KR19980047926A - Power train for automatic transmission - Google Patents

Abstract

The object of the present invention is to implement the 5th forward and the 1st forward speed by using three planetary gear sets and six friction elements, while minimizing the power loss by eliminating elements that rotate faster than the input shaft and the output shaft when overdrive. In addition, the present invention provides a power train for an automatic transmission that can achieve miniaturization and light weight of an automatic transmission.

The power train for an automatic transmission according to the present invention is the input shaft to receive the rotational power of the engine from the turbine of the torque converter to rotate the output shaft, the output shaft to adjust the number of outputs for the output according to the number of the rotational power of the input shaft And a single pinion planetary gear set having an element variably connected to the transmission housing and an element fixedly connected to the transfer drive gear, the single pinion planetary gear set for shifting according to the power transmitted from the single pinion planetary gear set. The two planets to shift according to the power transmitted from the double pinion planetary gear set, the single pinion planetary gear set and the double pinion planetary gear set having an element fixedly connected to the element and an element variablely connected to the transmission housing. On the elements of the gear set Another single pinion planetary gear set having a statically connected element and an element variably connected to an element of the double pinion planetary gear set and an element fixedly connected to the transmission housing, wherein the rotational force of the input shaft is converted to a single pinion planetary gear set. Clutch is variably installed between one element of the single-pinion planetary gear set and the input shaft so as to transmit to one element of the element, and variably installed between them to variably connect the elements of the double-pinion planetary gear set and the other single-pinion planetary gear set. Means, each variable variablely installed between the elements and the transmission housing to secure one element of the single pinion planetary gear set and one element of the double pinion planetary gear set and the elements of the three planetary gear sets which are fixedly connected. Is configured to include brake means .

Description

Power train for automatic transmission

The present invention relates to an automatic transmission for a vehicle, and more specifically, by using three simple planetary gear sets, to realize the 5 forward speed and 1 reverse speed to minimize the power loss during the overdrive, and to pursue the miniaturization and light weight of the automatic transmission It relates to a power train for an automatic transmission.

BACKGROUND ART In general, an automatic transmission for a vehicle includes a transmission control unit (TCU) for automatically controlling a transmission ratio according to a change in a traveling speed and an engine load of a vehicle.

The transmission control unit (TCU) inputs any one of three elements of the planetary gear set (i.e., sun gear, planet carrier, and ring gear) by controlling a plurality of friction elements installed in the gear train in an active or non-operating state. Element, and control the other element as reaction force to adjust the number of rotation of the output stage.

A power train capable of outputting a transmission ratio of substantially five forward speeds and one reverse speed has at least two planetary gear sets constituting the peripheral speed and one planet gear set constituting the sub transmission, and operates the planetary gear sets. 6 and 7 friction elements are used.

However, the powertrain for the automatic transmission as described above causes an element that rotates at a higher speed than the input shaft and the output shaft during overdrive, thereby increasing power loss, and causing a limitation in miniaturization and weight reduction of the automatic transmission because a large number of friction elements are used. Let's do it.

Therefore, the present invention was invented to overcome the above limitations, and an object of the present invention is to realize the 5th forward and the 1st forward speed by using three friction blade sets and six friction elements, The present invention provides a power train for an automatic transmission that can minimize power loss by eliminating elements that rotate at a higher speed than the input shaft and the output shaft, and pursue miniaturization and light weight of the automatic transmission.

A specific object of the present invention is to connect the ring gear of the single pinion planetary gear set to the double pinion planetary gear set, and to connect the sun gear of the single pinion planetary gear set and the planetary carrier of the double pinion planetary gear set and other single pinion planetary gear sets. Ring gear fixedly connected, the sun gear of another single pinion planetary gear set is fixed to the transmission housing, and the ring gear of the double pinion planetary gear set and the planetary carrier of the other single pinion planetary gear set are variablely connected. It is to provide a power train for an automatic transmission that minimizes the power loss and prevents the automatic transmission from rotating at a higher speed than the input shaft or the output shaft.

In order to achieve this, the power train for an automatic transmission according to the present invention adjusts the number of rotations of the output to the input according to the number of input shafts that receive rotational power of the engine from the turbine of the torque converter and the number of rotational powers of the input shafts. Single pinion planetary gear set having elements variably connected to the input shaft and transmission housing and elements fixedly connected to the transfer drive gear for outputting the power supply, and the single pinion to shift according to the power transmitted from the single pinion planetary gear set. A double pinion planetary gear set having an element fixedly connected to an element of the planetary gear set and an element variablely connected to the transmission housing, and shifting according to the power transmitted from the single pinion planetary gear set and the double pinion planetary gear set. 2 meteor to remind Another single pinion planetary gear set having an element fixedly connected to the element of the set, an element variablely connected to the element of the double pinion planetary gear set and an element fixedly connected to the transmission housing, the rotational force of the input shaft described above. It is variably installed between the elements of the single pinion planetary gear set and the input shaft so as to be transmitted as an element of the single pinion planetary gear set, and is variable between them to variably connect the elements of the double pinion planetary gear set and the other single pinion planetary gear set. Between the elements and the transmission housing to secure one element of the single pinion planetary gear set and one element of the double pinion planetary gear set and the elements of the three planetary gear sets which are fixedly connected. Variable brake means Include.

The powertrain for the automatic transmission configured as described above enables or disables the clutch means and the brake means to implement 5 forward speeds and 1 reverse speed, and rotates a set of 3 planetary gears in an overdrive state such as 4 forward and 5 forward speeds. Prevents the element from rotating faster than the input or output shaft.

Hereinafter, the preferred configuration and operation of the present invention will be described in more detail with reference to the accompanying drawings.

1 is a first configuration diagram of a power train for an automatic transmission according to the present invention.

2 is a second configuration diagram of a power train for an automatic transmission according to the present invention.

1 is a first configuration diagram of a power train for an automatic transmission according to the present invention, in which the torque of the engine E may be converted into torque in the torque converter T to be transmitted to the input shaft 1 of the gear train. consist of.

In the above, the input shaft 1 receives torque from the turbine of the torque converter T to transmit torque to the single pinion planetary gear set 3 of the gear train, and the single pinion planetary gear set 3 is a single pinion planetary gear. Torque is transmitted to the set (5), and the double pinion planetary gear set (5) forms a clutch hook-up to transfer the torque shifted to another single pinion planetary gear set (7).

The input shaft 1 is connected via first and second clutches C1 and 2 therebetween so as to transfer power to one element or another element and two elements of the double pinion planetary gear set 3. .

That is, the first clutch C1 enables power transmission and interruption between the input shaft 1 and the sun gear 15 of the single pinion planetary gear set 3, and the second clutch C2 is the single input shaft 1 and the single gear. The pinion gear 11 of the pinion planetary gear set 3 is provided to enable power transmission and interruption between the planet carriers 13 provided with the pinion gear 11.

In addition, the planetary carrier 19 on which the ring gear 15 of the double pinion planetary gear set 5 and the pinion gear 17 of the other single pinion planetary gear set 7 is installed is provided so that power transmission and interruption therebetween are possible. 3 is connected to the variable coupling structure by the clutch (C3).

In addition, the ring gear 21 of the single pinion planetary gear set 3 and the sun gear 23 of the double pinion planetary gear set 5 are fixedly coupled by the power transmission member 25 so that they can always be integrally driven and stopped. It is connected by a structure.

The ring gear of the planetary carrier 29 and the other single pinion planetary gear set 7 in which the sun gear 9 of the single pinion planetary gear set 3 and the pinion gear 27 of the double pinion planetary gear set 5 are installed. 31 is always connected in a fixed coupling structure by another power transmission member 33 so that it can be driven and stopped integrally.

The sun gear 35 of the other single-pinion planetary gear set 7 is connected to the transmission housing 37 in a fixed coupling structure so that it can always be stopped.

In addition, when the gear train consisting of the three planetary gear sets (3, 5, 7) connected in a variable and fixed coupling structure as described above to realize the shift, the three planetary gear sets (3, 5, First, second and third brakes B1, 2, 3 are provided between the specific element of 7) and the transmission housing 37.

That is, the first brake B1 is a sun gear 9 of the single pinion planetary gear set 3, a planet carrier 9 of the double pinion planetary gear set 5, and a ring gear of the other single pinion planetary gear set 7. It is variably provided between the other power transmission member 33 and the transmission housing 37 so that the other power transmission member 33 which integrally connects 31 can be stopped and operated as a reaction force element.

The second brake B2 is variably installed between the ring gear 15 and the transmission housing 37 to fix the ring gear 15 of the double pinion planetary gear set 5 to operate as a reaction force element. .

In addition, the third brake B3 is variably installed between the planetary carrier 13 and the transmission housing 37 so that the planetary carrier 13 of the single-pinion planetary gear set 3 can be fixed and operated as a reaction force element. .

Meanwhile, the transfer drive gear 39 formed integrally with the ring gear 21 of the single pinion planetary gear set 3 is gear-coupled with a transfer driven gear (not shown) and shifted to a differential device through a final reduction gear. In the present configuration, such a structure is omitted since a known one can be used, and any structure can be used to realize the object intended by the present invention.

The power train for the automatic transmission of the present invention made as described above comprises three elements of three planetary gear sets 3, 5 and 7 by friction elements (clutch and brake) which are selectively activated or deactivated by the transmission control unit. One element (sun gear, planet carrier, ring gear) is selected as an input element, and the other element is selected as a reaction element, and the transmission ratios of 5 forward speeds and 1 reverse speed will be described.

The transmission control unit activates or deactivates the friction element as shown in [Table 1].

TABLE 1

Friction element operating table for each gear.

When the shift lever (not shown) is selected as the forward D range and the opening amount of the throttle valve is increased, the transmission control unit is hydraulically operated by the first and third clutches C1 and 3 so that the gear train can output the first speed ratio. These friction elements are operated by supplying.

Hereinafter, the first, second and third clutches C1, 2 and 3 and the first, second and third brakes B1, 2 and 3 mean that hydraulic pressure is supplied from the hydraulic control system.

When the first and third clutches C1 and 3 are operated, the ring gear 15 of the double pinion planetary gear set 5 is connected to the planet carrier 19 of the other single pinion planetary gear set 7. The single pinion planetary is different from the planetary carrier 29 of the double pinion planetary gear set 5 in which the input shaft 1 is fixedly connected to the sun gear 9 of the single pinion planetary gear set 3 and the other power transmission member 33. It is connected to the ring gear 31 of the gear set 7.

Therefore, the rotational power of the input shaft 1 is the sun gear 9 of the single pinion planetary gear set 3, the planetary carrier 9 of the double pinion planetary gear set 5, and the other single pinion planetary gear set 7 as the input elements. It is transmitted to the ring gear 31 of the forward rotation thereof.

The rotational power transmitted to the ring gear 31 of the other single-pinion planetary gear set 7 is connected to the planet carrier 19 through the pinion gear 17 with the third clutch C3 by the reaction force of the sun gear 35. It is transmitted to the ring gear 15 of the double pinion planetary gear set 5 with reduced forward rotational power.

The forward rotational power transmitted to the ring gear 15 and the planet carrier 29 of the double pinion planetary gear set 5 is transmitted to the sun gear 23 through the pinion gear 27 and thus the power transmission member 25. It is transmitted to the ring gear 21 of the single-pinion planetary gear set (3) connected fixedly.

At the same time, the forward rotational power transmitted to the sun gear 9 of the single pinion planetary gear set 3 is transmitted to the ring gear 21 through the pinion gear 11.

The forward rotational power transmitted to the ring gear 21 outputs a speed ratio of 1 speed to the transfer drive gear 39 formed integrally thereto.

When the vehicle speed increases in the first speed state, the transmission control unit deactivates the first clutch C1 and operates the second clutch C2 while the third clutch C3 is operated.

By the above-described action, rotational power of the input shaft 1 transmitted to the sun gear 9 of the single-pinion planetary gear set 3 and the other power transmission member 33 fixedly connected thereto is blocked, and the planetary carrier 13 The input shaft 1 is connected to the planet carrier 13 of the single pinion planetary gear set 3 so as to transmit rotational power to the furnace.

Therefore, the rotational power of the input shaft 1 transmitted to the planet carrier 13 is transmitted through the pinion gear 11 of the sun gear 9, the other power transmission member 33, and the ring gear of the other single pinion planetary gear set 7. Delivered to (31) to rotate them forward.

The forward rotational power transmitted to the ring gear 31 is connected to the third clutch C3 in a decelerated state as in the first speed through the pinion gear 17 to the planetary carrier 19 by the reaction force of the sun gear 35. It is transmitted to the ring gear 15 of the double pinion planetary gear set 5 to rotate it forward.

As described above, the forward rotational power is transmitted to the ring gear 15, and the forward rotational power is transmitted to the planet carrier 29 connected to the other power transmission member 33, so that the single pinion planetary gear connected to the power transmission member 25 is transmitted thereto. The forward rotational power is transmitted to the ring gear 21 of the set 3.

At this time, the ring gear 21 is further rotated by the rotation of the pinion gear 11 of the single-pinion planetary gear set 3 to output the speed ratio of 2 speeds to the transfer drive gear 39 formed integrally therewith.

When the vehicle speed increases in the second speed state, the transmission control unit deactivates the third clutch C3 and operates the first clutch C1 while the second clutch C2 is operated.

By the above operation, the sun gear 9 and the planet carrier 13 of the single pinion planetary gear set 1 are connected to the input shaft 1 to receive the rotational power of the input shaft 1 at two places.

Therefore, the single-pinion planetary gear set 3 is locked and transmits the rotational power of the input shaft 1 to the ring gear 21 as it is (shift ratio 1: 1) while transferring the speed ratio of three speeds with the transfer drive gear 39 formed integrally therewith. Will print.

When the vehicle speed increases in the third speed state, the transmission control unit deactivates the first clutch C1 and operates the first brake B1 while the second clutch C2 is operated.

Double fixedly connected to the sun gear 9 and the other power transmission member 33 of the single pinion planetary gear set 3 in the state connected to the planetary carrier 13 of the single pinion planetary gear set 3 by the above-described action. The planetary carrier 29 of the pinion planetary gear set 5 and the ring gear 31 of the other single pinion planetary gear set 7 are fixed to stop the entire other single pinion planetary gear set 7.

Therefore, the rotational power of the input shaft 1 transmitted to the planet carrier 13 of the single-pinion planetary gear set 3 is transmitted to the ring gear 21 while being increased through the pinion gear 11 thereof by the reaction force of the sun gear 9. As a result, the transmission speed of the fourth speed is output to the transfer drive gear 39 integrally formed thereon.

In the four-speed state as described above, the single-pinion planetary gear set 7 is stopped together with the sun gear 35 fixed by the operation of the first brake B1 to rotate faster than the input shaft 1 and the output shaft (not shown). To reduce power loss.

When the vehicle speed increases in the fourth speed state, the transmission control unit deactivates the first brake B1 and operates the second brake B2 while the second clutch C2 is operated.

Since the ring gear 15 of the double pinion planetary gear set 5 acts as a reaction element by the above action, the rotation of the input shaft 1 transmitted to the planet carrier 13 of the single pinion planetary gear set 3 is performed. Power is transmitted to the planet carrier 9 of the double pinion planetary gear set 5 connected to the other power transmission member 33 while rotating the sun gear 9 through the pinion gear 11 to reverse it.

Therefore, the reverse rotational power transmitted to the planet carrier 9 of the double pinion planetary gear set 5 is combined with the forward rotational power transmitted through the pinion gear 11 of the single pinion planetary gear set 3 and its pinion gear 27. It is transmitted to the ring gear 21 of the single-pinion planetary gear set (3) connected to the sun gear (23) and the power transmission member (25) through this to rotate it forward.

Therefore, the forward rotation of the double pinion planetary gear set 5 of the input shaft 1 transmitted to the planet carrier 13 of the single pinion planetary gear set 3 is transmitted to the planet carrier 29 by the reaction force of the ring gear 15. The power is transmitted to the sun gear 23 through the pinion gear 27 thereof, and further rotates it, thereby further rotating the ring gear 21 fixedly connected to the power transmission member 25, thereby forming a transfer drive gear 39 integrally therewith. Will output a gear ratio of five speeds.

In the 5-speed state as described above, the second brake B2 is operated to fix the ring gear 15 of the double-pinion planetary gear set 5 to remove the high-speed rotating element so that the power loss is reduced.

On the other hand, when the reverse R range is selected by the shift lever, the transmission control unit TCU operates the first clutch C1 and the third brake B3.

By the above-described action, since the sun gear 9 of the single-pinion planetary gear set 3 is connected to the input shaft 1 and the planet carrier 13 is fixed and acts as a reaction element, the input shaft transmitted to the sun gear 9 thereof ( The forward rotational power of 1) is transmitted to the ring gear 21 through the pinion gear 11 and reversely rotates, thereby outputting a gear ratio of reverse speed 1 through the transfer drive gear 39 formed integrally therewith.

On the other hand, Figure 2 is a second configuration of the power train for automatic transmission according to the present invention, the first configuration and its overall configuration and operation is the same, so the detailed description thereof will be omitted and only the other parts will be described.

That is, in the first configuration, the first brake B1, which is operated to stop the other single pinion planetary gear set 7 in the forward 4, is connected to the other power transmission member 33 and the transmission fixedly connected to the ring gear 31 thereof. Although variablely installed in the housing 37, in the second configuration, there is only a difference in which the first brake B1 is variably installed between its planetary carrier 19 and the transmission housing 37.

As described above, the power train for the automatic transmission according to the present invention implements 5 forward speeds and 1 reverse speed by operating or deactivating the clutch means and the brake means, and the three planetary gears in the overdrive state such as the forward 4 and 5 speeds. It is possible to minimize power loss by preventing the rotating elements of the set from rotating at a higher speed than the input shaft or the output shaft, and to reduce the size and weight of the automatic transmission by using a small number of friction elements.

Claims (5)

An input shaft that receives rotational power of the engine from the turbine of the torque converter and an element that is variably connected to the input shaft and the transmission housing to adjust and output the output rotation speed according to the number of rotational powers of the input shaft. Single pinion planetary gear set with elements fixedly connected to the transfer drive gear, an element and transmission housing fixedly connected to elements of the single pinion planetary gear set to shift according to the power transmitted from the single pinion planetary gear set. A double pinion planetary gear set having an element variably connected to the element, the element fixedly connected to an element of the two planetary gear set to shift according to the power transmitted from the single pinion planetary gear set and the double pinion planetary gear set. Double Pinion Meteor Another single pinion planetary gear set having an element variably connected to the elements of the set and an element fixedly connected to the transmission housing, a single pinion planetary to transfer the rotational force of the input shaft to one element of the single pinion planetary gear set. Clutch means which are variably installed between the elements of the gear set and the input shaft and variably installed between them so as to variably connect the elements of the double pinion planetary gear set and the other single pinion planetary gear set, the single pinion planetary gear set described above. A power train for an automatic transmission comprising brake means variably installed between the elements and the transmission housing for securing one element and one element of the double pinion planetary gear set and the elements of the three planetary gear sets which are fixedly connected. . The method of claim 1, The clutch means is a first clutch which is installed between the input shaft and the sun gear of the single pinion planetary gear set so as to transmit and block power, and the planetary body of the input shaft and the single pinion planetary gear set so that the single pinion planetary gear set can have two input elements. The second clutch, which is installed so as to transmit and cut off power between the carriers, is installed to enable power transmission and interruption between the ring gears of the double pinion planetary gear set and the planetary carrier of the single pinion planetary gear set. Power train for automatic transmission with 3 clutches. The method of claim 1, The brake means rotates and locks the ring gear of the first brake, double pinion planetary gear set, which is installed between one element of the single pinion planetary gear set and the transmission housing so that the entire other single pinion planetary gear set can be fixed in forward D4. For an automatic transmission comprising a second brake installed between the ring gear and the transmission housing so as to enable rotation, and a third brake installed between the planet carrier and the transmission housing to rotate and fix the planet carrier of the single-pinion planetary gear set. Power train. The method of claim 3, wherein The first brake is provided between a transmission gear for fixing the sun gear of the single pinion planetary gear set, the planetary carrier of the double pinion planetary gear set and the ring gear of the other single pinion planetary gear set and the transmission housing. Power train. The method of claim 3, wherein And a first brake is installed between the planetary carrier of the other single-pinion planetary gear set and the transmission housing.