JP2002349697A - Gear speed changer for vehicle transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gear speed changer of vehicle transmission, which is compact and easy to power control. SOLUTION: The gear speed changer 14 is equipped with a shift 11, a shift yoke 12, a gear selection mechanism and a gear shift mechanism 14. The shift yoke 12 is mounted on the shaft 11, in a way such that it is movable in the longitudinal direction of the shaft 11 but is not rotatable relative to it. The gear shift mechanism 14 comprises a planetary carrier 41, a planetary gear 42, first and second ring gears 43, 44, a housing 45, a coupler 46, a sun gear 47 and a motor 48. The first gear 43 differs in the number of gear teeth from that of the second ring gear 44; the housing 45 fixes the first ring gear 43; the coupler 46 couples the second ring gear 44 with the shaft 11; and the motor 48 makes the sun gear 47 rotates.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gear transmission for a vehicular transmission, and more particularly to an apparatus for operating a gear shift mechanism by a motor.

[0002]

2. Description of the Related Art Manual transmissions are mainly used in large vehicles such as buses and trucks even today. In a manual transmission, a transmission lever and a transmission in a driver's seat are mechanically connected by a link mechanism such as a control rod.
Then, at the time of gear shifting, the driver operates the lever to physically drive the gear mechanism. For this reason, when the shift is frequently required, the lever operation requiring a certain amount of force places a heavy burden on the driver.

[0003] In order to solve this problem, a gear transmission operated by a motor is provided in a manual transmission.
A remotely operated manual transmission provided with a transmission ECU for controlling the gear transmission by an electric signal has been developed. In this transmission, the motor drives the gear mechanism, so that the gear can be shifted with a small force that merely operates the shift lever, and the burden on the driver regarding the shift lever operation is reduced.

Generally, in a manual transmission, a plurality of spools are provided side by side in a select direction. The gear transmission provided in the manual transmission connects and disconnects gears by driving the spool selected by the gear selection mechanism in the shift direction. The gear transmission usually includes a shift yoke having one end engageable with each spool, a shaft in which the shift yoke is splined in a non-rotatable manner, a gear select mechanism for moving the shift yoke on the shaft in a select direction, and a shift yoke. A gear shift mechanism that moves the spool in the shift direction is provided. For example, an electric ball screw mechanism is adopted as the gear select mechanism or the gear shift mechanism.

[0005]

A manual transmission usually has a synchronizing device including a cone clutch and a meshing mechanism. In the synchro device, a speed is changed by a method in which a load within a certain range (different depending on each transmission) is applied by a spool fork fixed to a spool, a cone clutch is pushed, the rotation is synchronized, and the meshing is performed. The spool is pushed linearly by the swinging motion of the shift yoke, which is in spline engagement with the shaft, at an angle of about 10 degrees. Therefore, it is necessary to control the rotation (rotation) of the shaft (shift yoke) in accordance with the synchro load.

However, in the conventional electric gear shift mechanism, the rotation of the electric motor is converted into linear motion by using a screw feed mechanism, and the lever connected to the shaft is swung by the linkage, or a high reduction gear ratio is used. A structure is employed in which rotation of an electric motor is converted into swing using a worm gear mechanism. Since these screw feed mechanism and worm gear mechanism need to be arranged at right angles to the shaft that holds the shift yoke, a large space is required,
Efficiency is reduced in the transmission of force. Further, there are problems such as difficulty in controlling the rotational force of the shaft with respect to the synchro load by current control of the electric motor, and the fact that a bending force other than the rotational force acts on the shaft.

SUMMARY OF THE INVENTION An object of the present invention is to provide a gear transmission for a transmission that performs gear shifting using a motor, which is compact and facilitates force control.

[0008]

According to a first aspect of the present invention, a gear transmission for a vehicle transmission comprises a shaft, a shift yoke, a gear select mechanism, and a gear shift mechanism. The shift yoke is mounted on the shaft and is movable in the longitudinal direction of the shaft. The shift yoke is mounted on the shaft such that relative rotation with the shaft is disabled. The gear select mechanism is a mechanism that moves the shift yoke in the longitudinal direction of the shaft and selectively makes the shift yoke correspond to an arbitrary spool. The gear shift mechanism is a mechanism that applies a force from a shift yoke to a spool by swinging a shaft, and causes a shift gear to be connected and disconnected by movement of the spool. The gear shift mechanism includes a planet carrier, a planet gear, a first ring gear, a second ring gear, a housing, a connecting portion, a sun gear, and a motor. The planet gear is supported by the planet carrier. The first ring gear and the second ring gear mesh with the planet gears, respectively. The number of teeth of the first ring gear and the number of teeth of the second ring gear are different from each other. The housing fixes the first ring gear. The connecting portion connects the second ring gear to the shaft. Sungear meshes with planetary gears. The motor rotates the sun gear. With such a configuration, the gear shift mechanism converts the rotation of the motor into a swinging motion of the shaft.

In the apparatus according to the first aspect, the rotation of the sun gear by the motor is converted into the turning / rotating motion of the planetary gear by the fixed first ring gear, and the second ring gear (the second ring gear) meshed with the planetary gear. The rotation reduced in speed from one ring gear (having a different number of teeth from the ring gear) is transmitted to the shaft. By using the speed reduction structure of this configuration, the gear shift mechanism of this device is compact while maintaining a high reduction ratio, and is not disposed at right angles to the shaft as in the conventional screw feed mechanism and worm gear mechanism. , Can be arranged coaxially with the shaft.

Further, by disposing the gear shift mechanism coaxially with the shaft and reducing the torque of the motor and transmitting the torque to the shaft as it is, the power transmission efficiency is improved as compared with the conventional case, and the torque of the shaft is controlled by the current control of the motor. Control becomes easy. Further, it is possible to prevent the bending force other than the rotation force from acting on the shaft.

According to a second aspect of the present invention, a gear transmission for a vehicle transmission includes a shaft, a shift yoke, a gear select mechanism, and a gear shift mechanism. The shift yoke is mounted on the shaft and is movable in the longitudinal direction of the shaft. The shift yoke is mounted on the shaft such that relative rotation with the shaft is not possible. The gear select mechanism is a mechanism that moves the shift yoke in the longitudinal direction of the shaft and selectively makes the shift yoke correspond to an arbitrary spool. The gear shift mechanism is a mechanism that causes a force to act on a spool from a shift yoke by swinging a shaft, and causes the shift gear to be connected or disconnected by movement of the spool. The gear shift mechanism includes a planet carrier, a planet gear, a first ring gear, a second ring gear, a housing, a connecting portion, and a motor. The planet gear is supported by the planet carrier. First
The ring gear and the second ring gear mesh with the planet gears, respectively. Further, the number of teeth of the first ring gear and the number of teeth of the second ring gear are different from each other. The housing is
The first ring gear is fixed. The connecting portion connects the second ring gear to the shaft. The motor rotates the planet carrier. With such a configuration, the gear shift mechanism converts the rotation of the motor into a swinging motion of the shaft.

In the apparatus according to the second aspect, the rotation of the planetary carrier (turning of the planetary gear) by the motor is converted into the rotational movement of the planetary gear by the fixed first ring gear, and the second gear meshes with the planetary gear. The rotation reduced from the two ring gears (having a different number of teeth from the first ring gear) is transmitted to the shaft. By using the speed reduction structure of this configuration, the gear shift mechanism of this device is compact while maintaining a high reduction ratio, and is not disposed at right angles to the shaft as in the conventional screw feed mechanism and worm gear mechanism. , Can be arranged coaxially with the shaft.

Further, by disposing the gear shift mechanism coaxially with the shaft and decelerating the torque of the motor and transmitting it directly to the shaft, the power transmission efficiency is improved as compared with the prior art, and the torque of the shaft is controlled by the current control of the motor. Control becomes easy. Further, it is possible to prevent the bending force other than the rotation force from acting on the shaft.

According to a third aspect of the present invention, there is provided a gear transmission for a vehicle transmission according to the first or second aspect, wherein the planetary gear is a single gear that meshes with each of the first and second ring gears. Has the number of teeth.

According to a fourth aspect of the present invention, there is provided a gear transmission for a vehicle transmission according to the first or second aspect, wherein the planetary gear includes a first gear portion and a second gear portion. The first gear portion meshes with the first ring gear. The second gear portion is a portion that meshes with the second ring gear, and has a different number of teeth from the first gear portion.

Here, since the number of teeth of the first gear portion and the number of teeth of the second gear portion are different, a higher reduction ratio can be obtained. A gear transmission for a vehicle transmission according to claim 5 is the device according to any one of claims 1 to 4,
The first ring gear is fixed to the housing via a damper in a rotational direction.

Here, since the damper is inserted into the fixed portion of the first ring gear by the housing, the first ring gear can play a role of absorbing a shock in the rotation direction. As a result, the shock due to the rotational inertia of the motor and the gear shift mechanism, which may occur during the gear shifting, is reduced.

[0018] A gear transmission for a vehicle transmission according to a sixth aspect includes a shaft, a shift yoke, a gear select mechanism, and a gear shift mechanism. The shift yoke is mounted on the shaft and is movable in the longitudinal direction of the shaft. The shift yoke is mounted on the shaft such that relative rotation with the shaft is not possible. The gear select mechanism is a mechanism that moves the shift yoke in the longitudinal direction of the shaft and selectively makes the shift yoke correspond to an arbitrary spool. The gear shift mechanism is a mechanism that causes a force to act on a spool from a shift yoke by swinging a shaft, and causes the shift gear to be connected or disconnected by movement of the spool. The gear shift mechanism includes a planet carrier, a planet gear, a first sun gear, a second sun gear, a housing, a connecting portion, a ring gear, and a motor. The planet gear is supported by the planet carrier. The first sun gear and the second sun gear mesh with the planet gears, respectively. The number of teeth of the first sun gear is
The number of teeth is different from the number of teeth of the second sun gear. The housing fixes the first sun gear. The connecting portion connects the second sun gear to the shaft. The ring gear meshes with the planet gears. The motor rotates the ring gear. With such a configuration, the gear shift mechanism converts the rotation of the motor into a swinging motion of the shaft.

In the apparatus according to the sixth aspect, the rotation of the ring gear by the motor is converted into the turning and rotating motion of the planetary gear by the fixed first sun gear, and the second sun gear (the first sun gear) meshing with the planetary gear is converted. The rotation decelerated from the sun gear having a different number of teeth) is transmitted to the shaft.
By using the speed reduction structure of this configuration, the gear shift mechanism of this device is compact while maintaining a high reduction ratio, and is not disposed at right angles to the shaft as in the conventional screw feed mechanism and worm gear mechanism. , Can be arranged coaxially with the shaft.

Further, by disposing the gear shift mechanism coaxially with the shaft and reducing the torque of the motor and transmitting the torque to the shaft as it is, the power transmission efficiency is improved as compared with the conventional case, and the torque of the shaft is controlled by the current control of the motor. Control becomes easy. Further, it is possible to prevent the bending force other than the rotation force from acting on the shaft.

According to a seventh aspect of the present invention, a gear transmission for a vehicle transmission includes a shaft, a shift yoke, a gear select mechanism, and a gear shift mechanism. The shift yoke is mounted on the shaft and is movable in the longitudinal direction of the shaft. The shift yoke is mounted on the shaft such that relative rotation with the shaft is not possible. The gear select mechanism is a mechanism that moves the shift yoke in the longitudinal direction of the shaft and selectively makes the shift yoke correspond to an arbitrary spool. The gear shift mechanism is a mechanism that causes a force to act on a spool from a shift yoke by swinging a shaft, and causes the shift gear to be connected or disconnected by movement of the spool. The gear shift mechanism includes a planet carrier, a planet gear, a first sun gear, a second sun gear, a housing, a connecting portion, and a motor.
The planet gear is supported by the planet carrier. The first sun gear and the second sun gear are respectively meshed with the planet gears. The number of teeth of the first sun gear is different from the number of teeth of the second sun gear. The housing fixes the first sun gear. The connecting portion connects the second sun gear to the shaft. The motor rotates the planet carrier. With such a configuration, the gear shift mechanism converts the rotation of the motor into a swinging motion of the shaft.

In the apparatus according to the seventh aspect, the rotation of the planetary carrier by the motor is converted into the rotational movement of the planetary gear by the fixed first sun gear, and the second sun gear (the first sun gear and the first sun gear) meshing with the planetary gear is converted. (The number of teeth is different) is transmitted to the shaft. By using the speed reduction structure of this configuration, the gear shift mechanism of this device is compact while maintaining a high reduction ratio, and is not disposed at right angles to the shaft as in the conventional screw feed mechanism and worm gear mechanism. , Can be arranged coaxially with the shaft.

Further, by disposing the gear shift mechanism coaxially with the shaft and decelerating the torque of the motor and transmitting it directly to the shaft, the power transmission efficiency is improved as compared with the prior art, and the torque of the shaft is controlled by the current control of the motor. Control becomes easy. Further, it is possible to prevent the bending force other than the rotation force from acting on the shaft.

[0024] A gear transmission for a vehicle transmission according to claim 8 is the apparatus according to claim 6 or 7, wherein the planetary gear has a single tooth meshing with each of the first and second sun gears. Have a number.

According to a ninth aspect of the present invention, there is provided a gear transmission for a vehicle transmission according to the sixth or seventh aspect, wherein the planetary gear includes a first gear portion and a second gear portion. The first gear portion meshes with the first sun gear. The second gear portion is a second gear portion.
This is a portion that meshes with the sun gear, and has a different number of teeth from the first gear portion.

Here, since the number of teeth of the first gear portion and the number of teeth of the second gear portion are different, a higher reduction ratio can be obtained. A gear transmission for a vehicle transmission according to a tenth aspect is the gear transmission according to any one of the fifth to ninth aspects, wherein the first sun gear is fixed to the housing via a damper in a rotational direction. .

Here, since the damper is inserted into the fixed portion of the first sun gear by the housing, the first sun gear
The sun gear can play a role of absorbing a shock in a rotational direction. As a result, the shock due to the rotational inertia of the motor and the gear shift mechanism, which may occur during the gear shifting, is reduced.

[0028]

DESCRIPTION OF THE PREFERRED EMBODIMENTS <Outline of Manual Transmission Automatic Transmission System> FIG. 1 shows a manual transmission automatic transmission system including a transmission (vehicle transmission) according to an embodiment of the present invention.

In FIG. 1, a clutch 3 including a dry single-plate clutch disk is disposed between an engine 1 and a transmission 2. A gear transmission 4 is provided as an actuator for driving the transmission 2. As an actuator for driving the clutch 3, a clutch actuator 5 is provided.
The clutch actuator 5 has a master cylinder connected via a hydraulic circuit to a slave cylinder 6 provided near the clutch 3.

This system is provided with an engine ECU 51 and a transmission ECU 52, which can communicate with each other. For example, they can exchange engine rotation information and accelerator opening information.

The engine ECU 51 controls the engine 1, and receives an accelerator opening signal from an accelerator pedal 54. The transmission ECU 52 mainly performs clutch control and shift control, and outputs a clutch control signal to the clutch actuator 5 and a shift control signal to the gear transmission 4. These control signals are signals for driving various motors.

The transmission ECU 52 receives signals from various sensors. In particular,
Idle signal from accelerator pedal 54, shift lever 5
5, a shift position signal, a clutch stroke signal from the clutch pedal 56, a clutch stroke signal and a hydraulic signal from the clutch actuator 5, a clutch 3
, A clutch rotation signal, a vehicle speed signal from the transmission 2, and a shift / select stroke signal from the gear transmission 4 are input to the transmission ECU 52.

In the system described above, the transmission ECU 52 automatically controls the clutch operation and the gear shifting operation. Further, a manual operation of performing a gear shift operation by operating the shift lever 55 can be selectively used.

The second master cylinder 57 linked to the clutch pedal 56 is connected to the slave cylinder 6 via an oil passage. Therefore, when the driver operates the clutch pedal 5
When the user operates the cylinder 6, the hydraulic pressure is supplied from the second master cylinder 57 to the slave cylinder 6, and the clutch connection / disconnection operation is performed. In this embodiment, the clutch pedal 56 is for emergency use only when a failure occurs in the electrical relationship of the clutch actuator 5 and the like, and is folded during normal running.

<Gear Transmission> The gear transmission 4 will be described in detail with reference to FIGS. (Overview) The gear transmission 4 is a transmission ECU
This is a device for connecting and disconnecting the transmission gear of the transmission 2 based on the transmission control signal from the transmission 52. As shown in FIGS. 2 and 3, the spools 10 of the transmission 2 that are each held so as to move linearly by the shift rail 9 are arranged in the select direction Ds (see FIG. 2). The gear transmission 4 includes one of these spools 10.
By selecting and pressing one, the spool 10 is moved along the shift rail 9. Specifically, the claw 12b (described later) of the shift yoke 12 of the gear transmission 4 enters the notch 10b of the spool yoke 10a of the spool 10,
The spool 10 moves by the swinging motion of the shaft 11. Then, due to the linear movement of the spool 10, the transmission gear is connected / disconnected via a synchronization mechanism including a not-shown cone clutch.

The gear transmission 4 mainly includes the shaft 1
1, a shift yoke 12, a gear select mechanism 13,
A gear shift mechanism 14 is provided. (Shaft) The vicinity of both ends of the shaft 11 is supported by the housing 45 via bearings. A spline 11 a is formed on the outer peripheral surface of the central portion of the shaft 11.

(Shift Yoke) The shift yoke 12 has an inner peripheral spline 12 a
a. Therefore, the shift yoke 12
Although it is movable in the longitudinal direction of the shaft 11, its rotation is restricted with respect to the shaft 11. In addition, the shift yoke 12 swings the notch 10
b has a claw 12b that can be inserted.

(Gear Select Mechanism) Gear Select Mechanism 1
Reference numeral 3 denotes a mechanism for moving the shift yoke 12 in the longitudinal direction of the shaft 11 (selection direction Ds) and selectively making the shift yoke 12 correspond to an arbitrary spool 10. Here, the gear select mechanism 13 is configured using an electric ball screw mechanism (not shown).

(Gear shift mechanism) Gear shift mechanism 14
Is obtained by swinging the shaft 11 so that the shift yoke 12
This mechanism applies a force to the spool 10 to move the spool 10 to connect and disconnect the speed change gear. The gear shift mechanism 14 mainly includes a planet carrier plate 41, a planet gear 42, a first ring gear 43,
A ring gear 44, a housing 45, a connecting portion 46,
It has a sun gear 47 and an electric motor 48.

Three planetary support pins 40 are press-fitted into the planet carrier plate 41. The three planet gears 42 are rotatably mounted on the pivot pins 40 via bushes. That is, the three planet gears 42 are supported by the planet carrier plate 41 via the support pins 40.

First ring gear 43 and second ring gear 4
4 are in mesh with the planetary gears 42, respectively. The number of teeth Zr1 of the first ring gear 43 and the second ring gear 4
The number of teeth Zr2 with 4 differs from each other due to the transition.

The first ring gear 43 is fixed to the housing 45 by a fixing member 45a. However, as shown in FIGS. 3 and 4, a damper mechanism 49 including a spring seat 49a and a spring 49b
5 is inserted between the first fixing member 45 a and the first ring gear 43. Specifically, three notches are provided on the outer peripheral portion of the first ring gear 43, and the damper mechanism 49 is inserted into those notches. Also, the fixing member 4
5a is formed with an internal slit that allows the first ring gear 43 to swing. That is, the first ring gear 4
3 is via a damper mechanism 49 acting in the rotation direction,
It is fixed to the housing 45. Therefore, the first ring gear 43 is allowed to rotate (swing) with respect to the housing 45 by a predetermined angle.

The connecting portion 46 serves to connect the second ring gear 44 to the end of the shaft 11. This connecting part 4
6 is formed integrally with the second ring gear 44. The connecting portion 46 is connected to the shaft 11 by press fitting or welding.

The sun gear 47 meshes with the planetary gear 42 and rotates by the operation of the electric motor 48.
The sun gear 47 has the number of teeth Zs1. In addition,
A first ring gear 43 (number of teeth Zr1) and a second ring gear 44 (number of teeth Zr2) having different numbers of teeth due to shifting with respect to the longer planetary gears 42 that are supported by the planet carrier plate 41.
And the sun gear 47 (the number of teeth Zs1) mesh with each other. The condition of the number of teeth with which the gears 43, 44, and 47 mesh with the planetary gear 42 is as follows, assuming that the equally arranged arrangement of the planetary gear 42 is n. become. Meshing condition (1): (Zr1−Zr2) is a multiple of n Meshing condition (2): (Zr1 + Zs1) is a multiple of n The output rotation speed Nout to the shaft 11 is Assuming that the input rotation speed is Nin, Nout = (1−Zr1 / Zr2) × ｛1 / (1 + Zr1 / Zs)
1) It becomes｝ × Nin. Therefore, in the case of the present embodiment in which the number of equally divided planetary gears 42 is three (n = 3), if Zr1 = 72, Zr2 = 75, Zs1 = 15, then Nout = 0.006897 × Nin: The reduction ratio becomes 145.

(Features) Gear shift mechanism 14 of this embodiment
Then, the rotation of the sun gear 47 by the electric motor 48 is converted into the rotation of the planetary gear 42 by the fixed first ring gear 43, and the rotation reduced from the second ring gear 44 meshing with the planetary gear 42 11 is transmitted. Since the high speed reduction structure having such a configuration is used, the gear shift mechanism 14 is lightweight and compact while maintaining a high speed reduction ratio, and is not disposed at right angles to the shaft as in a conventional screw feed mechanism or worm gear mechanism. , FIG.
As shown in FIG.

The gear shift mechanism 14 is connected to the shaft 11
And the rotation is transmitted to the shaft 11 while reducing the rotational force of the electric motor 48, so that the power transmission efficiency is improved as compared with the conventional case, and the rotational force of the shaft 11 is controlled by the electric current of the electric motor 48. Control is also easy. Further, it is possible to prevent a bending force other than the rotation force from acting on the shaft 11, and it is possible to reduce the cost of the shaft 11.

The rotation of the electric motor 48 is zero until the cone clutch of the synchronizing device (not shown) comes into contact and the rotation of the cone clutch is synchronized. At the moment when it becomes 0, a shock may be generated by the electric motor 48 and the rotational inertia of each gear, and the cone clutch may be damaged. However, in the above-described gear shift mechanism 14, since the damper mechanism 49 is provided on the fixed portion of the first ring gear 43, the shock is reduced, and the damage to the cone clutch is suppressed.

In the gear shift mechanism 14 described above, the synchro load can be controlled by controlling the electric current of the electric motor 48, but the synchro load can also be controlled using the damper mechanism 49.

[Other Embodiments] In a gear transmission, usually, the maximum rotation speed is 2000 to 7000 [rpm].
m], and a small DC motor having a torque of 0.5 to 5.0 [N · m] is used. On the other hand, since the torque required for the shaft is 50 to 100 [N · m], the reduction ratio required for the gear shift mechanism is about 10 to 200.

On the other hand, in the above embodiment, the reduction ratio is 1
Although the gear shift mechanism 14 is 45, other structures and reduction ratios as described below can be selected as necessary.

(Other Embodiment A) A sun gear 47 in which the gear shift mechanism 14 shown in FIG.
In the gear shift mechanism 14a shown in FIG. 5, the planetary gear 42 is rotated and rotated by directly rotating the planetary carrier plate with the electric motor 48 while omitting the sun gear.

In this case, Nout = (1−Zr1 / Zr2) × Nin. Therefore, if Zr1 = 72 and Zr2 = 75, then Nout = 0.04 × Nin: reduction ratio 25.

(Other Embodiment B) The gear shift mechanism 14 shown in FIG. 2 and the like employs a planetary gear 42 having a single number of teeth, whereas the gear shift mechanism 14b shown in FIG. Different first and second gear portions 42b1 and 4
The planetary gear 42b formed with 2b2 is employed. The first gear portion 42b1 is a portion that meshes with the first ring gear 43, and has the number of teeth Zp1. Second gear portion 42b2
Is a portion that meshes with the second ring gear 44, and the number of teeth Z
p2.

In this case, the condition of the number of teeth in which each gear 43, 44, 47 meshes with the planetary gear 42b is as follows.
Assuming that the equal arrangement of b is n, the following is obtained. Engagement condition (1): (Zr1 + Zs1) is a multiple of n Engagement condition (2): (Zr1-Zp1) = (Zr2-Zp2) The output rotational speed Nout is: Nout = ｛1- (Zp2 / Zp1) ) (Zr1 / Zr2)｝ × ｛1
/ (1 + Zr1 / Zs1)｝ × Nin. Therefore, in the case of the present embodiment in which the number of equally arranged planetary gears 42b is three (n = 3), Zr1 = 75, Zr2 = 74, Zp1 = 30, Zp2 = 29, Z
If s1 = 15, then Nout = 0.00338 × Nin: reduction ratio 296.

As described above, here, the first gear portion 42b1
Since the planetary gear 42b having a different number of teeth between the gear shift mechanism 14 and the second gear portion 42b2 is used, the gear shift mechanism 14 shown in FIG.
A reduction ratio higher than (reduction ratio 145) can be obtained.

(Other Embodiment C) While the gear shift mechanism 14b of the above-described embodiment B rotates the sun gear 47 meshing with the planetary gear 42b with the electric motor 48, the gear shift mechanism 14c shown in FIG. And the planetary gear 42b is turned and rotated by directly rotating the planetary carrier plate by the electric motor 48.

In this case, Nout = {1− (Zp2 / Zp1) (Zr1 / Zr2)} × Nin. Therefore, if Zr1 = 75, Zr2 = 74, Zp1 = 30, Zp2 = 29, then Nout = 0.0202 × Nin: reduction ratio 49.

(Other Embodiment D) The following gear shift mechanism 14d shown in FIG. 8 is employed in place of the gear shift mechanism 14 shown in FIG.

The gear shift mechanism 14d mainly includes a planet carrier plate 141, a planet gear 142, a first sun gear 143, a second sun gear 144, and the housing 1
45, a connecting portion 146, a ring gear 147, and an electric motor 48.

The planet gear 142 is supported by the planet carrier plate 41 via a support pin. The first sun gear 143 and the second sun gear 144 mesh with the planetary gear 142, respectively. The number of teeth Zs1 of the first sun gear 143 and the number of teeth Zs2 of the second sun gear 144 are different from each other due to the transition.

The housing 145 includes a first sun gear 143.
Are fixed via a damper mechanism acting in the rotation direction. Therefore, the first sun gear 143 is allowed to rotate (swing) with respect to the housing 145 by a predetermined angle.

The connecting portion 146 serves to connect the second sun gear 144 to the end of the shaft 11. The connecting portion 146 is formed integrally with the second sun gear 144. The ring gear 147 meshes with the planetary gear 142 and rotates by the operation of the electric motor 48. The sun gear 147 has the number of teeth Zr1.

The first planetary gear 143 (teeth number Zs1) and the second sun gear 144 (teeth number Zs2), which have different numbers of teeth due to shifting, and a ring are attached to the longer planetary gear 142 which is supported by the planetary carrier plate 141. Gear 147 (number of teeth Zr
1) and these gears 143, 14
The condition of the number of teeth in which 4,147 meshes with the planetary gear 142 is as follows:
Assuming that the equally divided arrangement of the planet gears 142 is n, the following is obtained. Meshing condition (1): (Zs1-Zs2) is a multiple of n Meshing condition (2): (Zr1 + Zs1) is a multiple of n The output rotation speed Nout to the shaft 11 is Assuming that the input rotation speed is Nin, Nout = (1−Zs1 / Zs2) × ｛1 / (1 + Zs1 / Zr)
1) It becomes｝ × Nin. Therefore, if there are three equally arranged planetary gears 42 (n = 3) and Zr1 = 48, Zr2 = 51, Zs1 = 84, then Nout = 0.03743 × Nin: reduction ratio 27.

(Other Embodiment E) While the gear shift mechanism 14d of the above-described Embodiment D rotates the ring gear 147 meshing with the planetary gear 142 with the electric motor 48, the gear shift mechanism 14e shown in FIG. The planetary gear 142 is turned and rotated by directly rotating the planetary carrier plate 141 with the electric motor 48 without the ring gear.

In this case, Nout = (1−Zs1 / Zs2) × Nin. Therefore, if Zs1 = 48 and Zs2 = 51, then Nout = 0.0588 × Nin: reduction ratio 17

(Other Embodiment F) The planetary gear 142 having a single number of teeth has the gear shift mechanism 14d of the above-described Embodiment D.
In contrast, the gear shift mechanism 14f shown in FIG. 10 employs a planetary gear 142f in which a first gear portion 142f1 and a second gear portion 142f2 having different numbers of teeth are formed. The first gear portion 142f1 is provided with a first sun gear 1
43, which has the number of teeth Zp1. Second
The gear portion 142f2 is a portion that meshes with the second sun gear 144, and has the number of teeth Zp2.

In this case, the gears 143, 144, 1
The condition of the number of teeth with which the planet 47 meshes with the planetary gear 142f is as follows, assuming that the number of equally arranged planetary gears 142f is n. Engagement condition (1): (Zr1 + Zs1) is a multiple of n Engagement condition (2): (Zs1 + Zp1) = (Zs2 + Zp2) And the output rotational speed Nout is: Nout = ｛1− (Zp2 / Zp1) (Zs1 / Zs2)｝ × ｛1
/ (1 + Zs1 / Zr1)｝ × Nin. Therefore, the equal arrangement of the planet gears 142f is 3
(N = 3), Zs1 = 48, Zs2 = 49, Zp1 = 18, Zp2 = 17, Z
If r1 = 84, then Nout = 0.0476 × Nin: reduction ratio 21

(Other Embodiment G) While the gear shift mechanism 14f of Embodiment F described above rotates the ring gear 147 meshing with the planetary gear 142f by the electric motor 48, the gear shift mechanism 14g shown in FIG. The ring gear is omitted and the planetary carrier plate 141 is driven by the electric motor 48.
Is directly rotated to rotate and rotate the planetary gear 142f.

In this case, Nout = {1− (Zp2 / Zp1) (Zs1 / Zs2)} × Nin. Therefore, if Zs1 = 48, Zs2 = 49, Zp1 = 18, Zp2 = 17, then Nout = 0.0748 × Nin: reduction ratio 13

[0070]

By using the gear transmission according to the present invention,
The gear shift mechanism becomes compact while maintaining a high reduction ratio, and the gear shift mechanism can be arranged coaxially with the shaft, instead of being arranged at right angles to the shaft as in a conventional screw feed mechanism or worm gear mechanism. Also,
By arranging the gear shift mechanism coaxially with the shaft and reducing the torque of the motor and transmitting it directly to the shaft, the power transmission efficiency is improved as compared to conventional models, and the torque of the shaft can be controlled by controlling the motor current. It will be easier. Further, it is possible to prevent the bending force other than the rotation force from acting on the shaft.

[Brief description of the drawings]

FIG. 1 is a diagram of a manual transmission automatic transmission system including a transmission (vehicle transmission) according to an embodiment of the present invention.

FIG. 2 is a schematic diagram of a gear transmission.

FIG. 3 is a sectional view of a gear shift mechanism.

FIG. 4 is a sectional view taken along the line IV-IV in FIG. 3;

FIG. 5 is a schematic diagram of a gear shift mechanism according to another embodiment A.

FIG. 6 is a schematic diagram of a gear shift mechanism according to another embodiment B.

FIG. 7 is a schematic diagram of a gear shift mechanism according to another embodiment C.

FIG. 8 is a schematic diagram of a gear shift mechanism according to another embodiment D.

FIG. 9 is a schematic diagram of a gear shift mechanism according to another embodiment E.

FIG. 10 is a schematic diagram of a gear shift mechanism according to another embodiment F.

FIG. 11 is a schematic diagram of a gear shift mechanism according to another embodiment G.

[Explanation of symbols]

 2 Transmission 10 Spool 11 Shaft 12 Shift yoke 13 Gear select mechanism 14 Gear shift mechanism 41, 141 Planetary carrier plate 42, 42b, 142, 142f 42b1, 142f1 42b2, 142f2 43 First ring gear 44 Second ring gear 45, 145 Housing 46 , 146 Connecting part 47 Sun gear 48 Electric motor 143 First sun gear 144 Second sun gear 147 Ring gear

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Toru Kagei 1-1-1 Kidamotomiya, Neyagawa-shi, Osaka F-term in EXEDY Corporation (reference) 3J067 AA01 AA21 AB23 AC01 BA52 BA58 BB14 CA02 CA09 CA23 DA43 DB32 EA31 FB83 GA01

Claims (10)

[Claims] A shaft; a shift yoke mounted on the shaft so as to be movable in a longitudinal direction of the shaft and not to rotate relative to the shaft; and moving the shift yoke in a longitudinal direction of the shaft. A gear select mechanism for selectively causing the shift yoke to correspond to an arbitrary spool; and causing the shift yoke to apply a force to the spool by swinging the shaft. A gear shift mechanism for making contact with the planetary gear, wherein the gear shift mechanism includes a planetary carrier, a planetary gear rotatably supported by the planetary carrier, and first and second ring gears having different numbers of teeth meshing with the planetary gear. A housing for fixing the first ring gear, a connecting portion for connecting the second ring gear to the shaft, A gear transmission for a vehicle transmission, comprising: a sun gear that meshes with the planetary gear; and a motor that rotates the sun gear, and that converts rotation of the motor into swinging motion of the shaft. 2. A shaft, a shift yoke mounted on the shaft such that the shaft is movable in a longitudinal direction of the shaft and is not rotatable relative to the shaft, and the shift yoke is moved in a longitudinal direction of the shaft. A gear select mechanism for selectively causing the shift yoke to correspond to an arbitrary spool; and causing the shift yoke to apply a force to the spool by swinging the shaft. A gear shift mechanism for making contact with the planetary gear, wherein the gear shift mechanism includes a planetary carrier, a planetary gear rotatably supported by the planetary carrier, and first and second ring gears having different numbers of teeth meshing with the planetary gear. A housing for fixing the first ring gear, a connecting portion for connecting the second ring gear to the shaft, And a motor for rotating the planetary carrier, and converting the rotation of the motor into a swinging motion of the shaft. 3. The planetary gear having a single number of teeth meshing with each of the first and second ring gears.
Or a gear transmission for a vehicle transmission according to item 2. 4. The planetary gear includes a first gear portion meshing with the first ring gear, and a second gear portion meshing with the second ring gear and having a different number of teeth from the first gear portion. A gear transmission for a vehicle transmission according to claim 1 or 2. 5. The first ring gear is fixed to the housing via a damper in a rotational direction.
A gear transmission for a vehicle transmission according to any one of claims 1 to 4. 6. A shaft, a shift yoke mounted on the shaft such that the shaft is movable in a longitudinal direction of the shaft and cannot rotate relative to the shaft, and the shift yoke is moved in a longitudinal direction of the shaft. A gear select mechanism for selectively causing the shift yoke to correspond to an arbitrary spool; and causing the shift yoke to apply a force to the spool by swinging the shaft. A gear shift mechanism for making contact, the gear shift mechanism comprises: a planetary carrier; a planetary gear rotatably supported by the planetary carrier; first and second sun gears having different numbers of teeth meshing with the planetary gear; The first
A housing for fixing a sun gear, a connecting portion for connecting the second sun gear to the shaft, a ring gear meshing with the planetary gear, and a motor for rotating the ring gear; A gear transmission for a vehicular transmission that converts to oscillating motion. 7. A shaft, a shift yoke mounted on the shaft such that the shaft is movable in a longitudinal direction of the shaft and cannot rotate relative to the shaft, and the shift yoke is moved in a longitudinal direction of the shaft. A gear select mechanism for selectively causing the shift yoke to correspond to an arbitrary spool; and causing the shift yoke to apply a force to the spool by swinging the shaft. A gear shift mechanism for making contact, the gear shift mechanism comprises: a planetary carrier; a planetary gear rotatably supported by the planetary carrier; first and second sun gears having different numbers of teeth meshing with the planetary gear; The first
For a vehicle, comprising: a housing for fixing a sun gear; a connecting portion for connecting the second sun gear to the shaft; and a motor for rotating the planetary carrier, wherein the rotation of the motor is converted into a swinging motion of the shaft. Transmission gear transmission. 8. The gear transmission according to claim 6, wherein the planetary gear has a single number of teeth that mesh with each of the first and second sun gears. 9. The planetary gear includes a first gear portion meshing with the first sun gear, and a second gear portion meshing with the second sun gear and having a different number of teeth from the first gear portion.
A gear transmission for a vehicle transmission according to claim 6. 10. The first sun gear is fixed to the housing via a damper in a rotational direction.
10. The gear transmission for a vehicle transmission according to any one of claims 1 to 9.