KR19980046723A - Power train for automatic transmission - Google Patents

Abstract

In the powertrain for automatic transmission, a compound planetary gear system consisting of two double pinion planetary gear sets consisting of a fixed coupling structure and a variable coupling structure is used to reduce friction loss of a friction element that does not operate in clutch hook-up at each shift stage. In order to minimize, a double pinion planetary gear set for adjusting the rotational speed of the output to the input according to the number of elements transmitted to the rotational power of the engine from the turbine of the torque converter, the rotational power of the input shaft, the Another double pinion planetary gear set with elements fixedly connected to the elements of the double pinion planetary gear set and with elements fixed to the transmission housing to shift according to the power transmitted from the double pinion planetary gear set. Double the rotational power of the input shaft Clutch means for acting either as transmission to one of the three elements of the pinion planetary gear set and another double pinion planetary gear set and to two or more elements, one element and the double pinion of the double pinion planetary gear set described above. Another clutch means for selectively connecting one element of the planetary gear set, wherein the clutch means causes one planet element to act as an input element and at least two elements act as input elements. And a brake means installed between the element and the transmission housing to select the element of the gear sets as a reaction force element.

Description

Power train for automatic transmission

The present invention relates to an automatic transmission for a vehicle, and more particularly, for an automatic transmission in which two or three elements of two double pinion planetary gear sets are variably connected to minimize friction loss of a friction element that does not operate. It's about the power train.

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

The transmission control unit controls a plurality of friction elements installed in the gear train in an active or non-operating state so that any one of three elements of the planetary gear set (ie, input element, reaction force element, and output element) is input. And, by controlling the other element to the reaction element to adjust the number of rotation of the output stage.

At least five friction elements should be used to design a gear train that can output a gear ratio of four forward speeds and one reverse speed.

Among these friction elements, the rotation radius of the friction element used as the clutch means must be smaller than the rotation radius of the output element in order for the clutch means to be connected to the input shaft, and there is a structural constraint to be smaller than the rotation radius of the reaction force element.

In general, a compound planetary gear device has a direct structure in which at least two different elements can be used in common. This is because in the case of the four-speed automatic transmission, the planetary gear unit has four independent speeds, but the six planetary gear units using two simple planetary gear units having three independent speeds cannot obtain six independent speeds. to be.

In addition, the planetary gear device of the automatic transmission device for a vehicle is generally used in the type of planetary gear device of Lavigne type, Simpson type and two-simple type.

In order to be used as a transmission means in a vehicle, the compound planetary gear device has a structure in which the rib type shares a ring gear and connects the planetary carrier, and the Simpson type has a structure in which the planet carrier and the ring gear are connected while sharing the sun gear. The two-simple type has a structure in which a planetary carrier and a ring gear are interconnected.

Therefore, in the above-described compound planetary gear device, a friction element that does not operate at any shift stage and does not affect the shift in realizing a shift is generated, and this friction element causes friction between its drive shaft and the driven side to reduce friction loss. Will result.

Therefore, the present invention has been invented to solve the above problems, an object of the present invention is to provide a power train for an automatic transmission that minimizes the frictional loss of the friction elements that do not operate in the clutch hook-up for each shift stage. It is.

A specific object of the present invention is to securely connect one element of the double pinion planetary gear set and another element of the double pinion planetary gear set, and one element of the double pinion planetary gear set and another element of the other double pinion planetary gear set. The variable connection provides a power train for an automatic transmission that minimizes frictional losses of friction elements.

In order to realize this, the power train for an automatic transmission according to the present invention is the number of rotations of the output to the input in accordance with the number of the input shaft rotates by receiving the rotational power of the engine from the turbine of the torque converter, the rotational power of the input shaft Double pinion planetary gear set for regulating the element, which is fixedly connected to the element of this double pinion planetary gear set, and the element is variably connected to the transmission housing Other double pinion planetary gear sets for shifting accordingly, the rotational power of the input shaft being transmitted to one of the three elements of the double pinion planetary gear set and the other double pinion planetary gear sets described above, and to two or more elements. Clutch means for any one action, the double pinion described above Another clutch means for selectively connecting one element of the set of gears and one element of the double pinion planetary gear set, said element of the planetary gear set acting as an input element by means of said clutch means and two or more elements serving as input elements Brake means for selecting the element of the planetary gear sets as a reaction element in any one of the acting.

The sun gear of the other double pinion planetary gear set is fixedly installed in the transmission housing.

The clutch means is installed between the input shaft and the sun gear of the double pinion planetary gear set to clamp the power transmission, and the clutch means is installed between the input shaft and the planetary carrier of the other double pinion planetary gear set to interrupt the power transmission. Two clutch means.

The clutch means also includes a third clutch means installed between one element of the double pinion planetary gear set and one element of the other double pinion planetary gear set to interrupt power transmission.

The third clutch means is provided between the planetary carrier of the double pinion planetary gear set and the ring gear of the other double pinion planetary gear set to interrupt power transmission between the planetary carrier of the double pinion planetary gear set and the ring gear of the other double pinion planetary gear set. Is installed on.

The third clutch means is provided between the ring gear of the double pinion planetary gear set and the planetary carrier of the other double pinion planetary gear set to interrupt power transmission between the ring gear of the double pinion planetary gear set and the planet carrier of the other double pinion planetary gear set. Is installed on.

The clutch means comprises a fourth clutch means installed between the ring gear and the planet carrier of the other double pinion planetary gear set to interrupt power transmission between the ring gear and the planet carrier of the other double pinion planetary gear set.

The brake means is provided between the sun gear of the double pinion planetary gear set and the transmission housing to fix the sun gear of the double pinion planetary gear set, one of the elements of the two double pinion planetary gear sets and the transmission housing. And a second brake means provided between the second brake means to fix the element to output the reverse speed ratio to the output element.

The second brake means is provided between the sun gear and the planet carrier of the other double pinion planetary gear set to fix the entire other double pinion planetary gear set.

The second brake means is provided between the ring gear of the double pinion planetary gear set and the transmission housing to fix the ring gear of the double pinion planetary gear set.

The ring gear of the double pinion planetary gear set and the planet carrier of the other double pinion planetary gear set are connected in a fixed coupling structure by a power transmission member.

The planetary carrier of the double pinion planetary gear set and the ring gear of the other double pinion planetary gear set are connected in a fixed coupling structure by a power transmission member.

The planetary carrier of the double pinion planetary gear set described above and the ring gear of the other double pinion planetary gear set are connected in a variable engagement structure by clutch means.

The ring gear and the planet carrier of the other double pinion planetary gear set described above are connected in a variable engagement structure by clutch means.

The ring gear of the double pinion planetary gear set described above and the planet carrier of the other double pinion planetary gear set are connected in a variable engagement structure by clutch means.

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;

3 is a third 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 rotational power of the engine E is torque converted from the torque converter T and transmitted to the input shaft 1 of the transmission portion. Have

In the above, the input shaft 1 receives torque from the turbine of the torque converter T to transmit torque to the double pinion planetary gear set 3, and the double pinion planetary gear set 3 is another double pinion planetary gear set ( 5) Clutch hook up to transmit power.

That is, a first clutch means C1 is provided between the input shaft 1 and the sun gear 7 of the double pinion planetary gear set 3, and the first clutch means C1 rotates the input shaft 1. It is made of a structure that can transmit or block the power to the sun gear (7).

And second clutch means between the planetary carrier 11 of the planetary gear set 3 in which the input shaft 1 and the pinion gear 9 are installed so that the double pinion planetary gear set 3 can have two input elements. (C2) is provided, the second clutch means (C2) is made of a structure that can transmit or block the rotational power of the input shaft (1) to the planet carrier (11).

As described above, the double pinion planetary gear set 3 receiving power from the input shaft 1 is connected to the other double pinion planetary gear set 5 in a fixed coupling structure and a variable coupling structure. The sun gear 13 of the other double pinion planetary gear set 5 is fixed to the transmission housing 15.

That is, a third clutch means C3 is provided between the planet carrier 11 of the double single pinion planetary gear set 3 and the ring gear 17 of the other double pinion planetary gear set 5, and the third clutch The means C3 has a structure that can transmit or block rotational power transmitted to the ring gear 17 of the other double pinion planetary gear set 5 to the planet carrier 11 of the double pinion planetary gear set 3. That is, the planet carrier 11 of the double pinion planetary gear set 3 and the ring gear 13 of the other double pinion planetary gear set 5 are connected in a variable coupling structure.

The first, second and third clutch means C1, 2 and 3 described above may use a multi-plate clutch that is generally used for a power train of an automatic transmission for a vehicle.

On the other hand, brake means are provided which allow the planetary gear set to adjust the output rotation speed with respect to the input when one or more of the above clutch means are operated.

That is, a first brake means B1 is provided between the sun gear 7 of the double pinion planetary gear set 3 and the transmission housing 15, and the first brake means B1 is a double pinion planetary gear set 3. The sun gear 7 of) is fixed to the transmission housing 15 or made of a structure capable of rotating independently.

Further, a second brake means B2 is provided between the planetary carrier 23 and the sun gear 13 of the other double pinion planetary gear set 5, and the second brake means B2 is the planetary gear set 5. By connecting the planetary carrier 23 to the sun gear 13 is made of a structure capable of fixing the entire planetary gear set (5).

The planetary carrier 23 of the other double pinion planetary gear set 5, in which the ring gear 19 of the double pinion planetary gear set 3 and the other pinion gear 21 are installed, is fixed by the power transmission member 25. It is connected by a coupling structure.

Meanwhile, the transfer drive gear 27 formed integrally with the planet carrier 11 of the double pinion planetary gear set 3 is gear-coupled with a transfer driven gear (not shown) to transfer power to the differential device through the final reduction gear. However, in this configuration, such a structure has been omitted since a known one can be used, and any intended structure can be used to realize the intended purpose of the present invention.

The power train for the automatic transmission according to the present invention made as described above has three elements of a planetary gear set (sun gear, planet carrier) according to friction elements (clutch means and brake means) selectively activated or deactivated by the transmission control unit. And one of the elements as the input element and the other element as the reaction force element, and outputs the speed ratio of the fourth forward speed and the first reverse speed, which will be described later.

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 driven by the first and third clutch means C1 and 3 so that the gear train can output the speed ratio of the first speed. These clutches are operated by supplying hydraulic pressure.

Hereinafter, the clutch means and the brake means to operate means that the hydraulic pressure is supplied from the hydraulic control system.

When the first and third clutch means C1 and 3 are operated, rotational power transmitted to the connected sun gear 7 of the input shaft 1 is driven by the ring gear 19 of the double pinion planetary gear set 3. It is transmitted to the planet carrier 23 of the other double pinion planetary gear set 5 connected by the transmission member 25 to receive the reaction force of the sun gear 13 and rotate the ring gear 17 forward.

Accordingly, the planetary carrier 11 of the double-pinion planetary gear set 5 connected to the ring gear 17 by the third clutch means C3 rotates forward, and outputs a speed ratio of 1 speed to the transfer drive gear 27 formed integrally therewith. Done.

When the vehicle speed increases in such a first speed state, the transmission control unit operates the first clutch means C1 and the second clutch means C2 while the third clutch means C3 operates.

By the above-described action, the input element is changed from the sun gear 7 of the double pinion planetary gear set 3 to the planet carrier 23 of the other double pinion planetary gear set 5 while the first speed and the reaction force element are the same. The rotational power transmitted to the input shaft 1 is transmitted to the planet carrier 11 of the double pinion planetary gear set 3 connected to the ring gear 17 of the planetary gear set 5 by the third clutch means C3. do.

Therefore, the pinion gear 9 installed in the planetary carrier 11 of the double pinion planetary gear set 3 rotates around the outer gear 7 while rotating the sun gear 7, so as to rotate the pinion gear 9. The planet carrier 1 rotates more than the first speed, and outputs a transmission ratio of two speeds to the transfer drive gear 27 formed integrally therewith.

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

Since the sun gear 7 and the ring gear 19 of the double pinion planetary gear set 3 act as input elements at the same time, the planetary gear set 3 rotates integrally.

Therefore, the transfer drive gear 27 formed on the planet carrier 11 of the double pinion planetary gear set 3 transmits the rotational power of the input shaft 1 as it is and outputs a speed ratio of three speeds.

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

By the above-described action, the ring gear 19 of the double pinion planetary gear set 3 acts as an input element, and the sun gear 7 acts as a reaction force element by the first brake means B1. The speed increase is performed in the gear set 3 to output the speed ratio of the fourth speed to the transfer drive gear 27 formed integrally with the planet carrier 11.

On the other hand, when the shift lever is moved to the reverse R range, the transmission control unit operates the first clutch means C1 and the second brake means B2. At this time, since the planetary carrier 23 is connected to the linear 13 while the sun gear 13 of the other double pinion planetary gear set 5 is fixed to the transmission housing 15, the entire planetary gear set 5 is full. Is fixed.

By the above operation, the sun gear 7 of the double pinion planetary gear set 3 acts as an input element, and the ring gear 19 of the double pinion planetary gear set 3 acts as a reaction force element. The reverse outputs the speed ratio through the transfer drive gear 27 formed integrally with the planet carrier 11 of the planet gear set 3.

FIG. 2 is a second configuration diagram of a power train for an automatic transmission according to the present invention, in which the second brake means is provided between the planetary carrier 23 and the sun gear 13 of another double pinion planetary gear set 5 in the first configuration. (B2) is installed to connect the planetary carrier 23 and the sun gear 13 to secure the entire planetary gear set (5), but in this configuration the ring of another double pinion planetary gear set (5) A fourth clutch C4 is installed between the gear 17 and the planet carrier 23 to connect the ring gear 17 and the planet carrier 23 in a variable coupling structure to fix the entire planet gear set 5. It is configured to be.

Therefore, the power train for the automatic transmission according to the second configuration has a frictional element actuated or deactivated by the transmission control unit as shown in [Table 2]. Since the same operation as the first configuration, a detailed description thereof will be omitted.

TABLE 2

Friction element operating table for each gear

However, in the reverse R range, when outputting the same speed ratio as in the first configuration, the fourth clutch means C4 is actuated instead of the second brake means B2 to fix the entire double pinion planetary gear set 5. There is only a difference.

FIG. 3 is a third configuration diagram of a power train for an automatic transmission according to the present invention, wherein in the first configuration, the planets of the double pinion planetary gear set 3 are different from the ring gear 19 and the double pinion planetary gear set 5. Although the carrier 23 is connected to the power transmission member 25, in this configuration, the planetary carrier 11 of the double pinion planetary gear set 3 and the ring gear 17 of the other double pinion planetary gear set 5 are driven. The transmission member 25 was connected to the fixed coupling structure.

In the first configuration, a third clutch means C3 is provided between the planet carrier 11 of the double pinion planetary gear set 3 and the ring gear 17 of the other double pinion planetary gear set 5 to variably couple them. In this configuration, the third clutch means 3 is provided between the ring gear 19 of the double pinion planetary gear set 3 and the planetary carrier 23 of the other double pinion planetary gear set 5. These were connected in a variable coupling structure.

In the first configuration, the second brake means B2 is provided between the sun gear 13 and the planet carrier 23 of the other double-pinion planetary gear set 5 to fix the whole planet gear set 5 to the rear diagnosis. Although the reaction force element is determined at, the second brake means B2 is installed between the ring gear 19 of the double pinion planetary gear set 5 and the transmission housing 15 so as to provide a double pinion planetary gear set 3. Is configured to determine the ring gear 19 as the reaction force element in the reverse stage.

Therefore, the power train for the automatic transmission according to the third configuration operates in the same way as the first configuration in the forward D range and the reverse R range since the friction elements are activated or deactivated by the transmission control unit as shown in [Table 1]. Therefore, detailed description thereof will be omitted.

As described above, the power train for an automatic transmission according to the present invention can provide four forward shift stages and one reverse stage, and does not draw by fixing sun gear of another double pinion planetary gear set in the entire shift range. Since the slip of the element can be reduced, the frictional loss due to the slip of the friction element can be minimized.

Claims (15)

An input shaft that receives rotational power of the engine from the turbine of the torque converter and a double pinion planetary gear set that adjusts the number of rotations of the output according to the number of elements to which the rotational power of the input shaft is transmitted, and the double pinion planetary gear Another double pinion planetary gear set having an element fixedly connected to an element of the set and an element fixedly connected to the transmission housing and shifting according to the power transmitted from the double pinion planetary gear set, the input shaft described above. A clutch means for transmitting any one of three elements of the above-mentioned double pinion planetary gear set and another double pinion planetary gear set and transmitting to two or more elements, said double pinion planetary gear One element of the set and one yaw of the double pinion planetary gear set Other clutch means for selectively connecting the elements, the element of the planetary gear set acting as an input element by the clutch means and the two or more elements acting as input elements to react the elements of the planetary gear sets. A power train for an automatic transmission comprising brake means installed between the element and the transmission housing to select with the element. The power train for an automatic transmission according to claim 1, wherein the sun gear of another double pinion planetary gear set is fixedly installed in the transmission housing. 2. The clutch according to claim 1, wherein the clutch means is provided between the input shaft and the sun gear of the double pinion planetary gear set to interlock power transmission, and is installed between the input shaft and the planetary carrier of the other double pinion planetary gear set. A power train for an automatic transmission comprising a second clutch means for interrupting transmission. 2. The power train of claim 1, wherein the clutch means comprises a third clutch means installed between one element of the double pinion planetary gear set and one element of the other double pinion planetary gear set to interrupt power transmission. 5. The third clutch means according to claim 4, wherein the third clutch means is adapted to interrupt power transmission between the planetary carrier of the double pinion planetary gear set and the ring gear of the other double pinion planetary gear set. Power train for automatic transmission, characterized by being installed between sets of ring gears. 5. The third clutch means according to claim 4, wherein the third clutch means is configured to interrupt power transmission between the ring gear of the double pinion planetary gear set and the planetary carrier of the other double pinion planetary gear set and the other of the double pinion planetary gear set. Power train for an automatic transmission, characterized by being installed between sets of planetary carriers. 2. The clutch means according to claim 1, wherein the clutch means comprises a fourth clutch means installed between the ring gear of the other double pinion planetary gear set and the planet carrier to interrupt power transmission between the ring gear of the other double pinion planetary gear set and the planet carrier. Power train for automatic transmission. 2. The brake means according to claim 1, wherein the brake means is provided between the sun gear of the double pinion planetary gear set and the transmission housing to fix the sun gear of the double pinion planetary gear set, one of the elements of the two double pinion planetary gear sets. And a second brake means provided between the element and the transmission housing to fix the element to output the reverse speed ratio to the output element. 9. The power train for an automatic transmission according to claim 8, wherein the second brake means is installed between the sun gear and the planet carrier of the other double pinion planetary gear set to fix the entire other double pinion planetary gear set. 9. The power train of claim 8, wherein the second brake means is installed between the ring gear of the double pinion planetary gear set and the transmission housing to fix the ring gear of the double pinion planetary gear set. The power train for an automatic transmission according to claim 1, wherein the ring gear of the double pinion planetary gear set and the planet carrier of the other double pinion planetary gear set are connected in a fixed coupling structure by a power transmission member. The power train for an automatic transmission according to claim 1, wherein the planetary carrier of the double pinion planetary gear set and the ring gear of the other double pinion planetary gear set are connected in a fixed coupling structure by a power transmission member. The power train for an automatic transmission according to claim 1, wherein the planetary carrier of the double pinion planetary gear set and the ring gear of the double pinion planetary gear set are connected in a variable coupling structure by clutch means. 2. The power train of claim 1, wherein the ring gear and the planet carrier of another double pinion planetary gear set are connected in a variable engagement structure by clutch means. The power train for an automatic transmission according to claim 1, wherein the ring gear of the double pinion planetary gear set and the planet carrier of the other double pinion planetary gear set are connected in a variable coupling structure by clutch means.