KR20090096127A - Make use of differential gear and variable slanted disk for continuously variable transmission and working processor - Google Patents

Abstract

A differential gear and variable slanted disk for continuously variable transmission and working processor are provided to enforce the successive transmission. The continuously variable transmission uses the differential gear and variable slope disc. The transmission input shaft(13) delivers the power to the differential assembly. The delivered power is directly delivered to the transmission output axis(15). The signal transmitted from the prime mover rpm sensor and the traveling direction control device active sensor are input to the TCU which is the transmission control computer. The TCU controls the transmission output axis brake device and shift control device.

Description

MAKE USE OF DIFFERENTIAL GEAR AND VARIABLE SLANTED DISK FOR CONTINUOUSLY VARIABLE TRANSMISSION AND WORKING PROCESSOR}

The present invention is to provide a differential gear assembly and a temporary disk for the configuration of a continuously variable transmission to enable a continuously variable transmission of a continuously variable transmission function of a continuously variable transmission applied in a relationship between a prime mover and a transmission used in a vehicle, a ship, or other ranges. Allows the assembly to perform auxiliary occlusal operation and then acts on a continuously variable transmission using differential gears and modifier discs to enable continuous gear-free gearshifts in real time by coordinating and controlling them using the transmission control computer unit (TCU). Relates to a processor.

The present invention is a conventional stepped transmission, weight and volume weighting and production cost and maintenance cost increase problem according to the separate installation of the clutch or torque converter and the durability of the prime mover and the transmission itself due to the shift shock, deterioration of the driving comfort of the operator (driver), etc. In addition, in the continuously variable transmission using the belt and the variable pulley, the power is transmitted by the friction force between the belt and the variable pulley, thereby reducing the power transmission efficiency due to the sliding phenomenon of the belt and the pulley, and the difficulty of the large power transmission and the transmission range. Of power transmission efficiency and rotational body due to the problem of limitation of volume, uncomfortable volume, wear and difficulty of layout, and sliding phenomenon due to power transmission by rolling contact of the rotor even in the conventional Trojan-type continuously variable transmission Degradation of durability due to abrasion of liver and power transmission rate within shift range It is to solve problems such as nonuniformity.

The present invention is to enable the operation of the continuously variable transmission to the stepless prime mover in order to solve the above problems, the operation function of the continuously variable transmission to the mutual matching and perturbation action of the differential gear assembly and the modulated disk assembly. Four different bevel gears having the same number of teeth are formed at right angles to the differential gear, so that different types and types of differential gears such as bevel cross-type differential gears and planetary differential gears can be applied. It is possible to derive the optimum transmission ratio by applying the operating condition for each gear element and the rotational formula for each element according to the gear. Conversion drift by operation of fork side gear and auxiliary input drive gear Power is finally transmitted to the transmission output shaft through the auxiliary input shaft, the output drive gear and the transmission output shaft gear, thereby enabling real-time continuously without step difference. The continuously variable transmission operates as described above by using a transmission control computer device (TCU). Trouble with conventional problems by real-time continuous automatic control by braking the transmission input shaft braking system and controlling the transmission control unit by braking and control operation (adjustment) function of each type of input sensor received by the TCU. Resolved.

The present invention enables the interlocking and engagement operation of the differential gear assembly and the modulator disk assembly in the operation mechanism of the continuously variable transmission, and by applying an operation processor for controlling another shift control through the transmission control computer device (TCU). Up to 0, no need for clutch or torque converter, compact size, simple structure, continuous shift without stepping without any impact, and shifting by gear speed change. As it is infinite or infinite, it has the effect of excellent running performance, and it is possible to transmit power through gears between the gears. Therefore, it is possible to transmit power through continuously variable gears, and to change the arrangement and shape of various elements including gears as necessary. Also available The layout is excellent with ease because of the effect.

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

1 shows a process diagram of a stepless transmission using a differential gear and a modifier disk, FIG. 2 shows a side cross-sectional schematic diagram of a continuously variable transmission using a differential gear and a modifier disk, and FIG. A cross-sectional schematic diagram, a forward cross-sectional schematic diagram, a flat cross-sectional schematic diagram, and a rocking motion schematic diagram are shown.

1 to 3 together, first, the power of the prime mover 10 in FIG. 1 is transmitted to the continuously variable transmission 14 through the transmission input shaft 13 and then the differential gear assembly 14a and the temporary disk assembly ( 14b) transmits the power of the prime mover 10 to the transmission output shaft 15 without changing the power of the prime mover 10 in one gear element and the perturbation and perturbation of the gear gear in the other gear element. The shifted output is derived to the transmission output shaft 15 and finally transmitted to the drive shaft 16a by the driving direction control device 16. The continuously variable transmission 14 is controlled by a transmission control computer unit (TCU) 17. It is automatically controlled by the operation processor, and the shift control device 18 is connected to the TCU 17 through signals input from the driving direction control device operation sensor 17a, the prime mover throttle opening sensor 17d, and the prime mover rpm sensor 17e. Transmission input system By controlling and braking the device 19 in real time, the control of the continuously variable transmission of the continuously variable transmission 14 is controlled. The above-described motive gear opening degree sensor 17d represents the state of the amount of energy supplied to the prime mover 10 and represents an internal combustion engine. Applies only to

The TCU 17, which is responsible for the core functions of the continuously variable transmission 14, has an rpm (rpm speed) of the prime mover 10 according to the throttle opening degree when the prime mover 10 is in the best condition, that is, at the optimum load. Values are continuously inputted, and the prime mover rpm sensor 17e and prime mover throttle opening sensor 17d of the TCU 17 detect the prime mover rpm and the throttle opening value in real time and continuously, and according to the rpm optimum input value. To operate continuously variable speed in real time, and when the prime mover 10 is not optimal load, that is, when it is overloaded, if the rpm value drops due to excessive load according to the throttle opening, it corresponds to the rpm optimum input value. The speed is lowered until the speed is lowered. On the contrary, when the motor is under the proper load state, the rpm value of the prime mover 10 is increased so that the high speed is shifted until it matches the rpm input value. .

In addition, when the transmission output shaft 15 and the driving drive shaft 16a are released from the transmission mode due to the neutral mode of the driving direction controller 16, the continuously variable transmission 14 has no load, and thus the power of the prime mover 10 remains unchanged. The transmission is continuously transmitted by the input value of the TCU 17. In this case, since the transmission output shaft 15 continues to rotate, there is a problem in that the driving direction cannot be controlled. When the control device 16 is in the neutral mode, the transmission output shaft braking device 19 is operated to brake the transmission output shaft 13 so as not to move.

2 and 3 show a side cross-sectional schematic diagram of a continuously variable transmission using a differential gear and a modifier disk controlled and controlled by the operating processor as described above, and a cross-sectional schematic view of the modifier disk assembly 14b. The transmission input shaft 13 discharged from the prime mover 10 is connected to the differential gear case 20 to transmit power of the prime mover 10, and the casing gear 20a is attached to the differential gear case 20. As it is engaged with the inclined disk drive gear 23b and perturbates, it can be seen that the transmission input shaft 13 simultaneously transmits power to the differential gear case 20 and the inclined disk drive gear 23b.

In addition, the pinion gears 22a and 22b facing each other inside the differential gear case 20b while being connected to the differential gear case 20b are side gear A 21a on the left side and side gear B 21b on the right side, respectively. While being engaged to the pinion gears 22a and 22b, the pinion gears 22a and 22b are rotated by themselves while being rotated by the differential gear case 20b under the influence of the side gears 21a and 21b.

The auxiliary input shaft 26 is connected to the side gear A 21a in the differential gear case 20b and passes through a circular opening drilled in the center of the side gear B 21b, and then the outside of the differential gear case 20b. Is connected to the auxiliary input gear A (26a) and the auxiliary input gear B (26b), wherein the auxiliary input shaft 26, side gear A (21a), auxiliary input gear A (26a) and auxiliary input gear B (26b) The auxiliary input shaft 26 and the side gear B 21b are freely rotated without interfering with each other, and the side gear B 21b has a circular opening in the center thereof. Pass the auxiliary input shaft into the opening of the gear, and the end is attached to the output shaft drive gear 27 from the outside of the differential gear case 20b while transmitting power of the prime mover prime mover 10 to the transmission output shaft gear 28 without change or shifting.It performs the function of transmitting the power.

The auxiliary input gear A (26a) and the auxiliary input gear B (26b) are connected to the auxiliary input shaft (26), and are respectively assisted to engage and perturb with the auxiliary input drive gear A (24b) and the auxiliary input drive gear B (25b). The input drive gears A 24b and B 25b transfer the auxiliary power converted from the temporary modulator disk assembly 14b to an element of the differential gear assembly 14a. Consider the power variable mechanism of

The inclined disc drive gear 23b which perturbes with the casing gear 20 transmits power to the temporary change disk 30 which is attached to the inclined disc shaft 23a and connected to the end opposite to the inclined disc shaft 23a. At this time, the temporary changeable disk 30 may cause a free angle change around the connection point, the spin fork 31 is connected to the circumferential end of the temporary changeable disk 30, The front rotational motion does not interfere, but the side rocking motion due to the inclination of the temporary modulator disk 30 is disturbed by the interference of the spin fork 31, and the spin fork gear 31a is attached to the end of the spin fork 31. On the left side of the spin fork gear 31a, the spin fork side gear B 32b and the right side of the spin fork side gear A 32a are engaged with each other and perturbate, and the axis of the spin fork side gear B 32b is the spin fork side gear. The one-way clutch B is connected to the auxiliary input drive gear B 25b by forming a one-way clutch structure through a circular opening drilled in the center of A 32a, and connected to the shaft of the spincop side gear B 32b. When the one-way clutch connected to the shaft of the spin fork side gear A 32a and the one-way clutch A 33a is referred to as 33b, the above-described spin cope side gear B 32b and the spin fork side gear A 32a are Each one-way clutch perturbing the corresponding one-way clutch only when working with the rotation direction set in the one-way clutch B 33b and A 33a, respectively.

3A shows a side cross-sectional schematic diagram of the temporary modulator disk assembly 14b, 3B shows a rocking motion schematic, 3C a front cross-sectional schematic diagram, and 3D a flat cross-sectional schematic diagram, wherein the auxiliary input drive gears 24b and 25b are shown. Although there is one one-way clutch per unit, the auxiliary input drive gears 24b and 25b may have two or more one-way clutches per unit in order to minimize the work penalty at the moment when the rotation direction changes.

While the release sleeve 30b surrounds the temporary modulating disk shaft 23a in a cylindrical shape, the inward spline of the release sleeve 30b and the outward spline of the temporary modulating disk shaft 23a are engaged with each other, while being able to slide in the axial direction. It rotates like the temporary change disk shaft 23a, and the tappet rod 30a is connected to the release sleeve 30b at one end and the other end is connected to one point of the temporary change disk 30 so that the release sleeve The axial sliding motion of the 30b is towed to cause an angular change of the temporary changeable yarn disk 30.

The bevel cross-type differential of the four bevel gears 21a, 21b, 22a and 22b is meshed with each other at right angles to set conditions for the operation mechanism of the temporary modulator disk assembly 14b having the above structure. Using gears, the number of teeth of the four differential gears is the same, the injection force to the differential gear case 20b, the auxiliary input to the side gear A, the output to the side gear B, and the rotation direction of the injection force shaft and the auxiliary input shaft. In the same setting state, when the rotary power discharged from the prime mover 10 is transmitted to the differential gear case 20b, the temporary modulator disk 30 also rotates due to the engagement of the casing gear 20a and the disc drive gear 23b. In this case, the spin fork 31 detects a rocking motion of the side surface of the disk caused by the inclination angle of the temporary modulator disk 30 and transmits the result to the pair of spin fork side gears 32a and 32b. Spin The side gears 32a and 32b are alternately intermittently rotated by the one-way clutches 33a and 33b, and the auxiliary input drive gears 24b and 25b are used as the auxiliary input shaft gears. (26a) and (26b), the auxiliary input shaft 26 transmits a complete rotational motion without an interval, and the side gear A 21a connected to the auxiliary input shaft 26 rotates in the same manner as the auxiliary input shaft 26, with a bevel cross. When the side gear B 21b is influenced through the pinion gears 22a and 22b of the differential gear, the side gear B 21b is rotated according to the formula shown in Table 2-2 below and the side gear B is rotated again. 21b transmits the shifted power to the transmission output shaft through the transmission output shaft gear 28, and when the temporary change disk 30 makes a large inclination angle, the side wall portion has a large radial swing motion within the unit time. The amount of rotation is transmitted to the input shaft 26 In addition, according to the formula of Table 2, the low shift is made. On the contrary, the smaller the inclination angle of the temporary modifier disk 30 is, the higher the shift is. .

Table 1 shows the gear ratios of continuously variable transmissions using differential gears.The setting conditions are as follows: First, four bevel gears with the same number of teeth are perpendicular to each other. Second, the rotational direction of the injection force shaft and the auxiliary input shaft represents the speed ratio of the sequential combination of each gear element.

TABLE 1

 Table 1-a ① Main input: Side gear A ② Auxiliary input: Side gear B ③ Output: Differential gear case Rotational direction of injection force shaft and output shaft Top gear ratio Transmission ratio Same ∞ 0.5

 Table 1-b ① Main input: Differential gear case ② Auxiliary input: Side gear A ③ Output: Side gear B Rotational direction of injection force shaft and output shaft Top gear ratio Transmission ratio opposite direction 2 0

 Table 1-c ① Main input: Side gear A ② Auxiliary input: Differential gear case ③ Output: Side gear B Rotational direction of injection force shaft and output shaft Top gear ratio Transmission ratio Reverse direction when auxiliary input shaft speed is less than 1/2 of injection force shaft speed ∞ 0

Table 2 below shows the rotational speed comparison of the differential gear case 20b and the side gear A 21a and the side gear B 21b according to the role change in the bevel cross differential gear. Four teeth are the same, and second, the injection force and the rotational direction of the auxiliary input are the same.

TABLE 2

Table 2-1 Table 2-2 Table 2-3 ㆍ (Side Gear A + Side Gear B) × 1/2 = Differential Gear Case ㆍ (2 × Differential Gear Case) -Side Gear A = Side Gear B ㆍ The direction of rotation of main input shaft and that of output shaft are reversed ㆍ (2 × Differential Gear Case) -Side Gear A = Side Gear B ㆍ When the rotational speed of the auxiliary input shaft is less than 1/2 of the rotational speed of the injection force shaft, the output shaft is opposite the injection force shaft. Injection force Auxiliary input Print Injection force Auxiliary input Print Injection force Auxiliary input Print Side gear A Side gear B Differential gear case Differential gear case Side gear A Side gear B Side gear A Differential gear case Side gear B 1,000 0 500 1,000 0 2,000 1,000 0 -1,000 1,000 200 600 1,000 200 1,800 1,000 200 -600 1,000 500 750 1,000 500 1,500 1,000 500 0 1,000 1,000 1,000 1,000 1,000 1,000 1,000 1,000 1,000 1,000 1,500 1,250 1,000 1,500 500 1,000 1,500 2,000 1,000 2,000 1,500 1,000 2,000 0 1,000 2,000 3,000 1,000 3,000 2,000 1,000 1,000 3,000 5,000 1,000 6,000 3,500 1,000 1,000 5,000 9,000

In Table 2, a bevel cross type differential gear is applied to the differential gear application type, and various types and types of differential gears such as planetary differential gears can be applied.

When comparing the speed ratio and the rotational speed according to the setting conditions when the bevel cross type differential gear is applied, see Table 1 and Table 2. If the bevel cross type differential gear is applied, the number of four gear teeth may be the same or different. However, if the number of gear teeth is the same, the main power rotation direction and the auxiliary power rotation direction may be the same or vice versa. If the same rotation direction is applied, the main power is transmitted to the differential gear case 20b and the side gear A 21a is applied. ), Or a method of deriving the output from the side gear B (21b), or may be applied differently.

First, in the bevel cross type differential gear, the number of teeth of the pair of pinion gears 22a, 22b and the pair of side gears 21a, 21b is the same, the main power rotation direction and the auxiliary power rotation direction are the same, and the side gear A ( 21a) When the main power is input, the auxiliary power is input to the side gear B (21b) and output from the differential gear case 20b, the rotation formula between the elements is the number of revolutions of the differential gear case = ( Rotational speed + rotational speed of side gear B) x 1/2, and the comparison of the rotational speed between the elements based on this formula is shown in Table 2-1 above, and the transmission ratio based on this formula is shown in Table 1-a. Likewise, the maximum speed ratio is ∞ and the minimum speed ratio is up to 0.5.

Secondly, the other conditions are the same as those described in the first above, and the main power is applied to the differential gear case 20b, and the auxiliary power is applied to the side gear A 21a and output from the side gear B 21b. The rotation formula between the elements is the rotational speed of the side gear B = (2 x differential gear case rotational speed)-the rotational speed of the side gear A. Table 2 compares the rotational speed between the elements based on this formula. It is equal to -2, and the transmission ratio based on this formula is as shown in Table 1-b. The maximum speed is 2 and the minimum speed is 0.

Third, the other conditions are the same as described above, the rotational ratio between each element when the injection force to the side gear A (21a) and auxiliary input to the differential gear case (20b) and output from the side gear B (21b), Rotational speed of side gear B = (2 x differential gear case rotational speed)-Rotational speed of side gear A. Based on this formula, the rotational speed comparison between the elements is shown in Table 2-3 and the gear ratio is shown in Table 1 As in -c, it is the lowest 0 at the maximum ∞. However, in this case, when the rotation speed of the auxiliary input shaft 26 is less than 1/2 of the rotation speed of the injection force shaft, the direction of rotation of the output shaft is opposite to the rotation direction of the injection force shaft. There are disadvantages that the irregular rotation direction should be improved by supplementing other technical points such as (33a) and (33b).

As described above, one of the several gear elements 20, 21a and 21b which have an organic influence on each other in the differential gear is invariably transmitting the power of the prime mover 10, and the power of the prime mover is transferred to the other place. Variable and transmitted through the control device, and in another place except the two of the former to derive the shifted output, the modifier disk 30 receives the power of the prime mover as it is, the simple rotational movement toward the front side but from the side The oscillating motion is to convert the oscillating motion into the rotational motion and transfer the converted power to one element of the differential gear device by converting the power of the prime mover.

1 is a process diagram of an operating processor of a continuously variable transmission,

2 is a side cross-sectional schematic diagram of a continuously variable transmission,

3 is a cross-sectional schematic diagram of the elements of the temporary modulator disk assembly.

<Description of the symbols for the main parts of the drawings>

(10)-prime mover (13)-transmission input shaft

(14)-Stepless Transmission (14a)-Differential Gear Assembly

(14b)-Modifier Disc Assembly (15)-Transmission Output Shaft

(16)-Drive Direction Control (16a)-Drive Shaft

(17)-Computer control system for transmission control (17a)-Driving sensor

(17d)-Motor throttle opening sensor (17e)-Motor rpm sensor

(18)-shift control (19)-transmission output shaft brake

(20)-Differential Gears (20a)-Casing Gears

(20b)-Differential Gear Case (21a)-Side Gear A

(21b)-Side Gear B (22a) (22b)-Pinion Gear

(23a)-inclined disc shaft (23b)-disc drive gear

(24a)-Auxiliary input drive shaft A (24b)-Auxiliary input drive gear A

(25a)-Auxiliary input drive shaft B (25b)-Auxiliary input drive gear B

(26)-Auxiliary input shaft (26a)-Auxiliary input gear A

(26b)-Auxiliary input gear B (27)-Output shaft drive gear

(28)-Transmission output shaft gear (30)-Modifier disc

(30a)-tappet rod (30b)-release sleeve

(30c)-Release Fork (31)-Spinfork

(31a)-Spinfork Gears (32a)-Spinfork Side Gears A

(32b)-Spinfork Side Gear B (33a)-One-way Clutch A

(33b)-One-way clutch B

Claims (6)

With regard to the continuously variable transmission 14 using the differential gear 20 and the temporary modifier disk 30, and thus the operating processor, the transmission input shaft 13 discharged from the prime mover 10 may include the differential gear assembly 14a and the temporary modifier. Power is transmitted to the continuously variable transmission 14 that is engaged with the disk assembly 14b, and the transmitted power is variablely shifted by the transmission power itself or by the temporary modulator disk assembly 14b and is transmitted to the transmission output shaft 15 at shift power. In the course of the final transmission to the drive shaft 16a by the driving direction control device 16, the driving direction control device operation sensor 17a, the prime mover throttle opening degree sensor 17d, and the prime mover rpm sensor 17e are transmitted. A signal is inputted and received by the TCU 17, a transmission control computer device, to operate the brake to control the transmission output shaft braking device 19 and the transmission control device 18. How to ensure that the speed is carried out smoothly. The four bevel gears 21a, 21b, 22a, and 22b are perpendicular to each other in the continuously variable transmission 14 of claim 1, which is composed of a differential gear assembly 14a and a variable disk assembly 14b. The four gears 21a, 21b, 22a and 22b have the same number of gears as the setting method of applying the interlocking bevel cross type differential gear, and the main power rotation method and the auxiliary power rotation direction are the same. The converted auxiliary power detection method of the temporary changeable disk assembly 14b together with the main power to the case 20b, the auxiliary power to the side gear A 21a, and the side gear B 21b to shift the output. A method of applying a special rotating chain modulated disk 30 and using two or more one-way clutches 33a and 33b per auxiliary input drive gear 24b and 25b. The method according to claim 1, wherein all kinds of differential gears (20) and all kinds of special rotating bodies can be applied to the differential gear (20) and the special rotating body modulated disk (30). 2. A method according to claim 1, wherein the planetary differential gear is applied to the differential gear assembly (14a) of the continuously variable transmission (14). According to claim 1, the rpm control of the prime mover (10) is set continuously according to the state of the energy supply when the prime mover (10) is a proper load in the TCU (17) for the transmission control computer device, and the TCU (17) through the sensor Method to detect the prime mover (10) rpm and energy supply state in real time and continuously to operate the shift control device (18) according to the preset value to enable continuous stepless speed change in real time. 2. The method according to claim 1, wherein the transmission output shaft brake (19) is operated to brake the transmission output shaft (13) so that it does not move when the traveling direction steering device (16) is in the neutral mode.

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