost of the entire device can be reduced.

When the drive motor is stopped, the drive motor may run idle due to inertial force. Before the drive motor is stopped, the engagement between the engagement member and the plurality of engagement portions is released. In this case, the rotation torque transmitted to the output shaft due to the idling of the drive motor does not exceed the locking force of the detent member. For this reason, there is an effect that deviation of the rotation angle of the output shaft due to idling of the drive motor can be prevented.

According to the gear ratio switching device of the sixth aspect,
In addition to the effects achieved by the speed ratio switching device according to any one of claims 1 to 5, the rotational torque of the output shaft is such that the engaging member and the plurality of engaging portions are engaged by the differential reduction gear. In this state, the output shaft can be rotated irrespective of the manual plate being locked by the detent member since the locking force is made larger than the locking force of the detent member. Therefore, it is not necessary to separately provide a device for releasing the manual plate from being detained by the detent member in order to start the rotation of the output shaft, and the manufacturing cost of the entire device can be reduced accordingly. is there.

[Brief description of the drawings]

FIG. 1 is an external view of a gear ratio switching device according to an embodiment of the present invention.

FIG. 2 is a sectional view of the transmission ratio switching device taken along the line II-II in FIG.

FIG. 3 is a system configuration diagram showing an example of use of a speed ratio switching device.

[Explanation of symbols]

DESCRIPTION OF REFERENCE NUMERALS 1 speed ratio switching device 3 drive motor 4 output shaft 5 valve position sensor (part of control device) 6 solenoid valve (part of control device) 6a sliding pin (engaging member) 8, 12 sun gear (first sun) Gear, second sun gear, part of differential reduction gear) 13 Fixing plate 14 Worm wheel (worm wheel,
14a Gear teeth (worm gear teeth) 15, 18 Carrier plate (part of ring gear) 17 Worm 17a Worm teeth (worm teeth) 20 Planetary gear shaft (first planetary gear and second planetary gear) 21 and 22 planetary gears (parts of the first planetary gear, second planetary gear, and differential reduction gear) 26 manual plate 27 lock pin (part of detent member) 28 detent spring (of detent member) 30) Automatic transmission (transmission) C Range switching control circuit (part of control device)

Continued on front page F term (reference) 3J067 AA02 AA16 AA21 AB02 AB23 AC12 BA03 BA52 BA56 CA32 DA34 DA52 DA73 DB32 DB34 EA01 EA11 EA11 EA84 FA04 FA62 FA84 FB83 GA01

Claims (6)

[Claims] 1. A gear ratio switch comprising: an output shaft connected to a manual plate that is swung to change the gear ratio of a transmission; and a drive motor that supplies a rotating torque for rotating the output shaft. In the apparatus, a ring gear rotatably fitted to the output shaft and rotated by transmitting the rotation torque of the drive motor, and is rotatably supported at a position inside the outer peripheral edge of the ring gear. A first planetary gear, a second planetary gear connected to the center of rotation of the first planetary gear and having the same center of rotation as the first planetary gear, and meshed with the first planetary gear; A differential sun reduction gear having a first sun gear provided, a second sun gear meshed with the second planetary gear and rotatably fitted to the output shaft; 2 coupled with sun gear A plurality of engaging portions are provided on an outer periphery of the rotating member, and are formed so as to be protrudable toward the rotating member. A gear ratio switching device comprising: an engaging member to be locked. 2. The ring gear further includes a worm threaded on its outer periphery and connected to the drive motor, wherein the ring gear has gear teeth on its outer periphery that can be meshed with the worm teeth. 2. The gear ratio switching device according to claim 1, further comprising a worm wheel having a center of rotation intersecting with the axial direction of the worm. 3. When the rotation angle of the output shaft becomes equal to or more than a predetermined amount, the engaging member is retracted in the anti-projection direction, and the plurality of engaging portions of the engaging member and the rotating member are provided. 3. The gear ratio switching device according to claim 1, further comprising a control device that releases the engagement state with the drive motor and stops supply of the rotation torque by the drive motor. 4. 4. A control device for continuously releasing the engagement state between the engagement member and the plurality of engagement portions of the rotating member when the drive motor is stopped. The gear ratio switching device according to any one of claims 1 to 3. 5. The rotation of the output shaft is stopped by a detent member that restrains the swinging of the manual plate, and the differential reduction gear controls the rotation torque of the output shaft. 2. The device according to claim 1, wherein when the engagement state between the engagement member and the plurality of engagement portions is released, the engagement force of the detent member is reduced.
5. The gear ratio switching device according to any one of claims 1 to 4. 6. The output shaft is configured so that rotation is stopped by a detent member that restrains swinging of a manual plate, and the differential reduction gear transmits rotation torque of the output shaft. The structure according to any one of claims 1 to 5, wherein when the engaging member and the plurality of engaging portions are engaged, the engaging force of the detent member is larger than the engaging force. Gear ratio switching device.