KR100210937B1 - Automatic transmission for a vehicle - Google Patents

Abstract

The speed range of the driving 'D' range can be changed to the high-speed and low-speed range, so that the number of speed change stages is increased so as to optimize the required torque according to the load of the driving vehicle to increase the torque efficiency and transmission feel. A torque converter that receives the driving force of the engine and performs torque conversion; A first transmission mechanism connected to an input shaft on a turbine side of the torque converter and configured to determine a direction of forward and reverse rotation and an angular speed stage by operation of respective frictionally controlled hydraulic members; The first speed change mechanism is connected to the first speed change mechanism and the speed of each speed step output from the first speed change mechanism is decelerated and the speed is increased so that the number of the speed change stages is increased and the driving force is transmitted to the differential device And a second transmission mechanism.

Description

Automotive automatic transmission

FIG. 1 is a configuration diagram of an automatic transmission for a vehicle according to the present invention. FIG.

FIG. 2 is a table of operating elements for each speed of an automatic transmission for a vehicle according to the present invention; FIG.

3 is a speed diagram for each speed of the automatic transmission for a vehicle according to the present invention.

[Industrial Applications]

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to an automatic transmission for a vehicle, and more particularly, to an automatic transmission for a vehicle that adapts to a required torque according to a load of a traveling vehicle in an optimal state to increase torque efficiency and transmission feeling.

BACKGROUND ART [0002]

The transmission of the vehicle has a function of the engine transmitting the driving force to the drive wheels. The transmission includes a manual transmission that selects a transmission directly to the driver's will, and a transmission And an automatic transmission that automatically shifts according to the running condition of the vehicle.

2. Description of the Related Art Generally, an automatic transmission includes a torque converter that converts torque output from an engine, and a multi-speed transmission mechanism that is connected to the torque converter to change the direction of forward and reverse rotation and the traveling speed of the vehicle. And a friction member for selecting one of the gear stages of the mechanism.

This automatic transmission has a forward gear position of forward 3, forward gear position 1, reverse gear position 2, or a gear position of forward gear 5 reverse gear 1 when the auxiliary gear shift device is mounted.

[Problems to be solved by the present invention]

However, since the above-described automatic transmission for a vehicle has a small number of speed stages, it can not adapt to the required torque according to the load of the traveling vehicle in an optimal state, resulting in deterioration of torque efficiency and transmission feeling.

SUMMARY OF THE INVENTION Accordingly, the present invention has been made keeping in mind the above problems occurring in the prior art, and it is an object of the present invention to provide a vehicle speed control system for a vehicle, And the torque efficiency and the shift feeling are increased by corresponding to the required torque according to the load of the automatic transmission.

[MEANS FOR SOLVING THE PROBLEM]

In order to achieve this, an automatic transmission for a vehicle according to the present invention includes: a torque converter that receives torque from an engine and converts torque; A first transmission mechanism connected to an input shaft on a turbine side of the torque converter and configured to determine a direction of forward and reverse rotation and an angular speed stage by the operation of each of the frictionally controlled hydraulic friction elements; The speed ratio of the speed stage connected to the first transmission mechanism is increased to increase the number of speed stages by transmitting one of the deceleration and the constant speed and the driving force is transmitted to the differential device And the second transmission mechanism.

Wherein the first transmission mechanism is a complex planetary gear set consisting of a single pinion planetary gear and a double pinion planetary gear that share the ring gear as an output element and the sun gear of the single pinion planetary gear is connected to the input shaft via a first friction member And the first power transmitting member is selectively connected to the transmission housing via a second friction member and a first one-way clutch for selectively activating the sun gear of the single pinion planetary gear with the reaction element and the idle element, The sun gear of the double pinion planetary gear is connected to the second power transmitting member connected to the input shaft via the third friction member and the planetary carrier is selectively connected to the input shaft via the fourth friction member at one side thereof , And is selectively connected to the transmission housing via the fifth friction member to the other side.

The planetary carrier connecting the plurality of pinion gears that are in contact with the sun gear is connected to the transfer drive gear and the output shaft of the planetary gear set. The planetary gear set is a simple planetary gear set, and the sun gear is mounted on a transfer shaft receiving drive force from the first transmission mechanism. And the ring gear is connected to the transfer shaft by the second one-way clutch to one side thereof and selectively connected to the transmission housing via the sixth friction member to the other side.

The first, third and fourth friction elements use a multi-plate clutch as the clutch means. The second, fifth, and sixth friction elements use band brakes as breaking means.

[Action]

The automatic transmission configured as described above operates the sixth friction element of the second transmission mechanism at one speed stage in the forward 'D' range 1, 2, 3, and 4 to perform low speed control, The operation of the element is released and the second one-way clutch is operated to perform the high-speed step control.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

[Example]

FIG. 1 is a configuration diagram of an automatic transmission for a vehicle according to the present invention. Reference numeral 1 is referred to as a torque converter 1.

The torque converter 1 includes a pump impeller 5 that rotates directly on the crankshaft of the engine 3 so as to receive power from the engine 3 and a pump impeller 5 disposed opposite to the pump impeller 5, Way clutch 11 which is disposed between the turbine runner 7 and the pump impeller 5 and is mounted on the transmission housing 9 is provided with a turbine runner 7 rotating by the output of oil according to the rotation of the turbine runner 5, And a stator 13 whose one side is fixed and which increases the rotational force of the pump emplayer 5.

Therefore, when the engine 3 is driven, the oil filled in the torque converter 1 is spouted from the pump impeller 5 and supplied to the turbine runner 7 to drive the turbine runner 7, ≪ / RTI >

The oil introduced into the stator 13 is changed in the direction and flows again into the pump impeller 5. At this time, the turbine runner 7 And the rotational force of the pump impeller 5, so that torque conversion is performed.

On the input shaft 15 to which the turbine runner 7 is directly connected, a first transmission mechanism 17 for determining forward and reverse rotation and respective speed change stages is mounted via a friction member.

This first transmission mechanism mechanism 17 uses a complex planetary gear set that shares the single-pinion planetary gear and the double pinion planetary gear with the ring gear as an output element.

The sun gear 19 of the single pinion planetary gear is connected to a first power transmitting member 20 which is selectively connected to the input shaft 15 via a first friction member C1 so as to be operated as an input element. The first power transmitting member 20 is selectively connected to the transmission housing 9 by the second friction member B1 so as to actuate the sun gear 19 as a reaction element, Is connected to the transmission housing (9) by the first one-way clutch (F1).

The sun gear 21 of the double pinion planetary gear is connected to the input shaft 15 via the third friction member C2 so as to be operated by the other input element of the first transmission mechanism 17, (23).

A plurality of inner pinion gears 25 which are in contact with the sun gear 21 of a double pinion planetary gear that operates as an input element by the second power transmitting member 23 and a plurality of inner pinion gears 25, And an outboard pinion gear 27, which communicates with the sun gear 19 of the sun gear 19, is connected by a planetary carrier 29.

The planetary carrier 29 is selectively connected to the input shaft 15 via a fourth friction element C3 to one side thereof so as to be operable with a reaction element and an input element and a fifth friction element B2 And is selectively connected to the transmission housing 9 via the transmission housing.

The ring gear 30 in contact with the outboard pinion gear 27 connected by the planetary carrier 29 is configured to transmit the driving force of the forward and reverse rotation direction and the speed change stage determined by the first transmission mechanism 17 to the second transmission mechanism And is engaged with a driven gear 35 mounted on the transfer shaft 33 as an output element to be output to the output shaft 31.

The sun gear 35, which is an input element of the second transmission mechanism 31 constituted by a simple planetary gear set, is mounted on the transfer shaft 33 rotating forward and backward by a driving force transmitted to the driven gear 35.

The planetary carrier 39 connecting the plurality of pinion gears 37 that are in contact with the sun gear 35 is connected to the transfer drive gear 41 as an output element.

The ring gear 43 in contact with the pinion gear 37 is engaged with the transmission housing 9 via a sixth friction element B3 on one side thereof so as to act as a reaction force element and a locking means of the second transmission mechanism 31, And is locked with the sun gear 35 by the second one-way clutch F2 when the sixth friction element B3 is not operating.

The transfer drive gear 41 is engaged with the differential gear 51 of the differential device 49 on which the drive shafts 45 and 47 are mounted.

As is well known, the differential device 49 includes a pair of side gears 53, 53 disposed on the inner left and right sides of a transfer case (not shown) and coupled to drive shafts 45, 47, 55 and a pair of pinion gears 57, 59 engaged with the front and rear sides of the side gears 53, 55.

In the automatic transmission for a vehicle configured as described above, as the driver actuates the select lever (not shown), each friction element is operated and non-operated by a hydraulic control mechanism (not shown) as shown in the table of FIG. 2, The speed ratio according to the lever analysis method as shown in FIG.

The lever L in FIG. 3 represents the first speed change mechanism 17, and its left end is connected to a first node Node 1 (N 1) where the sun gear 19 of the single pinion planetary gear is located, A third node N3 in which the ring gear 30 is present at another adjacent position and a fourth node N3 in which the right end is the fourth node N3 in which the sun gear 21 of the double pinion planetary gear exists, And is represented by a node N4.

The left end of the lever 1 indicating the second transmission mechanism 31 is connected to the fifth node N5 where the sun gear 35 exists and the position adjacent to the fifth node N5 is the sixth node N3, (N6), and the right end thereof is denoted by a seventh node N7 in which the ring gear 43 is present.

On the other hand, if the driver selects the parking 'P' range with the select lever, all the friction elements, ie the first, second, third, fourth, fifth and sixth friction elements C1, B1, C2, C3, B2 and B3, Since the driving force of the engine is not input to the first transmission mechanism 17, the vehicle remains in a stopped state.

The first node N1 corresponding to the sun gear 19 of the single pinion planetary gear is driven by the operation of the first friction member C1 of the first transmission mechanism 17, The second node N2 corresponding to the planetary carrier 29 becomes the fixed end by the operation of the fifth friction element B2 and the second node N2 at any position of the first node N1 And the line R obtained by connecting the vertical line on the lever L at the third node N3 corresponding to the ring gear 30 which is the output end thereof is connected to the straight line LR.

The first reverse rotation speed R is input to the sun gear 35 of the second transmission mechanism 31 so that the fifth node N5 corresponding to the sun gear 35 becomes the input end and the sixth friction element B3 The seventh node N7 corresponding to the ring gear 43 becomes a fixed end due to the operation of the third node N3 and the fifth node N7 having the same size as the first reverse speed R of the third node N3, The line 7 is obtained by connecting the seventh node N7 at the position of the planetary carrier N5 at the position of the planetary carrier N5 and the line at the sixth node N6 corresponding to the planetary carrier 39, r) is in the second reverse position.

That is, this second reverse speed is decelerated again in the first reverse speed. That is, the speed is reduced from R to r.

In the neutral N range, the fifth and sixth frictional elements B2 and B3 are operated to prepare the first D range, while the power transmission of the engine 3 to the input shaft 15 is interrupted.

If the 'D' range is selected, the vehicle will automatically shift to 1, 2, 3 or 4 speed according to the operation of the accelerator pedal, and will be shifted from low speed to high speed.

First, in the 'D' range 1, the third and fifth friction elements C2 and B2 of the first transmission mechanism 17 and the first one-way clutch F1 are operated.

The fourth node N4 corresponding to the planetary carrier 29 of the double pinion planetary gear of the first transmission mechanism 17 is the input end and the second node N2 corresponding to the planetary carrier 29 is fixed And the first node N1 corresponding to the sun gear 19 of the single pinion planetary gear is the revolving element rotating in the reverse direction so that the second node N2 at any position of the fourth node N4, And the line D1 obtained by connecting the vertical line on the lever L at the third node N3 corresponding to the output end of the ring gear 30 is the first-order first speed.

This first-order first-speed is again shifted to the first-speed high-speed stage which is the same speed as the first-speed low-speed stage decelerated by the second transmission mechanism 31.

The fifth node N5 corresponding to the sun gear 35 is the input end and the sixth friction element B6 is operated and the seventh node N7 corresponding to the ring gear 43 And the seventh node N7 is connected to the straight line L1 'at the position of the fifth node N5 having the same size as the first-order first-order D1 of the third node N3 and opposite in direction, And the line D1 'obtained by connecting the vertical line on the lever 1 at the sixth node N6 corresponding to the planetary carrier 39, which is the output end thereof, becomes a first speed low speed stage.

The sixth friction element B3 is released and the second one-way clutch F2 is operated so that the sun gear 35 and the ring gear 43 are locked and the sun gear 35 and the ring gear 43 The fifth and seventh nodes N5 and N7 corresponding to the first node N1 and the seventh node N5 corresponding to the first node N1 and the seventh node N5 and N7 corresponding to the third node N3 are simultaneously input, N5 and N7 are connected by the straight line L1 and the line D1 obtained by connecting the vertical line on the lever 1 at the sixth node N6 corresponding to the planetary carrier 38, High-speed stage.

In the 'D' range 2, the third and second friction elements C2 and B1 of the first transmission mechanism 17 are actuated.

Accordingly, the fourth node N4 corresponding to the sun gear 21 of the double pinion planetary gear of the first transmission mechanism 17 becomes the input end and the first node N1 corresponding to the sun gear 19 of the single- And the second node N2 corresponding to the planetary carrier 29 becomes the idle element so that the first node N1 is connected to the straight line L2 at an arbitrary position of the fourth node N4, And a line D2 obtained by connecting the vertical line on the lever L at the third node N3 corresponding to the ring gear 30 serving as the output end thereof is the second order primary.

This first-order second-speed is shifted again to the second-speed high-speed stage which is the same speed as the second-speed low-speed stage decelerated by the second transmission mechanism 31. [

The fifth node N5 corresponding to the sun gear 35 serves as the input end and the sixth friction element B6 serves as the input end and the seventh node N7 corresponding to the ring gear 43 The seventh node N7 is connected to the straight line L2 'at the position of the fifth node N5 having the same size as the first-order second-speed D1 of the third node N3 and the opposite direction, And the line D2 'obtained by connecting the vertical line on the lever 1 at the sixth node N6 corresponding to the planetary carrier 39, which is the output end thereof, becomes a first speed low speed stage.

The sixth friction element B3 is released and the second one-way clutch F2 is operated so that the sun gear 35 and the ring gear 43 are locked and the sun gear 35 and the ring gear 43 And the fifth and seventh nodes N5 and N7 corresponding to the third node N3 and the seventh and ninth nodes N5 and N7 corresponding to the third node N3 are simultaneously input to the first and second nodes D3 and D3, N5 and N7 are connected by a straight line L2 and a line D2 obtained by connecting the vertical line on the lever 1 at a sixth node N6 corresponding to the planetary carrier 38 as an output terminal thereof is connected to a second High-speed stage.

In the 'D' range 3, the third and fourth friction elements C2 and B3 of the first transmission mechanism 17 are actuated.

The fourth node N4 corresponding to the sun gear 21 of the double pinion planetary gear of the first transmission mechanism 17 and the second node N2 corresponding to the planetary carrier 29 become the input ends, The same arbitrary position of the fourth node N4 and the second node N2 is connected by a straight line L3 and the sun gear 19 of the planetary gear is connected to the ring gear 30 And the line D3 obtained by connecting the vertical line on the lever L at the corresponding third node N3 becomes the first-order third speed.

The first-order third-speed is shifted again to the third-speed high-speed stage, which is the same speed as the third-speed low-speed stage decelerated by the second transmission mechanism 31. [

The fifth node N5 corresponding to the sun gear 35 is the input end and the sixth friction element B6 is operated and the seventh node N7 corresponding to the ring gear 43 And the seventh node N7 is connected to a straight line L3 'at a position of the fifth node N5 whose size is the same as the first-order third speed D3 of the third node N3 and the direction is opposite, And the line D3 'obtained by connecting the vertical line on the lever 1 at the sixth node N6 corresponding to the planetary carrier 39, which is the output terminal thereof, becomes a third speed low speed stage.

The third frictional element B3 is released and the second one-way clutch F2 is operated so that the sun gear 35 and the ring gear 43 are locked and the sun gear 35 and the ring gear 43 The fifth and seventh nodes N5 and N7 corresponding to the third node N3 and the third and fourth nodes N3 and N3 corresponding to the third node N3 are simultaneously input to the first and third nodes D3 and D3, N5 and N7 are connected by the straight line L3 and the line D3 obtained by connecting the vertical line on the lever 1 at the sixth node N6 corresponding to the planetary carrier 38, High-speed stage.

In the 'D' range 4, the fourth and second friction elements C3 and B1 of the first transmission mechanism 17 are actuated.

Therefore, the second node N2 corresponding to the sun gear 21 of the double pinion planetary gear of the first transmission mechanism 17 becomes the input end, the sun gear 19 of the single pinion planetary gear becomes the fixed end, The sun gear 19 of the planetary gear serves as a revolving element so that an arbitrary position of the first node N1 and the second node N2 thereof is connected by a straight line L4 and corresponds to the ring gear 30, The line D4 obtained by connecting the vertical line on the lever L at the third node N3 is the first-order fourth-order.

The first-order fourth-speed is shifted again to the fourth-speed high-speed stage which is the same speed as the fourth-speed low-speed stage decelerated by the second transmission mechanism 31. [

The fifth node N5 corresponding to the sun gear 35 is the input end and the sixth friction element B6 is operated and the seventh node N7 corresponding to the ring gear 43 And the seventh node N7 is connected to the straight line L4 'at the position of the fifth node N5 whose size is the same as the first-order fourth speed D4 of the third node N3 and the direction is opposite, And the line D4 'obtained by connecting the vertical line on the lever 1 at the sixth node N6 corresponding to the planetary carrier 39 as the output terminal thereof becomes the fourth speed low speed stage.

The sixth friction element B3 is released and the second one-way clutch F2 is operated so that the sun gear 35 and the ring gear 43 are locked and the sun gear 35 and the ring gear 43 The fifth and seventh nodes N5 and N7 corresponding to the first node 4 and the fourth node N4 corresponding to the first node 4 and the fourth node N4 having the same size as the first node 4 and having the same size as the first node 4, N5 and N7 are connected by the straight line L4 and the line D4 obtained by connecting the vertical line on the lever 1 at the sixth node N6 corresponding to the planetary carrier 38, High-speed stage.

[Effects of the Invention]

As described above, in the automatic transmission for a vehicle according to the present invention, one of the first, second, third, and fourth speeds is changed from the low speed to the high speed to increase the number of speed change stages by the second transmission mechanism, So that the torque efficiency and the shift feeling can be increased.

Claims (1)

A single pinion planetary gear unit and a double pinion planetary gear unit which are connected to the turbine side of the torque converter and determine the forward and reverse rotation directions and the respective gear stages by the operation of the respective frictionally controlled hydraulic members and share the ring gear as an output element The sun gear of the single pinion planetary gear is selectively connected to the transmission housing by the second friction member and the first one-way clutch so as to be selectively connected to the input shaft via the first friction member and the reaction element and the revolving element, The sun gear of the double pinion planetary gear is connected to the input shaft via the third friction member, the planetary carrier is selectively connected to the input shaft via the fourth friction member on one side thereof, and the sun gear of the double pinion planetary gear is selectively connected to the input shaft via the fourth friction member, A first transmission mechanism selectively connected to the housing, and a second transmission mechanism And a second transmission mechanism for increasing the number of gear stages by transmitting the rotational speeds of the respective gear stages outputted from the second transmission mechanism and decelerating the rotational speeds of the respective gear stages to transmit the driving force to the drive shaft, And the sun gear is mounted on a transfer shaft which receives a driving force from the first transmission mechanism, the planetary carrier is connected to a transfer drive gear, and the ring gear is connected to one side of the transfer gear by a second one- And is selectively connected to the transmission housing via a sixth frictional element on the other side of the automatic transmission.