KR20130039350A

KR20130039350A - Multi stage automatic transmission

Info

Publication number: KR20130039350A
Application number: KR1020110101792A
Authority: KR
Inventors: 현경열
Original assignee: (주)유티글로벌
Priority date: 2011-10-06
Filing date: 2011-10-06
Publication date: 2013-04-22

Abstract

PURPOSE: An automatic multilevel transmission is provided to have a compact size by comprising two multilevel transmission parts in one transmission shaft. CONSTITUTION: Multiple input side gears(30) rotate an input shaft(20). Multiple output side gears(50) rotate an output shaft(40). Multiple first transmission gears(60) form a non-circular first cam space inside. A second transmission gears(70) form a non-circular second cam space inside. A transmission shaft(80) is arranged between the first cam space and the second space. A first transmission part selectively controls the connection of the multiple first transmission gears and multiple input side gears. A second transmission part delivers the rotatory power of the transmission shaft to the output shaft. The second transmission part selectively controls the connection of the multiple second transmission gears and multiple output side gears.

Description

Multi-speed automatic transmission {MULTI STAGE AUTOMATIC TRANSMISSION}

The present invention relates to a multi-stage automatic transmission, and more particularly, to a multi-stage automatic transmission having two multi-stage transmission units that are independent of each other on one transmission shaft, and to realize various shift ranges by a combination of two multi-stage transmission units. It is about.

BACKGROUND OF THE INVENTION [0002] The multi-speed gearbox mechanism of an automatic transmission, which is applied to vehicles and industrial machines, usually consists of a combination of a plurality of planetary gear sets.

When a plurality of planetary gear sets are combined, a gear train performs a function of shifting a multi-stage transmission to a output side when rotational power is input from a torque converter that converts and transmits engine torque.

The power train of such an automatic transmission is known to be advantageous in terms of power performance and fuel consumption rate as the more gear stages are retained. Therefore, the research on the gear train that can realize more shift stages continues.

However, even if the same shift stage is implemented, the durability, power transmission efficiency, size, and weight vary greatly depending on the combination method of the planetary gear set. Therefore, the development of a gear train that is more robust and compact while minimizing power loss can be achieved. Efforts are ongoing.

Currently, the development direction of the gear train using the planetary gear set is how to combine the existing single pinion planetary gear set and the double pinion planetary gear set, and how to put the clutches, brakes, and one-way clutch in any position The focus is on whether the dog can be deployed to achieve the desired speed and hence the transmission ratio without any possible power loss.

On the other hand, in the case of the manual transmission, too many shift stages may cause inconvenience that the driver must shift frequently.

However, in the case of an automatic transmission, the computer transmission control unit (CJU) automatically controls the operation of the gear train in accordance with the driving state to perform the shift. Therefore, developing a gear train that can realize more shift stages is possible. It is a very important value.

For example, in the case of a conventional automatic transmission for a six-speed or eight-speed transmission, six or eight pairs of external gears, which are rotated in opposite directions to each other by an input shaft and an output shaft, And 6-speed or 8-speed shifting has been carried out by selecting a desired one of the pair of external differentials among 6 or 8 pairs of external differentials.

However, in order to increase the range of the shift, such conventional automatic transmissions are required to mount a differential gear by a desired number of shift stages along the longitudinal direction of the input shaft and the output shaft, thereby increasing the size of the automatic transmission and limiting the implementation of various shift ranges There is a problem.

An object of the present invention is to provide a multi-stage automatic transmission in which the size of the transmission becomes compact and various shift ranges can be realized.

The above object is achieved by an input device comprising: an input shaft; A plurality of input side gears fixed in a radially outer side of the input shaft and rotating together with the input shaft; An output shaft; A plurality of output-side gears fixed in a radially outer side of the output shaft and rotating together with the output shaft; A plurality of first transmission gears whose outer surfaces are tooth-engaged to rotate in opposite directions with the plurality of input side gears, and wherein a non-circular first cam space is formed therein; A plurality of second transmission gears whose outer surfaces are tooth-engaged to rotate in opposite directions with the plurality of output side gears, and wherein a non-circular second cam space is formed therein; A shift shaft disposed in the first cam space and the second cam space in a state in which the plurality of first transmission gears and the plurality of second transmission gears are separated from each other; Selectively controlling the connection of the plurality of input side gears and the plurality of first transmission gears so that the shift shaft rotates by shifting by a pair of gears selected from the plurality of input side gears and the plurality of first transmission gears. A first transmission unit; The plurality of output side gears and the plurality of second transmission gears are shifted by a pair of gears selected from the plurality of output side gears and the plurality of second transmission gears, and transmit rotational force of the transmission shaft to the output shaft. It is achieved by a multi-stage automatic transmission characterized in that it comprises a second transmission for selectively controlling the.

Here, the transmission shaft is formed with a receiving chamber, characterized in that it comprises a passage passage rod inserted into the receiving chamber and connected to the transmission shaft.

The first transmission portion may include: a plurality of first communication paths formed on the outer surface of the transmission shaft in communication with the accommodation chamber in a circumferential direction so as to correspond to the plurality of first transmission gears, respectively; A plurality of first flow passages provided inside the flow passage passage rod and communicating with the plurality of first communication passages and corresponding ones; A plurality of first pistons reciprocally coupled to the plurality of first communication paths, the plurality of first pistons being operated by hydraulic pressure provided to the first flow paths; A plurality of first connecting pins connected to the plurality of first pistons to be in close contact with the first transmission gear based on the operation of the first pistons; A first corresponding to the first connecting pin such that the rotational force of the selected input side gear is transmitted to the shift shaft by bringing the corresponding first connecting pin of the first transmission gear corresponding to any one selected from the plurality of input side gears into close contact; And a control unit for controlling the supply of hydraulic pressure to the flow path.

The second transmission portion may include: a plurality of second communication paths formed on the outer surface of the transmission shaft so as to correspond to the plurality of second transmission gears so as to communicate with the accommodation chamber along the circumferential direction; A plurality of second flow passages provided inside the flow passage passage rod and communicating with the plurality of second communication passages and corresponding ones; A plurality of second pistons reciprocally coupled to the plurality of second communication paths, the plurality of second pistons being operated by hydraulic pressure provided to the second flow paths; A plurality of second connecting pins connected to the plurality of second pistons to closely contact and release the second transmission gear based on the operation of the second pistons; A second flow path corresponding to the second connecting pin such that the rotational force of the transmission shaft is transmitted to the output shaft by bringing the corresponding second connecting pin of the second transmission gear corresponding to any one selected from the plurality of output side gears into close contact; And a control unit for controlling the supply of hydraulic pressure.

The plurality of first connecting pins may be arranged at equal intervals along the circumferential direction with respect to the accommodation chamber.

The plurality of second connecting pins may be arranged at equal intervals along the circumferential direction with respect to the accommodation chamber.

According to the present invention, by providing two multi-speed transmission units that are independent of each other on one transmission shaft provided between the input shaft and the output shaft, the size of the transmission becomes compact, and various transmission ranges can be realized by a combination of the two multi-speed transmission units.

1 is a schematic internal structural diagram of a multi-stage automatic transmission according to an embodiment of the present invention,
FIG. 2 is a view illustrating an arrangement state between an input gear, a first gear, a second gear, and an output gear of FIG. 1;
3 is an exploded perspective view of a first gear shift gear and a second gear shift gear in FIG. 1;
4 is a perspective view of the shift shaft of FIG. 1;
FIG. 5 is a layout view of an arrangement state between an input gear and a first transmission gear, in which a first transmission gear and a first connecting pin of FIG. 1 are connected to each other;
6 is an arrangement state structure diagram between an input gear and a first transmission gear in a state in which the first transmission gear and the first connecting pin of FIG. 1 are not connected;
FIG. 7 is a layout view of an arrangement state between an output side gear and a second transmission gear in a state in which a second transmission gear and a second connecting pin of FIG. 1 are connected;
FIG. 8 is a layout view of an arrangement state between an output gear and a second transmission gear, in which the second transmission gear and the second connecting pin of FIG. 1 are not connected.

Hereinafter, the present invention will be described in detail with reference to the accompanying drawings.

1 to 8 illustrate a multi-stage automatic transmission according to an embodiment of the present invention.

Referring to these drawings, but mainly referring to FIG. 1, the multi-stage automatic transmission of the present embodiment includes a main body housing 10, an input shaft 20 as an input side configuration, a plurality of input side gears 30, and an output shaft as an output side configuration ( 40) and the plurality of output side gears 50, the plurality of first transmission gears 60, the second transmission gear 70, the transmission shaft 80, the first transmission portion 100 and the second as the shifting configuration. It includes a transmission unit 110. Hereinafter, each configuration will be described.

First, the main body housing 10 is a part which forms the external appearance of the multistage automatic transmission of this embodiment. The body housing 10 may be made of a rigid metal material.

Most of the configuration is assembled in a form accommodated in the body housing 10. However, for operation, one region of the input shaft 20 and one region of the output shaft 40 are partially exposed to the outside of the main housing 10. Between the input shaft 20 and the main housing 10, between the output shaft 40 and the main housing 10, and between the shifting shaft 80 and the main housing 10, the passage passage rod 90 and the shifting shaft 80 Between the bearing 11 for smooth rotation is interposed. In addition, there is further interposed a packing 13 for sealing.

The input shaft 20 receives power for driving. The input power is output after being adjusted through the output shaft 40 by a structure to be described later. Acceleration may include both speed and torque.

The input side gear 30 is fixed in a pyramid shape on the radially outer side of the input shaft 20 and rotates together with the input shaft 20.

In the multi-stage automatic transmission according to the present embodiment, since the first transmission unit 100 has one reverse shift stage and three forward shift stages, a total of four pyramidal input gears 30 are provided. Since four input gears 30 are provided, a total of four first transmission gears 60 are also provided.

Of course, since this is one embodiment, the input side gear 30 and the first transmission gear 60 of this embodiment may be at least or more than four, in this case, the input side gear 30 and the first transmission gear 60. It is enough if it is provided with a corresponding number of stages.

Hereinafter, for the convenience of illustration and description, reference numerals by positions of the input side gear 30 and the first transmission gear 60 will not be distinguished, and will be described by giving letters and numbers to the drawings.

The output shaft 40 outputs the power input from the input shaft 20.

The output side gear 50 is fixed in a pyramid shape on the radially outer side of the output shaft 40 and rotates together with the output shaft 40.

In the multi-stage automatic transmission of the present embodiment, since the second transmission unit 110 has three shift stages, a total of three pyramidal output gears 50 are provided. Since the output side gear 50 is provided in total of three, the second transmission gear 70 corresponding thereto is also provided in total of three.

Of course, since this is one embodiment, the output side gear 50 and the second transmission gear 70 of this embodiment may be at least or more than three, in this case, the output side gear 50 and the second transmission gear 70. It is enough if it is provided with a corresponding number of stages.

Hereinafter, for convenience of illustration and description, the reference numerals for the positions of the output gear 50 and the second transmission gear 70 will not be distinguished, and will be described by giving letters and numbers to the drawings.

The plurality of first transmission gears 60 are provided in a pyramid shape similarly to the input side gear 30, but are tooth-engaged with the input side gear 30 one by one so as to rotate in the opposite direction to the input side gear 30. A non-circular first cam space 61 is formed inside the first transmission gear 60. In addition, the inner periphery of each of the first transmission gear 60 has a predetermined radius of curvature in the radially inward direction of the first transmission gear 60 at regular intervals, so that the first connecting pin 107 to be described below is held. A plurality of first catching jaws 63 are formed. In the present exemplary embodiment, four first locking jaws 63 are provided on the inner circumference of one first gear 60, but the number of first locking jaws 63 is not limited thereto.

The plurality of second transmission gears 70 are provided in a pyramid shape similarly to the output side gear 50, but are tooth-engaged with the output side gear 50 one by one so as to rotate in the opposite direction to the output side gear 50. A non-circular second cam space 71 is formed inside the second transmission gear 70. In addition, the inner circumference of each second transmission gear 70 has a predetermined radius of curvature in the radially inward direction of the second transmission gear 70 at regular intervals, so that the second connection pin 117 to be described below is held. A plurality of second catching jaws 73 are formed. In the present embodiment, four second locking jaws 73 are provided on the inner circumference of one second transmission gear 70, but the number of second locking jaws 73 is not limited thereto.

The shift shaft 80 is parallel to the input shaft 20 and the output shaft 40, and the first cam space is separated from each of the plurality of first transmission gears 60 and the plurality of second transmission gears 70, respectively. 61 and the second cam space 71 is disposed. An accommodation chamber 81 is formed inside the transmission shaft 80, and a passage passage rod 90 connected to the transmission shaft 80 is inserted into the accommodation chamber 81.

One region of the passage passage rod 90 is provided in the accommodating chamber 81 of the transmission shaft 80, and the other region has a rod shape exposed to the outside of the main body housing 10.

The passage passage rod 90 is coupled to the shift shaft 80, and the passage passage rod 90 is manufactured in a state separated from the shift shaft 80, and then may be keyed or fitted to each other. However, since the scope of the present invention does not need to be limited thereto, the passage passage rod 90 and the shift shaft 80 may be integrated.

On the other hand, since the transmission shaft 80 is provided in a state separated from the first transmission gear 60, the transmission shaft 80 does not rotate even if the input gear 30 is rotated. However, the transmission shaft 80 may be rotated only when the transmission shaft 80 is connected to any one of the first transmission gears 60 by the first transmission unit 100 by a structure and an operation to be described later.

In order to realize the operation thereof, the plurality of input side gears 30 are shifted by a pair of gears selected from the plurality of input side gears 30 and the plurality of first transmission gears 60 and the shift shaft 80 rotates. And selectively control the connection of the plurality of first transmission gears 60.

The first transmission portion 100 includes a plurality of first communication paths 101, a plurality of first flow paths 103, a plurality of first pistons 105, and a plurality of first connection pins 107. The control unit 120 includes.

The plurality of first communication paths 101 are formed on the outer surface of the transmission shaft 80 so as to correspond to the plurality of first transmission gears 60 so as to communicate with the housing chamber 81 along the circumferential direction. The plurality of first communication paths 101 are arranged on the outer surface of the transmission shaft 80 around the storage chamber 81 at equal intervals along the circumferential direction.

The plurality of first flow paths 103 are formed inside the flow path passageway 90 to communicate with the plurality of first communication paths 101 and corresponding ones. Each first flow path 103 is connected to each hydraulic supply pipe 125 by a rotary joint (not shown), and each hydraulic supply pipe 125 is connected to the hydraulic pump 127. The controller 120 controls ON / OFF of a solenoid valve (not shown) provided in each of the hydraulic supply pipes 125 to select any one of the first flow paths selected from the plurality of first flow paths 103 ( Supply hydraulic pressure to 103).

The plurality of first pistons 105 are reciprocally coupled to the plurality of first communication paths 101 and are operated by hydraulic pressure provided to the first channel path 103. As shown in FIG. 1, the plurality of first pistons 105 are reciprocally coupled to each of the first communication paths 101 of the transmission shaft 80 and connected to a corresponding stage of the first transmission gear 60. When the hydraulic pressure flows into the first communication path 101 of the transmission shaft 80, the radially outer side is operated to press the first connecting pins 107 connected to the first piston 105 radially outward. Do it. Of course, when the pressure is released, the first piston 105 and the first connecting pins 107 are returned to their original positions.

The plurality of first connecting pins 107 are connected to the plurality of first pistons 105 and move radially outwardly based on the operation of the first pistons 105 and are formed on the inner circumference of the first transmission gear 60. Close contact and release. The first connection pins 107 may be provided to correspond to the first piston 105 one by one.

In the present embodiment, the first connecting pin 107 is disposed to be accessible to the first communication path 101 formed on the transmission shaft 80. In the present embodiment, four first connecting pins 107 are provided at spaced intervals along the circumferential direction of the transmission shaft 80 to correspond to the first transmission gear 60 of the corresponding stage.

These first connecting pins 107 serve to keep in close contact with any one selected from the first transmission gear 60 of the fourth stage.

For example, when the hydraulic pressure is supplied to the second position as shown in FIG. 1 and the first pistons 105 of the second position are operated radially outwardly, the first connecting pins 107 of the second position are interlocked. The first transmission gear 60 in the second position is caught by the first catching jaw 63 of the first transmission gear 60 in the second position as the contact pressure is applied to the inner surface of the first transmission gear 60 in the second position. And the shift shaft 80 form a body, the shift shaft 80 is shifted and rotated by the gear ratio of the input gear 30 in the second position and the first transmission gear 60 in the second position. do. At this time, the remaining first transmission gears 60 idle.

The multistage automatic transmission of the present embodiment is configured to enable such a series of structures, that is, any one selected from the plurality of first transmission gears 60 and the transmission shaft 80 so that the transmission shaft 80 rotates. The control unit 120 for controlling the supply path of the hydraulic pressure supplied to the passage passage rod 90 from the (). That is, the control unit 120 is in close contact with the first connecting pin 107 of the first transmission gear 60 corresponding to any one selected from the plurality of input side gear 30, the rotational force of the selected input side gear 30 The supply of the hydraulic pressure supplied to the first passage passage 103 and the first communication passage 101 corresponding to the first connecting pin 107 from the hydraulic pump 127 is transmitted to the transmission shaft 80.

In addition, since the transmission shaft 80 is provided in a state separated from the second transmission gear 70, the second transmission gear 70 and the output shaft 40 do not rotate even when the transmission shaft 80 rotates. However, the second transmission gear 70 and the output shaft 40 only when the transmission shaft 80 is connected to any one of the second transmission gear 70 by the second transmission unit 110 by the structure and operation to be described later. Can be rotated.

In order to implement the operation thereof, the plurality of second transmission gears 70 and the gears are shifted by a pair of gears selected from the plurality of second transmission gears 70 and the output side gear 50 and the output shaft 40 rotates. The connection of the output gear 50 is selectively controlled.

The second transmission unit 110 includes a plurality of second communication paths 111, a plurality of second flow paths 113, a plurality of second pistons 115, a plurality of second connection pins 117, and The control unit 120 includes. Here, the control unit of the second transmission unit 110 is the same as the control unit 120 of the first transmission unit 100 described above.

The plurality of second communication paths 111 are formed in communication with the housing chamber 81 along the circumferential direction on the outer surface of the transmission shaft 80 so as to correspond to the plurality of second transmission gears 70, respectively. The plurality of second communication paths 111 are arranged on the outer surface of the transmission shaft 80 at equal intervals along the circumferential direction with the accommodation chamber 81 as the center.

The plurality of second flow paths 113 are formed inside the flow path passageway 90 to communicate with the plurality of second communication paths 111 and corresponding ones. Each second flow passage 113 is connected to each hydraulic supply pipe 125 by a rotary joint (not shown), and each hydraulic supply pipe 125 is connected to the hydraulic pump 127. The controller 120 controls ON / OFF of a solenoid valve (not shown) provided in each of the hydraulic supply pipes 125 to select any one of the second flow paths selected from the plurality of second flow paths 113. Supply hydraulic pressure to 113).

The plurality of second pistons 115 are reciprocally coupled to the plurality of second communication paths 111 and are operated by hydraulic pressure provided to the second flow paths 113. As shown in FIG. 1, the plurality of second pistons 115 are reciprocally coupled to the respective second communication paths 111 of the transmission shaft 80, and are connected to the corresponding stages of the second transmission gear 70. When the hydraulic pressure flows into the second communication path 111 of the formed shift shaft 80, the radially outer side is operated to press the second connecting pins 117 connected to the second piston 115 to the radially outer side. Do it. Of course, when the pressure is released, the second piston 115 and the second connecting pins 117 are returned to their original positions.

The plurality of second connecting pins 117 are connected to the plurality of second pistons 115 and move radially outward based on the operation of the second pistons 115 and are formed on the inner circumference of the second transmission gear 70. Close contact and release. The second connection pins 117 may be provided to correspond to the second piston 115 one by one.

In the present embodiment, the second connecting pin 117 is disposed to be accessible to the second communication path 111 formed on the transmission shaft 80. In the present embodiment, four second connecting pins 117 are provided at spaced intervals along the circumferential direction of the transmission shaft 80 to correspond to the second transmission gear 70 of the corresponding stage.

These second connecting pins 117 serve to keep in close contact with any one selected from the third speed gear 70 of the three stages.

For example, when the hydraulic pressure is supplied to the "C" position as shown in FIG. 1 and the second pistons 115 of the "C" position are operated radially outward, the second connection pin of the "C" position ( 117 are pressed against the inner surface of the second transmission gear 70 in the "C" position to catch the second catching jaw 73 of the second transmission gear 70 in the "C" position, and thus the first position in the "C" position. Since the two transmission gear 70 and the transmission shaft 80 form a body, the output shaft 40 is connected to the gear ratio of the second transmission gear 70 in the "C" position and the output side gear 50 in the "C" position. It shifts and can rotate. At this time, the remaining second transmission gears 70 idle.

In order to enable such a series of structures, that is, any one selected from the plurality of second transmission gears 70 and the transmission shaft 80 are connected so that the output shaft 40 rotates, that is, the control unit 120 includes a plurality of second transmissions. The second connecting pin 117 of the output gear 50 corresponding to the selected one of the gears 70 is brought into close contact with each other so that the rotational force of the selected second transmission gear 70 and the output gear 50 is output to the output shaft 40. The supply of the hydraulic pressure supplied to the second passage passage 113 and the second communication passage 111 corresponding to the corresponding second connection pin 117 from the hydraulic pump 127 to be transmitted to.

Looking at the operation and the shifting operation of the multi-stage automatic transmission according to an embodiment of the present invention having such a configuration as follows.

As shown in FIG. 1 by the controller 120, when the hydraulic pressure is supplied to the position 2 of the first transmission unit 100 and the position “C” of the second transmission unit 110 simultaneously, 5, the pistons 105 are operated radially outward, and the first connecting pins 107 in position 2 are pressed against the inner surface of the first transmission gear 60 in position 2. As described above, the first transmission gear 60 and the transmission shaft 80 of the second position are caught by the first locking jaw 63 of the first transmission gear 60 of the second position to form a body. 80 is shifted and rotated by the gear ratio of the input gear 30 in the second position and the first transmission gear 60 in the second position. At this time, since the hydraulic pressure is not supplied to the first flow path 103 of the remaining first transmission gears 60 by the controller 120, the controller 120 corresponds to the remaining first transmission gears 60 as shown in FIG. 6. The first connecting pins 107 are not caught by each of the first catching jaws 63 of the remaining first transmission gear 60, so that the remaining first transmission gears 60 idle.

At the same time, the first pistons 105 in the "C" position are operated radially outwards, and the second connecting pins 117 in the "C" position are connected to the second transmission gear 70 in the "C" position. As the contact pressure is applied to the inner surface, as shown in FIG. 80 forms one body, and the output shaft 40 is shifted and rotated by the gear ratio of the second transmission gear 70 in the "C" position and the output gear 50 in the "C" position. At this time, since the hydraulic pressure is not supplied to the second flow path 113 of the remaining second transmission gears 70 by the controller 120, the controller 120 corresponds to the remaining second transmission gears 70 as shown in FIG. 8. The second connecting pins 117 are not caught by the second catching jaws 73 of the remaining second transmission gears 70, and the remaining second transmission gears 70 idle.

Therefore, the power input through the input shaft 20 is input gear 30 of the selected position 2 and the corresponding first transmission gear 60, the transmission shaft 80, the second transmission gear of the selected "C" position 70 and the output side gear 50 and the output shaft 40 corresponding thereto are sequentially output through the output shaft 40.

On the other hand, in the process of transmitting power from the input shaft 20 to the output shaft 40, the rotation speed of the input shaft 20 is driven by the input side gear 30 and the first transmission gear 60 corresponding thereto in the selected second position The first shift is transmitted to the transmission shaft 80, and the rotation speed of the primary shift transmission shaft 80 is controlled by the second transmission gear 70 at the selected " C " position and the output gear 50 corresponding thereto. The secondary shaft is shifted, and the output shaft 40 rotates at the finally rotated secondary speed.

That is, as an example, the gear ratio of the input side gear 30 in the second position and the first transmission gear 60 corresponding thereto is 1: 2, and the second transmission gear 70 in the “C” position and corresponding thereto When the transmission ratio of the output gear 50 is 1: 3, the rotation speed of the input shaft 20 is shifted at a ratio of 1: 6, which is a product of the transmission ratios of the first transmission unit 100 and the second transmission unit 110, The output shaft 40 is rotated at a gear ratio of 1: 6 with respect to the rotational speed of the input shaft 20.

On the other hand, the reverse drive of the multi-stage automatic transmission according to the present invention will be described.

When the hydraulic pressure is simultaneously supplied to the reverse position of the first transmission portion 100 and the "C" position of the second transmission portion 110 by the controller 120, the first pistons 105 of the reverse position are radially outward. As the first connection pins 107 in the reverse position are pressed against the inner surface of the first transmission gear 60 in the reverse position, the first transmission gear in the reverse position as shown in FIG. The first transmission gear 60 and the shifting shaft 80 of the reverse position are caught by the first catching jaw 63 of 60, and the shifting shaft 80 is connected to the input side gear 30 of the reverse position. The gear ratio of the first transmission gear 60 in the reverse position is shifted and rotated. At this time, since the hydraulic pressure is not supplied to the first flow path 103 of the remaining first transmission gears 60 by the controller 120, the controller 120 corresponds to the remaining first transmission gears 60 as shown in FIG. 6. The first connecting pins 107 are not caught by each of the first catching jaws 63 of the remaining first transmission gear 60, so that the remaining first transmission gears 60 idle.

At the same time, the first pistons 105 in the "C" position are operated radially outwards, and the second connecting pins 117 in the "C" position are connected to the second transmission gear 70 in the "C" position. As the contact pressure is applied to the inner surface, as shown in FIG. 7, the second transmission gear 70 and the transmission shaft of the "C" position are caught by the second locking jaw 73 of the second transmission gear 70 of the "C" position. 80 forms one body, and the output shaft 40 is shifted and rotated by the gear ratio of the second transmission gear 70 in the "C" position and the output gear 50 in the "C" position. At this time, since the hydraulic pressure is not supplied to the second flow path 113 of the remaining second transmission gears 70 by the controller 120, the controller 120 corresponds to the remaining second transmission gears 70 as shown in FIG. 8. The second connecting pins 117 are not caught by the second catching jaws 73 of the remaining second transmission gears 70, and the remaining second transmission gears 70 idle.

Accordingly, the reverse driving force input through the input shaft 20 is the input gear 30 of the selected reverse position and the corresponding first gear 60, the gear shaft 80, the second gear of the selected "C" position. 70 and the output side gear 50 and the output shaft 40 corresponding thereto are sequentially output through the output shaft 40, the multi-stage automatic transmission according to the present invention is to drive backward.

Therefore, in the multi-stage automatic transmission in the present embodiment, since the first shift speed is composed of 1 reverse gear and 3 forward gear speeds, and the second gear speed is composed of 3 gears, the combination of the first gear speed and the second gear speed is made. By this, a total of nine shifts and one reverse stage can be realized.

That is, the multi-stage automatic transmission according to the present invention may be variously adjusted by adjusting the first and second gearshift speeds, thereby realizing a variety of shift ranges by combining the first and second gearshift speeds.

Thus, according to the present invention, by providing two multi-speed transmission units that are independent of each other on one transmission shaft provided between the input shaft and the output shaft, the size of the transmission is compact, the combination of the two multi-stage transmission unit to vary the range of the transmission range It can be implemented.

It will be apparent to those skilled in the art that various modifications and variations can be made in the present invention without departing from the spirit or scope of the invention. Accordingly, such modifications or variations are intended to fall within the scope of the appended claims.

10: main body housing 20: input shaft
30: input gear 40: output shaft
50: output side gear 60: first transmission gear
70: second transmission gear 80: shift shaft
90: passage passage rod 100: first transmission portion
101: first passage 103: first passage
105: first piston 107: first connecting pin
110: second transmission portion 111: second communication path
113: second euro passage 115: second piston
117: second connection pin 120: control unit

Claims

An input shaft;
A plurality of input side gears fixed in a radially outer side of the input shaft and rotating together with the input shaft;
An output shaft;
A plurality of output-side gears fixed in a radially outer side of the output shaft and rotating together with the output shaft;
A plurality of first transmission gears whose outer surfaces are tooth-engaged to rotate in opposite directions with the plurality of input side gears, and wherein a non-circular first cam space is formed therein;
A plurality of second transmission gears whose outer surfaces are tooth-engaged to rotate in opposite directions with the plurality of output side gears, and wherein a non-circular second cam space is formed therein;
A shift shaft disposed in the first cam space and the second cam space in a state in which the plurality of first transmission gears and the plurality of second transmission gears are separated from each other;
Selectively controlling the connection of the plurality of input side gears and the plurality of first transmission gears so that the shift shaft rotates by shifting by a pair of gears selected from the plurality of input side gears and the plurality of first transmission gears. A first transmission unit;
The plurality of output side gears and the plurality of second transmission gears are shifted by a pair of gears selected from the plurality of output side gears and the plurality of second transmission gears, and transmit rotational force of the transmission shaft to the output shaft. Multi-stage automatic transmission comprising a second transmission for selectively controlling the.

The method of claim 1,
The transmission shaft is formed in the accommodation chamber, the multi-stage automatic transmission characterized in that it comprises a passage passage rod inserted into the accommodation chamber and connected to the transmission shaft.

The method of claim 2,
The first transmission portion,
A plurality of first communication paths formed on the outer surface of the transmission shaft so as to correspond to the plurality of first transmission gears so as to communicate with the accommodation chamber along the circumferential direction;
A plurality of first passage passages provided in the passage passage rods and communicating with the plurality of first passage passages and corresponding ones;
A plurality of first pistons reciprocally coupled to the plurality of first communication paths, the plurality of first pistons being operated by hydraulic pressure provided to the first flow paths;
A plurality of first connecting pins connected to the plurality of first pistons to close and close contact with the first transmission gear based on an operation of the first piston;
A first corresponding to the first connecting pin such that the rotational force of the selected input side gear is transmitted to the shift shaft by bringing the corresponding first connecting pin of the first transmission gear corresponding to any one selected from the plurality of input side gears into close contact; A multistage automatic transmission comprising a control unit for controlling the supply of hydraulic pressure to the flow path.

The method of claim 2,
The second transmission portion,
A plurality of second communication paths formed on the outer surface of the transmission shaft so as to correspond to the plurality of second transmission gears so as to communicate with the accommodation chamber along the circumferential direction;
A plurality of second flow passages provided inside the flow passage passage rod and communicating with the plurality of second communication passages and corresponding ones;
A plurality of second pistons reciprocally coupled to the plurality of second communication paths, the plurality of second pistons being operated by hydraulic pressure provided to the second flow paths;
A plurality of second connecting pins connected to the plurality of second pistons to closely contact and release the second transmission gear based on the operation of the second pistons;
A second flow path corresponding to the second connecting pin such that the rotational force of the transmission shaft is transmitted to the output shaft by bringing the corresponding second connecting pin of the second transmission gear corresponding to any one selected from the plurality of output side gears into close contact; A multistage automatic transmission comprising a control unit for controlling the supply of hydraulic pressure.

The method of claim 3,
And the plurality of first connecting pins are arranged at equal intervals along the circumferential direction with respect to the accommodation chamber.

5. The method of claim 4,
And the plurality of second connection pins are disposed at equal intervals along the circumferential direction with respect to the accommodation chamber.