JPS60125444A - Gear transmission - Google Patents

Abstract

PURPOSE:To reduce the axial length, weight and cost of a gear transmission, by using two simple planetary gear sets, two clutches and three brakes to attain four forward stages and one backward stage. CONSTITUTION:The output shaft 2 of an engine 1 is coupled to the pump 4 of a torque converter 3. A turbine 5 is coupled to the input shaft 30 of a gear transmission 6 comprising two simple planet gear sets 10, 20, a first and a second clutches 41, 42, and a first, a second and a third brakes 51, 52, 53. The clutches 41, 42 are of a conventional multiple friction plate type. The first brake 51 is also of a multiple friction plate type. The second and the third brakes 52, 53 are of a conventional band type. These clutches and brakes are operated as shown in the table, to attain four forward stages and one backward stage.

Description

DETAILED DESCRIPTION OF THE INVENTION [Technical Field] The present invention relates to a gear transmission with four forward speeds and one reverse speed, which is suitable as a gear transmission for an automatic transmission of a vehicle such as an automobile.

[Prior art]

Conventionally, in a gear transmission of an automatic transmission using a hydraulic torque converter, the general method for configuring 4 forward speeds and 1 reverse speed is to use two simple planetary gear sets that ensure 3 forward speeds and 1 reverse speed. Furthermore, one set of simple planetary gear sets is added, and these three sets of simple planetary gear sets are arranged in series in the direction of the power transmission axis.

However, when using this conventional general configuration method, the increase in the number of simple planetary gear sets and the accompanying increase in control elements such as clutch devices and brake devices directly leads to the axial extension of the gear transmission, resulting in a gear shift This has the disadvantage of increasing the cost and weight of the device.

Furthermore, as a result of the longer shaft length of the gear transmission, it has become difficult to install the automatic transmission in a popular vehicle with a narrow mounting space.

This difficulty is particularly noticeable in front-engine, front-drive (FF) vehicles in which the engine is installed horizontally.

[Purpose of the invention]

Therefore, an object of the present invention is to obtain a gear stage of 4 forward stages and 1 reverse stage without changing the two sets of simple planetary gear sets required to obtain the conventional gear stage of 3 forward stages and 1 reverse stage. The aim is to make the shaft length of the gear transmission as short as possible by devising the connection method of each gear and the control of the clutch device and the brake device.

[Structure of the invention]

The configuration of the gear transmission of the present invention that achieves this objective will be described next.

First, the gear transmission of the present invention has an input shaft, an intermediate shaft, and an output shaft, and each of these shafts is arranged concentrically and rotatably supported by a transmission case.

In order to connect these respective shafts, two simple planetary gear sets, first and second, two clutch devices, first and second, and three brake devices, first to third. is provided.

The first and second simple planetary gear centers each include a pinion that is rotatably supported by a carrier and is meshed between a sun gear and a ring gear.

“And the ring gear of the second simple planetary gear set is provided with a first brake device between it and the transmission case, and both sun gears of the first and second simple planetary gear centers are coupled to the intermediate shaft, and the ring gear of the second simple planetary gear set is connected to the intermediate shaft. is connected to the input shaft via a first clutch device and also has a second brake device between it and the transmission case, and the carrier of the first simple planetary gear set is connected to the input shaft via the second clutch device. The ring gear of the first simple planetary gear set and the carrier of the second simple planetary gear set are coupled to the output shaft.

Then, by selectively operating the first and second clutch devices and the first to third brake devices described above, four forward speeds and one reverse speed are obtained.

〔Effect of the invention〕

As described above, the gear transmission device of the present invention includes two simple planetary gear sets, two clutch devices, and three
This system achieves four forward speeds and one reverse speed with two brake devices, and the number of simple planetary gear sets is two, the same as the conventional three forward speeds and one reverse speed, so the shaft length of the gear transmission is can be made comparable to the conventional case of 3 forward stages and 1 reverse stage, and can be made shorter than the axial length in the case of 4 forward stages and 1 reverse stage in the conventional general construction method.

As a result, the cost increase and weight increase of the gear transmission can be prevented, and the gear transmission can be easily installed even in a popular car with a narrow mounting space.

〔Example〕

Embodiments of the present invention will be described below based on the drawings.

The figure shows an embodiment of the invention. Note that this embodiment shows the case of an FF system in which the engine is placed horizontally.

In the figure, ■ indicates an engine, 3 indicates a hydraulic torque converter, and 6 indicates a gear transmission. The hydraulic torque converter 3 consists of a pump 4, a turbine 5, and a stator 8. The output shaft 2 is connected to a pump 4, and the turbine 5 is connected to an input shaft 30 of a gear transmission 6. As a result, the rotational torque of the engine 1 is increased by the hydraulic torque converter 3 and taken out to the input shaft 30. Note that the stator 8 is attached to the transmission case 7 via a one-way clutch 9.

In addition to the above-mentioned human power shaft 30, the gear transmission 6 has an intermediate shaft 31 and an output shaft 32 concentrically arranged, and is rotatably supported by the transmission case 7.

The three shafts 30, 31, and 32 are arranged in a partially fitted state, and are arranged in this order from the center: the input shaft 30, the intermediate shaft 31, and the output shaft 32.

The gear transmission 6 also includes two simple planetary gear sets 10.20, two clutch devices 41.42, first and second, and three brake devices 51.52, first to third. .53. The two clutch devices 41, 42 are constructed of the well-known friction multi-plate type. Further, the first brake device 51 is also configured in a friction multi-plate type.

Note that the second brake device 52 and the third brake device 53 are configured in the well-known brake band format.

The first clutch device 41 of the two clutch devices is
It is arranged at the rear position (right position in the figure) of the simple planetary gear set 10-20 of the set, and the second clutch device i! 42 is arranged at the front position (left position in the figure).

The first simple planetary gear set 10 and the second simple planetary gear cent 20 each have a sun gear 1.
1.21, a binion 13.23 rotatably supported on a carrier 12.22, and a ring gear 14.24, and as is well known, there is a Binions 13 and 23 are meshed together.

This first and second simple planetary gear set 1
0.20 gears, the connection relationship with the input shaft 30, intermediate shaft 31, and output shaft 32, and the two clutch devices 41 and 42, the first and second, and the three brakes, the first to the third. Device 5
The arrangement relationship of 1.52.53 is as follows.

First, the first simple planetary gear set lO and the second
Simple planetary gear cent 20, both sun gears 11
21 is connected to an intermediate shaft 31, and this intermediate shaft 31 is connected to the input shaft 30 via a first clutch device 41, and a second brake device is connected between it and the transmission case 7. 52 are provided.

Next, the carrier 12 of the first simple planetary gear set IO is connected to the input shaft 3 via the second clutch device 42.
0, and a third brake device 53 is provided between the transmission case 7 and the transmission case 7.

Furthermore, the ring gear 14 of the first simple planetary gear set 10 and the second simple planetary gear L
Twenty carriers 22 are coupled to an output shaft 32 . Note that a first brake device 51 is provided between the ring gear 24 of the second simple planetary gear set 20 and the transmission case 7.

An output gear 61 is attached to the output shaft 32 of the gear transmission 6, and this output gear 61 meshes with a transmission gear 63 attached to one end of the transmission shaft 62. Transmission shaft 62
An output gear 64 attached to the other end meshes with a final reduction gear 71 of a known final reduction gear 70. An axle shaft 80.80 is taken out from the final reduction gear 70, and a front wheel (not shown) is attached to this axle shaft 80.80.

The operation of the embodiment described above will now be described.

The output rotation of the engine 1 is increased in torque by the hydraulic torque converter 3, and is transmitted to the input shaft 30 of the gear transmission 6, where the gear transmission 6 performs a shift of four forward speeds and one reverse speed. It was taken out at 32. This output shaft 32
The drive rotation taken out is transmitted to the transmission gear 63 by the output key 1.61, and the transmission device 60
is transmitted to the output gear 64 of. The output gear 64 rotates the final reduction gear 71 of the final reduction fi 70 to rotate the front wheels (not shown) via the axle shafts 80, 80.

The gear transmission device 6 performs four forward speeds and one reverse speed shift by controlling the control elements of the two clutch devices 41, 42 and the three brake devices 51, 52, 53 as shown in Table 1. obtained by being selectively activated. In Table 1, each control element is indicated by the reference symbol attached to the figure, the operating state of each control element is indicated by a "0" mark, and the non-operating state is indicated by no mark. In addition, the gear ratio of each gear in the same table is the first simple planetary gear set 10.
The number of teeth of the sun gear 11 is 28, the number of teeth of the pinion 13 is 18, the number of teeth of the ring gear 14 is 64, and the number of teeth of the sun gear 21 of the second simple planetary gear set 20 is 3.
0, the pinion 23 has 12 teeth, and the ring gear 24 has 54 teeth.

Table 1 Next, the operation of each gear of the gear transmission 6 will be explained based on the operating state of each control element described above.

(First Speed) The first speed is achieved by activating the first clutch device 41 and the first brake device 51. By activating the first clutch device 41, the input shaft 30
and the intermediate shaft 31 are in a power connected state, and 300 rotations of the input shaft are transmitted to the sun gear 21 of the second simple planetary gear set 20 coupled to the intermediate shaft 31. On the other hand, due to the operation of the first brake device 51, the ring gear 24 of the second simple planetary gear set 20 is fixed to the transmission case 7.

As a result, the rotation transmitted to the sun gear 21 of the second simple planetary gear set 20 is transmitted to the pinion 23 meshing with the sun gear 21 and rotates the pinion 23, but this pinion 23 rotates the ring gear 24 which is in a fixed state. It revolves along its internal teeth while rotating on its own axis,
This revolution rotation is decelerated and taken out to the output shaft 32 via the carrier 22.

Note that in this first speed state, rotation is also transmitted to the sun gear 11 of the first simple planetary gear set 10, but the rotation is also transmitted to the second clutch device 42 and the third clutch device to which the carrier 12 supporting the pinion 13 is related. Since both brake devices 53 are in an inoperative state and the carrier 12 is in a free state, the pinion 13 freely rotates between both the sun gear 11 and the ring gear 14, and the first gear set by the second simple planetary gear set 20 described above It does not affect the speed gear ratio setting.

(Second Speed) The second speed is achieved by activating the second clutch device 42 and the first brake device 51. By activating the second clutch device 42, the input shaft 30
and the carrier 12 of the first simple planetary gear set 10 are in a power connected state, and the nion 13 supported by the carrier 12 is caused to revolve. On the other hand, due to the operation of the first brake device 51, the ring gear 24 of the second simple planetary gear mechanism 20 is fixed to the transmission case 7, as in the case of the first speed described above.

As a result, the revolution transmitted to the pinion 13 of the first simple planetary gear set 10 is transmitted to the sun gear 11 and ring gear 14 that mesh with the pinion 13, and the rotation of the sun gear 11 and ring gear 14 is transmitted to the intermediate shaft 31, respectively. and the sun gear 21 of the second simple planetary gear set 20 coupled via the output shaft 32
is transmitted to the pinion 23, and since the ring gear 24 of the second simple planetary gear set 20 is in a fixed state, the sun gear 21 and pinion 23 are operated under predetermined conditions in relation to the first simple planetary gear set 10. The rotation of the pinion 23 of the second simple planetary gear set 20 and the rotation of the ring gear 14 of the first simple planetary gear set 10 at this time are decelerated and taken out by the output shaft 32.

(Third Speed) The third speed is achieved by activating the first clutch device 41 and the second clutch device 42. By activating both clutch devices 41 and 42, rotation is transmitted to the intermediate shaft 31 and the carrier 12 of the first simple planetary gear set lO, so that the rotation is transmitted to the intermediate shaft 31 at the first simple planetary gear center lO. Since the rotation of the sun gear 11 and the revolution of the pinion 13 supported by the carrier 12 are the same rotation and integrally rotate, the ring gear 14 meshing with the pinion 13 also rotates integrally, and the rotation is caused by the rotation of the ring gear 14. from output shaft 3
It is taken out in 2.

As a result, in the third speed, the rotation of the input shaft 30 is directly output to the output shaft 32.

In addition, in this third speed state, the second simple planetary gear center 20 also connects the sun gear 21 and the output shaft 32.
Since the pinion 23 supported by the carrier 22 coupled with the pinion 23 rotates together, the ring gear 24 meshing with the pinion 23 also rotates integrally. That is, in this third speed state, the first and second simple planetary gear centers 1O120 rotate integrally. - (Fourth speed) The fourth speed is achieved by activating the second clutch device 42 and the second brake device 52. By activating the second clutch device 42, the input shaft 30
and the carrier 12 of the first simple planetary gear set 10 are in a power connected state, and 300 rotations of the input shaft are transmitted to the carrier 12. On the other hand, the second brake device 52
The intermediate shaft 31 is fixed to the transmission case 7 by the operation of
The sun gear 11 of the first simple planetary gear set 10 coupled to the intermediate shaft 31 is also kept in a fixed state.

As a result, the pinion 13 supported by the carrier 12 rotates around the sun gear 1 which is in a fixed state due to the revolution of the carrier 12.
The rotation of the pinion 13 causes the ring gear 14 to rotate, and the rotation of the ring gear 14 is outputted to the output shaft 32 at increased speed.

In this state, the rotation is also transmitted from the output shaft 32 to the carrier 22 of the second simple planetary gear center 20, but since the first brake device 51 is in an inactive state, the ring gear 24 is free to rotate. state, allowing free rotation of the pinion 23, and does not affect the setting of the fourth speed gear ratio by the first simple planetary gear set ID.

(Reverse) For reverse, the first clutch device 41 and the third brake device 5
This is achieved by activating 3. By activating the first clutch device 41, the input shaft 30 and the intermediate shaft 31 are brought into a power connected state, and the rotation of the input shaft 30 is caused by the sun gear of the first simple planetary gear set 10 coupled to the intermediate shaft 31. 11 will be informed. On the other hand, the third
When the brake device 53 is operated, the carrier 12 supporting the pinion 13 of the first simple planetary gear set 10 is fixed to the transmission case 7, and the pinion 13 is only allowed to rotate on its own axis.

As a result, the rotation transmitted to the sun gear 11 of the first simple planetary gear set 10 is transmitted to the ring gear +14 via the pinion 13 meshing with the sun gear 11, and the rotation of this ring gear 14 is transmitted to the output shaft 32 and the input shaft. 3
The rotation at 0 is reversed, the speed is decelerated, and the rotation is taken out.

Note that even in this state, rotation is being transmitted to the sun gear 21 of the second simple planetary gear set 20, but the first brake device 51 is in the inactive state, as in the case of the fourth gear described above. For some reason, ring gear 24
is in a free rotation state, allowing free rotation of the pinion 23, and does not affect the setting of the reverse gear ratio.

As mentioned above, in the above embodiment, the conventional forward movement 3
Similar to a gear transmission with one reverse gear, it is possible to achieve a gear transmission with four forward gears and one reverse gear with two simple planetary gear sets, so conventionally, three sets of simple planetary gear sets were generally used. The axial length can be significantly shortened compared to a structure in which two are arranged in series.

As a result, compared to the conventional gear transmission with a general configuration,
This has the practical advantage of being able to reduce weight and cost, and it also has the effect that it can be easily installed in popular vehicles with limited mounting space.

Further, in the above-described embodiment, since the overdrive gear ratio is set as the fourth speed, the engine speed can be lowered during high-speed operation, and a quiet running state can be ensured. Furthermore, fuel efficiency can also be improved.

Although specific embodiments illustrating the present invention have been described above, the present invention is not limited to such embodiments.
Various other embodiments are possible within the scope of the invention.

For example, in the above embodiment, the second clutch device 42 is located at the front and the first clutch device 41 is located at the rear.
A second clutch device 42 is arranged behind the clutch device 41.

[Brief explanation of drawings]

The figure is a skeleton diagram showing an embodiment of a gear transmission according to the present invention. Explanation of symbols 7... - Transmission case 10 - - - - First simple planetary gear set 20 - - Second simple planetary gear set 11.21 - - Sun gear 12.22 - - ---Carrier 13.23--Pinion 14.24--Ring gear 30--One-person power shaft 31--Intermediate shaft 32--One output shaft 41- ----First clutch device 42, ----Second clutch device 51, ----First brake device 52, ---Second brake device 53, --- -Third brake device procedural amendment (method) % formula % 2. Name of the invention Gear transmission device 3. Relationship with the person making the amendment Patent applicant address 1 Toyota-cho, Toyota-shi, Aichi Prefecture 471 1982
February 28, 2015 5, Specification subject to amendment 6, contents of amendment as shown in attached sheet

Claims (1)

[Claims] 1. The input shaft, intermediate shaft, and output shaft are arranged concentrically and rotatably supported by the transmission case, and two simple planetary gear sets, the first and second, are installed between each of these shafts. , two clutch devices, first and second, and three brake devices, first to third, and the first and second simple planetary gear sets each have a carrier between the sun gear and the ring gear. The ring gear of the second simple planetary gear set is provided with a first brake device between the transmission case and the first and second simple planetary gear sets. Both sun gears are coupled to an intermediate shaft, the intermediate shaft is coupled to the input shaft via a first clutch device, and is provided with a second brake device between it and the transmission case, and the first simple planetary gear The carrier of the set is connected to the input shaft via a second clutch device and has a third brake device between it and the transmission case,
The ring gear and gear of the first simple planetary gear set and the carrier of the second simple planetary gear center are connected to the output shaft, and four forward speeds and one reverse speed are achieved by selectively operating each of the clutch devices and brake devices. A gear transmission device characterized by: