JPS60125445A - Gear transmission - Google Patents

Abstract

PURPOSE:To attain four forward stages and one backward stages in transmission, by using two simple planetary gear sets to contrive a method of connecting gears and the control of clutches and brakes. 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 two brakes 41, 42 and the third brake 51 are of conventional multiple friction plate types, respectively. 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 the gear transmission system 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 sets of 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 type (FF type) 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, a first intermediate shaft, a second intermediate shaft, and an output shaft, and each of these shafts is arranged concentrically and rotates in the transmission case. Possibly supported.

In order to connect these respective shafts, two simple planetary gear sets, first and second, and first to third
Three clutch devices, and two brake devices, a first and a second brake device, are provided.

The first and second simple planetary gear sets each include a sun gear and a ring gear, and a binion rotatably supported by a carrier is meshed with the sun gear.

The sun gear of the first simple planetary gear set is coupled to the first intermediate shaft, and the first intermediate shaft is connected to the first intermediate shaft.
The ring gear of the first simple planetary gear cent and the carrier of the second simple planetary gear cent are coupled to the second intermediate shaft, and the first A brake device is provided, the second intermediate shaft is connected to the input shaft via a second clutch device, and the second sun gear is connected to the input shaft via a third clutch device and is connected to the transmission case. A first brake device is provided therebetween, and the carrier of the first simple planetary gear set and the ring gear of the second simple planetary gear set are coupled to the output shaft.

By selectively operating each of the first to third clutch devices and the first and second brake devices described above,
4 forward speeds and 1 reverse speed are obtained.

[Results of invention]

As described above, the gear transmission device of the present invention includes two simple planetary gear sets, three clutch devices, and two
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, an increase in cost and weight of the gear transmission can be prevented, and the gear transmission can be easily installed in a popular vehicle with a narrow mounting space without difficulty.

〔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 for engine control.

In the figure, l indicates an engine, 3 indicates a hydraulic torque converter, and 6 indicates a gear transmission. The output shaft 2 is connected to a pump 4, and the pulley 5 is connected to an input shaft 3o 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 input shaft 30, the gear transmission 6 includes a first intermediate shaft 31, a second intermediate shaft 32, and an output shaft 33, which are arranged concentrically and rotatably attached to the transmission case 7. Supported. Note that these four shafts 30, 31, 32, and 33 are arranged in a partially fitted state, and the input shaft 30 is connected from the center side.
, the second intermediate shaft 32, the first intermediate shaft 31, and the output shaft 33 are arranged in this order.

This gear transmission 6 also includes two simple planetary gear sets 10.20, three clutch devices 41, 42, 43 (first to third), and first and second 211! i
It has a brake device 51.52 of t. The three clutch devices 41, 42, and 43 are the well-known mechanisms! The first brake device 51 is also configured in a multi-disc type.The second brake device 52 is configured in a well-known brake band type.

Of the three clutch devices, the first clutch device 41 and the second clutch device 42 are arranged at the front position (left position in the figure) of the two sets of simple planetary gear sets 1O120, and the third clutch device 43 is arranged at the rear position (right position in the figure). Further, the first clutch device 41 and the second clutch device 42 disposed at the front position are arranged side by side in the axial direction.

The first simple planetary gear set 10 and the second simple planetary gear cent 20 each have a sun gear 1.
1.21, a pinion 13.23 rotatably supported on a carrier 12.22, and a ring gear 14.24.As is well known, the sun gear 11.21 and the ring gear 14
．． 24, and pinions 13 and 23 are meshed with each other.

Each gear of the first and second simple planetary gear set 1O120, the input shaft 30, and the first intermediate shaft 31
, the connection relationship with the second intermediate shaft 32 and the output shaft 33, and the arrangement of the three first to third clutch devices 41, 42, 43 and the two first and second brake devices 51, 52. The relationship is as follows.

First, the sun gear 11 of the first simple planetary gear set 10 is coupled to a first intermediate shaft 31, and this intermediate shaft 31 connects to the input shaft 3 via a first clutch device 41.
Connected to 0.

Next, the ring gear 14 of the first simple planetary gear set IO and the carrier 22 of the second simple planetary gear set 20 are coupled to the second intermediate shaft 32, and the first brake device is connected between them and the transmission case 7. The second intermediate shaft 32 is connected to the second clutch device 4.
It is connected to the input shaft 30 via 2.

Furthermore, the sun gear 21 of the second simple planetary gear set 20 is connected to the input shaft 30 via a third clutch device 43.
is connected to. The carrier 12 of the first simple planetary gear set 10 and the ring gear 24 of the second simple planetary gear set 2o are coupled to an output shaft 33.

An output gear 61 is attached to the output shaft 33 of the gear transmission 6, and this output gear 61 meshes with a transmission gear 63 attached to one end of a transmission shaft 62. Transmission shaft 6
An output gear 64 attached to the other end of 2 meshes with a final reduction gear 71 of a known final reduction gear 7o. The axle shaft 80.80 is taken out from the final reduction gear 70,
A front wheel (not shown) is attached to the axle shafts 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. The gear transmission 6 changes the speed to four forward speeds and one reverse speed. taken out. The drive rotation taken out to the output shaft 32 is transferred to the transmission gear 6 by the output gear 61.
3 and is transmitted to the output gear 64 of the transmission device 60 via the transmission shaft 62. The output gear 64 is the largest gear reducer 70
by rotating the final reduction gear 71 of the axle shaft 80.8.
The front wheel (not shown) is rotated through the

The gear transmission device 6 performs four forward speeds and one reverse speed shift by controlling each control element of the three clutch devices 41, 42, 43 and the two brake devices 51, 52 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 ratio.
The number of teeth of the sun gear 11 of the second simple planetary gear set 20 is 30, the number of teeth of the pinion 13 is 12, the number of teeth of the ring gear 14 is 54, the number of teeth of the sun gear 21 of the second simple planetary gear set 20 is 28, and the number of teeth of the pinion 23 is 54. 18 pieces, 24 ring gears
The case where the number of teeth is 64 is shown.

Table 1 Next, the operation of each gear stage 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 W41, the input shaft 30
and the first intermediate shaft 31 are in a power connected state, and the input shaft 3
0 rotation is transmitted to the sun gear 11 of the first simple planetary gear set 10 coupled to the first intermediate shaft 31. On the other hand, due to the operation of the first brake device 51, the first
simple planetary gear cent 10 ring gear 14
is fixed to the transmission case 7.

As a result, the first simple planetary system node IO
The rotation transmitted to the sun gear 11 is transmitted to the pinion 13 meshing with the sun gear 11 and rotates the pinion 13, but this pinion 13 rotates along the internal teeth of the ring gear 14 which is in a fixed state. This revolution is decelerated and taken out to the output shaft 33 via the carrier 12.

Note that in this first speed state, the carrier 22 of the second simple planetary gear set 20 is connected to the transmission case 7.
is in a fixed state, and the rotation of the output shaft 33 is transmitted to the ring gear 24, but the third clutch device 43 and the second brake device 52 to which the sun gear 21 is related are in an inactive state, and the sun gear 21 is free. Since the sun gear 21 is in a normal rotational state, the sun gear 21 rotates freely and does not affect the setting of the first speed gear ratio by the first simple planetary gear set IO described above.

(Second Speed) The second speed is achieved by activating the first clutch device 41 and the second brake device 52. By activating the first clutch device 41, the input shaft 30 and the first intermediate shaft 3
1 is in a power connected state, and the rotation of the input shaft 30 is transmitted to the sun gear 11 of the first simple planetary gear set 10 coupled to the first intermediate shaft 31. On the other hand, due to the operation of the second brake device 52, the sun gear 21 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 11 of the first simple planetary gear set 10 is transmitted to the pinion 13 meshing with the sun gear 11, and the rotation of this pinion 13 is transmitted to the second gear connected via the carrier 12. The information is transmitted to the ring gear 24 of the simple planetary gear set 20, and the sun gear 21 of the second simple planetary gear set 20 is in a fixed state, so that the pinion 22 and the ring gear 24 are connected to the first simple planetary gear set (1).
The ring gear 2 of the second simple planetary gear cent 20 at this time rotates under predetermined conditions in relation to
4 rotations and 1st simple planetary gear cent l
The revolution of the carrier 12 of O is decelerated and taken out by the output shaft 33.

(Third series) 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 first intermediate shaft 31 and the second intermediate shaft 32. Therefore, in the first simple planetary gear set 10, the first intermediate shaft Since the rotation of the sun gear 11 coupled to the shaft 31 and the rotation of the ring gear 14 coupled to the second intermediate shaft 32 rotate at the same rotation, the pinion C meshing with both 11 and 14 also rotates integrally. The rotation is extracted from the carrier 12 to the output shaft 33.

As a result, in the third speed, the rotation of the input shaft 30 is directly output to the output shaft 33.

In addition, in this third speed state, the second simple planetary gear set 20 also rotates at the same speed as the carrier 22 coupled to the second intermediate shaft 32 and the ring gear 24 coupled to the output shaft 33, so that the sun gear 21 also rotates integrally. . That is, in this third speed state, the first and second simple planetary gear sets 10.20 rotate as a whole.

(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 second intermediate shaft 32 are in a power connected state, and the input shaft 3
0 rotation is transmitted to the carrier 22 of the second simple planetary gearbox 1-20, which is connected to the second intermediate shaft 32.

On the other hand, by activating the second brake device 52, the sun gear 21 of the second simple planetary gear safety 1-20 is fixed.

As a result, the pinion 23 supported by the carrier 22 rotates around the sun gear 2 which is in a fixed state due to the revolution of the carrier 22.
The ring gear 24 is rotated by the rotation of the pinion 23, and the rotation of the ring gear 24 is accelerated and taken out by the output shaft 33.

In this state, the rotation of the output shaft 33 is being transmitted to the carrier 12 of the first simple planetary gear set 10, and 300 rotations of the input shaft are being transmitted to the ring gear 14. is in a non-operating state and the sun gear 11 is in a free rotation state,
This does not affect the setting of the fourth speed gear ratio by the second simple planetary gear set 20.

(Reverse) For reverse, the third clutch device 43 and the first brake device'f
? , 51 are activated. Third
By activating the clutch device 43, the rotation of the input shaft 30 is controlled by the second simple planetary gear set 20.
The information is transmitted to the sun gear 21. On the other hand, the carrier 22 of the second simple planetary gear set 20 is fixed to the transmission case 7 by the operation of the first brake device 51, and the pinion 22 is only allowed to rotate on its own axis.

As a result, the rotation transmitted to the sun gear 21 of the second simple planetary gear cent 20 is transmitted to the ring gear 24 via the pinion 23 meshing with the sun gear 21, and the rotation of this ring gear 24 is transmitted to the output shaft 33 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, the ring gear 14 of the first simple planetary gear set 10 is in a fixed state, and the output rotation is transmitted to the carrier 12.
As in the case of high speed, the first clutch device 41 is in an inactive state and the sun gear 11 of the first simple planetary gear set 10 is in a free rotation state, so it 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 the cylindrical parts 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.

In addition, in the embodiment described above, since the overdrive gear ratio is set as the fourth gear, the engine speed can be lowered during high-speed operation, and a quiet running state can be maintained at U (11). In addition, fuel efficiency can 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 may be provided within the scope of the present invention.
:It's a terrible thing.

For example, in the embodiment described in °C, the first and second
The explanation has been made of a configuration in which the clutch devices 41 and 42 are arranged at the rear, and the third clutch device 43 is arranged at the rear.
It is also possible to adopt a configuration in which the hydraulic torque converter 3 is arranged on the right side in the figure, in which the clutch devices 41 and 42 are arranged.

[Brief explanation of the drawing]

The figure is a skeleton diagram showing an embodiment of a gear transmission according to the present invention. Explanation of symbols 7-----1 Transmission case 10---11 First simple planetary gear set 20-----1 Second simple planetary gear set 1
1.21--Sun gear 12.22--Carrier 13.23--Pinion 14.24--Ring gear 30--Human power shaft 31--First intermediate Shaft 32--Second intermediate shaft 33--Output shaft 41--First clutch device 42--Second clutch device 43--First 3. Clutch device 51-1---First brake device 52.--1--Second brake device procedure amendment (method) 1. Display of case 1982 Patent Application No. 231829 2 Name of invention Gear transmission 3 Person making amendment Relationship to case Patent applicant address 1 Toyota-cho, Toyota City, Aichi Prefecture 471 1988
February 28, 2015 5, Specification subject to amendment 6, contents of amendment as shown in attached sheet

Claims (1)

[Claims] ■-9 An input shaft, a first intermediate shaft, a second intermediate shaft, and an output shaft are arranged concentrically and rotatably supported by the transmission case, and between each of these shafts, the first and a second two sets of simple planetary gear sets, three clutch devices, first to third, and two brake devices, first and second, and the first and second simple planetary gear sets. The sun gear of the first simple planetary gear set is connected to the first intermediate shaft, and the sun gear of the first simple planetary gear set is connected to the first intermediate shaft. The shaft is connected to the input shaft via a first clutch device, and the ring gear of the first simple planetary gear set and the carrier of the second simple planetary gear set are connected to the second intermediate shaft and connected to the transmission case. the second intermediate shaft is connected to the input shaft via a second clutch device, the second sun gear is connected to the input shaft via a third clutch device, and the second intermediate shaft is connected to the input shaft via a third clutch device, and the second intermediate shaft is connected to the input shaft via a third clutch device, and the second intermediate shaft is connected to the input shaft via a third clutch device. A first brake device is provided between the machine case and the carrier of the first simple planetary gear set and the ring gear of the second simple planetary gear center are coupled to the output shaft, and the clutch device and the brake device are selectively connected to each other. A gear transmission device characterized in that, through operation, four forward speeds and one reverse speed are obtained.