KR101012470B1 - Multi stage automatic transmission - Google Patents

Abstract

The present invention relates to a multi-stage automatic transmission, comprising: a body housing; An input side shaft coupled to one side of the body housing so that at least one region is exposed to the outside of the body housing and rotated by engine torque; A plurality of input side drive gears fixed in a radially outer side of the input side shaft and rotating together with the input side shaft; A one-way clutch interposed between the input side shaft and the input side drive gear; A plurality of output side driven gears having an outer surface formed in a pyramid shape so as to be toothed with the plurality of input side drive gears in opposite directions, and having a non-circular cam space formed therein; An output side shaft including a shaft body disposed in a pyramid shape so as to correspond to each of the plurality of output side driven gears one by one, and a shaft bar connected to the shaft body and exposed to the outside of the body housing; ; A hydraulic pressure supply pipe connected to the output side shaft to supply hydraulic pressure to a single pressure chamber formed inside the shaft body; A plurality of pistons movable radially inwardly or outwardly based on pressures provided in a plurality of branching passages respectively branching from the pressure chamber toward the plurality of output side driven gears; A plurality of friction members each connected to the plurality of pistons and selectively contacted and pressed against an inner circumferential surface of the output side driven gear while being operated by the pistons; And a control unit for controlling the hydraulic pressure provided from the hydraulic pump to the pressure chamber so that the output shaft is rotated by a pair of gears selected from the plurality of input side drive gears and the plurality of output side driven gears. As a result, it is possible to easily implement a multi-stage shift through a single pressure chamber, and can be applied to continuously shifted, stepped shifting, automatic shifting, and manual shifting, as well as to improve power transmission efficiency and shifting feeling more conventionally. Rather, it can reduce fuel consumption while increasing power performance.

Description

Multi-speed automatic transmission {MULTI STAGE AUTOMATIC TRANSMISSION}

The present invention relates to a multi-stage automatic transmission, and more particularly, it is possible to easily implement a multi-stage shift through a single pressure chamber, as well as to be applied to continuously variable, stepped shift, automatic shift and manual shift, power transmission. The present invention relates to a multi-stage automatic transmission that can not only improve efficiency and shift feeling more than conventionally, but also improve fuel performance while reducing fuel consumption.

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

A gear train in which a plurality of planetary gear sets are combined performs a function of shifting a multi-step gear to an output side when rotation 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.

In order to respond to this trend, various studies have been conducted, and recently, a gear train of an automatic transmission that can realize a shift stage of 6 forward speed and 8 forward speed has also been proposed.

Accordingly, the present inventors have easily proposed a new type of multi-stage automatic transmission sufficient to be applied to continuously shifted, stepped shifting, automatic shifting and manual shifting by easily implementing a multi-stage shift through a single pressure chamber.

The object of the present invention can be easily implemented in a multi-stage shifting through a single pressure chamber, as well as can be applied to continuously variable, stepped shift, automatic shift and manual shift, it is possible to improve the power transmission efficiency and shift more than conventional In addition, it provides a multi-stage automatic transmission that can increase fuel performance and reduce fuel consumption.

The object is a main body housing; An input side shaft coupled to one side of the body housing so that at least one region is exposed to the outside of the body housing and rotated by engine torque; A plurality of input side drive gears fixed in a radially outer side of the input side shaft and rotating together with the input side shaft; A one-way clutch interposed between the input side shaft and the input side drive gear; A plurality of output side driven gears having an outer surface formed in a pyramid shape so as to be toothed with the plurality of input side drive gears in opposite directions, and having a non-circular cam space formed therein; An output side shaft including a shaft body disposed in a pyramid shape so as to correspond to each of the plurality of output side driven gears one by one, and a shaft bar connected to the shaft body and exposed to the outside of the body housing; ; A hydraulic pressure supply pipe connected to the output side shaft to supply hydraulic pressure to a single pressure chamber formed inside the shaft body; A plurality of pistons each provided in a plurality of branching passages branched from the pressure chamber toward the plurality of output side driven gears and movable radially inward or outward based on the pressure provided; A plurality of friction members each connected to the plurality of pistons and selectively contacted and pressed against an inner circumferential surface of the output side driven gear while being operated by the pistons; And a control unit for controlling the hydraulic pressure provided from the hydraulic pump to the pressure chamber so that the output shaft is rotated by a pair of gears selected from the plurality of input side drive gears and the plurality of output side driven gears. Is achieved by automatic transmission.

Here, the combination of the plurality of input side drive gears and the plurality of output side driven gears may have one reverse stage and eight forward shift stages.

The input side drive gear and the output side driven gear in the high speed stage area higher than the corresponding gear stage when the gear stage selected from the eight forward stages are advanced by the hydraulic pressure provided from the hydraulic pump to the pressure chamber based on the control signal of the controller. Slip friction is rotated, and the input drive gear and the output driven gear in the low speed end region lower than the shift stage may be idling based on the stop friction rotation.

The reverse stage may form a hydraulic flow path independent of the eight forward shift stages.

Thrust bearings may be interposed between the input side driving gears.

The plurality of friction members may be arranged at equal intervals in the cam space along the circumferential direction.

The plurality of friction members may be arc shaped blocks or balls.

The plurality of pistons may be provided to correspond to the plurality of friction members one by one.

According to the present invention, it is possible to easily implement a multi-stage shift through a single pressure chamber, as well as to be applied to continuously variable, stepped shifting, automatic shifting and manual shifting, and to improve power transmission efficiency and shifting feeling more conventionally. In addition, it has the effect of reducing fuel consumption while increasing power performance.

Hereinafter, exemplary embodiments of the present invention will be described with reference to the accompanying drawings, and like reference numerals refer to like elements among the descriptions of the embodiments. In addition, hereinafter, a case in which the multi-stage automatic transmission according to the present invention is applied to a vehicle as an embodiment will be described.

Hereinafter, exemplary embodiments of the present invention will be described with reference to the accompanying drawings, and like reference numerals refer to like elements among the descriptions of the embodiments.

1 is a schematic internal structural diagram of a multi-stage automatic transmission according to a first embodiment of the present invention, FIG. 2 is a perspective view of a coupling state between an input side shaft and an input drive gear shown in FIG. 1, and FIG. 3 is an input side drive gear and an output side driven drive. Figure 4 is an exploded perspective view of the output side driven gear, Figure 5 is a perspective view of the coupling state between the hydraulic supply pipe and the output shaft, Figure 6 is an output side driven gear according to the operation of the friction member Fig. 1 shows the arrangement state of the input gears.

Referring to these drawings, but mainly referring to FIG. 1, the multistage automatic transmission of the present embodiment is largely the main body housing 100, the input side shaft 210 and the input side drive gear 220 as the input side configuration, and the output side driven as the output side configuration. It has a plurality of configurations including a gear 310 and an output shaft 320, a hydraulic supply pipe 400 connected to the output shaft 320, and a control unit (not shown) operated in conjunction with the hydraulic supply pipe 400. .

First, the body housing 100 is a part which forms the external appearance of the multistage automatic transmission of this embodiment. The body housing 100 may be made of a rigid metal material. Most of the configuration is assembled in a form accommodated in the body housing 100.

However, for operation, a portion of the input shaft 210 and the shaft bar 340 of the output shaft 320 are partially exposed to the outside of the main housing 100.

A bearing B for smooth rotation is interposed between the input shaft 210 and the main housing 100 and between the shaft bar 340 of the output shaft 320 and the main housing 100. In addition, there is further interposed a packing (not shown) for sealing.

The input side shaft 210 is a part rotated by engine torque. That is, power for driving the input side shaft 210 is input. The input power is output after being adjusted through the output side shaft 320 by the structure to be described later. Acceleration may include both speed and torque.

The input side drive gear 220 is fixed in a pyramid shape on the radially outer side of the input side shaft 210 and rotates together with the input side shaft 210.

The input side drive gear 220 is connected to the input side shaft 210 by a one way clutch 230 (see FIGS. 1 and 7) so that the input side drive gear 220 can be rotated together with the input side shaft 210. Combined. Of course, the input side drive gear 220 may be manufactured integrally with the input side shaft 210 without using the one-way clutch 230. A thrust bearing 260 is provided between the input side drive gears 220.

Since the multi-stage automatic transmission of the present embodiment has one reverse stage and eight forward shift stages, the pyramidal input side drive gear 220 is provided in nine stages.

Since the input side drive gear 220 is provided in 9 stages in total, the output side driven gear 310 and the shaft body 330 of the output side shaft 320 are also provided in 9 stages in total.

Of course, since this is one embodiment, the multi-stage automatic transmission of the present embodiment may be at least or more than eight forward speeds. In this case, the input side drive gear 220, the output side driven gear 310 and the output side shaft 320 The shaft body 330 is sufficient if provided in the corresponding number of stages.

Hereinafter, for convenience of illustration and description, reference numerals by positions of the input side driving gear 220 and the output side driven gear 310 will not be distinguished, and will be described by giving letters and numbers to the drawings.

Like the input side drive gear 220, the output side driven gear 310 is provided in a pyramid shape, but is arranged opposite to the input side drive gear 220 so as to be meshed with the input side drive gear 220 one by one in the opposite direction. The internal space of the output side driven gear 310 is provided in a non-circular shape.

As such, when the input side shaft 210 having the input side drive gear 220 and the output side shaft 320 having the shaft body 330 are provided in a multi-stage pyramid shape, the pressures of the respective shift stages may be the same. However, if a parallel shaft is used instead, the pressure at each shift stage must be configured differently.

In transmission, the gear circumference of each gear is different. If the circumference is different, the rotational force is also different. When the output shaft 320 and the output side driven gear 310 power transmission, the frictional force is also different due to the difference in the circumferential ratio. In the case of parallel shafts, different pressures are required for each gear. In the case of the multi-stage output side shaft 320 as in this embodiment, even if the circumference of the output side driven gear 310 increases, the circumference of the output side shaft 320 also increases, so that the output side shaft 320 and the output side driven gear 310 shaft The friction force of the cam gear is maintained even if the same pressure is applied to the entire shift stage without any change.

The output side shaft 320 may be largely divided into the shaft body 330 and the shaft bar 340. The shaft body 330 and the shaft bar 340 may be manufactured in one piece, or may be combined with each other after being manufactured separately.

The shaft body 330 is arranged in a pyramid shape so as to correspond to the output side driven gear 310 one by one in the output side driven gear 310, respectively, with the output side driven gear 310 and the cam space 331 (see FIG. 3) therebetween. Placed in a separated state. A single pressure chamber 332 is provided in the shaft body 330.

The shaft bar 340 is connected to the shaft body 330 but is exposed to the outside of the output side driven gear 310.

Since the output side shaft 320 is provided in a state separated from the output side driven gear 310 as described above, even if the output side driven gear 310 is rotated, the output side shaft 320 is idling as a sliding friction state.

However, when any one of the shaft body 330 is pressed against any one of the output side driven gear 310 by the structure and operation to be described later, the output side shaft 320 may be rotated until they form one body.

In order to realize its operation, that is, any one of the shaft body 330 is pressed against any one of the output side driven gear 310 so that they form a body, the hydraulic supply pipe 400, a plurality of piston 600 And a plurality of friction members 700 and a controller (not shown) for controlling pressure from the hydraulic pump 810.

The hydraulic pressure supply pipe 400 is connected to the output side shaft 320 and serves to supply hydraulic pressure to a single pressure chamber 332 formed inside the shaft body 330.

The plurality of pistons 600 are moved radially inward or outward on the basis of the pressure provided in each of the plurality of branch flow passages 333 which are respectively branched from the single pressure chamber 332 toward the output driven gears 310. .

In other words, the plurality of pistons 600 are respectively coupled to the shaft body 330 of the output side shaft 320 by position. That is, a plurality of shaft shafts 330, which are provided in a nine-stage pyramid shape, are provided with a plurality of equal intervals along the circumferential direction.

As shown in FIG. 6, when the hydraulic pressure flows into the pressure chamber 332 formed at the corresponding end of the shaft body 330 of the output shaft 320, the pistons 600 are operated outward in a radial direction. The friction member 700 connected to the 600 serves to press the radially outward. Of course, when the pressure is released, the piston 600 and the friction member 700 are returned to their original positions.

As described above, the plurality of friction members 700 are connected to the plurality of pistons 600 and move radially outward based on the operation of the pistons 600. The friction member 700 may be provided to correspond to the piston 600 one by one.

In the present embodiment, the friction member 700 has an arc block structure, and allows the friction member 700 to enter and exit the friction member groove 710 (see FIG. 5) formed in the shaft body 330 of the output shaft 320. Is placed. In this embodiment, four friction members 700 are provided at intervals along the circumferential direction.

These friction members 700 serve to keep any one selected from the shaft body 330 provided in the nine-stage pyramid form in close contact with any one of the plurality of output-side driven gear 310 corresponding thereto.

The control unit (not shown) is connected to the pressure chamber 332 from the hydraulic pump 810 so that the output shaft 320 is rotated by a pair of gears selected from the plurality of input side drive gears 220 and the plurality of output side driven gears 310. It serves to control the hydraulic pressure provided.

In other words, when any one shift stage selected from the eight forward stages is advanced by the hydraulic pressure provided from the hydraulic pump 810 to the pressure chamber 332 based on the control signal of the controller, The input side drive gear 220 and the output side driven gear 310 are slid frictionally rotated, and the input side drive gear 220 and the output side driven gear 310 in the low speed end region lower than the shift stage are based on the stop frictional rotation. Idling.

In summary, in the multi-stage automatic transmission of the present embodiment, when the input shaft 210 is driven, the input side drive gear 220 and the output side driven gear 310 mesh with each other to rotate. The inner peripheral surface of the input shaft 210 is a one-way clutch 230, the outer peripheral surface of the output side driven gear 310 is a gear, and the inner peripheral surface is a cam or an eccentric ring gear. It is separated from the input shaft 210.

And the pressure chamber 332 is formed on the inner circumferential surface of the output side shaft 320 of the output side multi-stage shape, when the piston 600 is pushed by the hydraulic pressure, the friction member 700 is an output side driven gear 310, the cam gear The power is transmitted to the output side driven gear 310 by the input side driving gear 220 in close contact with the inner circumferential surface of the space.

Investigate the neutral state of shifting. When zero pressure is applied to the pressure chamber 332, that is, when no hydraulic pressure is supplied, the friction member 700 inserted into the output shaft 320 is cam ring because there is no pressure to push the piston 600. The projection (not shown) of the sliding frictionless load because it is idle. The input side drive gear 220 and the output side driven gear 310 rotate in engagement with each other, but the output side shaft 320 is not rotated and is neutral due to sliding of the friction member 700 and the output side driven gear 310.

The case of reverse will be described with reference to FIG. 1. In the case of the reverse, unlike the forward eight speed, there is a pressure chamber 332a that is independent, so that only the reverse pressure chamber 332a is given pressure, so that only the reverse is performed. The reverse gear, not shown, is engaged with the driven gear 310, the intermediate gear, and the drive gear 220. In another embodiment, the driving gear 220 and the driven gear 310 may be connected by a chain so that reverse rotation is possible. At this time, since the pressure is given to the first 1 to 8 steps forward (zero), the slide is idle idling without load, the reverse is only stop friction rotation is transmitted power. As a result, it can be seen that the transmission consists of one forward pressure chamber 332 and one reverse pressure chamber 332a.

On the other hand, the structure of the static friction rotation and sliding friction rotation, the cam space 331 while the piston 600 reciprocates up and down by pressure in the pressure chamber 332 located on the inner peripheral surface of the output side shaft 320 As the friction member 700 is engaged or released, stop friction rotation or sliding friction rotation is performed. That is, the inner circumferential surface of the output side driven gear 310 has a cam shape, and is formed of a protrusion and a space of the cam, and thus stop friction rotation or sliding friction rotation.

If the pressure is equal to or greater than the set pressure, the piston 600 does not exceed the protrusion of the cam, and stops frictionally rotating. If the pressure is less than the set pressure, the piston is pushed, which exceeds the protrusion of the cam, and is thus frictionally rotated. When the stop frictional rotation does not exceed the projection portion, the output side shaft 320 is rotated, if the sliding friction rotation over the projection portion, the rotational speed of the output side shaft 320 is reduced or the rotation of the output side shaft 320 is stopped. Since the output shaft 320 and the output side driven gear 310 are separated, the static friction is in the engaged state and the sliding friction is in the separated state.

The process of shifting based on such a configuration will be described as follows.

First, it is a case where one shift is performed. When the low pressure is applied to the first stage, the first stage is statically rubbed and rotates by one speed. At this time, since the reverse pressure is a state of zero (zero) is a sliding idle rotation, the input side drive gear 220 is rotated in engagement with the output side driven gear 310 to the 1 ~ 8 stage, the output side driven gear 310 is 1 In the case of the stage, the static friction rotation is performed, and the load sliding friction rotation is performed in the 2 to 8 stage.

Next, the case where the four-speed shift is made. Given the intermediate pressure (pressure for four stages), the four stages are loaded with four loads. 1 to 3 stages of the input side drive gear 220 are idling by the one-way clutch 230, and 4 to 8 stages are load rotating with the output side driven gear 310. At this time, the first to fourth stages of the output side driven gear 310 is subjected to the stop friction rotation, and the 5 to 8 stages of the load sliding friction rotation.

Next, an eight-speed shift is performed. Given the highest pressure (8-speed), eight shifts are made. At this time, the first to seventh stage of the drive gear 220 is idling by the one-way clutch 230, only eight stages of the load rotation is transmitted to the power. 1 to 8 stages of the output-side driven gear 310 are rotated by static friction. However, since the first to seventh stages of the input side drive gear 220 are idling by the one-way clutch 230, the first to seventh stages of the output side driven gear 310 are idling. The higher the pressure, the shift shifting to the high speed stage, and the lower the pressure, the shift shifting to the lower speed stage.

As a specific example, the shift process will be described as follows. Let's look at the power transmission when the maximum traction is 100.

First, it is a case where one shift is performed. When the traction force 100 is divided by 8 (8 stages), 12.5, the pressure pushing the piston 600 to each stage becomes 12.5. Given a pressure of 12.5, only one stage is loaded and power is transmitted and rotated. The first stage on the output side is loaded from the low-speed end point where the static frictional power is 12.5 ㅧ 7 = 87.5 + 12.5 = 100, that is, the total torque is 100. 1 to 8 stages of the drive gear 220 are engaged with the output driven gear 310 to rotate the load, and only 1 stage of the output side driven gear 310 stops frictional rotation, and 2 to 8 stages of the output side driven gear 310 and the sliding friction rotation. do.

Next, a case where two shifts are made. When the traction force 100 is divided by 7 (corresponding to the seventh stage except the first stage because the first stage is idling in the second stage), 14.3, the pressure pushing the piston 600 to each stage becomes 14.3. Given a pressure of 14.3, two shifts are achieved. At this time, the first stage of the input drive gear 220 is idling by the one-way clutch 230, the load is rotated to the second to eighth stage. The first and second stages of the output side driven gear 310 rotate frictionally, and the three to eight stages rotate the load friction. At this time, the first stage is idling by the input side drive gear 220.

The same applies to three-speed and four-speed shifts.

Next, a five-speed shift is performed. Since the traction force is divided by 4 to 25, the pressure for pushing the piston 600 to each stage is 25, and when the pressure of 25 is given, five speed shifts are made. At this time, the input side drive gear 220 rotates to the first to fourth stages, and the load to the fifth to eighth stages. The output side driven gear 310 is subjected to the static friction rotation up to 1 to 5 stages, and the sliding friction rotation is performed up to the 6 to 8 stages.

Next, an eight-speed shift is performed. Given 100 pressures, there is an eight-speed shift. The input side drive gear 220 is idling by the one-way clutch 230 to the first to seventh stages, and only eight stages are load-rotated. 1 to 8 stages of the output driven driven gear 310 is subjected to static friction rotation, and up to 1 to 7 stages are idled by the input side drive gear 220.

On the other hand, if the gear shifting to the sixth stage for climbing during the eight-speed driving to provide a pressure of 33.3, which corresponds to the six-speed shift, the sixth shift. Then, the seventh to eighth stages of the output driven driven gear 310 are lower than the set pressure, and thus the sliding friction rotation is performed, and the first to sixth stages are the stop friction rotation. At this time, since the circumferential speeds between the input side drive gear 220 and the output side driven gear 310 are different from 1 to 5 stages, the input side drive gear (A) is driven by the difference in the number of teeth between the input side drive gear 220 and the output side driven gear 310. 220 is rotated faster, then idling by the one-way clutch 230 provided on the input side. When the input side drive gear 220 idles, the output side driven gear 310 which stops frictionally rotates also idles.

On the other hand, in another example, when the road is made flat during the three-stage running with the pressure of 16.6, the seventh speed is made when the seventh pressure is 50. The eighth-stage frictional frictional force 50 and the seventh-stage rotational force 50 add up to 100, resulting in a seventh-stage rotational force of 100, resulting in a shift from a lower stage to a higher stage with a total pressure of 100.

The operation of the multi-stage automatic transmission having such a configuration will be described as follows.

When starting, the input side drive gear 220 and the output side driven gear 310 is engaged to rotate. At this time, the output side driven gear 310 is idle while sliding frictionless load. Therefore, the output shaft 320 also does not rotate.

When the drive (D) mode is selected on the selector lever at the start, weak hydraulic pressure is transmitted to the cylinders in each stage, so that the vehicle moves forward slowly. At this time, if the brake is applied, the entire shift stage is frictionally rotated under load. When the brake is released and the forward accelerator pedal is pressed, the pressure gradually increases, and continuously shifting is continuously performed at a high stage.

To shift to the lower speed, reduce the pressure. If the pressure is continuously increased, the shift is continuously made to the high speed stage, and if the pressure is continuously reduced, the speed is continuously changed to the low speed stage.

When starting, climbing, accelerating, reversing, and moving forward, all operations are controlled by the hydraulic pump rotation speed by the TCU (Transmission Control Unit) signal and the pressure is adjusted by the difference in capacity.

For example, when shifting from the first stage to the second stage, the pressure corresponding to the second stage is given step by step, and the second stage is shifted step by step. Assuming that the 1st stage pressure is 100 and the 2nd stage pressure is 120, if the pressure is 110, the first stage and the second stage intermediate pressures, the first stage and the second stage of shifting are made. Even if there is no shift stage between the first and second stages, the first and second intermediate speed ratios, that is, the first and second speed shifts, are achieved. If the pressure of 105 is applied, the gear shift is made in one-stage quarters, and if the pressure is applied in an unauthorized manner, it is known that the gear is made in an unauthorized manner.

As the pressure changes, the load sliding frictional force also changes. Each stage is given the same pressure. Then, the load is applied from the high stage, and if it is lower than the set pressure, the sliding friction rotation is performed, and the stop friction rotation occurs at the stage corresponding to the set pressure while continuously shifting to the next stage. If you keep increasing the pressure, the shift is made up to the highest speed and stops at the highest speed because there is no higher gear. On the contrary, if the pressure is lowered continuously, the gear shifts to the lowest speed and stops.

For reference, although the belt-type continuously variable transmission is known, the belt-type continuously variable transmission is limited to the tension of the belt and can only be applied to a small vehicle having a small driving force. However, the present invention is determined only based on the pressure difference. If only the pressure corresponding to the driving force can be provided, there is an advantage that can be applied to all vehicles regardless of the driving force.

As such, according to the present embodiment, it is possible to easily implement a multi-stage shift through a single pressure chamber 332, and can be applied to stepless shifting, step shifting, automatic shifting and manual shifting, and the like. Not only can it be improved more than before, but it is also possible to reduce fuel consumption while increasing power performance.

Although the description is omitted in the above-described embodiment, in the present embodiment, the stepless speed change, the stepped speed change, the automatic speed change, and the manual speed change are possible.

Stepless speed change is a case where the stepless pressure change without a separate step is continuously connected without breaking the power by the load sliding friction rotation is possible to continuously change the speed.

Step shifting gives pressure step by step, for example, 1st stage pressure 12.5, 3rd stage pressure 16.7, 6th stage pressure 33.3, 8th stage pressure 100, etc. Can be implemented accordingly.

The automatic transmission may be implemented by operating the hydraulic pump or adjusting the rotation speed of the hydraulic pump by a TCU (Transmission Control Unit) signal.

Manual shifting can be implemented by operating the inverter DC motor by means of a selector lever.

At this time, the friction clutch of the manual transmission or the fluid torque converter of the automatic transmission are not necessary. When pressure is given in the pressure chamber of the output side driven gear 310, sliding friction rotation is performed from 1 to 8 stages. The sliding force generates the rotational force on the output shaft. At this time, the generated rotational force is the same as the torque of the torque converter to act as a torque converter. In addition, when the pressure is turned on / off, the sliding friction rotation when the pressure is zero, the stop friction rotation when the pressure is given to act as a clutch. All actions such as reverse, forward, neutral, clutch, etc. are made by the working pressure in accordance with the TCU signal or the select lever signal. And the hydraulic discharge amount is adjusted by the DC motor rotation control. The higher the speed, the higher the pressure. The lower the speed, the lower the pressure. If the rotation speed is high, the amount of discharge is large, and the pressure is increased internally while passing through the orifice. When the rotation speed is low, the discharge amount is small, and the flow rate through the orifice is small, so the pressure is lowered inside.

In the above-described embodiment, the pressure chamber 332 is provided on the output side, but the same effect can be provided even on the input side.

7 to 10 are layout diagrams of the arrangement state between the output side driven gear and the input side drive gear according to the operation of the friction member in the multi-stage automatic transmission according to the third to fifth embodiments of the present invention.

Referring to FIG. 7, unlike the first embodiment, two friction members 700a are provided along the circumferential direction. In this case, the internal space structure of the output side driven gear 310a is formed slightly different, and the rest of the configuration and operation are the same as in the first embodiment.

Referring to FIG. 8, four friction members 700b are provided in the circumferential direction, which is the same as the first embodiment, but differs from the first embodiment in that the internal space structure of the output side driven gear 310b is circular. . However, even if the structure as shown in FIG. 8 is applied, there is no problem in providing the effect of the present invention.

Referring to FIG. 9, the friction member 700c has a ball structure instead of an arc block structure. In this case, the internal space structure of the output side driven gear 310c is formed slightly different, and the rest of the configuration and operation are the same as in the first embodiment.

10, the configuration of the output side driven gear 310 side is the same as that of the first embodiment. However, in the embodiment of FIG. 10, the one-way clutch 230a in the input side drive gear 220 is provided differently from the above-described embodiment.

Although the description is omitted in the above-described embodiment, the multi-stage automatic transmission of the present embodiment can be applied to a general passenger vehicle, a heavy-duty vehicle, various industrial machines, and the like.

As described above, the present invention is not limited to the described embodiments, and various modifications and changes can be made without departing from the spirit and scope of the present invention, which will be apparent to those skilled in the art. Therefore, such modifications or variations will have to be belong to the claims of the present invention.

1 is a schematic internal structure diagram of a multi-stage automatic transmission according to a first embodiment of the present invention,

Figure 2 is a perspective view of the coupling state of the input shaft and the input side drive gear shown in FIG.

3 is a perspective view of a state between the input side drive gear and the output side driven gear, except for the reverse stage;

4 is an exploded perspective view of an output side driven gear;

5 is a perspective view of the coupling state of the hydraulic supply pipe and the output shaft;

6 is a configuration diagram of an arrangement state between an output side driven gear and an input side drive gear according to the operation of the friction member;

7 is an arrangement state structure diagram between an output side driven gear and an input side drive gear according to an operation of a friction member in a multi-stage automatic transmission according to a second embodiment of the present invention;

8 is an arrangement state structure diagram between an output side driven gear and an input side drive gear according to an operation of a friction member in a multi-stage automatic transmission according to a third embodiment of the present invention;

9 is a configuration diagram of a state of arrangement between an output driven gear and an input drive gear according to an operation of a friction member in a multi-stage automatic transmission according to a fourth embodiment of the present invention;

FIG. 10 is a layout view of an arrangement state between an output driven gear and an input drive gear according to an operation of a friction member in a multistage automatic transmission according to a fifth embodiment of the present invention.

* Explanation of symbols for the main parts of the drawings

100: main body housing 210: input side shaft

220: input side drive gear 310: output side driven gear

320: output shaft 400: hydraulic supply pipe

500: hydraulic supply pipe housing 600: piston

700: friction member 810: hydraulic pump

Claims (8)

Body housing; An input side shaft coupled to one side of the body housing so that at least one region is exposed to the outside of the body housing and rotated by engine torque; A plurality of input side drive gears fixed in a radially outer side of the input side shaft and rotating together with the input side shaft; A one-way clutch interposed between the input side shaft and the input side drive gear; A plurality of output side driven gears having an outer surface formed in a pyramid shape so as to be toothed with the plurality of input side drive gears in opposite directions, and having a non-circular cam space formed therein; An output side shaft including a shaft body disposed in a pyramid shape so as to correspond to each of the plurality of output side driven gears one by one, and a shaft bar connected to the shaft body and exposed to the outside of the body housing; ; A hydraulic pressure supply pipe connected to the output side shaft to supply hydraulic pressure to a single pressure chamber formed inside the shaft body; A plurality of pistons each provided in a plurality of branch passages branched from the pressure chamber toward the plurality of output side driven gears and movable radially inward or outward based on the pressure provided; A plurality of friction members each connected to the plurality of pistons and selectively contacted and pressed against an inner circumferential surface of the output side driven gear while being operated by the pistons; And And a control unit for controlling the hydraulic pressure provided from the hydraulic pump to the pressure chamber such that the output shaft is rotated by a pair of gears selected from the plurality of input side drive gears and the plurality of output side driven gears. Transmission. The method of claim 1, And the combination of the plurality of input side drive gears and the plurality of output side driven gears has one reverse stage and eight forward shift stages. The method of claim 2, The input side drive gear and the output side driven gear in the high speed stage area higher than the corresponding gear stage when the gear stage selected from the eight forward stages are advanced by the hydraulic pressure provided from the hydraulic pump to the pressure chamber based on the control signal of the controller. Is slip-friction rotated, and the input side drive gear and the output side driven gear in the low speed end region lower than the shift stage are idling based on the stop frictional rotation. The method of claim 2, The reverse stage is a multi-stage automatic transmission, characterized in that for forming a hydraulic flow path independent of the eight forward gear. The method of claim 1, And a thrust bearing is interposed between the input side drive gears. The method of claim 1, The plurality of friction members are arranged in the cam space at equal intervals in the circumferential direction with each other. The method of claim 1, And the plurality of friction members are arc-shaped blocks or balls. The method of claim 1, And the plurality of pistons are provided to correspond to the plurality of friction members one by one.

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