KR100256754B1 - Power train of automatic transmission - Google Patents

Abstract

PURPOSE: A power train for an automatic transmission minimizes the friction loss of non-operating friction elements. CONSTITUTION: The torque of an engine(E) is transmitted to an input shaft(1) of a speed change device after being converted in a torque converter(T). The input shaft(1) transmits the torque to a single pinion planetary gear set(3) after receiving the torque from the turbine of the torque converter(T). The single pinion planetary gear set(3) transmits the torque to a double pinion planetary gear set(5). Thus, a power train provides four advance speed ranges and a reverse speed range. The sun gear(19) of the double pinion planetary gear set(5) is fixed on the total ranges of speed change. Further, the total double pinion planetary gear set(5) is fixed on the fourth speed of a D range and the first speed of an R range. Thus, the slip of a non-operating friction element is reduced, thereby minimizing the friction loss of friction elements.

Description

Power train for automatic transmission

The present invention relates to an automatic transmission for a vehicle, and more particularly, frictional loss of a friction element that does not operate by variably connecting four or five elements of a single pinion planetary gear set and a double pinion planetary gear set. A power train for automatic transmission is minimized.

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, that is, an input element, a reaction force element, and an output element, is used as an input element. 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 use such a compound planetary gear device as a transmission means in a vehicle, the rib type has a structure in which a planetary carrier is connected while sharing a ring gear, and the Simpson type has a structure in which a planetary carrier and a ring gear are connected while sharing a 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 variably connect the sun gear of the single pinion planetary gear set and the planetary carrier of the double pinion planetary gear set, and variably connect the ring carrier of the planetary carrier of the single pinion planetary gear set and the double pinion planetary gear set, It is to provide a power train for an automatic transmission in which the double pinion planetary gear set elements are variably connected to each other and the sun gear of the double pinion planetary gear set is fixed to the transmission housing to minimize the frictional loss of the inoperative friction elements.

In order to realize 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 the input shaft rotates by receiving the rotational power of the engine from the turbine of the torque converter, the number of rotational power of the input shaft is transmitted Single pinion planetary gear set, which has a variable variable element to the element of the single pinion planetary gear set, and has a structure that is fixedly connected to the transmission housing, shifting according to the power transmitted from the single pinion planetary gear set A double pinion planetary gear set for carrying out, a clutch for acting to transmit the rotational force of the input shaft to one element of the single pinion planetary gear set and the double pinion planetary gear set and to the other element. Sudan, one of the single pinion planetary gear sets described above It includes another clutch means for varying the predetermined connection and an element of the double pinion planetary gear set and variably coupling the element and the other element of the double pinion planetary gear set of double-pinion planetary gear set.

The clutch means is installed between the input shaft and the sun gear of the single pinion planetary gear set to clamp the power transmission, and the second clutch that is installed between the input shaft and the planetary carrier of the single pinion planetary gear set to interrupt power transmission. Clutch means.

The clutch means is installed between the sun gear of the single-pinion planetary gear set and the planetary carrier of the double-pinion planetary gear set to clamp the power transmission, the ring of the planetary carrier of the single-pinion planetary gear set and the double-pinion planetary gear set. And a fourth clutch means installed between the gears for intermittent power transmission and a fifth clutch means for selecting and variably connecting two elements of the double pinion planetary gear set.

The fifth clutch means is installed between the sun gear and the planet carrier of the double pinion planetary gear set to connect and fix the planet carrier of the double pinion planetary gear set to the sun gear.

The fifth clutch means is installed between the sun gear and the ring gear of the double pinion planetary gear set to connect and fix the ring gear of the double pinion planetary gear set to the sun gear.

The fifth clutch means is installed between the ring gear of the double pinion planetary gear set and the planet carrier so as to connect the ring gear of the double pinion planetary gear set to the planet carrier.

The sun gear of the double pinion planetary gear set is fixed to the transmission housing.

The sun gear of the single pinion planetary gear set and the planet carrier of the double pinion planetary gear set are connected in a variable coupling structure by clutch means.

The planetary carrier of the single-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.

The sun gear and the planet carrier of the double pinion planetary gear set are connected in a variable coupling structure by clutch means.

The sun gear and the ring gear of the double pinion planetary gear set are connected in a variable coupling structure by clutch means.

The planetary carrier and the ring gear of the double pinion planetary gear set are connected in a variable coupling 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 single pinion planetary gear set 3, and the single pinion planetary gear set 3 is a double pinion planetary gear set 5. Clutch hook up to deliver torque.

That is, a first clutch means C1 is provided between the input shaft 1 and the sun gear 7 of the single-pinion planetary gear set 3, and the first clutch means C1 applies the rotational power of the input shaft 1. The single pinion planetary gear set (3) is made of a structure that can be transmitted or blocked to the sun gear (7).

A second clutch means C2 is provided between the input shaft 1 and the planet carrier 11 on which the pinion gear 9 is installed so that the single pinion planetary gear set 3 can have two input elements. The second clutch means C2 is configured to transmit or block the rotational power of the input shaft 1 to the planet carrier 11 of the single pinion planetary gear set 3.

The single pinion planetary gear set 3, which receives rotational power from the input shaft 1, is variably connected to the double pinion planetary gear set 5 by other clutch means.

That is, the third clutch means C3 is installed between the sun gear 7 of the single pinion planetary gear set 3 and the planet carrier 15 of the double pinion planetary gear set 5 on which the other pinion gear 13 is installed. The third clutch means C3 is configured to transmit or block the rotational power of the input shaft 1 to the planet carrier 15 of the planetary gear set 5.

That is, the sun gear 7 of the single pinion planetary gear set 3 and the planetary carrier 15 of the double pinion planetary gear set 5 are connected in a variable coupling structure.

The fourth clutch means C4 is provided between the planet carrier 11 of the single pinion planetary gear set 3 and the ring gear 17 of the double pinion planetary gear set 5, and the fourth clutch means. (C4) is made of a structure that can transmit or block the rotational power of the input shaft (1) to the double pinion planetary gear set (5) ring gear (17).

That is, the planet carrier 11 of the single pinion planetary gear set 3 and the ring gear 17 of the double pinion planetary gear set 5 are connected in a variable coupling structure.

The sun gear 19 of the double pinion planetary gear set 5 is fixed to the transmission housing 21 so as to act as a reaction force element in the entire shift region.

In addition, a fifth clutch means C5 is installed between the sun gear 19 and the planet carrier 15 of the double pinion planetary gear set 5 fixedly installed to the transmission housing 21 as described above. (C5) has a structure that allows the planetary carrier 15 of the double pinion planetary gear set 5 to be fixed or rotated independently.

That is, the sun gear 19 and the planet carrier 15 of the double pinion planetary gear set 5 are connected in a variable coupling structure.

The above-described first, second, third, fourth and fifth clutch means C1, 2, 3, 4, and 5 may use a multi-plate clutch used for a power train of a general automatic transmission for a vehicle.

Meanwhile, the transfer drive gear 25 formed integrally with the ring gear 23 of the single pinion planetary gear set 3 is gear-coupled to the transfer driven gear (not shown) to transfer power to the differential device through the final reduction gear. However, in this configuration, such a structure is omitted since a known one can be used, and any object of the structure can be used to realize the object intended by the present invention.

The power train for an automatic transmission according to the present invention made as described above has three elements of a planetary gear set (sun gear, planet carrier, ring gear) according to friction elements (clutch means) selectively activated or deactivated by the transmission control unit. ), Any one element is selected as an input element, and the other element is selected as a reaction element, and a transmission ratio of 4 forward speeds and 1 reverse speed, which will be described later, is output.

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

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 causes the first clutch means C1 and the third and fourth to allow the gear train to output the first speed ratio. Hydraulic pressure is supplied to the clutch means C3, C4 to operate these clutches.

Hereinafter, the clutch means operating means that the hydraulic pressure is supplied from the hydraulic control system.

When the first clutch means C1 and the third and fourth clutch means C3 and 4 operate, the sun gear 7 of the single-pinion planetary gear set 3 connected by the third clutch means C3 and The planet carrier 15 of the double pinion planetary gear set 5 serves as an input element.

Therefore, the rotational power of the input shaft 1 is transmitted to the planet carrier 15 of the double pinion planetary gear set 5, which is an input element, and rotates forward. The sun gear 19 acts as a reaction force element, so the double pinion planetary gear set ( 5) the forward rotation of the ring gear 17 and the planetary carrier 11 of the single pinion planetary gear set 3 connected to the fourth clutch means C4, thereby forward rotation of the single pinion planetary gear set 3 The speed ratio of the first gear is output to the transfer drive gear 25 formed integrally with the ring gear 23.

When the vehicle speed increases in the first speed state, the transmission control unit deactivates the first clutch means C1 while the third and fourth clutch means C3 and 4 are operated, and the second clutch means C2 is turned off. It works.

By the above action, the reaction force element is the same as the first speed, but the input element of the double pinion planetary gear set 5 connected to the sun gear 7 of the single pinion planetary gear set 3 and the third clutch means C3 is connected thereto. The planetary carrier 15 is changed from the planetary carrier 11 to the single pinion planetary gear set 3.

Therefore, the rotational power of the input shaft 1 is transmitted to the planet carrier 15 of the double pinion planetary gear set 5 through the ring gear 17 of the double pinion planetary gear set 5, and the planet carrier 15 is Since the reaction force of the sun gear 19 is transmitted to the sun gear 7 of the single pinion planetary gear set 3 connected by the third clutch means C3 to the transfer drive gear 25 formed integrally with the ring gear 23. Delivered.

At this time, while the pinion gear 9 installed in the planetary carrier 11 of the single-pinion planetary gear set 3 rotates, the planetary carrier 11 is further rotated by this rotation to output the second speed ratio.

When the vehicle speed increases in the second speed state, the transmission control unit deactivates the fourth clutch means C4 while the second and third clutch means C2 and 3 are operated, and the first clutch means C1 is turned off. It works.

Since the sun gear 7 and the planet carrier 11 of the single pinion planetary gear set 3 act as input elements at the same time, the planet gear set 3 rotates integrally.

Therefore, the transmission power of the input shaft 1 is transmitted as it is through the transfer drive gear 25 formed integrally with the ring gear 23 of the single-pinion planetary gear set 3, thereby outputting a third speed ratio.

When the vehicle speed is increased in the third speed state, the transmission control unit deactivates the first clutch means C1 and operates the fifth clutch means C5 while the second and third clutch means C2 and 3 are operated. Let's do it. At this time, since the sun gear 19 and the planet carrier 15 are connected by the fifth clutch means C5 while the sun gear 19 of the double pinion planetary gear set 5 is fixed to the transmission housing 21, the double pinion is connected. The entire planetary gear set 5 is fixed.

By the above-described action, the planetary carrier 11 of the single-pinion planetary gear set 3 acts as an input element, and the sun gear 7 acts as a reaction force element by the third clutch means C3. The speed increase is performed in the gear set 3 so that the transfer drive gear 25 formed integrally with the ring gear 23 also outputs a speed ratio of four speeds.

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 fourth and fifth clutch means C4 and 5. At this time, since the sun gear 19 of the double pinion planetary gear set 5 is fixed to the transmission housing 21, the sun gear 19 and the planet carrier 15 are connected by the fifth clutch means C5. The entire pinion planetary gear set 5 is fixed.

By the above operation, the sun gear 7 of the single-pinion planetary gear set 3 acts as an input element, and the planet carrier 11 is transmitted by the fourth and fifth clutch means C4 and 5 to the transmission housing 21. Since the ring gear 23 is reversely rotated so as to act as a reaction force element, the reverse gear ratio is outputted to the transfer drive gear 25 formed integrally therewith.

FIG. 2 is a second configuration diagram of a power train for an automatic transmission according to the present invention. In the first configuration, a fifth clutch means (5) is formed between the sun gear 9 and the planet carrier 15 of the double-pinion planetary gear set 5. C5) is installed to fix the planet carrier 15 of the double pinion planetary gear set 5, but in this configuration, the sun gear 19 and the ring gear 17 of the double single pinion planetary gear set 5 are fixed. The fifth clutch means (C5) is provided between the () and the variable coupling between the ring gear 17 and the sun gear 19 is configured to be fixed to the ring gear (15).

That is, the ring gear 17 and the sun gear 19 of the double pinion planetary gear set 5 are connected in a variable coupling structure.

Therefore, in the power train for the automatic transmission according to the second configuration, as shown in [Table 1], since the friction element is activated or deactivated by the transmission control unit, the fifth clutch means C5 does not operate. In the 2nd and 3rd speeds, the same operation as in the first configuration is omitted.

However, as in the first configuration, the second, third and fifth clutch means C2, 3 and 5 are operated at the driving D range four speeds to output the D range four speeds as in the first configuration and the reverse R range state. Ring gear of the double pinion planetary gear set 5 when the transmission control unit operates the first, fourth and fifth clutch means C1, 4 and 5 to output the gear ratio of reverse 1 speed as in the first configuration. There is only a difference that the whole planetary gear set 5 is fixed by interconnecting the sun gear 19 fixed to the transmission gear 21 and the transmission housing 21.

3 is a third configuration diagram of a power train for an automatic transmission according to the present invention. In the first configuration, a fifth clutch means (5) is formed between the sun gear 19 and the planet carrier 15 of the double-pinion planetary gear set 5. C5) is installed to fix the planetary carrier 15 of the double pinion planetary gear set 5, but in this configuration, the planetary carrier 15 and the ring gear ( The fifth clutch means (C5) is provided between the 17 and 17 so that the planet carrier 15 and the ring gear 17 can be variably connected.

That is, the planet carrier 15 and the ring gear 17 of the double pinion planetary gear set 5 are connected in a variable coupling structure.

Therefore, in the power train for the automatic transmission according to the third configuration, as shown in [Table 1], since the friction element is activated or deactivated by the transmission control unit, the fifth clutch means C5 does not operate. In the 2nd and 3rd speeds, the same operation as in the first configuration is omitted.

However, as in the first configuration, the second, third and fifth clutch means C2, 3 and 5 are operated at the driving D range four speeds to output the D range four speeds as in the first configuration and the reverse R range state. When the transmission control unit operates the first, fourth and fifth clutch means C1, 4 and 5 to output the transmission ratio of reverse 1 speed as in the first configuration, the sun gear 19 is connected to the transmission housing 21. There is only a difference that the planetary carrier set 5 of the double pinion planetary gear set 5 and the ring gear 17 are connected to each other in a fixed state to fix the entire planetary gear set 5.

As described above, the power train for the automatic transmission according to the present invention can provide 4 forward speeds and 1 reverse speed, which fixes the sun gear of the double pinion planetary gear set in the entire speed range, and the D range 4 speeds and the R ranges. By fixing the entire double pinion planetary gear set at 1 speed, it is possible to reduce the slip of the friction element that is not working, thereby minimizing the friction loss due to the slip of the friction element.

Claims (3)

Combination of single pinion planetary gear set and double pinion planetary gear set on the same axis as the input shaft that receives rotational power from the engine to form a power train for automatic transmission for vehicles that can achieve 4th speed forward and 1st speed reverse. The single pinion planetary gear set is variably connected between the sun gear and the ring gear via the input shaft and the first and second clutch means, and the double pinion planetary gear set is fixedly connected to the transmission housing and always acts as a fixed element. Combination of the single-pinion planetary gear set, the sun gear and the planetary carrier variably connected to the planetary carrier and ring gear of the double-pinion planetary gearset via the third and fourth clutch means, respectively, the ring of the single-pinion planetary gearset The gear is the output element, and the planetary carrier of the double pinion planetary gear set is the fifth clutch. A power train for an automatic transmission, characterized in that it is variably connected to the sun gear of a double pinion planetary gear set via a tooth means. In combination with the single pinion planetary gear set and the double pinion planetary gear set on the same axis as the input shaft that receives the rotational power from the engine, it forms a power train for the automatic transmission that can achieve 4th speed forward and 1st speed reverse. , A single pinion planetary gear set in which the sun gear and the ring gear are variably connected via the input shaft and the first and second clutch means, and a double pinion planetary gear set in which the sun gear is fixedly connected to the transmission housing and always acts as a fixed element. However, the sun gear and the planetary carrier of the single pinion planetary gear set are variably connected to the planet carrier and the ring gear of the double pinion planetary gear set via third and fourth clutch means, respectively, and the ring gear of the single pinion planetary gear set. Is the output element, and the fifth gear means is opened by the ring gear of the double pinion planetary gear set. A power train for an automatic transmission, characterized in that it is variably connected to the sun gear of a double pinion planetary gear set. Combination of single pinion planetary gear set and double pinion planetary gear set on the same axis as the input shaft that receives rotational power from the engine to form a power train for automatic transmission for vehicles that can achieve 4th speed forward and 1st speed reverse. The single pinion planetary gear set is variably connected between the sun gear and the ring gear via the input shaft and the first and second clutch means, and the double pinion planetary gear set is fixedly connected to the transmission housing and always acts as a fixed element. Combination of the single-pinion planetary gear set, the sun gear and the planetary carrier variably connected to the planetary carrier and ring gear of the double-pinion planetary gearset via the third and fourth clutch means, respectively, the ring of the single-pinion planetary gearset The gear is the output element, and the ring gear of the double pinion planetary gear set is the fifth clutch A power train for an automatic transmission, wherein the transmission is variably connected to a planet carrier of a double pinion planetary gear set.