KR101344380B1 - Multi stage automatic transmission - Google Patents

Abstract

The present invention relates to a multi-stage automatic transmission, comprising: an input shaft; A plurality of input side gears fixed in a radially outer side of the input shaft in a pyramid shape and rotating together with the input shaft; An output shaft; A plurality of output side transmission gears disposed separately in the radially outer side of the output shaft; A first shift shaft and a second shift shaft disposed to face each other with the input shaft interposed therebetween; A plurality of first transmission gears that are tooth-engaged to rotate in opposite directions with the plurality of input side gears and are respectively disposed on the first transmission shaft; A plurality of second transmission gears which are tooth-engaged to rotate in opposite directions with the plurality of input side gears, and are disposed separated from each other on the second transmission shaft; A plurality of output side power transmission gears which are tooth-engaged to rotate in a direction opposite to the plurality of output side gears, and which are fixed to the first shift shaft and rotate together with the first shift shaft; A first for selectively controlling the connection of the plurality of input side gears and the plurality of first transmission gears so as to be shifted by a pair of gears selected from the plurality of input side gears and the plurality of first transmission gears and the first transmission shaft rotates. A transmission unit; A second for selectively controlling the connection of the plurality of input side gears and the plurality of second transmission gears so as to be shifted by a pair of gears selected from the plurality of input side gears and the plurality of second transmission gears and the second transmission shaft rotates. A transmission unit; Optionally, the connection of the plurality of output power transmission gears and the plurality of output transmission gears is shifted by a pair of gears selected from the plurality of output power transmission gears and the plurality of output transmission gears, and the rotational force of the first transmission shaft is transmitted to the output shaft. An output side transmission portion controlled by the controller; And a control unit configured to selectively control any one of the first transmission unit and the second transmission unit, and to shift the output side transmission unit.

Description

Multi-speed automatic transmission {MULTI STAGE AUTOMATIC TRANSMISSION}

The present invention relates to a multi-stage automatic transmission, and more particularly, to each of the two transmission shafts selectively connected to the input shaft, each having a multi-stage transmission independent of each other, and at the same time additionally provided a multi-stage transmission to the output shaft, The present invention relates to a multi-stage automatic transmission that can realize various shift ranges by a combination of a multi-speed transmission unit.

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 transmission gears disposed separately in the radially outer side of the output shaft; A first transmission shaft and a second transmission shaft disposed opposite to each other with the input shaft therebetween; A plurality of first transmission gears which are tooth-engaged to rotate in opposite directions to the plurality of input side gears and are respectively separated from the first transmission shafts; A plurality of second transmission gears that are toothed to rotate in opposite directions to the plurality of input side gears and are respectively separated from the second transmission shafts; A plurality of output side power transmission gears which are tooth-engaged to rotate in the opposite directions to the plurality of output side gears, and which are fixed to the first gear shaft and rotate together with the first gear shaft; The connection of the plurality of input side gears and the plurality of first transmission gears may be selectively shifted by a pair of gears selected from the plurality of input side gears and the plurality of first transmission gears to rotate the first transmission shaft. A first transmission portion controlled by; The connection of the plurality of input side gears and the plurality of second transmission gears may be selectively shifted by a pair of gears selected from the plurality of input side gears and the plurality of second transmission gears so that the second transmission shaft rotates. A second transmission part controlled by; The plurality of output side power transmission gears and the plurality of output sides so as to be shifted by a pair of gears selected from the plurality of output side power transmission gears and the plurality of output side transmission gears and to transmit rotational force of the first transmission shaft to the output shaft. An output side transmission portion for selectively controlling a connection of the transmission gear; And a control unit configured to selectively control any one of the first transmission unit and the second transmission unit, and to control the output side transmission unit.

Here, it characterized in that it comprises a power transmission unit for transmitting the rotational force of the second transmission shaft to the first transmission shaft.

The power transmission unit includes: a first power transmission gear coupled to the first transmission shaft and rotating together with the first transmission shaft; A second power transmission gear coupled to the second transmission shaft and rotating together with the second transmission shaft; And an idler gear rotatably supported by the input shaft and engaged with the first power transmission gear and the second power transmission gear to rotate respectively.

A first accommodation chamber is formed in the first transmission shaft, and a first passage passage rod is connected to the first transmission shaft in the first accommodation chamber, and a second accommodation chamber is formed in the second transmission shaft. The second receiving passage is provided with a second passage passage rod connected to the second transmission shaft, and the output shaft is formed with an output side accommodating chamber, and the output side accommodating chamber has an output side passage passage rod connected with the output shaft.

The first transmission portion may include: a plurality of first communication paths formed on the outer surface of the first transmission shaft to communicate with the first accommodation chamber along the circumferential direction so as to correspond to the plurality of first transmission gears, respectively; A plurality of first flow paths provided inside the first flow path rods and communicating with the plurality of first communication paths 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; And a plurality of first connecting pins connected to the plurality of first pistons to close and close the first transmission gear based on the operation of the first pistons, wherein the control unit is selected from the plurality of input side gears. The first connecting path of the first transmission gear corresponding to any one of the hydraulic pressure in the first passage passage corresponding to the first connecting pin so that the rotational force of the selected input side gear is transmitted to the first transmission shaft. It is characterized by controlling the supply.

The second transmission portion includes: a plurality of second communication paths formed on the outer surface of the second transmission shaft to communicate with the second accommodation chamber along the circumferential direction so as to correspond to the plurality of second transmission gears, respectively; A plurality of second flow paths provided in the second flow path rods and communicating with the plurality of second communication paths 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; And a plurality of second connecting pins connected to the plurality of second pistons to close and close the second transmission gear based on the operation of the second pistons, wherein the control unit selects one of the plurality of input side gears. The second passage passage corresponding to the second connecting pin is connected to the second channel so that the rotational force of the selected input side gear is transmitted to the second transmission shaft in close contact with the corresponding second connecting pin of the second transmission gear. It is characterized by controlling the supply.

The output side transmission section includes: a plurality of output side communication paths formed on the outer surface of the output shaft so as to correspond to the plurality of output side transmission gears so as to communicate with the output side receiving chamber along the circumferential direction; A plurality of output side flow paths provided in the output side flow path rods and communicating with the plurality of output side communication paths and corresponding ones; A plurality of output side pistons reciprocally coupled to the plurality of output side communication paths, the plurality of output side pistons being operated by hydraulic pressure provided to the output side flow paths; A plurality of output side connecting pins connected to the plurality of output side pistons to closely contact and release the output transmission gears based on the operation of the output side pistons, wherein the control unit is any one selected from the plurality of output power transmission gears. It is characterized in that the supply of the hydraulic pressure to the output side passage passage corresponding to the output side connecting pins so as to contact the output side connecting pins of the output transmission gear corresponding to the transmission force to the output shaft.

Reverse gears of the plurality of input side gears in charge of the reverse gear is characterized in that the coupling.

According to the present invention, the two transmission shafts provided between the input shaft and the output shaft are each independently provided with a multi-stage transmission section, and at the same time, the output shaft is provided with a multi-stage transmission section, whereby the size of the transmission becomes compact, and the combination of the three multi-stage transmission sections is provided. Various shift ranges can be realized.

1 is a schematic internal structural diagram showing a shifting process of a multistage automatic transmission according to the present invention;
Figure 2 is a schematic internal structure showing another shifting process of the multi-stage automatic transmission according to the present invention,
3 is a perspective view illustrating an arrangement state between an input gear, a first transmission gear, a second transmission gear, an output power transmission gear, and an output transmission gear except for the reverse rotation intermediate gear of FIG. 1;
4 is a side view illustrating an arrangement state between an input side gear, a first transmission gear, and a second transmission gear except for the reverse rotation intermediate gear of FIG. 1;
5 is a side view illustrating an arrangement state of the power transmission unit of FIG. 1;
6 is a perspective view of the output shaft of FIG.
7 is a perspective view of the first shift shaft of FIG. 1;
8 is a perspective view of a second shift shaft of FIG. 1;
FIG. 9 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;
FIG. 10 is a layout view of an arrangement state between an input gear and a first transmission gear, in which the first transmission gear and the first connecting pin of FIG. 1 are not connected.
FIG. 11 is a layout view of an arrangement state between an input gear and a second transmission gear, in which a second transmission gear and a second connecting pin of FIG. 1 are connected;
FIG. 12 is a layout view of an arrangement state between an input gear and a second transmission gear in a state in which the second transmission gear and the second connecting pin of FIG. 1 are not connected;
FIG. 13 is a layout view of an arrangement state between an output power transmission gear and an output transmission gear, in which the output transmission gear and the output connection pin of FIG. 1 are connected;
FIG. 14 is a configuration diagram illustrating an arrangement state between the output power transmission gear and the output transmission gear, in which the output transmission gear and the output connection pin of FIG. 1 are not connected.

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

1 to 14 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 has a main body 10, an input shaft 20 and a plurality of input side gears 30 as an input side configuration, and an output shaft (as an output side configuration). 40, the first shift shaft 60 and the second shift shaft 80, the plurality of first transmission gears 100, the plurality of second transmission gears 110, and the plurality of output side transmission gears ( 50, a plurality of output side power transmission gears 120, a first transmission unit 130, a second transmission unit 140, an output transmission unit 150, and a controller 160. 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 body housing 10, between the output shaft 40 and the body housing 10, and between each of the transmission shafts 60 and 80 and the body housing 10, each passage passage rod 45, 70, The bearing 11 for smooth rotation is interposed between the 90 and the body housing 10. In addition, there is further interposed a packing 13 for sealing.

The input shaft 20 receives power for driving. The input power is output through the output shaft 40 after being subtracted by the 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 of the present embodiment, since the first transmission unit 130 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 in total, four first transmission gears 100 corresponding thereto are also provided.

Of course, since this is one embodiment, the input side gear 30 and the first transmission gear 100 of this embodiment may be at least or more than four, in this case, the input side gear 30 and the first transmission gear 100. It is enough if it is provided with a corresponding number of stages.

In addition, in the multi-stage automatic transmission of the present embodiment, since the second transmission unit 140 has four forward shift stages, a total of four second transmission gears 110 are also provided corresponding to the input side gear 30.

Of course, since this is one embodiment, the second transmission gear 110 of the present embodiment may be at least or more than four, and the second transmission gear 110 is provided in the number of stages corresponding to the input side gear 30. that is enough.

Hereinafter, for convenience of illustration and description, reference numerals for the positions of the input gear 30, the first gear 100 and the second gear 110 are not distinguished from each other. To explain.

On the other hand, when moving forward while being freely shifted by each forward shift stage, there is a difference in speed and torque, but the rotation direction of the output shaft 40 is the same. However, in the case of reverse, the output shaft 40 should be rotated in the opposite direction. To this end, a reverse rotation intermediate gear 35 is coupled to a gear (represented by letters in the drawing) that is responsible for reversing among the plurality of input side gears 30.

The reverse rotation intermediate gear 35 further includes one gear between the input side gear 30, that is, the input side gear 30 and the first gear 30 so as to rotate in the opposite direction to the input side gear 30 and the first transmission gear 100. Tooth engagement with the first transmission gear 100, serves to reverse the rotation direction of the first transmission gear (100).

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

An output side accommodating chamber 41 is formed inside the output shaft 40, and an output side passage passage rod 45 connected to the output shaft 40 is inserted into the output side accommodating chamber 41 as illustrated in FIG. 6.

One region of the output side passage passage rod 45 is provided in the output side accommodating chamber 41 of the output shaft 40, and the remaining region has a rod shape exposed to the outside of the main housing 10. The output side passage passage rod 45 is coupled to the output shaft 40, and the output side passage passage rod 45 may be manufactured in a state separated from the output shaft 40, 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 output side passage passage rod 45 and the output shaft 40 may be integrated.

The output transmission gear 50 is arranged in a radially outer side of the output shaft 40 in a pyramid shape, respectively.

In the multi-stage automatic transmission of the present embodiment, since the output side transmission unit 150 has three shift stages, the output side transmission gear 50 is provided in total of three. Since the output transmission gear 50 is provided in total of three, the output power transmission gear 120 corresponding thereto is also provided in total of three.

Of course, since this is one embodiment, the output transmission gear 50 and the output power transmission gear 120 of the present embodiment may be at least or more than three, in this case, the output transmission gear 50 and the output power transmission gear ( 120 is provided if the number of stages corresponding thereto is sufficient.

Hereinafter, for convenience of illustration and description, reference numerals by positions of the output transmission gear 50 and the output transmission power transmission gear 120 will be described by giving letters and numbers to the drawings instead of distinguishing them.

On the other hand, the plurality of output side transmission gear 50 is toothed meshing with the output side power transmission gear 120 one by one to rotate in the opposite direction to the output side power transmission gear 120. Inside the output side gear 50, a non-circular output side cam space 51 through which the drive shaft 40 penetrates is formed. In addition, the inner periphery of each of the output transmission gear 50 has a predetermined radius of curvature in the radially inward direction of the output transmission gear 50 at a predetermined interval, protruding, a plurality of output side locking jaws that the output side connecting pin to be described later is held 53 is formed. In the present embodiment, four output side engaging jaws 53 are provided on the inner circumference of one output side gear 50, but the number of output side engaging jaws 53 is not limited thereto.

7 and 8 illustrate a first shift shaft 60 and a second shift shaft 80, respectively. The first shift shaft 60 and the second shift shaft 80 are disposed in parallel with the input shaft 20 with the input shaft 20 interposed therebetween. A plurality of first transmission gears 100 are disposed in a separated state on the first transmission shaft 60, and a plurality of second transmission gears 110 are disposed in a separate state on the second transmission shaft 80. .

The first accommodation chamber 61 is formed inside the first transmission shaft 60, and the first flow passage rod 70 connected to the first transmission shaft 60 is inserted into the first accommodation chamber 61. . In addition, a second accommodation chamber 81 is formed in the second transmission shaft 80, and a second flow path rod 90 connected to the second transmission shaft 80 is inserted in the second accommodation chamber 81. .

One region of the first passage passage rod 70 is provided in the first accommodation chamber 61 of the first transmission shaft 60, and the remaining region has a rod shape exposed to the outside of the main housing 10. The first flow path rod 70 is coupled to the first shift shaft 60, and the first flow path rod 70 is manufactured in a state separated from the first shift shaft 60, and then coupled or fitted with each other. It can be customized. However, since the scope of the present invention does not need to be limited thereto, the first passage passage rod 70 and the first transmission shaft 60 may be integrated.

In addition, one region of the second passage passage rod 90 is provided in the second accommodation chamber 81 of the second transmission shaft 80, and the remaining region has a rod shape exposed to the outside of the main housing 10. . The second flow path rod 90 is coupled to the second speed change shaft 80, and the second flow path rod 90 is manufactured to be separated from the second speed shift shaft 80, and then the keys are coupled or fitted to each other. It can be customized. However, since the scope of the present invention does not need to be limited thereto, the second passage passage rod 90 and the second transmission shaft 80 may be integrated.

The plurality of first transmission gears 100 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. The non-circular first cam space 101 through which the first transmission shaft 60 penetrates is formed in the first transmission gear 100. In addition, the inner circumference of each of the first transmission gear 100 has a predetermined radius of curvature in the radially inward direction of the first transmission gear 100 at regular intervals, and the first connection pin 137 to be described below is held. A plurality of first catching jaw 103 is formed. In the present embodiment, four first locking jaw 103 is provided on the inner circumference of one first gear 100, but the number of first locking jaw 103 is not limited thereto.

The plurality of second transmission gears 110 are provided in the same pyramid shape as 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. The non-circular second cam space 111 through which the second transmission shaft 80 penetrates is formed in the second transmission gear 110. In addition, the inner circumference of each second transmission gear 110 has a predetermined radius of curvature in the radially inner direction of the second transmission gear 110 at a predetermined interval to protrude, and the second connection pin 147 to be described below is held. A plurality of second catching jaw 113 is formed. In the present embodiment, four second locking jaws 113 are provided on the inner circumference of one second transmission gear 110, but the number of second locking jaws 113 is not limited thereto.

Meanwhile, the multi-stage automatic transmission according to the present invention includes a plurality of output side power transmission gears 120 that are fixed in a pyramid shape on the radially outer side of the first transmission shaft 60 and rotate together with the first transmission shaft 60. do.

The plurality of output side power transmission gears 120 are tooth-engaged with the output side gear 50 so as to rotate in a direction opposite to the plurality of output side gears 50 and rotate together with the first transmission shaft 60.

Meanwhile, in the multi-stage automatic transmission according to the present invention, as shown in FIG. 4, the first transmission shaft 60 is provided in a state in which the first transmission gear 100 is separated from the second transmission shaft 80. Since the second transmission gear 110 is provided in a separated state, the first gear shaft 60 and the second gear shaft 80 do not rotate even when the input gear 30 is rotated. However, when the first transmission shaft 60 is connected to any one of the first transmission gears 100 by the first transmission unit 130, the first transmission shaft 60 is rotated by a structure and operation which will be described later. In addition, the second transmission shaft 80 may be rotated when the second transmission shaft 80 is connected to any one of the second transmission gears 110 by the second transmission unit 140.

In order to implement the operation thereof, a shift process of the first transmission unit 130 will be described as follows.

The control unit 160 is shifted by a pair of gears selected from the plurality of input side gears 30 and the plurality of first transmission gears 100, and the plurality of input side gears ( 30) and selectively control the connection of the plurality of first transmission gears 100.

The first transmission unit 130 may include a plurality of first communication paths 131, a plurality of first flow paths 133, a plurality of first pistons 135, and a plurality of first connection pins 137. Include.

The plurality of first communication paths 131 are formed to communicate with the first accommodation chamber 61 along the circumferential direction on the outer surface of the first transmission shaft 60 so as to correspond to the plurality of first transmission gears 100, respectively. . The plurality of first communication paths 131 are arranged on the outer surface of the first transmission shaft 60 at equal intervals along the circumferential direction with respect to the first accommodation chamber 61.

The plurality of first flow paths 133 are formed inside the first flow path rod 70 and communicate with the plurality of first communication paths 131 and the corresponding ones. Each first flow path 133 is connected to each hydraulic supply pipe 161 by a rotary joint (not shown), each hydraulic supply pipe 161 is connected to the hydraulic pump 165. The control unit 160 controls the on / off solenoid valve (not shown) provided in each of the hydraulic supply pipes 161 so as to control any one of the first flow paths selected from the plurality of first flow paths 133. Supply hydraulic pressure to 133).

The plurality of first pistons 135 are reciprocally coupled to the plurality of first communication paths 131 and operate by hydraulic pressure provided to the first flow path 133. As shown in FIG. 1, the plurality of first pistons 135 are reciprocally coupled to each of the first communication paths 131 of the first transmission shaft 60, and corresponding to the first transmission gear 100. When hydraulic pressure flows into the first communication path 131 of the first transmission shaft 60 formed at the stage, the first connecting pins 137 connected to the first piston 135 are radially outer side while being operated radially outward. It serves to pressurize. Of course, when the pressure is released, the first piston 135 and the first connecting pins 137 are returned to their original positions.

The plurality of first connecting pins 137 are connected to the plurality of first pistons 135 to move radially outward based on the operation of the first piston 135 and to the inner circumference of the first transmission gear 100. Close contact and release. The first connection pin 137 may be provided to correspond to the first piston 135 one by one.

In this embodiment, the first connecting pin 137 is disposed to be accessible to the first communication path 131 formed on the first transmission shaft 60. In the present embodiment, four first connecting pins 137 are provided at spaced intervals along the circumferential direction of the first transmission shaft 60 to correspond to the first transmission gear 100 of the corresponding stage.

These first connection pins 137 serves to keep in close contact with any one selected from the first gear 100 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 135 of the second position are operated radially outward, the first connecting pins 137 of the second position are interlocked. As contact and pressure is applied to the inner surface of the first transmission gear 100 in the second position, the second position is caught by the first locking jaw 103 of the first transmission gear 100 in the second position as shown in FIG. 9. Since the first transmission gear 100 and the first transmission shaft 60 of the body form a body, the first transmission shaft 60 is the input gear 30 of the second position and the first transmission gear of the second position ( The gear ratio of 100 makes it possible to rotate and rotate. At this time, the remaining first transmission gear 100 is idling.

In order to enable such a series of structures, that is, any one selected from the plurality of first transmission gears 100 and the first transmission shaft 60 are connected so that the first transmission shaft 60 rotates. The supply path of the hydraulic pressure supplied from the pump 165 toward the first flow path rod 70 is controlled. That is, the controller 160 is in close contact with the first connecting pin 137 of the first transmission gear 100 corresponding to any one selected from the plurality of input side gear 30, the rotational force of the selected input side gear 30 is Control the supply of the hydraulic pressure supplied from the hydraulic pump 165 to the first passage passage 133 and the first communication passage 131 corresponding to the first connecting pin 137 to be transmitted to the first transmission shaft 60. do.

Next, a shift process of the second transmission unit 140 will be described.

The controller 160 is shifted by a pair of gears selected from the plurality of input side gears 30 and the plurality of second transmission gears 110, and the plurality of input side gears 30 are rotated so that the second transmission shaft 80 rotates. ) And selectively connect the plurality of second transmission gears 110.

The second transmission unit 140 includes a plurality of second communication paths 141, a plurality of second flow paths 143, a plurality of second pistons 145, and a plurality of second connection pins 147. Include.

The plurality of second communication paths 141 are formed on the outer surface of the second transmission shaft 80 so as to correspond to the plurality of second transmission gears 110 so as to communicate with the second accommodation chamber 81 along the circumferential direction. . The plurality of second communication paths 141 are arranged on the outer surface of the second transmission shaft 80 at equal intervals along the circumferential direction with the second accommodation chamber 81 as the center.

The plurality of second flow paths 143 are formed in the second flow path rods 90 to communicate with the plurality of second communication paths 141 and the corresponding ones. Each second flow passage 143 is connected to each hydraulic supply pipe 161 by a rotary joint (not shown), and each hydraulic supply pipe 161 is connected to the hydraulic pump 165. The control unit 160 controls the on / off solenoid valve (not shown) provided in each of the hydraulic supply pipes 161 to control any one of the second channel passages selected from the plurality of second channel passages 143. Supply hydraulic pressure to 143).

The plurality of second pistons 145 are reciprocally coupled to the plurality of second communication paths 141, and are operated by hydraulic pressure provided to the second channel paths 143. As shown in FIG. 1, the plurality of second pistons 145 are reciprocally coupled to the respective second communication paths 141 of the second transmission shaft 80, and corresponding to the second transmission gears 110. When the hydraulic pressure flows into the second communication path 141 of the second transmission shaft 80 formed at the end, the second connecting pins 147 connected to the second piston 145 while operating radially outward are radially outward. It serves to pressurize. Of course, when the pressure is released, the second piston 145 and the second connecting pins 147 are returned to their original positions.

The plurality of second connecting pins 147 are connected to the plurality of second pistons 145 to move radially outwards based on the operation of the second pistons 145 and to the inner circumference of the first transmission gear 100. Close contact and release. The second connection pins 147 may be provided to correspond to the second piston 145 one by one.

In the present embodiment, the second connecting pin 147 is disposed to be accessible to the second communication path 141 formed on the second transmission shaft 80. In the present embodiment, four second connecting pins 147 are provided at intervals along the circumferential direction of the second transmission shaft 80 to correspond to the second transmission gear 110 of the corresponding stage.

These second connection pins 147 serve to keep in close contact with any one selected from the second gear 100 of the fourth stage.

For example, as shown in FIG. 2, when the hydraulic pressure is supplied to the sixth position and the second pistons 145 of the sixth position are operated radially outwardly, the second connecting pins 147 of the sixth position may be interlocked. As contact and pressure is applied to the inner surface of the second transmission gear 110 in the sixth position, the sixth position is caught by the second locking jaw 113 of the second transmission gear 110 in the sixth position as shown in FIG. Since the second transmission gear 110 and the second transmission shaft 80 of the body form a body, the second transmission shaft 80 is the input gear 30 of the sixth position and the second transmission gear of the sixth position ( The gear ratio of 110 allows the gear to rotate and rotate. At this time, the remaining second transmission gear 110 is idling.

In order to enable such a series of structures, that is, any one selected from the plurality of second transmission gears 110 and the second transmission shaft 80 are connected so that the second transmission shaft 80 rotates. The supply path of the hydraulic pressure supplied from the pump 165 toward the second flow path rod 90 is controlled. That is, the controller 160 is in close contact with the corresponding second connecting pin 147 of the second transmission gear 110 corresponding to any one selected from the plurality of input side gear 30, the rotational force of the selected input side gear 30 Controls the supply of the hydraulic pressure supplied from the hydraulic pump 165 to the second passage passage 143 and the second communication passage 141 corresponding to the second connecting pin 147 so as to be transmitted to the second transmission shaft 80. do.

In addition, since the multi-stage automatic transmission according to the present invention is provided in a state in which the output shaft 40 is separated from the output transmission gear 50, the output transmission power transmission gear 120 and the output transmission shaft 120 are rotated by the rotation of the first transmission shaft 60. Even if the output side gear 50 rotates, the output shaft 40 does not rotate. However, when the output shaft 40 is connected to any one of the output transmission gear 50 by the output transmission unit 150 by the structure and operation to be described later, the output shaft 40 can be rotated.

In order to implement the operation thereof, the controller 160 is shifted by a pair of gears selected from the plurality of output side power transmission gears 120 and the output transmission gear 50 and the output shaft 40 is rotated so that the output shaft 40 rotates. The connection of the power transmission gear 120 and the output transmission gear 50 is selectively controlled.

The output side transmission part 150 includes a plurality of output side communication paths 151, a plurality of output side flow paths 153, a plurality of output side pistons 155, and a plurality of output side connecting pins 157.

The plurality of output side communication paths 151 are formed on the outer surface of the output shaft 40 so as to correspond to the plurality of output side transmission gears 50 so as to communicate with the output side accommodation chamber 41 along the circumferential direction. The plurality of output side communication paths 151 are arranged on the outer surface of the output shaft 40 around the output side accommodating chamber 41 at equal intervals along the circumferential direction.

The plurality of output side passage passages 153 are formed inside the output side passage passage rod 45 to communicate with the corresponding output side passage passages 151. Each output side flow path 153 is connected to each hydraulic supply pipe 161 by a rotary joint (not shown), and each hydraulic supply pipe 161 is connected to the hydraulic pump 165. The control unit 160 controls an on / off solenoid valve (not shown) provided in each of the hydraulic supply pipes 161 to output one of the output side flow paths 153 selected from the plurality of output side flow paths 153. Supply hydraulic pressure to

The plurality of output side pistons 155 are reciprocally coupled to the plurality of output side communication paths 151 and are operated by hydraulic pressure provided to the output side flow path 153. As illustrated in FIG. 1, the plurality of output side pistons 155 are reciprocally coupled to each output side communication path 151 of the output shaft 40, and an output shaft 40 formed at a corresponding stage of the output side gear 50. When the hydraulic pressure flows into the output side communication path 151 of the (), it acts radially outward serves to press the output side connecting pins 157 connected to the output side piston 155 radially outward. Of course, when the pressure is released, the output side piston 155 and the output side connecting pins 157 are returned to their original positions.

The plurality of output side connecting pins 157 are connected to the plurality of output side pistons 155 to move radially outwards based on the operation of the output side pistons 155, and close and close contact with the inner circumference of the output side gear 50. do. The output side connecting pin 157 may be provided to correspond to the output side piston 155 one by one.

In this embodiment, the output side connecting pin 157 is arranged to be accessible to the output side communication path 151 formed on the output shaft (40). In the present embodiment, four output side connecting pins 157 are provided at intervals along the circumferential direction of the output shaft 40 to correspond to the output side transmission gear 50 of the corresponding stage.

The output side connecting pins 157 serve to keep close contact with any one selected from the output gears of the three stages.

For example, when the hydraulic pressure is supplied to the "C" position as shown in Figure 1 so that the output piston 155 in the "C" position is operated radially outwards, the output side connecting pin 157 of the "C" position in conjunction with this Are pressed against the inner surface of the output transmission gear 50 in the "C" position, the hooks 53 of the output transmission gear 50 of the output transmission gear 50 in the "C" position are caught as shown in FIG. As the output side transmission gear 50 and the output shaft 40 at the position form a body, the output shaft 40 is formed by the output side transmission gear 50 at the " C " position and the output side transmission gear 50 at the " C " position. It is shifted by the gear ratio and can rotate. At this time, the remaining output transmission gears 50 idle.

In order to enable such a series of structures, that is, any one selected from the plurality of output transmission gears 50 and an output power transmission gear 120 corresponding thereto are connected so that the output shaft 40 rotates, that is, the control unit 160 includes a plurality of output gears. Rotational force of the selected output side power transmission gear 120 and the output side transmission gear 50 by bringing the corresponding output side transmission pins 157 of the output side transmission gear 50 corresponding to any one selected from among the output side power transmission gear 120 of The supply of the hydraulic pressure supplied from the hydraulic pump 165 to the output side passage passage 153 and the output side communication passage 151 corresponding to the output side connecting pin 157 is controlled to be transmitted to the output shaft 40.

Meanwhile, the controller 160 of the multi-stage automatic transmission according to the present invention selectively controls any one of the first transmission unit 130 and the second transmission unit 140, and simultaneously controls the output side transmission unit 150. . Accordingly, the multi-stage automatic transmission according to the present invention shifts the power of the input shaft 20 through the output shaft 40 via the first transmission unit 130, the first transmission shaft 60, and the output side transmission unit 150. Alternatively, the power of the input shaft 20 is shifted through the output shaft 40 via the second transmission unit 140, the power transmission unit 170, the first transmission shaft 60, and the output side transmission unit 150, and then outputted. do.

In addition, the multi-stage automatic transmission according to the present invention further includes a power transmission unit 170 for transmitting the rotational force of the second transmission shaft (80) to the first transmission shaft (60).

As shown in FIG. 5, the power transmission unit 170 includes a first power transmission gear 171, a second power transmission gear 171, and an idle gear 175.

The first power transmission gear 171 is coupled to the first transmission shaft 60 and rotates together with the first transmission shaft 60.

The second power transmission gear 173 is coupled to the second transmission shaft 80 and rotates together with the second transmission shaft 80.

The idle gear 175 is rotatably supported by the input shaft 20, and rotates in engagement with the first power transmission gear 171 and the second power transmission gear 173, respectively. The idle gear 175 is rotatably supported by the input shaft 20 by a bearing 177 provided on the inner circumference of the idle gear 175.

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.

First, a process of shifting and outputting the power of the input shaft 20 through the output shaft 40 via the first transmission unit 130, the first transmission shaft 60, and the output side transmission unit 150 will be described below. same.

As shown in FIG. 1, the control unit 160 simultaneously supplies hydraulic pressure to the position 2 of the first transmission unit 130 and the position “C” of the output side transmission unit 150, and the second transmission unit 140. ) Does not supply hydraulic pressure.

Then, the first pistons 135 at the second position are operated radially outwardly, and the first connecting pins 137 at the second position contact the inner surface of the first transmission gear 100 at the second position. As it is pressurized, as shown in FIG. 9, it is caught by the first engaging jaw 103 of the first transmission gear 100 in the second position, and the first transmission gear 100 and the first transmission shaft 60 in the second position. ) Forms a body, and the first transmission shaft 60 is shifted and rotated by the gear ratio of the input side gear 30 in the second position and the first transmission gear 100 in the second position. In this case, since the hydraulic pressure is not supplied to the first flow path 133 of the remaining first transmission gears 100 by the controller 160, the controller 160 corresponds to the remaining first transmission gears 100 as shown in FIG. 10. The first connecting pins 137 are not caught by each of the first catching jaws 103 of the remaining first transmission gear 100, so that the remaining first transmission gears 100 idle.

At the same time, the output side pistons 155 in the "C" position are operated radially outwards, and the output connection pins 157 in the "C" position contact the inner surface of the output transmission gear 50 in the "C" position. As it is pressurized, as shown in FIG. 13, the output side transmission gear 50 and the output shaft 40 of the "C" position are caught by the output side engaging jaw 53 of the output side transmission gear 50 of the "C" position. The output shaft 40 is shifted and rotated by the gear ratio of the output side power transmission gear 120 at the "C" position and the output side gear 50 at the "C" position. At this time, since the hydraulic pressure is not supplied to the output side flow path 153 of the remaining output side shift gears 50 by the controller 160, the output side connection corresponding to the remaining output side shift gears 50 is illustrated in FIG. 14. The pins 157 are not caught by each output side engaging jaw 53 of the remaining output side gear 50, so that the remaining output side gear 50 is idle.

On the other hand, as the hydraulic pressure is not supplied to the second transmission unit 140, the second transmission gears 110 rotate together with the input side gears 30 to idle at the second transmission shaft 80.

In addition, as the first transmission shaft 60 rotates, the first power transmission gear 171, the idle gear 175, the second power transmission gear 173, and the second transmission shaft 80 rotate, but the second transmission shaft 60 rotates. Since the hydraulic pressure is not supplied to the transmission unit 140, the second transmission shaft 80 idles with respect to the second transmission gears 110.

Therefore, the power input through the input shaft 20 is the input side gear 30 of the selected position 2 and the corresponding first transmission gear 100, the first transmission shaft 60, the output side power of the selected "C" position The transmission gear 120, the output gear shift 50 corresponding thereto, and the output shaft 40 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 by the input side gear 30 of the selected second position and the corresponding first transmission gear 100 The first shift is transmitted to the first shift shaft 60, and the rotation speed of the first shift shaft 60 is shifted to the output side power transmission gear 120 at the selected " C " position and the corresponding output side shift gear. The output shaft 40 is rotated at the rotation speed secondaryly shifted by 50, and finally the secondary shift.

That is, as an example, the gear ratio of the input side gear 30 in the second position and the first transmission gear 100 corresponding thereto is 1: 2, and the output side power transmission gear 120 and the corresponding position in the “C” position thereof are 1: 2. When the transmission ratio of the output transmission gear 50 is 1: 4, the rotation speed of the input shaft 20 is shifted at a ratio of 1: 8, which is the product of the transmission ratios of the first transmission unit 130 and the output transmission unit 150. The output shaft 40 is rotated at a gear ratio of 1: 8 relative to the rotational speed of the input shaft 20.

Next, the power of the input shaft 20 is shifted and output through the output shaft 40 via the second transmission unit 140, the power transmission unit 170, the first transmission shaft 60, and the output side transmission unit 150. The process is as follows.

As shown in FIG. 2, the control unit 160 simultaneously supplies hydraulic pressure to the sixth position of the second transmission unit 140 and the “C” position of the output side transmission unit 150, and the first transmission unit 130. ) Does not supply hydraulic pressure.

Then, the second pistons 145 at the sixth position are operated radially outwardly, and the second connecting pins 147 at the sixth position contact the inner surface of the second transmission gear 110 at the sixth position. As it is pressurized, as shown in FIG. 11, it is caught by the second locking jaw 113 of the second transmission gear 110 in the sixth position, and the second transmission gear 110 and the second transmission shaft 80 in the sixth position. ) Forms a body, and the second transmission shaft 80 is shifted and rotated by the gear ratio of the input gear 30 at the sixth position and the second transmission gear 110 at the sixth position. At this time, since the hydraulic pressure is not supplied to the second flow path 143 of the remaining second transmission gears 110 by the controller 160, the controller 160 corresponds to the remaining second transmission gears 110 as shown in FIG. 12. The second connecting pins 147 are not caught by the second catching jaws 113 of the remaining second transmission gears 110, and the remaining second transmission gears 110 idle.

At the same time, the output side pistons 155 in the "C" position are operated radially outwards, and the output connection pins 157 in the "C" position contact the inner surface of the output transmission gear 50 in the "C" position. As it is pressurized, as shown in FIG. 13, the output side transmission gear 50 and the output shaft 40 of the "C" position are caught by the output side engaging jaw 53 of the output side transmission gear 50 of the "C" position. The output shaft 40 is shifted and rotated by the gear ratio of the output side power transmission gear 120 at the "C" position and the output side gear 50 at the "C" position. At this time, since the hydraulic pressure is not supplied to the output side flow path 153 of the remaining output side shift gears 50 by the controller 160, the output side connection corresponding to the remaining output side shift gears 50 is illustrated in FIG. 14. The pins 157 are not caught by each output side engaging jaw 53 of the remaining output side gear 50, so that the remaining output side gear 50 is idle.

On the other hand, as the hydraulic pressure is not supplied to the first transmission unit 130, the first transmission gears 100 rotate together with the input side gears 30 to idle rotation about the first transmission shaft 60.

Therefore, the power input through the input shaft 20 is input gear 30 of the selected position 6 and the corresponding second transmission gear 110, the second transmission shaft 80, the second power transmission gear 173. , The output gear (175) through the idle gear 175, the first power transmission gear 171, the output power transmission gear 120 of the selected "C" position, and the corresponding output transmission gear 50, the output shaft 40 in sequence Is output via 40).

Meanwhile, 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 controlled by the input gear 30 and the second transmission gear 110 corresponding thereto at the selected sixth position. The first shift is transmitted to the second shift shaft 80, and the rotation speed of the second shift shaft 80, which is primarily shifted, is selected via the power transmission unit 170 and the first shift shaft 60 and selected "C." Is shifted secondary by the output side power transmission gear 120 and the corresponding output side transmission gear 50 at the "" position, so that the output shaft 40 rotates at the secondly-shifted speed.

That is, as an example, the gear ratio of the input gear 30 at the 6th position and the second transmission gear 110 corresponding thereto is 1: 3, and the output power transmission gear 120 at the position “C” and the corresponding gear ratio are When the transmission ratio of the output transmission gear 50 is 1: 4, the rotation speed of the input shaft 20 is shifted at a ratio of 1:12, which is the product of the transmission ratios of the second transmission unit 140 and the output transmission unit 150. The output shaft 40 is rotated at a gear ratio of 1:12 with respect to the rotation 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 unit 130 and the "C" position of the output side transmission unit 150 by the controller 160, the first pistons 135 of the reverse position operate radially outward. As the first connecting pins 137 in the reverse position are pressed against the inner surface of the first transmission gear 100 in the reverse position, the first transmission gear 100 in the reverse position as shown in FIG. The first transmission gear 100 and the first transmission shaft 60 of the retracted position to be caught by the first locking jaw 103 of the) forms a body, the first transmission shaft 60 is the input side gear ( 30) and the gear ratio of the first transmission gear 100 in the reverse position is shifted and rotated. In this case, since the hydraulic pressure is not supplied to the first flow path 133 of the remaining first transmission gears 100 by the controller 160, the controller 160 corresponds to the remaining first transmission gears 100 as shown in FIG. 10. The first connecting pins 137 are not caught by each of the first catching jaws 103 of the remaining first transmission gear 100, so that the remaining first transmission gears 100 idle.

At the same time, the output side pistons 155 in the "C" position are operated radially outwards, and the output connection pins 157 in the "C" position contact the inner surface of the output transmission gear 50 in the "C" position. As it is pressurized, as shown in FIG. 13, the output side transmission gear 50 and the output shaft 40 at the "C" position are caught by the output side engaging jaw 53 of the output side transmission gear 50 at the "C" position. The output shaft 40 is shifted and rotated by the gear ratio of the output side power transmission gear 120 at the "C" position and the output side gear 50 at the "C" position. At this time, since the hydraulic pressure is not supplied to the output side flow path 153 of the remaining output side shift gears 50 by the controller 160, the output side connection corresponding to the remaining output side shift gears 50 is illustrated in FIG. 14. The pins 157 are not caught by each output side engaging jaw 53 of the remaining output side gear 50, so that the remaining output side gear 50 is idle.

In addition, since the hydraulic pressure is not supplied to the second transmission unit 140, the second transmission gears 110 rotate together with the input side gears 30 to idle at the second transmission shaft 80.

Therefore, the reverse driving force input through the input shaft 20 is the input side gear 30, the reverse rotation intermediate gear 35 and the corresponding first transmission gear 100, the first transmission shaft 60, The multi-stage automatic transmission according to the present invention is output through the output shaft 40 through the output side power transmission gear 120 at the selected "C " position and the corresponding output side transmission gear 50 and the output shaft 40 in sequence. Will be driven.

Therefore, in the multi-stage automatic transmission in the present embodiment, since the first gear shift stage is 1 reverse gear and 3 forward gear shift gears, the second gear shift gear is 4 gears and the output gear shift gear gear is composed of 3 gears. The combination of the gear shift stage and the output gear shift stage implements nine forward shifts and one reverse gear, and the combination of the second gear shift stage and the output gear shift stages achieves 12 forward shifts. The multi-stage automatic transmission can realize 21 forward shifting and 1 reverse gear.

That is, the multi-stage automatic transmission according to the present invention adjusts the first gear shift speed, the second gear shift speed, and the output gear shift speed in various ways, thereby combining the first gear shift speed and the output gear shift speed, and the second gear shift speed and the output gear shift speed. Combination makes it possible to implement various shift ranges.

As described above, according to the present invention, the two transmission shafts selectively connected to the input shaft are respectively provided with independent multi-stage transmission units, and at the same time, the multi-stage transmission unit is added to the output shaft, whereby the size of the transmission becomes compact and the three multi-stage units are provided. The combination of the transmission unit enables various transmission ranges to be realized.

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
45: output passage passage rod 50: output transmission gear
60: first transmission shaft 70: first flow path rod
80: second shift shaft 90: second flow path rod
100: first transmission gear 110: second transmission gear
120: output side power transmission gear 130: first transmission portion
140: second transmission portion 150: output side transmission portion
160 control unit 170 power transmission unit
171: first power transmission gear 173: second power transmission gear
175: idle gear

Claims (8)

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 transmission gears disposed separately in the radially outer side of the output shaft;
A first transmission shaft and a second transmission shaft disposed opposite to each other with the input shaft therebetween;
A plurality of first transmission gears which are tooth-engaged to rotate in opposite directions to the plurality of input side gears and are respectively separated from the first transmission shafts;
A plurality of second transmission gears that are toothed to rotate in opposite directions to the plurality of input side gears and are respectively separated from the second transmission shafts;
A plurality of output side power transmission gears which are tooth-engaged to rotate in the opposite directions to the plurality of output side gears, and which are fixed to the first gear shaft and rotate together with the first gear shaft;
The connection of the plurality of input side gears and the plurality of first transmission gears may be selectively shifted by a pair of gears selected from the plurality of input side gears and the plurality of first transmission gears to rotate the first transmission shaft. A first transmission portion controlled by;
The connection of the plurality of input side gears and the plurality of second transmission gears may be selectively shifted by a pair of gears selected from the plurality of input side gears and the plurality of second transmission gears so that the second transmission shaft rotates. A second transmission part controlled by;
The plurality of output side power transmission gears and the plurality of output sides so as to be shifted by a pair of gears selected from the plurality of output side power transmission gears and the plurality of output side transmission gears and to transmit rotational force of the first transmission shaft to the output shaft. An output side transmission portion for selectively controlling a connection of the transmission gear;
And a control unit configured to selectively control any one of the first transmission unit and the second transmission unit, and to shift the output side transmission unit. The method of claim 1,
And a power transmission unit for transmitting the rotational force of the second transmission shaft to the first transmission shaft. 3. The method of claim 2,
The power transmission unit includes:
A first power transmission gear coupled to the first transmission shaft and rotating together with the first transmission shaft;
A second power transmission gear coupled to the second transmission shaft and rotating together with the second transmission shaft;
And an idler gear rotatably supported by the input shaft and engaged with the first power transmission gear and the second power transmission gear to rotate respectively. The method of claim 1,
A first accommodation chamber is formed in the first transmission shaft, and a first passage passage rod is connected to the first transmission shaft in the first accommodation chamber, and a second accommodation chamber is formed in the second transmission shaft. The second chamber passage is provided with a second passage passage rod connected to the second transmission shaft, the output shaft is formed in the output side receiving chamber, the output side receiving chamber is provided with an output side passage passage rod connected to the output shaft Automatic transmission. 5. The method of claim 4,
The first transmission portion,
A plurality of first communication paths formed on the outer surface of the first transmission shaft so as to correspond to the plurality of first transmission gears so as to communicate with the first accommodation chamber along the circumferential direction;
A plurality of first flow paths provided inside the first flow path rods and communicating with the plurality of first communication paths 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;
And a plurality of first connecting pins connected to the plurality of first pistons to close and close the first transmission gear based on the operation of the first pistons.
The controller may be configured to contact the corresponding first connecting pin of the first transmission gear corresponding to any one selected from the plurality of input side gears so that the rotational force of the selected input side gear is transmitted to the first transmission shaft. A multistage automatic transmission characterized in that for controlling the supply of hydraulic pressure to the first passage passage corresponding to the. 5. The method of claim 4,
The second transmission portion,
A plurality of second communication paths formed on the outer surface of the second transmission shaft to communicate with the second accommodation chamber along the circumferential direction so as to correspond to the plurality of second transmission gears, respectively;
A plurality of second flow paths provided in the second flow path rods and communicating with the plurality of second communication paths 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 close and close contact with the second transmission gear based on an operation of the second piston;
The control unit is in contact with the corresponding second connecting pin of the second transmission gear corresponding to any one selected from the plurality of input side gears to transmit the rotational force of the selected input side gear to the second transmission shaft, A multistage automatic transmission characterized in that for controlling the supply of hydraulic pressure to the second passage passage corresponding to the. 5. The method of claim 4,
The output side transmission portion,
A plurality of output side communication paths formed on the outer surface of the output shaft so as to correspond to the plurality of output side transmission gears so as to communicate with the output side receiving chamber along the circumferential direction;
A plurality of output side flow paths provided in the output side flow path rods and communicating with the plurality of output side communication paths and corresponding ones;
A plurality of output side pistons reciprocally coupled to the plurality of output side communication paths, the plurality of output side pistons being operated by hydraulic pressure provided to the output side flow paths;
And a plurality of output side connecting pins connected to the plurality of output side pistons, the plurality of output side connection pins contacting and releasing the output gears based on the operation of the output pistons.
The control unit is configured to closely contact a corresponding output side connecting pin of an output transmission gear corresponding to any one selected from the plurality of output side power transmission gears, so that the rotational force of the first transmission shaft is transmitted to the output shaft. A multistage automatic transmission characterized by controlling the supply of hydraulic pressure to the passage. The method of claim 1,
And a reverse rotation intermediate gear is coupled to a gear that is responsible for reversing among the plurality of input side gears.

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