KR100797544B1 - Shift gears assembly - Google Patents

Abstract

A shift gear assembly is provided to minimize a mechanical shock on the shift gear assembly during a speed shifting process by continuously adjusting a rotation speed and a torque. An input member(200) includes an input gear and an input side carrier disk. The input gear is implemented on a main shaft(100). Plural input side planetary gears are radially arranged in the input side carrier disk, so that the planetary gears are rotated according to a rotation force inputted from a power source. An output member(300) includes an output side carrier disk and an output gear. Plural output side planetary gears are rotatably arranged in the output side carrier disk, so that the rotation force from the input side planetary gear is outputted. A pair of torque couplers(400) are connected between the input and output members. The torque couplers change the rotation force of the input side planetary gear into a continuous rotation ratio and deliver the continuous rotation ratio to the output side planetary gear.

Description

Transmission gear assembly {SHIFT GEARS ASSEMBLY}

The present invention relates to a transmission gear assembly, and more particularly, to a transmission gear assembly that efficiently uses power generated from a power source and continuously changes a torque ratio to reduce shock caused by shifting and to increase power transmission efficiency. will be.

As is well known, in power-driven equipment such as vehicles or machine tools, transmissions are used to obtain appropriate rotational speeds and torques. Among these transmissions, planetary gear units are widely used because they are easy to shift and control.

The conventional planetary gear unit is composed of a ring gear, a sun gear arranged at a centrifugal position of the ring gear, a plurality of planetary gears engaged between the sun gear and the ring gear, and a carrier connecting the shafts of the plurality of planetary gears.

Therefore, the power generated in the engine of the vehicle is shifted to the speed increase, the deceleration, the neutral, the direct connection, and the reverse state by fixing any one component or driving or free state.

7 is a graph showing the driving speed of the vehicle speed and the engine, it can be seen that in the conventional automatic transmission in which the gear ratio of each stage is fixed, the driving force varies greatly according to each shift stage. That is, as the shift curve of the automatic transmission shown by a solid line falls sharply without drawing a constant curve at each shift stage, there is a problem that the acceleration performance decreases and the response occurs due to the shift and the shock occurs due to the shift.

Furthermore, the conventional transmission has a problem that the engine speed is lowered at every initial shift during upshift, leading to energy loss due to the additional loss of fuel until the engine speed is restored.

The present invention has been made to solve the conventional problems as described above, the object of the present invention is to continuously use the power generated from the power source while continuously changing the torque ratio to reduce the shock caused by the transmission To provide an assembly.

The present invention to achieve the above object, the main shaft; An input member including an input gear provided on the main shaft and an input side carrier disk radially provided with a plurality of input side planetary gears to be engaged by the input gear and rotated by a rotational force input from a power source; An output member including an output side carrier disk rotatably provided with a plurality of output side planetary gears connected to output the rotational force input from the input side planetary gear, and an output gear meshed to output the rotational speed of the output side planetary gear; Connected between the output member and the input member, and comprises a pair of torque coupler to convert the rotational force of the input planetary gear to a continuous rotation ratio by the phase difference of each carrier disk to transmit to the output planetary gear.

The input gear may be implemented as an input side sun gear or an input side ring gear installed in the main shaft to engage the input side planetary gear, and the output gear may be implemented as an output side sun gear or output side ring gear installed in the main shaft to engage the output side planetary gear.

The pair of torque couplers are connected to the rotary shaft of the input planetary gear, a rail coupler having a guide rail, and an operation pin provided to slide along the guide rail of the rail coupler, and a pin connected to the rotary shaft of the output planetary gear. Preferably, the coupler is composed of a plurality of pairs of torque couplers to be connected to the rotary shafts of the plurality of input planetary gears and the output planetary gears, and the output planetary gears are provided with clutches to output the fastest from the rail coupler. The extracted torque is continuously extracted.

The guide rail is made up of a plurality of angles between them form a conformal angle, wherein the actuating pin is made of a plurality of guide rails to correspond to the plurality of guide rails.

And it further comprises an eccentric control means for continuously adjusting the centrifugal or eccentric of the pair of torque coupler, the eccentric control means is made of a control pin provided on each carrier disk to adjust the centrifugal or eccentricity of the torque coupler. In addition, while the built-in input member and output member and the torque coupler further includes a drum case formed with a guide hole to guide the operation of the adjustment pin of each carrier disk, along the axial direction of the main shaft by the drum case transfer means Transferred.

The conveying means includes a slider connected to the drum case to be transportable along the axial direction of the main shaft, a ball screw connected to convey the slider, and a drive motor connected to drive the ball screw.

Optionally, the eccentric control means may be implemented with a worm wheel provided as an outer circumferential surface of each carrier disk, a worm engaged with the worm wheel, and a worm motor connected to drive the worm.

According to the present invention configured as described above, as centrifugal and eccentricity of the torque coupler is made while the guide rail and the operating pin of the torque coupler are slid, the rotation speed and the torque are continuously adjusted to minimize the occurrence of shock due to the shift stage according to the shift. It can work.

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

The gear shift assembly of the present invention includes an input member 200 and an output planetary gear including an input carrier disk 230 having a main shaft 100, an input gear installed on the main shaft 100, and an input planetary gear 220. An output member 300 including an output side carrier disk 330 and an output gear 310 provided with a 320 and an input planetary gear 220 and an output planetary gear 320 are connected to each other continuously. It includes a torque coupler 400 for converting the rotation ratio.

Referring to FIG. 3, the transmission gear assembly of the present invention includes a main shaft 100 fixed at both ends, an input member 200 and an output member 300 installed at the main shaft 100, and the input member. It is roughly divided into a torque coupler 400 connected between the 200 and the output member 300.

As shown in FIG. 4, the input member 200 includes an input gear installed on the main shaft 100, that is, an input side sun gear 210 and a plurality of input side planetary gears disposed radially to engage the input side sun gear 210. The input side carrier disk 230 is rotatably installed on the main shaft 100 so that the idle of the 220 is possible.

In addition, the input sun gear 210 is fixed to the main shaft 100 by key coupling, and the three input planetary gears 220 engaged with the input sun gear 210 have an angle between the respective rotation shafts 222 at an input side. It is rotatably installed on the carrier disk 230, whereby the input planetary gear 220 rotates along the circumference of the input carrier disk 230 and rotates while engaging the input side sun gear 210. In FIGS. 2 to 5, three input planetary gears are illustrated, but it is apparent that the number of input planetary gears may be selectively varied.

In addition, as shown in Figures 2 to 4, the input side carrier disk 230 is composed of a pair of substantially disks between the rotating shaft 222 of both ends of the input planetary gear 220 is rotatably installed, The outer circumferential surface of the input side carrier disk 230 is provided with an input side adjustment pin 232 to adjust the phase difference with the output side carrier disk 330.

As shown in FIG. 4, the output member 300 includes an output gear rotatably installed on the main shaft 100, that is, an output side sun gear 310, and a plurality of output side planetary gears meshing with the output side sun gear 310. The output side carrier disk 330 is rotatably installed on the main shaft 100 so that the idle of the 320 is possible.

In addition, three output side planetary gears 320 engaged with the output side sun gear 310 may be rotatably installed on the output side carrier disk 330 to correspond to the input side planetary gear 220, thereby output side planetary gear 320. Rotates along the circumference of the output carrier disk 330 and rotates the output sun gear 310.

In addition, the output side carrier disk 330 also comprises a pair formed of a disk like the input side carrier disk 230, between both ends of the rotation shaft 322 of the output planetary gear 320 is rotatably installed, the output side carrier disk ( The outer circumferential surface of the 330 is provided with an output side adjustment pin 332 to adjust the phase difference with the input side carrier disk 230.

A pair of torque couplers 400 are connected between the input member 200 and the output member 300 configured as described above, and the torque coupler 400 is connected to the rotation shaft 222 of the input planetary gear 220. It consists of a pin coupler 430 connected to the rotary coupler 322 of the rail coupler 410 and the output planetary gear 320.

As shown in FIG. 3, the rail coupler 410 is provided with at least one guide rail 412 to be orthogonal to the main shaft 100, and the pin coupler 430 is operated to slide along the guide rail 412. Pin 432 is provided.

And the guide rail 412 is formed in a V-shape as shown in Figure 5a to form a structure symmetrical about the axis, the operation pin 432 is sliding along the guide rail 412 to form a centrifugal or eccentric rail coupler 410 Rotation of the pin coupler 430, thereby converting the rotational speed of the input planetary gear 220 to a continuous rotation ratio and transmitted to the output planetary gear 320, as a result, the output side sun gear 310 The rotation speed, that is, the torque, is output through

This torque varies depending on whether the centers of rotation C1 and C2 of the rail coupler 410 and the pin coupler 430 are set to centrifugal or eccentric. That is, as shown in Figure 5a, according to the distance r between the center of rotation (C1) (C2) of the rail coupler 410 and the pin coupler 430, the rotational speed of the rail coupler 410 and the pin coupler 430 ), The rotational speed is different, whereby the output planetary gear 320 connected to the pin coupler 430 rotates the output side sun gear 310 at a different rotational speed.

In particular, since the rail coupler 410 is rotated by the input planetary gear 220 having the same rotational speed by meshing with the input side sun gear 210, the three are rotated at the same rotational speed, but each guide rail 412 is shown in FIG. As shown in FIG. 5A, the guide rail 412 disposed at the center of the upper portion of the guide pin 412 rotates the closest operating pin 432 to achieve a high rotational speed. Output to the pin coupler 430. That is, one operation pin 432 adjacent to the guide rail 412 is rotated by the rail coupler 410 to transmit the rotational force to the pin coupler 430.

Subsequently, the rail coupler 410 disposed above the center of FIG. 5A is disposed to the upper right side of FIG. 5B and the lower right side of FIG. 5C while rotating and revolving in the direction of the arrow, wherein the rail coupler disposed on the lower left side of FIG. 5C. As the guide rail 412 of 410 is closest to the operating pin 432, and outputs the highest rotational speed to the pin coupler 430 as described above, such a series of operations to be made continuously do.

As described above, the output of the fastest rotation speed is enabled by the clutch 340 installed on the rotation shaft 322 of the output planetary gear 320. The clutch 340 extracts the rotational speed of the fastest pin coupler 430 and outputs it to the output planetary gear 320, while the other pin coupler 430 achieves the idling state, and the output side sun gear due to the difference in rotational speed. Damage and malfunction of the 310 and the output planetary gear 320 are prevented in advance.

Here, the clutch 340 is preferably implemented as a one-way clutch to intermittent one-way rotation of the pin coupler 430, it is obvious that it can be implemented as a bidirectional clutch, if necessary.

The center of rotation of the above-described rail coupler 410 and the pin coupler 430 is centrifugally or eccentrically continuously adjusted by the phase difference of each of the carrier disks 230 and 330 by the eccentric control means.

The eccentric control means is implemented by an input side control pin 232 provided on the input side carrier disk 230 and an output side control pin 332 provided on the output side carrier disk 330, each of which control pins 232 and 332. Drum case 500 formed with a guide hole 510 to guide the operation of the input member 200, the output member 300 and the torque coupler 400 is built. And the case disk 520 closing the open both sides of the drum case 500 is installed to be transported along the axial direction of the main shaft (100).

The drum case 500 guides the operation of each of the adjustment pins 232 and 332 while being transported along the axial direction of the main shaft 100, whereby each of the carrier disks 230 and 330 is the main shaft 100. Because of the phase difference while rotating around the torque coupler 400 is centrifugal or eccentric is to be adjusted.

The drum case 500 is conveyed in the axial direction of the main shaft 100 by the conveying means 600, the conveying means 600, the drum case 500 to be transported along the axial direction of the main shaft 100. ), A ball screw 620 connected to transfer the slider 610, a screw frame 630 rotatably supporting the ball screw 620, and a ball screw 602. It includes a drive motor 650 connected to drive.

Here, the slider 610 is connected to any one case disk 520 closing both ends of the drum case 500. The ball screw 620 is disposed in the axial direction of the main shaft 100, and one end thereof is connected to a screw member (not shown) provided in the slider 610, and a driven pulley 622 is provided at the other end thereof. Installed and rotated, the screw frame 630 is fixed to support the rotation of such a ball screw 620. In addition, the drive pulley 652 is installed on the motor shaft of the drive motor 650 for rotating the ball screw 620 is connected to the driven pulley 622 by a belt 640.

Accordingly, the driven pulley 622 and the ball screw 620 connected to the belt 640 are rotated by the driving motor 650, and the slider 610 is rotated by the main shaft (620) by the rotation of the ball screw 620. Since it is conveyed in the axial direction of the 100, the drum case 500 is also conveyed in the axial direction of the main shaft 100 and each control pin 232, 332 is guided to the guide hole 510 as described above.

When described in detail according to the accompanying drawings the overall operating relationship of the present invention configured as follows.

When explaining the most easy operation relationship, the input side carrier disk 230 is rotated in one direction by the power source, the input side sun gear 210 is fixed to the main shaft 100, so the input side planetary gear 220 is the input side While rotating with the carrier disk 230, the rotation is to be rotated, thereby the rail coupler 410 also serves to rotate and rotate.

Subsequently, the rail coupler 410 of the input carrier disk 230 having a phase difference with the output carrier disk 330 rotates the pin coupler 430, so that the output planetary gear 320 rotates with the output carrier disk 330. Revolving together, the output sun gear 310 is to output the rotational speed of the output planetary gear 320.

Here, the action of the torque coupler 400 is the same as the following operation relationship will be described later.

Referring to the accompanying drawings and the other operating relationship as described above are as follows.

First, the power means 10 for generating a power source includes a driven flywheel 12 connected to the output side carrier disk 330 and a drive flywheel 14 connected to the driven flywheel 12 by a belt 16. It includes a motor 18 installed.

Accordingly, the output carrier disk 330 is rotated in one direction about the main shaft 100 by the driving of the motor 18, and the output planetary gear 320 and the pin coupler are rotated by the rotation of the output carrier disk 330. 430 revolves with the output side carrier disk 330, wherein the output side sun gear 310 is rotatably installed on the main shaft 100, but the output side planetary gear 320 is output side carrier by the clutch 340. Rotation in the opposite direction of the disk 330 is intermittent and therefore does not rotate.

Subsequently, the rail coupler 410 and the input planetary gear 220 also revolve together with the input carrier disk 230 by the pin coupler 430, wherein the input planetary gear 220 engaged with the fixed input side sun gear 210 is rotated. ) Rotates because the rail coupler 410 also rotates. That is, the electromotive force of the output side carrier disk 330 rotates the input planetary gear 220 together with the revolution, thereby rotating the output planetary gear 320. Looking more closely, the three input side planetary gears 220 revolve simultaneously. While rotating while the input side carrier disk 230 has a phase difference with the output side carrier disk 330, the guide rail 412 of the rail coupler 410 rotating at the fastest angular velocity touches the operation pin 432 The coupler 430 rotates, and the output side sun gear 310 meshed with the pin coupler 430 outputs a rotational force.

The rotation speed of the output planetary gear 320 is adjusted by centrifugal or eccentricity with respect to the rotation shafts 222 and 322 of the input planetary gear 220 and the output planetary gear 320. For example, when the rotation shafts 222 and 322 of the input planetary gear 220 and the output planetary gear 320 are centrifuged, the rotation speeds of the input planetary gear 220 and the output planetary gear 320 become the same. However, when the rotation shafts 222 and 322 of the input planetary gear 220 and the output planetary gear 320 are eccentric as shown in FIG. 5A, the rotation shafts 222 and 322 of the respective planetary gears 220 and 320 are eccentric. Since the distance r is generated, the rotation speed of the output planetary gear 320 is faster than the rotation speed of the input planetary gear 220, and the output shaft sun gear 310 meshed with the output planetary gear 320 is also present. The speed of rotation becomes faster. As a result, the rotational speed, that is, torque, is output by the distance r generated between the two axes of each coupler 410 and 430.

Subsequently, the guide rail 412 of the rail coupler 410 shown in the upper right side in FIG. 5B rotates the operation pin 432 of the pin coupler 430, wherein the other two rail couplers 410 are clutches ( Since it is idling by the 340 to rotate the pin coupler 430 at the fastest angular speed.

The rail coupler 410 shown at the bottom right of FIG. 5C while being rotated by an angle following FIG. 5B can no longer rotate the pin coupler 430 at the fastest speed, but the rail coupler shown at the bottom left in FIG. 5C. Since the guide rail 412 of 410 rotates the pin coupler 430 at the fastest angular velocity, the fastest angular velocity is continuously transmitted to the pin coupler 430, and this series of processes is continued. At this time, the clutch 340 is to interrupt the rotation of the output planetary gear 320 so that the pin coupler 430 is rotated at the fastest angular velocity as described above.

Centrifugal or eccentricity of the above-mentioned torque coupler 400 is made by the eccentric control means, in more detail, the drum case 500 is transferred in the axial direction of the main shaft 100 by the transfer means 600, As a result, the guide slot 510 of the drum case 500 operates the adjustment pins 232 and 332 of each carrier disk 230 and 330.

Accordingly, the actuating pins 432 slide along the guide rails 412 of the torque coupler 400 to form a distance r between the centers of rotation of the couplers 410 and 420. Formation is to control the rotational speed and torque.

According to this embodiment of the present invention, since the continuous adjustment of the rotational speed and torque is implemented by sliding the guide coupler 412 and the operating pin 432 of the torque coupler 400, so-called shift stage generated when the shift is made The impact of becomes close to the abnormal curve (double dashed line) in FIG.

On the other hand, the input gear of the present invention may be implemented as an input side ring gear installed in the main shaft 100 to engage the input side planetary gear 220, wherein the input side ring gear is preferably fixed to the main shaft (100). . In addition, the output gear of the present invention may be implemented as an output side ring gear installed in the main shaft 100 to be engaged with the output side planetary gear 320, wherein the output side ring gear is rotatably installed in the main shaft 100. desirable.

On the other hand, Figures 6a and 6b shows another embodiment of the eccentric adjustment means of the present invention, the eccentric adjustment means of the present invention is formed of the outer peripheral surface of each of the input carrier disk 230 and output side carrier disk 330 A worm wheel 234, 334, a worm 710 engaged with the worm wheels 234, 334, and a worm motor 720 for driving the worm 710 are implemented. The worm wheels 234 and 334 may be partially formed on the outer circumferential surface of each carrier disk 230 and 330, and the worm 710 may be connected to the rotation shaft of the worm motor 720 so that each carrier disk 230 and 330 may be formed. Adjust the phase difference of).

The foregoing descriptions are merely illustrative of preferred embodiments of the present invention, and it is apparent that the present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the technical idea.

1 is a perspective view of the present invention.

Figure 2 is an exploded perspective view of the drum case of the present invention.

Figure 3 is an exploded perspective view of the input member and the output member of the present invention.

4 is a side view of the present invention.

5a to 5c is an operation of the torque coupler according to an embodiment of the present invention.

6a and 6b is an exemplary view showing another embodiment of the eccentric control means according to an embodiment of the present invention.

7 is a graph showing the driving force of the vehicle speed and the engine.

♠ Explanation of symbols on the main parts of the drawing ♠

100: main shaft 200: input member

210: input side sun gear 220: input side planetary gear

230: input side carrier disk 300: output member

310: output side sun gear 320: output side planetary gear

330: output side carrier disk 340: clutch

400: torque coupler 410: rail coupler

412: guide rail 430: pin coupler

432: operation pin 500: drum case

510: guide 600: conveying means

610: slider 620: ball screw

620: drive motor

Claims (14)

Main shaft 100; And an input gear provided on the main shaft 100 and an input side carrier disk 230 radially provided with a plurality of input side planetary gears 220 to be engaged by the input gear and rotated by a rotational force input from a power source. Member 200; An output side carrier disk 330 rotatably provided with a plurality of output side planetary gears 320 connected to output the rotational force input from the input side planetary gear 220, and to output the rotational speed of the output side planetary gear 320; An output member 300 that includes an output gear that is engaged; Is connected between the output member 300 and the input member 200, by converting the rotational force of the input planetary gear 220 to a continuous rotation ratio by the phase difference of each carrier disk 230, 330 output side planetary gear 320 A pair of torque couplers 400 for transmission; Transmission gear assembly comprising a. The method according to claim 1, The input gear is a gear shift assembly comprising an input side sun gear (210) installed on the main shaft (100) to engage the input side planetary gear (220). The method according to claim 1, And the input gear is an input side ring gear configured to engage the input planetary gear 220. The method according to claim 2 or 3, The output gear assembly is a gear shift assembly, characterized in that consisting of the output side sun gear 310 installed on the main shaft to engage the output planetary gear (320). The method according to claim 2 or 3, The output gear assembly is an output gear assembly, characterized in that made of an output side ring gear to be engaged with the output planetary gear (320). The method according to claim 1, The pair of torque couplers 400, A rail coupler 410 connected to the rotary shaft of the input planetary gear 220 and provided with a guide rail 412; Transmission gear assembly, characterized in that consisting of a pin coupler (430) is provided with a working pin (432) to slide along the guide rail (412) of the rail coupler (410) connected to the rotation shaft of the output planetary gear (320). The method according to claim 6, The pair of torque couplers 400 are formed in plural to be connected to the rotation shafts of the plurality of input planetary gears 220 and the output planetary gears 320, respectively. Transmission gear assembly, characterized in that the output planetary gear 320 is a clutch 340 is installed to continuously extract the rotational force output from the rail coupler (410) the fastest. The method according to claim 6 or 7, The guide rail (412) is composed of a plurality of transmission gear assembly, characterized in that the angle between them form a conformal angle. The method according to claim 8, The actuating pin 432 is a transmission gear assembly, characterized in that formed in plural to correspond to the plurality of guide rails (412). The method according to claim 1 or 6, Transmission gear assembly characterized in that it further comprises an eccentricity control means for continuously adjusting the centrifugal or eccentricity of the pair of torque coupler (400). The method according to claim 10, The eccentric control means is a gear shift assembly, characterized in that consisting of the control pins (232, 332) provided on each carrier disk (230) (330) to adjust the centrifugal or eccentricity of the torque coupler (400). The method according to claim 11, The guide 510 is configured to guide the operation of the adjustment pins 232 and 332 of the carrier disks 230 and 330 while the input member 200, the output member 300, and the torque coupler 400 are built-in. Further comprising a drum case 500, wherein the drum case 500 is a gear shift assembly characterized in that the conveying means is transported along the axial direction of the main shaft (100) by the conveying means (600). The method according to claim 12, The conveying means 600, the slider 610 connected to the drum case 500 to be transportable along the axial direction of the main shaft 100, and the ball screw 620 connected to convey the slider 610 and And a drive motor (650) connected to drive the ball screw (620). The method according to claim 10, The eccentric control means, the worm wheels 234 and 334 provided on the outer circumferential surface of each of the carrier disks 230 and 330, the worm 710 engaged with the worm wheels 234 and 334, and the worm 710 A transmission gear assembly comprising a drive motor 720 connected to drive a).

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