JPH0637927B2 - Transmission for vehicle - Google Patents

Description

Description: [Object of the Invention] The present invention relates to an improvement of a vehicle transmission that achieves four forward gears and one reverse gear including overdrive.

[Prior Art] An automatic transmission configured to achieve four forward gears and one reverse gear including overdrive by using two sets of simple planetary gears is disclosed in Japanese Patent Application No. 60-1395.
Many are known, including those described in the specification No. 3.

[Problems to be Solved by the Present Invention]

However, the one described in the above-mentioned Japanese Patent Application No. 60-13953 is, as shown in FIG. 2 of the same application, when shifting from the first speed to the second speed in which the driving force transmitted is particularly large. ，
The second clutch is released and the first clutch is engaged while the engagement state of the second brake is maintained.
As described above, in the structure in which the shift from the first speed to the second speed is achieved by releasing and engaging the clutch, the rotating members having different rotating speeds must be smoothly engaged with each other. Therefore, the control of the hydraulic pressure and the like supplied to the clutch becomes complicated, and there is a problem that gear shift shock is likely to occur.

Further, it has two sets of simple planetary gear devices, and the carrier of one of the planetary gear devices passes through the outside of the other gear device and the other gear device is connected via a connecting shaft having a clutch with which the connection can be interrupted. In the grooved type, which is connected to the ring gear of the above and further provided with a brake for stopping the coaxial rotation on the outside of the connecting shaft, the clutch is arranged on the outside in the radial direction of the other gear device. Therefore, there was a problem that the outer diameter of the transmission became large.

[Structure of Invention]

The present invention has been proposed in view of the above, and rotatably supports an input shaft to which rotational power of an engine is input, a first sun gear, a first pinion gear meshing with the first sun gear, and a first pinion gear. Rotating a first carrier that is rotatable by itself, a first simple planetary gear device including a first ring gear that meshes with the first pinion gear, a second sun gear, a second pinion gear that meshes with the second sun gear, and a second pinion gear A second carrier that is freely supported and is rotatable, and a second gear that meshes with the second pinion gear.
A second simple planetary gear device including a ring gear, and the first
A first connecting shaft that connects the sun gear and the second sun gear, a second connecting shaft that connects the first carrier and the second ring gear, and a driving force to a drive axle of the vehicle that is connected to the second carrier An output shaft for transmission, a first clutch for connecting and disconnecting the connection between the input shaft and the first ring gear,
The second clutch that connects and disconnects the input shaft and the first connecting shaft, the third clutch that connects and disconnects the input shaft and the second connecting shaft, and the rotation of the first ring gear are stopped. A first brake for operating the second connecting shaft and a second brake for stopping the rotation of the second connecting shaft are provided. By selectively operating each of the clutches and brakes, four forward gears and one reverse gear can be changed. The gist of the invention is a vehicle transmission characterized in that it is configured to achieve a plurality of gears.

〔The invention's effect〕

According to the above configuration, the shift from the first speed to the second speed is performed by releasing the second brake and engaging the first brake while maintaining the engaged state of the second clutch. Since it is achieved only by releasing the second intermediate shaft and stopping the rotation of the first ring gear, it is possible to easily achieve a gear shift without a gear shift shock without complicated hydraulic control. . 1st carrier and 2nd
Since the ring gear is simply connected by the hollow second connecting shaft, it is not necessary to dispose the clutch on the outer side in the radial direction of the second simple planetary gear device, and the outer diameter of the transmission can be reduced. .

〔Example〕

An embodiment of the present invention will be described in detail below with reference to FIG. A drive shaft 10 directly connected to a crank shaft of an engine (not shown) is an input casing 14 of a torque converter 12.
Is connected to the pump 16 of the torque converter 12, and the stator 18 of the torque converter 12 is connected to the transmission casing 22 via the one-way clutch 20. Further, the turbine 24 of the torque converter 12 is connected to a clutch 28, a clutch 30 and a clutch 32 via an input shaft 26, and an output side of the clutch 28 is connected to a first intermediate shaft 34 having a tubular shape via a first intermediate shaft 34. The first carrier 38 of the simple planetary gear device 36 (hereinafter, simply referred to as the first gear device 36) and the second simple planetary gear device 40.
It is connected to a second ring gear 42 (hereinafter referred to as a second gear device 40) and is connected to a brake 44 for stopping the rotation of the first intermediate shaft 34, and the output side of the clutch 30 is connected to the first side. The first sun gear 48 of the first gear device 36 is inserted through the second intermediate shaft 46 that is inserted through the intermediate shaft 34.
And the second sun gear 52 of the second gear device 40,
The clutch 32 is the first ring gear 52 of the first gear device 36.
And a brake 54 for stopping the rotation of the ring gear 52. The first gear device 36 rotatably supports the first sun gear 48, the first pinion gear 56 meshing with the sun gear 48, the pinion gear 56, and is rotatable by itself.
The carrier 38 includes the first ring gear 52 that meshes with the first pinion gear 56, and the second gear device rotates the second sun gear 50, the second pinion gear 58 that meshes with the sun gear 50, and the pinion gear 58. The second carrier 60 includes a second carrier 60 that is freely supported and is rotatable, and a second ring gear 42 that meshes with the second pinion gear 58. The second carrier 6
0 is connected to an output shaft 62, and an output gear 64 is arranged on the output shaft 62. The output gear 62 is meshed with a driven gear 68 provided at the right end of an intermediate transmission shaft 66 arranged substantially parallel to the input shaft 26 via an idler 70, and the intermediate transmission shaft 66 is The left end of is connected to a gear 78 that meshes with a final reduction gear 76 connected to a drive axle 74 via a differential gear unit 72.

As is apparent from FIG. 1, the transmission casing 22 includes the torque converter 12 to the output gear 64,
The intermediate transmission shaft 66, the differential gear unit 72, etc. are included.

Each of the clutches and brakes is provided with an engaging piston device or a servo device, and is engaged and released by supplying and discharging hydraulic pressure. Then, the hydraulic pressure is selectively supplied to each clutch and brake by a hydraulic control device (not shown), and a combination of the operation of each clutch and brake achieves four forward gears and one reverse gear. . Table 1 shows the relationship between the operation of each clutch and brake and the status of the gear stage. In the table, "○" indicates engagement of the clutch or brake, and "-" indicates their release. Shows. Further, the gear ratios of the respective shift stages in the table are the same as those of the first gear device 36 and the second gear device 40 described above.
The case where the tooth number ratio between each ring gear and each sun gear is about 2 to 1 is shown.

In the above structure, when the brake 44 and the clutch 30 are engaged, the rotation of the second ring gear 42 is stopped to become a reaction force element, and the driving force from the drive shaft 10 causes the torque converter 12, the input shaft 26, the clutch 30, and the second Intermediate shaft 46
Is transmitted to the second sun gear 50 via the second pinion gear 58, the second carrier 60, the output shaft 62, the intermediate transmission shaft 66, and the final reduction gear 76, and is transmitted to the drive axle 74. Obviously, the first speed is achieved.

Next, when the brake 44 is released and the brake 54 is engaged while the engagement state of the clutch 30 is maintained, the rotation of the first ring gear 52 is stopped and the reaction element becomes the second force.
Intermediate shaft 46, first sun gear 48, first pinion gear 3
8, the driving force transmitted to the second ring gear 42 via the first intermediate shaft 34 and the second sun gear 5 via the second intermediate shaft 46.
The combined driving force with the driving force transmitted to 0 is transmitted to the output gear via the second carrier 60 and the output shaft 62, and the second speed is achieved.

Next, when the brake 54 is released and the clutch 28 is engaged while the engagement state of the clutch 30 is maintained, the second sun gear 50 and the second ring gear 42 rotate integrally, so that the second gear device. The entire 40 rotates integrally, and the third speed is achieved in which the input shaft 26 and the output gear 64 have the same rotation speed.

Further, when the clutch 30 is released and the brake 54 is engaged while the engagement state of the clutch 28 is maintained, the rotation of the first ring gear 52 is stopped and becomes a reaction force element, and the first intermediate shaft 34 and the first carrier 38. , First sun gear 48, second
The combined driving force of the driving force transmitted to the second sun gear 50 via the intermediate shaft 46 and the driving force transmitted to the second ring gear 42 via the first intermediate shaft 34 is the second carrier 60,
The fourth speed of overdrive is achieved in which the rotation speed of the output gear 64 is transmitted to the output gear 64 via the output shaft 62 so that the rotation speed of the output gear 64 is faster than the rotation speed of the input shaft 26. Next, Clutch 2
8 and the brake 54 are disengaged and the clutch 32 and the brake 44 are engaged, the first carrier 38 and the second ring gear 42 serve as reaction force elements, and the driving force becomes the first ring gear 52, the first pinion gear 56, It is transmitted to the output shaft 62 and the output gear 64 via the first sun gear 48, the second sun gear 50, the second pinion gear 58, and the second carrier 60, and the reverse gear stage is achieved.

According to the above configuration, the gear shift from the first speed to the second speed, to which a large driving force is transmitted, is achieved only by releasing the brake 44 and engaging the brake 54 while maintaining the engaged state of the clutch 30. That is, since the first ring gear 52 need only be fixed relative to the transmission casing 22, it is possible to easily achieve gear shifting without gear shifting shock without complicated hydraulic control.

Further, according to the above configuration, since the first carrier 38 and the second ring gear 42 are simply connected by the hollow first intermediate shaft 34, the clutch is arranged on the outer side in the radial direction of the second gear device 40. There is no need, and it is possible to reduce the outer diameter of the transmission.

[Brief description of drawings]

FIG. 1 is a skeleton diagram showing a schematic structure of an embodiment of the present invention. 10 ... Drive shaft, 12 ... Torque converter, 26 ...
Input shaft, 28, 30, 32 ... Clutch, 36 ... 1st
Simple planetary gear unit, 40 ... Second simple planetary gear unit, 4
4, 54 ... Brake, 64 ... Output gear, 66 ... Intermediate transmission shaft, 68 ... Driven gear, 74 ... Driving axle

Claims (1)

[Claims] A first sun gear, a first pinion gear meshing with the first sun gear, and a first pinion gear rotatably supported and capable of rotating itself. A carrier, a first simple planetary gear device including a first ring gear that meshes with the first pinion gear, a second sun gear, a second pinion gear that meshes with the second sun gear, and a second pinion gear that rotatably supports the gear itself. A second rotatable carrier and a second ring gear that meshes with the second pinion gear
A simple planetary gear device, a first connecting shaft that connects the first sun gear and the second sun gear, a second connecting shaft that connects the first carrier and the second ring gear, and the second
An output shaft connected to the carrier for transmitting a driving force to a drive axle of a vehicle, a first clutch for connecting and disconnecting the input shaft and the first ring gear, and a connection between the input shaft and the first connecting shaft A second clutch for connecting and disconnecting, and a third clutch for connecting and disconnecting the input shaft and the second connecting shaft,
A first brake for stopping the rotation of the first ring gear and a second brake for stopping the rotation of the second connecting shaft are provided, and by selectively operating the clutches and brakes, A transmission for a vehicle, characterized in that it is configured to achieve four forward gears and one reverse gear.