JP2003301944A - Transmission and gear shifting method - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a transmission and a gear shifting method wherein gear shift is smoothly operated by reducing a blank in transmission of the driving force when shifting a gear. <P>SOLUTION: A presser member is provided between a change gear for the lowest speed and a change gear for the second speed provided in an output shaft, and this presser member is brought in contact with a side surface of the change gear for the lowest speed or the change gear for the second speed at a first or a second contact part thereof by the displacing force. Contact force of the first or the second contact part becomes the force corresponding to the displacing force. With this structure, gear shifting operation is concluded by only switching the displacing force from one (for the lowest speed) to the other (second speed from the lowest). <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission and a transmission method for converting a rotation speed, and more particularly to a transmission and a transmission method suitable for smoothing a shift operation.

[0002]

2. Description of the Related Art In a vehicle such as a passenger car, a transmission is provided on the way of transmitting the output power of an engine, which is a power source, to driving wheels. Due to the presence of the transmission, the rotation speed of the engine can be appropriately set according to the speed change of the vehicle. That is, when the vehicle speed is slow, the gear ratio (output angular velocity / input angular velocity) is decreased to increase the engine rotation speed, and when the vehicle speed is high, the gear ratio is increased to increase the engine rotation speed. Make it small. As a result, the engine speed does not change as much as the change in the vehicle speed, and a more stable engine output can be obtained as the driving force.

Transmissions can be roughly classified into a manual type (so-called MT) operated by a change knob operation and an automatic type (so-called AT) in which a gear is automatically changed without any operation. In addition to this, in recent years, the MT is the basic mechanism, but the one in which the gear shifting operation is automated by an actuator (called “automated MT” etc.)
Has also appeared.

An example of the structure of a conventional transmission will be described with reference to FIG. FIG. 1 is a schematic diagram showing a configuration example of a conventional transmission (having 6 shifts and reverse).

As shown in FIG. 6, the drive shaft 101 includes a gear 102 from the lowest speed (1st speed) to a gear 1 from the highest speed (6th speed).
Up to 07, they are provided side by side in the axial direction of the drive shaft 101. The drive shaft 1 further outside the sixth speed gear 107
01 is provided with a reverse gear 108. These gears 102, 103, 104, 105, 106, 10
7, 108 are respectively fitted by, for example, key grooves (splines) provided in the drive shaft 101,
It always rotates at the same rotation speed as the drive shaft 101. A normal clutch mechanism (not shown) is provided on the left side of the drive shaft 101 in the drawing.
The driving force from the engine is transmitted via the.

The forward gears 102-107 mesh with the gears 110-115 provided on the output shaft 109, respectively. The reverse gear 108 meshes with the reversing gear 118 provided on the rotating shaft 117, and the reversing gear 118 is the gear 116 provided on the output shaft 109.
Meshes with. The rotation output is taken out from the right side (or left side) of the output shaft 109 in the drawing, and the drive wheel (not shown)
Be transmitted to.

These gears 1 provided on the output shaft 109
10, 111, 112, 113, 114, 115, 11
6 is not fixed to the drive shaft 109, but is supported so as to be able to idle with respect to the drive shaft 109 via, for example, a needle bearing (see the cross-section display portion). That is, when this transmission is in neutral, the engine rotation output is the drive shaft 101 and each gear 102 on the drive shaft side.
˜108 and the output shaft side gears 110 to 116 are simultaneously rotated, but the output shaft 109 is not rotationally driven.

A sleeve 119 is provided between the first speed gear 110 and the second speed gear 111 of the output shaft 109, and a third speed gear 11 is provided.
A sleeve 120 is provided between the second and fourth speed gears 113, and a sleeve 121 is similarly provided between the fifth speed gear 114 and the sixth speed gear 115. Further output shaft 109
A sleeve 122 is provided on the left side of the reverse gear 116.

These sleeves 119, 120, 12
Reference numerals 1 and 122 denote a substantially annular portion that fits in, for example, a key groove of the output shaft 109 and rotates integrally with the output shaft 109, and is provided further outside of the annular portion so as to be displaceable in the axial direction. A second generally annular portion. Both of these two annular parts rotate in synchronization with the output shaft 109.

The axially displaceable portion is adapted to generate a frictional force between each of the gears 110 to 116 due to the displacement. In order to generate such a frictional force, in practice, for example, the sleeves 119 to 122 and the gear 1 are
Further, one or more rings (each called a blocking ring, a taper cone ring, etc.) are interposed between 10 and 116. Further, a mechanism (synchro mechanism) is provided for restricting the sleeves 119 to 122 and the gears 110 to 116 thereof to rotate synchronously when a frictional force is generated and maintaining the state.
Below, these mechanisms will be collectively referred to as “sleeve 119”.
(120, 121, 122), etc. ”.

By displacing any of the sleeves 119 to 122 toward one of the gears 110 to 116,
As described above, a frictional force is generated between the sleeve and the gear, and the synchro mechanism causes the sleeve and the gear to rotate integrally. At this time,
The drive shaft 101 is rotated by the gear 102 on the drive shaft 101 side.
The output shaft 109 is rotated through any one of the gears 108, the gears 110 to 116 on the output shaft 109 side directly or indirectly engaged with the gear 108, and the sleeve that is in a state of rotating in synchronization therewith. This state is one shift state.

When such a speed change state is obtained, the speed change state is fixed by the mechanism itself such as the sleeves 119 to 122 as described above, and the speed change is performed unless a new axial displacement action is applied to the sleeves 119 to 122. The state is maintained. This is to prevent a problem in which the engine output is not transmitted to the drive wheels after the shift state is once established and the state is easily released.

The shift fork 12 serves as a mechanism for displacing the sleeves 119 to 122 in the axial direction as described above.
3,124,125,126 are provided as shown. Each shift fork 123-126 is associated with each sleeve 1
19 to 122, and a rod-shaped portion connected to the surrounding portion and provided in a direction parallel to the axial direction of each sleeve 119 to 122.

The rod-shaped portions of the shift forks 123 to 126 are displaced in either axial direction depending on the speed change state. As a result, one of the sleeves 119 to 122 is displaced to one of the gears 110 to 116,
The transmission is shifted to the above-described speed change state. The state in which none of the shift forks 123 to 126 is displaced is neutral as the transmission.

In the so-called MT, for example, the shift forks 123 to 12 are set depending on the left and right positions of the change knob.
6 is selected, and further, the shift fork and the sleeve are displaced by the forward and backward movement of the change knob so that the sleeve is positioned on either the left or right side of the drawing.

Further, in the automated MT, the selection and displacement of each shift fork 123-126 are provided by actuators such as hydraulic cylinders.

[0017]

SUMMARY OF THE INVENTION In the conventional transmission having the above-mentioned structure, the same shift fork prevents
A gear shift operation is performed for the third and fourth gears, which is the same for the third and fourth gears and the fifth and sixth gears, respectively. One of the reasons for having such a configuration is to reduce the number of shift forks as much as possible and simplify the mechanism.

With such a configuration, during a gear shift in the transmission, for example, the gear shift state of the first speed always transits to the gear shift state of the second speed through the neutral state. Moreover, in the 1st speed shift state, the sleeve 11 is not the shift fork 123.
The mechanism such as 9 maintains the synchronous rotation state, and releasing the maintenance state by the shift fork 123 also requires a certain amount of acting force and time. Also, when shifting from this state to the second speed shift state, a certain amount of force and time by the shift fork 123 are required until the mechanism such as the sleeve 119 itself shifts to establish the synchronous rotation state. Therefore, even if the clutch disengagement time is reduced as much as possible for the gear shifting operation, it is very difficult to reduce the time during which the engine output is not transmitted to the drive wheels (torque disengagement time).

The occurrence of such a driving force transmission blank period to a certain extent is a serious problem in the market especially when the transmission mechanism is an automated MT. That is, if a blank drive force (torque) occurs during a gear shift operation, the acceleration will suddenly decrease, and the passengers can easily perceive it and feel uncomfortable even in a short time. It is known that such a discomfort caused by the torque loss (feeling of idling) is difficult for the user to accept.

Since the uncomfortable feeling due to the torque loss is felt as much as the shift of the low speed gear, it is more important to take some measures for the shift of the lower speed gear.

The present invention has been made in consideration of the above circumstances, and in a transmission and a transmission method for converting a rotation speed, it is possible to reduce a blank period of driving force transmission at the time of a shift and to smoothly perform a shift operation. An object of the present invention is to provide a transmission and a transmission method capable of performing the above.

[0022]

In order to solve the above problems, a transmission according to the present invention includes a drive shaft having at least two drive side transmission gears for the lowest speed and the second speed from the lowest speed. Two for the lowest speed and for the second speed from the lowest speed, which are respectively engaged with the drive-side transmission gears for the lowest speed and the second speed from the lowest speed of the drive shaft, and are supported so as to idle with respect to the output shaft. The output shaft having at least an output side transmission gear, the output shaft between the lowest speed transmission gear of the output shaft and the second to lowest speed transmission gear of the output shaft, and the output shaft being integrated with the output shaft. Is provided so as to rotate to the side of the transmission gear for the lowest speed and the side of the transmission gear for the second speed from the lowest speed, and is displaced by the displacement force. Gearbox for The first contact portion that comes into contact with the side surface of the transmission gear for the lowest speed with the contact force corresponding to the displacement force when displaced to the side and the displacement gear is displaced from the low speed to the second transmission gear side. A pressing member having a second contact portion that comes into contact with a side surface of the transmission gear for the second speed from the low speed with a contact force corresponding to the displacement force is provided. ).

That is, a pressing member is provided between the transmission gear for the lowest speed of the output shaft and the transmission gear for the second speed, and the pressing member changes the transmission gear for the lowest speed of the output shaft by the displacement force. The first or second contact portion contacts the side surface of the gear or the side surface of the transmission gear for the second speed. At this time, the contact force with which the first or second contact portion contacts is a force corresponding to the displacement force.

As a result, when the displacement force is large to some extent, the pressing member and the transmission gear rotate in a synchronous manner (that is, the transmission state is maintained), and when the displacement force is less than that, the neutral state (or the neutral state). It becomes a state close to the state). In other words, the shifting operation is completed simply by switching the displacement force from one (for the lowest speed) to the other (for the second speed from the lowest speed). Therefore, it is necessary to go through a time-consuming process, such as the action of releasing the maintenance of one shift state once, the action of changing the position of the sleeve, and the action of shifting to the maintenance of another shift state. There is no.

Therefore, it is possible to reduce the blank period of the driving force transmission during the shift and smoothly perform the shift operation.

Further, the transmission according to the present invention is characterized in that the drive shaft is provided with at least two drive-side transmission gears for idling at a lowest speed and a second speed from the lowest speed, which are supported by the drive shaft so as to idle. , For the lowest speed of the drive shaft and 2 from the lowest
Output shaft having at least two output side transmission gears for the lowest speed and the second speed from the lowest speed, which mesh with the drive side transmission gears for the second speed, and the lowest speed transmission gear for the drive shaft. And 2 from the low speed of the drive shaft
So as to rotate integrally with the drive shaft between the transmission gear for the second speed and either the side of the transmission gear for the lowest speed or the side of the transmission gear for the second speed from the lowest speed. A first contact portion that is provided so as to be displaced by a displacement force, and contacts the side surface of the lowest speed transmission gear with a contact force corresponding to the displacement force when displaced toward the lowest speed transmission gear side by the displacement force; A first contact portion and a side surface of the speed change gear for the second speed from the low speed are contacted with a contact force corresponding to the displacement force when the contact part is displaced to the side of the second speed change gear from the low speed by the displacement force; And a pressing member having two contact portions (claim 2).

In this case, the pressing member is provided between the gear for the lowest speed and the gear for the second speed of the drive shaft, which is different from the above. Even with such a difference, the operation and effect described above can be obtained.

Further, as an embodiment, the transmission according to the present invention further comprises a mechanism for applying the displacement force to the pressing member. An actual speed change mechanism is provided.

Further, as an embodiment of the transmission according to the present invention, the mechanism has a force transmission member provided in connection with the pressing member and an actuator for displacing the force transmission member. The speed change mechanism has a force transmission member and an actuator for displacing the force transmission member, and is a preferable configuration particularly in the case of, for example, automated MT.

As an embodiment of the transmission according to the present invention, the actuator has a hydraulic cylinder mechanism. For example, a hydraulic cylinder mechanism as an actuator used in the automated MT is applied to the transmission of the present invention.

As an embodiment of the transmission according to the present invention, the hydraulic cylinder mechanism is driven by hydraulic pressure supplied from a hydraulic pressure supply source via an electromagnetic valve, and the electromagnetic valve is
It is controlled by an electric signal based on the result of detecting the displacement of the hydraulic cylinder mechanism. It is a structural example for making a hydraulic cylinder mechanism output predetermined displacement.

In the transmission according to the present invention, a drive shaft having a plurality of drive side transmission gears for low speed to high speed, and an output side transmission gear meshing with each of the drive side transmission gears are operated from low speed to high speed. A plurality of output shafts, and a third or lower speed of the output-side transmission gear / drive-side transmission gear, which is provided on the output shaft / drive shaft and is displaced in the axial direction of the output shaft / drive shaft. One of the above is the output shaft /
A sleeve for switching between a state of idling with respect to the drive shaft and a state of rotating synchronously with the drive shaft; and a sleeve provided on the output shaft for the lowest speed of the output side transmission gears of the output shaft and the output shaft. A first clutch mechanism capable of switching the relationship between idling and non-idling and maintaining the non-idling state by maintaining the action for switching to the non-idling, and the output shaft. A relation between the output shaft of the output side transmission gear of the output shaft for the second speed from the low speed and the output shaft can be switched to either idling or non-idling, and switching to non-idling can be performed. The non-idling state is maintained by maintaining the action for
And a clutch mechanism (1) are provided (Claim 7).

That is, the transmission gear for the lowest speed and the transmission gear for the second speed of the output shaft are each accompanied by a clutch mechanism capable of switching the relationship with the output shaft to either idling or non-idling. The clutch mechanism maintains the non-idle state by maintaining the action for switching to the non-idle state.

As a result, when the operation for switching to the non-idle state is maintained, the output shaft and the speed change gear are in a state of rotating synchronously (that is, the speed change state is maintained), and the above-mentioned operation is performed. It becomes a neutral state (or a state close to the neutral state) only by disappearing. In other words, the action for switching to the non-idle state is changed from the action for one shift gear (the one for the lowest speed) to the other shift gear (for the low speed to 2
The gear shifting operation is completed only by switching to the one for the second speed). Therefore, it is necessary to go through a time-consuming process, such as the action of releasing the maintenance of one shift state once, the action of changing the position of the sleeve, and the action of shifting to the maintenance of another shift state. There is no.

Therefore, it is possible to reduce the blank period of the driving force transmission at the time of gear shifting and smoothly perform the gear shifting operation.

In the transmission according to the present invention, the drive shaft having a plurality of drive side transmission gears for low speed to high speed and the output side transmission gears meshing with the drive side transmission gears are operated from low speed to high speed. A plurality of output shafts, and a third or lower speed of the output-side transmission gear / drive-side transmission gear, which is provided on the output shaft / drive shaft and is displaced in the axial direction of the output shaft / drive shaft. One of the above is the output shaft /
A sleeve for switching between a state of idling with respect to the drive shaft and a state of rotating synchronously with the drive shaft; and a sleeve provided on the drive shaft for the lowest speed among the drive side transmission gears of the drive shaft and the drive shaft. A first clutch mechanism capable of switching the relationship between idling and non-idling and maintaining the non-idling state by maintaining the action for switching to the non-idling, and the drive shaft. A relationship between the drive shaft of the drive-side transmission gear of the drive shaft, which is the second speed from the lowest speed, and the drive shaft can be switched between idling and non-idling, and switching to non-idling is possible. The non-idling state is maintained by maintaining the action for
And a clutch mechanism (1) (claim 8).

In this case, the first and second clutch mechanisms are provided between the shift gear for the lowest speed and the shift gear for the second speed of the drive shaft, which is different from the above. . Even with such a difference, the operation and effect described above can be obtained.

Further, as an embodiment of the transmission according to the present invention, the first clutch mechanism and / or the second clutch mechanism are rotatable in synchronization with a transmission gear supported by a shaft so as to be idle. A pressing member that presses the provided annular plate member in its thickness direction, and is connected to the pressing member,
A pressing member support member that rotates together with the pressing member in synchronization with the shaft that supports the transmission gear, and a pressing member that is provided on the pressing member support member and that presses the annular plate member. And a cylinder-piston mechanism for generating pressure. It is an example of a clutch mechanism suitable for accommodating a transmission gear.

As an embodiment of the transmission according to the present invention, the cylinder / piston mechanism is driven by drive oil supplied through a drive oil supply passage provided on the shaft, and the drive oil is: It is guided from the hydraulic pressure supply source to the drive oil supply path via a solenoid valve. It is an example for operating the cylinder / piston mechanism as desired.

Further, in the speed change method according to the present invention, the drive shaft is provided with at least two speed change gears for the lowest speed and the second speed from the lowest speed, and the lowest speed of the drive shaft and the second speed from the lowest speed. Output shaft including at least two output side transmission gears for the lowest speed and for the second speed from the lowest speed, which are meshed with the respective drive side transmission gears for each speed and supported so as to idle with respect to the output shaft. A gear for rotating at the lowest speed and a gear for rotating at the lowest speed of the output shaft and a gear for shifting from the lowest speed to the second speed of the output shaft so as to rotate integrally with the output shaft. It is provided so as to be displaced by a displacement force on either the gear side or the transmission gear side for the second speed from the low speed, and when the displacement force displaces to the side of the transmission gear for the lowest speed, For the lowest speed A first contact portion that comes into contact with a side surface of the transmission gear with a contact force corresponding to the displacement force and a second contact portion for the second speed from the low speed when the displacement force displaces to the second transmission gear side from the low speed. A shifting method in a transmission, comprising: a pressing member having a second contact portion that comes into contact with a side surface of a transmission gear with a contact force corresponding to the displacement force. By displacing the output shaft to the side of the lowest speed transmission gear to bring the first contact portion into contact with the side surface of the lowest speed transmission gear and maintaining the displacement force, And a displacement force is applied in a direction opposite to the step, so that the pressing member applies the pressing member to the second speed gear of the output shaft. To the side of the second contact portion The second speed transmission gear is placed in a non-idle state with respect to the output shaft by contacting the side surface of the second speed transmission gear and maintaining the displacement force in the opposite direction. And a step (claim 11).

According to this method, in the transmission described above, the displacement force is switched from one (for the lowest speed) to the other (for the second speed from the lowest speed). This completes the shift operation. Therefore, it is necessary to go through a time-consuming process, such as the action of releasing the maintenance of one shift state once, the action of changing the position of the sleeve, and the action of shifting to the maintenance of another shift state. There is no. Therefore, it is possible to reduce the blank period of transmission of the driving force at the time of shifting and smoothly perform the shifting operation.

Further, the speed change method according to the present invention is characterized in that the drive shaft is provided with at least two drive-side speed change gears for the lowest speed and the second speed from the lowest speed, which are supported so as to idle with respect to the drive shaft. , For the lowest speed of the drive shaft and 2 from the lowest
Output shaft having at least two output side transmission gears for the lowest speed and the second speed from the lowest speed, which mesh with the drive side transmission gears for the second speed, and the lowest speed transmission gear for the drive shaft. And 2 from the low speed of the drive shaft
So as to rotate integrally with the drive shaft between the transmission gear for the second speed and either the side of the transmission gear for the lowest speed or the side of the transmission gear for the second speed from the lowest speed. A first contact portion that is provided so as to be displaced by a displacement force, and contacts the side surface of the lowest speed transmission gear with a contact force corresponding to the displacement force when displaced toward the lowest speed transmission gear side by the displacement force; A first contact portion and a side surface of the speed change gear for the second speed from the low speed are contacted with a contact force corresponding to the displacement force when the contact part is displaced to the side of the second speed change gear from the low speed by the displacement force; And a pressing member having two contact portions, wherein a displacement force is applied to displace the pressing member to the side of the drive shaft for the slowest speed for the lowest speed. First contact portion and shift for the slowest speed A step of placing the transmission gear for the slowest by maintaining the side brought into contact with and the displacement force of the A to the state of non-idle with respect to said drive shaft,
A displacement force is applied in a direction opposite to that of the step to displace the pressing member to the side of the drive shaft for the second speed transmission gear to displace the second contact portion and the second speed use gear. Contacting the side surface of the transmission gear and maintaining the displacement force in the opposite direction, the transmission gear for the second speed is placed in a non-idle state with respect to the drive shaft. It is characterized (claim 12).

According to this method, in the transmission described above, the displacement force is switched from one (for the lowest speed) to the other (for the second speed from the lowest speed). This completes the shift operation. Therefore, it is necessary to go through a time-consuming process, such as the action of releasing the maintenance of one shift state once, the action of changing the position of the sleeve, and the action of shifting to the maintenance of another shift state. There is no. Therefore, it is possible to reduce the blank period of transmission of the driving force at the time of shifting and smoothly perform the shifting operation.

Further, in the speed change method according to the present invention, a drive shaft having a plurality of drive side speed change gears for low speed to high speed, and an output side speed change gear that meshes with each of the drive side speed change gears are changed from low speed to high speed. A plurality of output shafts, and a third or lower speed of the output-side transmission gear / drive-side transmission gear, which is provided on the output shaft / drive shaft and is displaced in the axial direction of the output shaft / drive shaft. A sleeve that switches between a state in which one of the gears rotates idly with respect to the output shaft / driving shaft and a state in which it rotates synchronously with the output shaft; and the lowest speed of the output side transmission gears of the output shaft A non-idle state is maintained by maintaining the action for switching to the non-idle state by switching the relationship between the output shaft and the output shaft to either idling or non-idling. Clutch mechanism of The relationship between the output shaft provided on the output shaft for the second speed from the output speed change gear of the output shaft and the output shaft can be switched between idling and non-idling and the non-idling And a second clutch mechanism in which the non-idling state is maintained by maintaining the action for switching to the output shaft, wherein the first clutch mechanism causes the output shaft to rotate. Setting the lowest speed transmission gear in a non-idle state with respect to the output shaft, and using the second clutch mechanism to change the second speed transmission gear from the lowest speed to the output shaft. To the non-idling state. (Claim 13).

According to this method, in the transmission described above, the action for switching to the non-idle state is applied to one transmission gear (the one for the lowest speed) to the other transmission gear (from the low speed to 2). (For the second speed) will be switched to the one targeted. This completes the shift operation. Therefore, it is necessary to go through a time-consuming process, such as the action of releasing the maintenance of one shift state once, the action of changing the position of the sleeve, and the action of shifting to the maintenance of another shift state. There is no. Therefore, it is possible to reduce the blank period of transmission of the driving force at the time of shifting and smoothly perform the shifting operation.

Further, in the speed change method according to the present invention, a drive shaft having a plurality of drive side speed change gears for low speed to high speed, and an output side speed change gear meshing with each drive side speed change gear are changed from low speed to high speed. A plurality of output shafts, and a third or lower speed of the output-side transmission gear / drive-side transmission gear, which is provided on the output shaft / drive shaft and is displaced in the axial direction of the output shaft / drive shaft. A sleeve for switching between a state in which one of the gears rotates idly with respect to the output shaft / drive shaft and a state in which the drive shaft rotates in synchronization with the output shaft / drive shaft; The first non-idling state is maintained by maintaining the function for switching to the non-idling state by maintaining the action for switching to the non-idling state by switching the relationship between the drive shaft and the drive shaft to either the idling or non-idling state. Clutch mechanism of The relationship between the drive shaft provided on the drive shaft and for the second speed from the low speed side of the drive side transmission gears of the drive shaft and the drive shaft can be switched between idling and non-idling and the non-idling And a second clutch mechanism in which the non-idle state is maintained by maintaining the action for switching to the drive shaft, the drive shaft being driven by the first clutch mechanism. Setting the lowest speed transmission gear in a non-idle state with respect to the drive shaft, and using the second clutch mechanism to change the second speed transmission gear from the lowest speed to the drive shaft. To the non-idling state. (Claim 14).

According to this method, in the above-described transmission, the action for switching to the non-idle state is performed from one gear (for the lowest speed) to the other gear (from low speed to 2). (For the second speed) will be switched to the one targeted. This completes the shift operation. Therefore, it is necessary to go through a time-consuming process, such as the action of releasing the maintenance of one shift state once, the action of changing the position of the sleeve, and the action of shifting to the maintenance of another shift state. There is no. Therefore, it is possible to reduce the blank period of transmission of the driving force at the time of shifting and smoothly perform the shifting operation.

[0048]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a configuration diagram schematically showing a transmission according to an embodiment of the present invention as a configuration for an automated MT.

As shown in the figure, this transmission has a drive shaft 1, a transmission gear 2 on the drive shaft 1 side, as a power transmission mechanism,
3, 4, 5, 6, 7, 8, output shaft 9, transmission gears 10, 11, 12, 13, 14, 15, 16 on output shaft 9 side, reversing gear rotating shaft 17, reversing gear 18, pressing It has a member 19 and sleeves 20, 21, 22. Contact portions 19 a and 19 b are provided on the side surface of the pressing member 19, and the transmission gear 1
The contacted portion 10 is provided on each of the opposite side surfaces of 0 and 11.
a and 11a are provided.

Further, this transmission has, as a transmission mechanism section,
Shift forks 23, 24, 25, 26, shift fork operating shaft 27, select control cylinders 28a, 28b,
Select control pistons 29a, 29b, shift control cylinders 30a, 30b, shift control pistons 31a, 31
b, electromagnetic valves 32 and 33, a hydraulic power source 34, and a transmission control unit 35.

Here, the shift forks 23, 24, 2
5, 26 have grooved protrusions 23a, 24, respectively.
a, 25a, and 26a are provided, and engage with any of the groove portions of the engaging projection 27 of the shift fork operating shaft 27.
a can be located. In addition, the select control piston 29a,
The pushed projection 27b of the shift fork operating shaft 27 is located between the shift control pistons 30a and 30b.
The pressed projection portion 27c of the shift fork operating shaft 27 is located between the two b. These relationships can also be referred to FIG. FIG. 2 is a view showing the axial direction of the shift fork operating shaft 27 as a direction perpendicular to the plane of the drawing, and corresponding parts are designated by the same reference numerals.

As shown in FIG. 1, on the drive shaft 1, from the lowest speed (1st speed) gear 2 to the highest speed (6th speed) gear 7,
They are arranged in the axial direction of the drive shaft 1 in the order of the second speed, the third speed, the fourth speed, the fifth speed, and the sixth speed. Further, a reverse gear 8 is provided on the drive shaft 1 further outside the sixth speed gear 7. These gears 2, 3, 4, 5, 6, 7, and 8 are fitted by, for example, key grooves (splines) provided on the drive shaft 1, and always rotate at the same rotational speed as the drive shaft 1. . The driving force from the engine is usually transmitted to the left side of the drive shaft 1 in the figure via a clutch mechanism (not shown).

The forward gears 2 to 7 are respectively connected to the output shaft 9
It meshes with gears 10 to 15 provided on the. The reverse gear 8 is the reverse gear 1 provided on the rotating shaft 17.
8, and the reversing gear 18 meshes with a gear 16 provided on the output shaft 9. The rotation output is taken out from the right side (or left side) of the output shaft 9 in the figure and transmitted to the drive wheels (not shown).

These gears 10 provided on the output shaft 9,
11, 12, 13, 14, 15, 16 are not fixed to the drive shaft 9 but are supported so as to be able to idle with respect to the drive shaft 9 via, for example, needle bearings. That is,
When the transmission is in neutral, the engine rotation output is the drive shaft 1 and the drive shaft side gears 2 to 2 respectively.
8, the output shaft side gears 10 to 16 are simultaneously rotated, but the output shaft 9 is not rotationally driven.

A pressing member 19 is provided between the first speed gear 10 and the second speed gear 11 of the output shaft 9, a sleeve 20 is provided between the third speed gear 12 and the fourth speed gear 13, and similarly, a fifth speed gear. Sleeves 21 are provided between the 14th gear and the sixth speed gear 15, respectively. Further, a sleeve 22 is provided on the left side of the reverse gear 16 of the output shaft 9.

The pressing member 19 has a substantially ring shape in which a key protrusion is fitted in a key groove of the output shaft 9 and rotates integrally with the output shaft 9, and is supported so as to be displaceable in the axial direction. There is. In addition, the first speed gear 10,
Contact portions 19a and 19b with the second speed gear 11 are provided, for example, in an annular shape. These contact portions 19a, 19b
Has a surface with a somewhat high coefficient of friction,
When the pressing member 19 is displaced toward the first speed gear 10 or the second speed gear 11 by the displacement force from the outside, it comes into contact with the contacted part 10a of the first speed gear 10 or the contacted part 11a of the second speed gear 11. Generates frictional force.

When the pressing member 19 is displaced toward the gear 10 or 11 by the displacement force and a frictional force is generated between the pressing member 19 and the gear 10 or 11, the pressing member 1
The 9 and the gear 10 or 11 are in a state of rotating integrally (non-idling state) as long as the frictional force continues. At this time, the rotation of the drive shaft 1 is caused by the gear 2 or 3 on the drive shaft 1 side, the gear 10 or 11 on the output shaft 9 side meshing with the gear 2 or 3,
The pressing member 1 that is in a state of rotating in synchronization with it
9, the output shaft 9 is rotated in sequence. This state is the first or second speed change state.

The sleeves 20, 21 and 22 have the key projections fitted in, for example, the key grooves of the output shaft 9 so that the output shaft 9 has the same shape.
And an approximately annular portion that rotates integrally with the annular portion, and a second approximately annular portion that is provided further outside the annular portion and that is axially displaceably supported. Both of these two annular parts rotate integrally with the output shaft 9.

Of these, the axially displaceable portion is adapted to generate a frictional force between each of the gears 12 to 16 due to the displacement. In order to generate such a frictional force, in practice, for example, the sleeves 20 to 22 and the gear 1 are
Further, one or more rings (each called a blocking ring, a taper cone ring, etc.) are interposed between 2 to 16. Further, a mechanism (synchronizing mechanism) is provided for restricting the sleeves 20 to 22 and the gears 12 to 16 to rotate synchronously when a frictional force is generated and maintaining the state. Since these mechanisms themselves can be the same as those already described as the prior art, further description is omitted here.

When any one of the sleeves 20 to 22 is displaced toward one of the gears 12 to 16, a frictional force is generated between the sleeve and the gear, as described above, and the synchro mechanism causes the frictional force. The sleeve and its gear are in a state of rotating together. At this time, drive shaft 1
Is rotated by any one of the gears 4 to 8 on the drive shaft 1 side, and the gears 12 to 16 on the output shaft 9 side directly or indirectly meshing therewith.
The output shaft 9 is in a state of being sequentially rotated through one of the sleeves, which is in a state of rotating in synchronization therewith. This state is one of the third, fourth, fifth, sixth, or reverse speed change states.

Shift forks 23, 24, 25 and 26 are provided as shown in the figure as a mechanism for axially displacing the pressing member 19 and the sleeves 20 to 22 as described above. Each shift fork 23-26 is connected to the annular outer side of the pressing member 19 or each sleeve 20-22, and a direction parallel to the axial direction of the pressing member 19 or each sleeve 20-22. And a rod-shaped portion provided on the.

The rod-shaped portions of the shift forks 23 to 26 are displaced in either axial direction depending on the speed change state. Thereby, the pressing member 19 or the sleeve 2
Any of 0 to 22 is displaced to the side of any of the gears 10 to 16, and the above-mentioned speed change state is established. A state in which none of the shift forks 23 to 26 is displaced is neutral as the transmission.

The rod-shaped portions of the shift forks 23 to 26 are provided with grooved projections 23a to 26a for receiving the acting force of the axial displacement thereof. In the neutral state, the grooved protrusions 23a to 26a are arranged so that the engagement protrusions 27a of the shift fork operating shaft 27 can move between the grooves.

The shift fork operating shaft 27 is axially and controllably displaced so that the engaging projection 27a moves between the grooves of the grooved projections 23a to 26a of the shift forks 23 to 26. Therefore, the shift fork operating shaft 2
The select control pistons 29a and 29b sandwich the front and rear of the pressed protrusion 27b provided on the No. 7 in the direction parallel to the axial direction of the shift fork operating shaft 27.

As a result, the select control piston 29
The shift fork operating shaft 27 is displaced in the axial direction by the above-described directional movements of a and 29b, and the engaging protrusions 27a have grooved protrusions 23a to
It can be located in the groove of 26a. Shift fork operating shaft 27
Such an action of corresponds to the selection of each of the shift forks 23 to 26, and is hereinafter referred to as "select operation".

The select control pistons 29a, 29
b are select control cylinders 28a and 28b, respectively.
And the select control pistons 29a, 29
b, the select control cylinders 28a and 28b are hydraulically controlled as select actuators as described later.

With the above mechanism, the shift forks 23-2
Following the selection of 6, each shift fork 23
The push-fork operating projection 27 is provided with a pressed projection 27c so that the rod-shaped portions of ~ 26 can be displaced in either axial direction depending on the speed change state. The pressed protrusion portion 27c is configured to be sandwiched by the shift control pistons 31a and 31b in a direction perpendicular to the axial direction of the shift fork operating shaft 27, whereby the shift fork operating shaft 27 is rotated around the shaft. Can be pressed. In addition, here, the shift fork operation shaft 2
7 is supported rotatably around its axis.

Referring to FIG. 2, the shift control piston 3
The shift fork operating shaft 27 is displaced in the rotational direction of the shaft by the above-mentioned directional movement of the shift forks 23 (25 to 26).
It can be seen that the shift fork 23 (25 to 26) can be displaced in the axial direction through the grooved projections 23a to 26a fitted in the. Since such an action of the shift fork operating shaft 27 corresponds to displacing each of the shift forks 23 to 26, it will be referred to as "shift operation" hereinafter.

The shift control pistons 31a and 31b
Are respectively fitted to the shift control cylinders 30a and 30b, and the shift control pistons 31a and 31b and the shift control cylinders 30a and 30b are hydraulically controlled as shift actuators as described later.

A hydraulic pressure is supplied from a hydraulic pressure source 34 to the cylinder inner chambers of the select control cylinder 28a and the piston 29b, which are the select actuators, and the select control cylinder 28b and the piston 29b, through a solenoid valve 32 for selection. The solenoid valve 32 is supplied with a control signal from the transmission control unit 35 in the form of an electric signal, and the transmission control unit 35 receives a displacement sensor output from the select control cylinder 28a and the piston 29b and the select control cylinder 28b and the piston 29b. Supplied.

The transmission control unit 35 sends a control signal to the solenoid valve 32 so that the displacement sensor output corresponds to a predetermined control displacement. In the solenoid valve 32, the control signal determines which side of the select control cylinders 28a, 28b the hydraulic pressure is supplied to. In this embodiment, the shift forks 23-26
Since there are four, the positions of the select control pistons 29a and 29b controlled by the transmission control unit 35 via the solenoid valve 32 are at least four positions.

Further, hydraulic pressure is supplied from the hydraulic power source 34 to the shift control cylinder 30a and the piston 31b, which are shift actuators, and the cylinder inner chambers of the shift control cylinder 30b and the piston 31b, through the electromagnetic valve 33 for shifting. The solenoid valve 33 is supplied with a control signal in the form of an electric signal from the transmission control unit 35, and the transmission control unit 35 receives a displacement sensor output from the shift control cylinder 30a and the piston 31b and the shift control cylinder 30b and the piston 31b. Supplied.

The transmission control unit 35 sends a control signal to the electromagnetic valve 33 so that the displacement sensor output corresponds to a predetermined control displacement. In the solenoid valve 33, the control signal determines which side of the shift control cylinders 30a, 30b the hydraulic pressure is supplied to. The positions of the shift control pistons 31a and 31b controlled by the transmission control unit 35 via the solenoid valve 33 are three positions including neutral.

As described above, the pressing member 19
When the first speed gear 10 or the second speed gear 11 is brought into a non-idle state by the pressing member 19, the pressing member 19 moves to the shift fork 23.
It is assumed that the displacement force due to is always received. Since such a continuous displacement force is generated, the shift fork 23
A force is transmitted from the shift control cylinder 30a and the piston 31b, and the shift actuators of the shift control cylinder 30b and the piston 31b to the shift fork operating shaft 27 that displaces the.

That is, in this case, the shift actuator functions not as a position servo mechanism but as a displacement force generator. The function of the shift actuator as a source of such a force that continuously presses the pressing member 19 toward the first speed gear 10 or the second speed gear 11 is that the sleeve 20 of the conventional example and this embodiment already described. It is unnecessary in ~ 22.

The shift control cylinder 30a and the piston 31b, and the shift actuator based on the cylinder-piston mechanism such as the shift control cylinder 30b and the piston 31b are preferable as the above-mentioned continuous force generation source. This is because the force can be continuously generated by maintaining the hydraulic pressure in each cylinder inner chamber.
For this purpose, instead of or in addition to the displacement sensor output to the transmission control unit 35, the output of the hydraulic pressure sensor may be fed back to the transmission control unit 35.

As described above, in this embodiment, the pressing member 19 is provided between the transmission gear 10 for the lowest speed and the transmission gear 11 for the second speed of the output shaft 9, and this pressing member 19 is provided. The first contact portion 19a or the second contact portion 19b of the output shaft 1 contacts the side surface of the transmission gear 10 for the lowest speed or the side surface of the transmission gear 11 for the second speed of the output shaft 1 due to the displacement force. . At this time, the contact force with which the first or second contact portions 19a and 19b contact is a force corresponding to the displacement force.

As a result, when the displacement force is large to some extent, the pressing member 19 and the transmission gear 10 (11) rotate in a synchronous manner (that is, the transmission state is maintained),
When the displacement force is less than that, the neutral state (or a state close to the neutral state) is reached. In other words, the shifting operation is completed only by switching the displacement force from one (11 for the lowest speed) to the other (12 for the second speed from the lowest speed). Therefore, it is necessary to go through a time-consuming process, such as the action of releasing the maintenance of one shift state once, the action of changing the position of the sleeve, and the action of shifting to the maintenance of another shift state. There is no.

Therefore, it is possible to reduce the blank period of the transmission of the driving force during the shift between the 1st and 2nd speeds and smoothly perform the shift operation. When it is applied to the automated MT as in the present embodiment, it is possible to prevent occurrence of torque loss and obtain comfortable running. The hydraulic power source 34 is also used in the case of the conventional automated MT transmission, and the hydraulic pressure output from the hydraulic power source 34 is used as a pressing force to the gear 10 or 11 of the pressing member 19, so that the hydraulic pressure is relatively reduced. Smoothing of the above gear shifting operation can be realized by making minor design changes. Further, when shifting from neutral to the first speed and shifting from the first speed to the second speed, the process of shifting to the state of maintaining the shifting state is not required, so that the generation of abnormal noise during the shifting can be suppressed to a low level. .

As described above, the gear shifting operation is particularly problematic in the low speed gear in order to prevent the torque loss. Therefore, the first gear and the second gear are gear-shifted via the pressing member 19. In addition to this, for example, similar mechanisms can be provided for the third speed and the fourth speed.

Further, as in this embodiment, not only the idling mechanisms of all the transmission gears are provided on the output shaft 9 side, but all the transmission gears are provided with the idling mechanism on the drive shaft 1 side or a part of the sleeves. Alternatively, the idling mechanism may be provided on the drive shaft 1 side only for the transmission gear related to (or the pressing member). Whether the idling mechanism is provided on the output shaft 9 side or the drive shaft 1 side, the sleeve or the pressing member is involved to switch between the idling state and the non-idling state, and the rotational driving force is transmitted through the gears that mesh with each other. This is because there is no change in transmission from the output shaft 9 to the output shaft 9. In general, it is better to provide a slipping mechanism and a sleeve (or a pressing member) on the shaft with a larger diameter of the gear by each transmission gear, because the force for displacing the sleeve (or the pressing member) required at the time of gear shifting is increased. It is advantageous to make it small.

Next, a transmission according to another embodiment of the present invention will be described with reference to FIG. FIG. 3 is a configuration diagram schematically showing a transmission according to another embodiment of the present invention as a configuration for automated MT. In the figure, the same numbers are assigned to the components already described. Hereinafter, description will be made while avoiding duplication with the previous embodiment.

In this embodiment, instead of the mechanism for switching the first speed gear 10 and the second speed gear 11 between idling and non-idling by the pressing member 19, a clutch mechanism such as used in AT is used. The difference between the above embodiments is that the gears 10 and 11 are switched between idling and non-idling.

This clutch mechanism corresponds to the gear 1 in FIG.
It is provided in the pressing member support member 41 shown between 0 and 11. FIG. 4 is a cross-sectional view showing the inside of the pressing member support member 41. As shown, the gears 10, 11
Is supported by the needle bearings 51 and 52 so as to be idle with respect to the drive shaft 9. This point is similar to the case of the previous embodiment.

As shown in FIG. 4, the pressing member support member 41
Is designed to rotate integrally with the output shaft 9, for example, the output shaft 9
It is fitted in the key groove of and surrounds the output shaft 9 and is provided in an annular shape. The annular member of the pressing member support member 41 is slightly inside, and a plurality of plate-like pressing members 54 are formed in an annular shape so as to fit therein.
(56) is provided. The pressing member 54 (56) is a groove 41 a (4) provided on the annular inner surface of the pressing member support member 41.
1b) and is supported by the pressing member support member 41 so as to be movable in the axial direction of the drive shaft 9.

Between the plurality of pressing members 54 (56), a plurality of plate-shaped annular plate members 53, which are annular members, are fitted.
The ring-shaped plate member 53 is guided by a groove 10a (10b) provided in a portion protruding from the gear 10 (11) in a ring shape so as to be movable in the axial direction of the drive shaft 9 above the gear 10 (11). It is supported by the protruding part.

A ring-shaped piston 57 (58), which is a movable member in the axial direction of the drive shaft 9, is provided on the annular inner surface of the pressing member support member 41 and behind the pressing member 54 (56). To be The piston 57 (58) is a movable member whose inner surface is an annular surface of the pressing member support member 41, and an O-ring 59 (61) is provided between the piston 57 (58) and the inner surface.
60 (62) is provided to seal the hydraulic oil. When the hydraulic pressure is not applied, the repulsion spring 64 (6) repulsed to the outside of the piston 57 (58).
By 5), the piston 57 (58) is located at the innermost part of the annular inner surface of the pressing member support member 41.

Drive oil supply passage 63 provided in the drive shaft 9
When the driving oil is supplied from the a (63b) to the pressing member supporting member 41 side, the driving oil pushes the internal space (cylinder inner chamber) formed by the pressing member supporting member 41 and the piston 57 (58). spread. This allows the piston 5
7 (58) compresses the repulsion spring 64 (65) and moves in the axial direction of the drive shaft 9.

As a result, the pressing member 54 (56) presses and grips the annular plate member 53 (55) in its thickness direction, and the pressing member supporting member 41 and the gear 10 (11) rotate integrally. Become. This state is the first speed or the second speed shift state (when the drive oil is supplied to the drive oil supply passage 63a is the first speed shift state, and when the drive oil is supplied to the drive oil supply passage 63b) Is in the 2nd speed.)

FIG. 5 is a diagram showing the above-described first speed shift state and second speed shift state. FIG. 5 (a) shows the first speed shift state, and FIG. 5 (b) shows the second speed shift state. In these figures, the parts corresponding to those in FIG. 4 are given the same numbers.

Since the shift mechanism is shifted to the first speed or the second speed by the clutch mechanism described above, the shift forks for the first speed gear 10 and the second speed gear 11 are unnecessary as shown in FIG. In response to this, the select control cylinder 2
The select operation of the shift fork operation shaft 27 by the 8a and 28b and the select control pistons 29a and 29b is also at least 3 positions.

Electromagnetic valves 42 and 43 are provided for controlling the supply of drive oil to the clutch mechanism. Solenoid valves 42, 4
3 is provided on each downstream side of the solenoid valve 33 for shift described above, and one of output sides thereof is guided to the shift control cylinders 30a and 30b. As a result, the shift fork operating shaft 27 is operated to shift in the third, fourth, fifth, sixth, or reverse shift states, as in the previous embodiment.

In order to bring the first speed gear 10 and the second speed gear 11 into the non-idle state (that is, the speed change state), the solenoid valve 33
The hydraulic pressure input to the solenoid valves 42 and 43 from the drive oil supply passage 63 is not supplied to the shift control cylinders 30a and 30b.
The solenoid valves 42 and 43 are controlled to output to the a and 63b sides. Control signals to the solenoid valves 42 and 43 for this purpose are supplied from the transmission control unit 35. As a result, the hydraulic pressure output of the solenoid valve 33 is guided to the drive oil supply passages 63a and 63b, so that the shift state is established as described above.

The displacement of the pistons 57 and 58 may be detected by a displacement sensor and fed back to the transmission control unit 35. As a result, more reliable gear shifting operation can be performed.

As described above, in this embodiment, the lowest speed transmission gear 10 and the second speed transmission gear 11 of the output shaft 9 are idle / non-reliable with respect to the output shaft 9, respectively. With a clutch mechanism that can be switched to either idle. This clutch mechanism maintains the action for switching to the non-idle state (that is, the drive oil supply passage 6
This non-idle state is maintained (by maintaining the hydraulic pressure supply to 3a, 63b).

As a result, when the action for switching to the non-idle state is maintained, the output shaft 9 and the transmission gear 10 are
Alternatively, 11 and 11 are synchronously rotated (that is, the gear shift state is maintained), and the neutral state (or a state close to the neutral state) is achieved only by eliminating the above-mentioned action. In other words, the action for switching to the non-idle state is applied to one transmission gear 10 (for the lowest speed) to the other transmission gear 11 (for the second speed from low speed). The gear shifting operation is completed only by switching to the one. Therefore,
There is no need to go through the time-consuming process of releasing the maintenance of one shift state once, changing the position of the sleeve, and shifting to the maintenance of another shift state as in the conventional case. .

Therefore, it is possible to reduce the blank period of the driving force transmission during the shift and smoothly perform the shift operation.
When it is applied to the automated MT as in the present embodiment, it is possible to prevent occurrence of torque loss and obtain comfortable running.
The hydraulic power source 34 is also used in the case of a conventional automated MT transmission, and the hydraulic pressure output from the hydraulic power source 34 is used as the clutch operating force of the clutch mechanism to make a relatively minor design change. As a result, it is possible to realize the smooth shift operation. Further, when shifting from neutral to the first speed and shifting from the first speed to the second speed, the process of shifting to the state of maintaining the shifting state is not required, so that the generation of abnormal noise during the shifting can be suppressed to a low level. .

As described above, the gear shift operation is particularly problematic in the low-speed gear in order to prevent the torque loss. Therefore, the first gear and the second gear are gear-shifted via the clutch mechanism. In addition to the above, similar mechanisms can be provided for the third speed and the fourth speed, for example.

Further, not only the idling mechanism of all the transmission gears is provided on the output shaft 9 side as in this embodiment, but the idling mechanism is provided on the drive shaft 1 side for all the transmission gears, or some sleeves are provided. Alternatively, the idling mechanism may be provided on the drive shaft 1 side only for the transmission gear related to (or the clutch mechanism). Whether the idling mechanism is provided on the output shaft 9 side or the drive shaft 1 side, a sleeve or a clutch mechanism is involved to switch between the idling state and the non-idling state, and the rotational driving force is transmitted through the meshing gears to the driving shaft 1 To output shaft 9
Because it will be transmitted to. In general, it is better to provide a slipping mechanism and a sleeve (or a clutch mechanism) on the shaft on the side of a larger gear diameter for each transmission gear, because this reduces the force required to displace the sleeve (or clutch) when shifting. It is advantageous to reduce the hydraulic pressure supplied to the mechanism.

[0100]

As described in detail above, according to the present invention,
A pressing member is provided between the transmission gear for the lowest speed of the output shaft or the drive shaft and the transmission gear for the second speed, and the pressing member is for the lowest speed of the output shaft or the drive shaft due to the displacement force. The first or second contact portion comes into contact with the side surface of the transmission gear or the side surface of the transmission gear for the second speed.

As a result, the shifting operation is completed only by switching the displacement force from one (for the lowest speed) to the other (for the second speed from the low speed). Therefore, as in the past,
There is no need to go through the time-consuming process of releasing the maintenance of one shift state once, shifting the position of the sleeve, and shifting to the maintenance of another shift state. It is possible to reduce the blank period of force transmission and smoothly perform the gear shifting operation.

Further, according to the present invention, the lowest speed transmission gear and the second speed transmission gear of the output shaft or the drive shaft respectively have a relationship of idling / output shaft or drive shaft.
With a clutch mechanism that can be switched to either non-idle state, this clutch mechanism is maintained in this non-idle state by maintaining the action for switching to non-idle state.

As a result, the action for switching to the non-idle state is applied to one transmission gear (for the lowest speed) to the other transmission gear (for the second speed from the low speed).
The gear shifting operation is completed only by switching to the one targeted for. Therefore, it is necessary to go through a time-consuming process, such as the action of releasing the maintenance of one shift state once, the action of changing the position of the sleeve, and the action of shifting to the maintenance of another shift state. Therefore, it is possible to reduce the blank period of the driving force transmission at the time of gear shifting and smoothly perform the gear shifting operation.

[Brief description of drawings]

FIG. 1 is a diagram showing an automated MT for a transmission according to an embodiment of the present invention.
The block diagram which shows typically as a structure for.

FIG. 2 is a view showing an axial direction of a shift fork operation shaft 27 shown in FIG. 1 as a direction perpendicular to a paper surface.

FIG. 3 is an automatic transmission M according to another embodiment of the present invention.
The block diagram which shows typically as a structure for T.

4 is a cross-sectional view showing the inside of the pressing member support member 41 in FIG.

5A and 5B are diagrams showing a first speed shift state and a second speed shift state of the pressing member support member 41 shown in FIG.

FIG. 6 is a schematic diagram showing a configuration example of a conventional transmission (having six shifts and reverse).

[Explanation of symbols]

1 ... Drive shaft 2 ... Drive shaft side first speed gear 3 ... Drive shaft side second speed gear 4 ... Drive shaft side third speed gear 5 ... Drive shaft side fourth speed gear
6 ... Drive shaft side fifth speed gear 7 ... Drive shaft side sixth speed gear 8 ... Drive shaft side reverse gear 9 ... Output shaft 10 ... Output shaft side first speed gear 10a ... Contacted portion 11 ... Output shaft side second speed gear 11a ... Contacted part 12 ... Output shaft side third speed gear 13
Output speed side 4th gear 14 Output shaft side 5th gear 15
Output shaft side 6th gear 16 ... Output shaft side reverse gear 17
... Rotary shaft 18 ... Reversing gear 19 ... Pressing member 19
a, 19b ... Contact portion 20, 21, 22 ... Sleeve 2
3, 24, 25, 26 ... Shift forks 23a, 24
a, 25a, 26a ... Grooved protrusion 27 ... Shift fork operating shaft 27a ... Engagement protrusion 2
7b ... Pressed protrusion 27c ... Pressed protrusion 28a, 28b ... Select control cylinder 29a, 29b ... Select control piston 3
0a, 30b ... Shift control cylinders 31a, 31b ...
Shift control piston 32 ... Select solenoid valve 33 ...
Solenoid valve for shift 34 ... Hydraulic pressure source 35 ... Transmission control unit 41 ... Pressing member support member 41a, 41b ...
Groove 42 ... 1st speed solenoid valve 43 ... 2nd speed solenoid valve 5
1, 52 ... Needle bearing 53, 55 ... Annular plate member 54, 56 ... Pressing member 57, 58 ... Piston
59, 60, 61, 62 ... O-rings 63a, 63b
… Driving oil supply channels 64, 65… Repulsion spring

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Kaigo             3-20-14 Higashi Gotanda, Shinagawa-ku, Tokyo             Mens VOD Auto             Within Tive Co., Ltd. F term (reference) 3J067 AA01 AB11 AC04 AC05 BA51                       FB71 GA01

Claims (14)

[Claims] 1. A drive shaft having at least two drive speed change gears for the lowest speed and the second speed from the low speed, and the drive speed change gear for the lowest speed and the second speed from the low speed of the drive shaft. The output shaft, which includes at least two output-side speed change gears for the lowest speed and the second speed from the lowest speed, which meshes with the respective gears and is supported so as to idle with respect to the output shaft, and the lowest speed of the output shaft. Between the low speed shift gear and the low speed second shift speed of the output shaft so as to rotate integrally with the output shaft. A side surface of the shift gear for the lowest speed when the displacement gear is provided on one side of the shift gear for the second speed so as to be displaced by the displacement force, and when the displacement gear is displaced to the side of the shift gear for the lowest speed. To the displacement force The displacement force is applied to the side surface of the transmission gear for the second speed from the low speed when the displacement is made to the side of the second transmission gear from the low speed by the first contact portion contacting with the corresponding contact force and the displacement force. A pressing member having a second contact portion that comes into contact with a corresponding contact force, and a transmission. 2. A drive shaft having at least two drive-side speed change gears for idling at a lowest speed and a second speed from the lowest speed, which are supported by a drive shaft so as to be idle, and a lowest speed of the drive shaft. And an output shaft having at least two output side transmission gears for the lowest speed and the second speed from the low speed, which mesh with the drive side transmission gears for the second speed from the low speed, respectively, and the lowest speed of the drive shaft. Between the low speed shift gear and the low speed second shift speed of the drive shaft so as to rotate integrally with the drive shaft. A side surface of the shift gear for the lowest speed when the displacement gear is provided on one side of the shift gear for the second speed so as to be displaced by the displacement force, and when the displacement gear is displaced to the side of the shift gear for the lowest speed. To the displacement force The displacement force is applied to the side surface of the transmission gear for the second speed from the low speed when the first contact portion that is in contact with the same contact force and the displacement force displaces to the second transmission gear side from the low speed. A pressing member having a second contact portion that comes into contact with a corresponding contact force, and a transmission. 3. The transmission according to claim 1, further comprising a mechanism that applies the displacement force to the pressing member. 4. The transmission according to claim 3, wherein the mechanism includes a force transmission member connected to the pressing member and an actuator that displaces the force transmission member. 5. The transmission according to claim 4, wherein the actuator has a hydraulic cylinder mechanism. 6. The hydraulic cylinder mechanism is driven by a hydraulic pressure supplied from a hydraulic pressure supply source via an electromagnetic valve, and the electromagnetic valve is controlled by an electric signal based on a result of detecting displacement of the hydraulic cylinder mechanism. The transmission according to claim 5, wherein: 7. A drive shaft having a plurality of drive speed change gears for low speed to high speed, an output shaft having a plurality of output speed change gears meshing with the drive side speed change gears for low speed to high speed, respectively. The output shaft / driving shaft is provided with one of the output-side speed change gear / the drive-side speed change gear for a speed from the third speed to the third speed or lower by displacing in the output shaft / drive shaft axial direction. / A sleeve for switching between a state of idling with respect to the drive shaft and a state of rotating synchronously with the drive shaft; and a sleeve provided on the output shaft for the lowest speed of the output side transmission gears of the output shaft and the output shaft. A first clutch mechanism capable of switching the relationship between idling and non-idling and maintaining the non-idling state by maintaining the action for switching to non-idling; and the output shaft Provided in the above Of the output side transmission gears of the force shaft, the relationship between the second speed gear from the low speed and the output shaft can be switched between idling and non-idling, and an action for switching to non-idling is provided. A second clutch mechanism that maintains the non-idle state by being maintained. 8. A drive shaft having a plurality of drive speed change gears for low speed to high speed, and an output shaft having a plurality of output speed change gears meshing with the drive side speed change gears for low speed to high speed, respectively. The output shaft / driving shaft is provided with one of the output-side speed change gear / the drive-side speed change gear for a speed from the third speed to the third speed or lower by displacing in the axial direction of the output shaft / drive shaft. / A sleeve for switching between a state of idling with respect to the drive shaft and a state of rotating synchronously with the drive shaft; a lowest speed one of the drive side transmission gears of the drive shaft, which is provided on the drive shaft, and the drive shaft. A first clutch mechanism capable of switching the relationship between idling and non-idling and maintaining the non-idling state by maintaining the action for switching to non-idling; and the drive shaft. Provided in the above The relationship between the drive-side transmission gear of the drive shaft for the second speed from the lowest speed and the drive shaft can be switched to either idling or non-idling, and an action for switching to non-idling is provided. A second clutch mechanism that maintains the non-idle state by being maintained. 9. The thickness of the first clutch mechanism and / or the second clutch mechanism is an annular plate member rotatably provided in synchronism with a speed change gear supported by an idle shaft. A pressing member that presses in a direction, a pressing member support member that is connected to the pressing member and that rotates together with the pressing member in synchronization with the shaft that supports the transmission gear, and that is provided on the pressing member support member, 8. The pressing member has a cylinder / piston mechanism for generating a pressing force for pressing the annular plate member.
Or the transmission according to item 8. 10. The cylinder / piston mechanism is driven by drive oil supplied via a drive oil supply passage provided in the shaft, and the drive oil is driven from a hydraulic pressure supply source via an electromagnetic valve. The transmission according to claim 9, wherein the transmission is guided to an oil supply path. 11. A drive shaft having at least two drive-side transmission gears for the lowest speed and the second speed from the lowest speed,
Two for the lowest speed and for the second speed from the lowest speed, which are respectively engaged with the drive-side transmission gears for the lowest speed and the second speed from the lowest speed of the drive shaft, and are supported so as to idle with respect to the output shaft. The output shaft having at least an output side transmission gear, the output shaft between the lowest speed transmission gear of the output shaft and the second to lowest speed transmission gear of the output shaft, and the output shaft being integrated with the output shaft. Is provided so as to rotate to the side of the transmission gear for the lowest speed and the side of the transmission gear for the second speed from the lowest speed, and is displaced by the displacement force. First contact portion that comes into contact with the side surface of the lowest speed transmission gear with a contact force corresponding to the displacement force when displaced to the side of the second transmission gear and the second transmission gear from the low speed due to the displacement force. Is displaced to the side of And a pressing member having a second contact portion that comes into contact with a side surface of the speed change gear for the second speed from the low speed with a contact force corresponding to the displacement force. A force is applied to displace the pressing member to the side of the output gear for the lowest speed for the output shaft to bring the first contact portion into contact with the side surface of the transmission gear for the lowest speed and to perform the displacement. Maintaining the force to put the transmission gear for the lowest speed in a non-idle state with respect to the output shaft; and applying a displacement force in a direction opposite to that of the step so that the pressing member pushes the output shaft. Of the second speed shifting gear to bring the second contact portion into contact with the side surface of the second speed shifting gear and maintain the reverse displacement force. The transmission gear for the second speed is And a step of keeping the output shaft in a non-idle state. 12. The drive shaft, which is provided with at least two drive-side speed change gears for the lowest speed and the second speed from the lowest speed, which are supported so as to idle with respect to the drive shaft, and the lowest speed of the drive shaft. And an output shaft having at least two output side transmission gears for the lowest speed and the second speed from the low speed which mesh with the drive side transmission gears for the second speed from the low speed and the lowest speed of the drive shaft, respectively. Between the low speed shift gear and the low speed second shift speed of the drive shaft so as to rotate integrally with the drive shaft. A side surface of the shift gear for the lowest speed when the displacement gear is provided on one side of the shift gear for the second speed so as to be displaced by the displacement force, and when the displacement gear is displaced to the side of the shift gear for the lowest speed. To the displacement force The displacement force is applied to the side surface of the transmission gear for the second speed from the low speed when the displacement is made to the side of the second transmission gear from the low speed by the first contact portion contacting with the corresponding contact force and the displacement force. Second contact with the appropriate contact force
A transmission member including a pressing member having a contact portion of, and a displacement force is applied to displace the pressing member to the side of the drive shaft for the lowest speed shift gear. Placing the lowest speed transmission gear in a non-idling state with respect to the drive shaft by contacting the contact portion of No. 1 with the side surface of the lowest speed transmission gear and maintaining the displacement force. , A displacement force is applied in a direction opposite to the step to displace the pressing member to the side of the drive gear for the second speed of the drive shaft to move the second contact portion and the second speed. Contacting the side surface of the transmission gear for the vehicle and maintaining the displacement force in the opposite direction, the transmission gear for the second speed is kept in a non-idle state with respect to the drive shaft. Shifting method characterized by. 13. A drive shaft having a plurality of drive speed change gears for low speed to high speed, and an output shaft having a plurality of output speed change gears meshing with the drive side speed change gears for low speed to high speed, respectively. The output shaft / driving shaft is provided with one of the output-side speed change gear / the drive-side speed change gear for a speed from the third speed to the third speed or lower by displacing in the axial direction of the output shaft / drive shaft. / A sleeve that switches between a state of idling with respect to the drive shaft and a state of rotating in synchronization with the drive shaft, and the lowest speed one of the output side transmission gears of the output shaft, and the output shaft The first clutch mechanism capable of switching the relationship between idling and non-idling and maintaining the non-idling state by maintaining the action for switching to non-idling, and the output shaft. Is installed in the Of the output side transmission gears of the force shaft, the relationship between the second speed gear from the low speed and the output shaft can be switched between idling and non-idling, and an action for switching to non-idling is provided. A transmission method for a transmission, comprising: a second clutch mechanism for maintaining the non-idle state by maintaining the rotation speed of the output shaft; Is placed in a non-idle state with respect to the output shaft, and the second clutch mechanism puts the transmission gear for the second speed from the low speed of the output shaft in a non-idle state with respect to the output shaft. And a step of setting. 14. A drive shaft having a plurality of drive speed change gears for low speed to high speed, an output shaft having a plurality of output speed change gears meshing with the drive side speed change gears for low speed to high speed, respectively. The output shaft / driving shaft is provided with one of the output-side speed change gear / the drive-side speed change gear for a speed from the third speed to the third speed or lower by displacing in the axial direction of the output shaft / drive shaft. / A sleeve for switching between a state of idling with respect to the drive shaft and a state of rotating synchronously with the drive shaft; and a drive shaft provided on the drive shaft for the lowest speed of the drive side transmission gears of the drive shaft and the drive shaft. The first clutch mechanism capable of switching the relationship between idling and non-idling and maintaining the non-idling state by maintaining the action for switching to non-idling; and the drive shaft. Is installed in the The relationship between the drive-side transmission gear of the drive shaft for the second speed from the lowest speed and the drive shaft can be switched to either idling or non-idling, and an action for switching to non-idling is provided. A transmission method for a transmission, comprising: a second clutch mechanism for maintaining the non-idle state by being maintained, wherein the first clutch mechanism is a shift gear for the lowest speed of the drive shaft. Is placed in a non-idle state with respect to the drive shaft, and the second clutch mechanism causes the transmission gear for the second speed from the low speed of the drive shaft to be in a non-idle state with respect to the drive shaft. And a step of setting.