KR20000036425A - Hydraulic stepless Automatic speed changer - Google Patents

Abstract

PURPOSE: A continuously variable transmission is provided to adjust an automatic adjustment range according to a traveling state and to prevent vibration by moving hydraulic pressure on a shaft as a center. CONSTITUTION: An output shaft(10-2) of a hydraulic motor is not rotated with no hydraulic pressure when a vein motor rotates. A moving bush(16-2) moves with the little movement of an operating piston(17) and then a rotor(13) moves to a spring(19) so a moving bush(16-1) moves together. Thus, a hydraulic standard point(16a) spaces with a rotary bush hydraulic standard point(16b). An automatic continuously variable transmission is 1/20 of the interval and 20 times of power compared with the present transmission. However, the transmission continuously changes a shafting rate and accelerates so that a vehicle starts without excessive engine power and a clutch is not slippery.

Description

Stepless automatic transmission {Hydraulic stepless Automatic speed changer}

The continuously variable automatic transmission according to the present invention is more than the technology filed in advance following the application filed 1999,01.28 (Application No. 10-1999-0002771) and 2000.01.05 (Application No. 10-2000- 0000364). It is the development of new and advanced technology, and it relates to a new continuously variable automatic transmission that will be applied to ordinary cars. The continuously variable automatic transmission of the present invention uses hydraulic pressure, and is a hydraulic transmission invented in a concept of a completely new method from the hydraulic transmission used in the related art. In a continuously variable automatic transmission there is no need for a clutch. In the hydraulic transmission, the hydraulic pump uses a vane pump. In this case, the shifting method generally shifts the center of the rotor rotating the vane of the pump to obtain a change in hydraulic pressure. will be . That is, the change in the pressure and the flow rate of the hydraulic pressure is made only within the moving range of the center of the rotating part. The hydraulic generation and the change of the flow rate of the present invention are made as follows. Instead of using a fixed volume vane pump chamber as in the conventional method, the volume of the parallel pump chamber can be varied from 0 to the required maximum volume. Here, the absence of the volume of the vane pump chamber means that no hydraulic pressure can be generated even when the vane rotates, and no rotational force is generated on the secondary output side even if a rotational force is applied to the primary input side of the continuously variable transmission. In the case of the conventional automatic and manual transmission, the input side and the output side are connected and disconnected depending on whether the clutch operates. In the automatic continuously variable transmission of the present invention, when the vehicle is operated by the driver's operation, the vehicle moves without an additional clutch, and acceleration, shifting, etc. are automatically made.

Referring to the non-load state diagram of the hydraulic pump for generating the hydraulic pressure shown in FIG. 1 of the continuously variable automatic transmission according to the present invention in detail, the hydraulic input shaft 10-1 connected to the rotational output shaft of the engine of the vehicle rotates. Will rotate. In the rotor 13, several vanes are inserted into the vane groove 3a-1 in the rotor 3a shown in FIG. 3 and are in contact with the cam ring 12-1 of FIG. On the other hand, the rotary bushing 15 inscribed in the cylinder on the rotor 13 is provided with a groove through which vanes can pass, as shown in Fig. 4-2. The rotating bush 15 in FIG. 1 is equipped with bearings 18-2 and 18-3 so as to rotate smoothly outside the rotor 13. Since the bearing 18-3 is pressurized by the movable bush 16-1, a thrust bearing is adopted. The problem to be described here is that the two reference planes, the hydraulic reference plane 16a of the rotary bush 15 and the hydraulic reference plane 16b of the movable bush 16-1, are in close contact with each other on the same line in FIG. In Fig. 1, the vane 14 rotating together with the rotary shaft 10-1 is a vane of a pump for generating hydraulic pressure, but the vane 14 of the rotary bush 15 and the movable bush 16-1 in close contact with the rotary bushing hydraulic reference point 16a. Since there is no space on the bush surface, it does not act as a pump and idles. In other words, if the rotational force of the engine idles, it can be seen that the clutch is disconnected in the conventional vehicle structure. At this time, the rotor 13 and the vane 14 inserted therein by applying hydraulic pressure to the operation hydraulic cylinder 17 shown in FIG. 19) If it is pushed in the direction, the position installed in the pump chamber of the rotary bush 15 is fixed, so that the gap is formed on the boundary surface of the hydraulic bushing reference point 16a of the rotary bush, and the pump chamber is formed to start the vane pump role. . When the hydraulic cylinder 17 for adjustment shown in FIG. 1 continues to operate and moves the rotor 13 in the direction of the spring 19, the state shown in FIG. 2 becomes the state shown in FIG. 2. At this time, the vane pump becomes a full load state and the operation of the continuously variable transmission Is the maximum rotation state of 1: 1. Here, the pressurized hydraulic pressure is applied to the inside of the body 11-1 shown in FIG. 1 through a passage of oil pressure, which is a dotted line, in the hydraulic chamber 3b-3 shown in FIG. 3 within the dotted line of the moving bush 16-1. The pressure oil passes through the hydraulic motor 21 to drive the circulation through the opposite side of the body (11-1) back to the hydraulic pump is to be repeated. Here, the hydraulic motor 21 uses a balanced vane motor as a standard, but considering the characteristics of the automobile, the hydraulic motor may be used even if an axial type or a radial piston motor is used. The CVT can be used without any problems. One of the most important actions in the continuously variable automatic transmission of the present invention is the relationship between the engine in the idle state and the start of the vehicle. In general, in the case of a passenger car, the transmission ratio of the transmission starts at 4 to 5: 1, and the starting rotation speed of the engine requires rotation of about 2,000 RPM even on a flat surface. Thus, the difference in rotation between the speed from stop to start and 2,000 RPM required for the starting torque of the engine is lost in frictional heat. In the continuously variable automatic transmission according to the present invention, since the clutch is not necessary, there is no friction loss caused by the above-described clutch, and thus the automatic automatic transmission is accelerated and shifted.

The technical problem to be achieved in the present invention is to eliminate the cause of friction loss caused by the clutch used essentially in the conventional automatic hydraulic transmission and to broaden the range of hydraulic pressure is instantaneous start even at a small hydraulic pressure and the operation of the adjustment hydraulic piston (17) In the case of the manual type, the engine reference stop at start, deceleration, and acceleration, and in the case of slip, sharp curve, steep slope, etc., the hydraulic reference point 16a of the rotating bush, which is the two hydraulic reference points on the same line by an automatic operation device, etc. Stepless gearbox has the advantage of creating a gap between the hydraulic reference point (16b) and the moving bush, but without the need for vibration by generating the required manual operation and the automatic adjustment range according to the state of operation and moving the hydraulic pressure about the axis. Invented

1-Detailed view of the hydraulic pump no-load state of the continuously variable automatic transmission according to the present invention

Figure 2-Full load state diagram in Figure 1

3-sectional and front view of the rota and vanes in FIG.

4-Structure diagram of the rotating bush in FIG.

<Code Description of Main Parts of Drawing>

10-1: hydraulic pump shaft 10-2: hydraulic motor shaft 11-1, 11-2: body 12-1, 12-2: cam ring

13: Rota 14: Vane 14-1: Pressure port 15: Rotating bush 16-1, 16-2: Moving bush

16a: Hydraulic reference point for rotating bushing 16b: Hydraulic reference point for operating bushing 17: Hydraulic cylinder for adjustment

18-1,18-2,18-3,18-4: Bearing 19: Spring 20: Hydraulic passage 21: Hydraulic motor

3a: sectional view and front view of a rotor 3b: front view and sectional view of a mobile bush 3c: bush

3d: Vane cross section 3d-1: Pressure flow port cross section 3a-1: Vane groove 3a-2: Shaft hole 3b-3: Hydraulic chamber

4-1: vane body 4-2: vane hole 4-3: rota hall

Referring to the configuration of the present invention, in the detailed view of the hydraulic pump shown in Fig. 1, the movable bushing hydraulic pressure which is the contact surface between the hydraulic reference point 16a of the rotary bushing, which is the contact surface of the rotary bushing 15, and the movable bush 16-1 of the hydraulic pump, Two hydraulic reference points, which are the reference points 16b, coexist on one line. That is, even if the vane motor in which the capacity of the pump is zero rotates, no hydraulic pressure is generated so that the hydraulic motor output shaft 10-2 does not rotate. At this time, when the operation piston 17 moves little by little to start the vehicle, and the moving bush 16-2 moves, the rota 13 moves toward the spring 19 and the moving bush 16-1 moves. Therefore, a gap is generated between the moving bush hydraulic reference point 16a and the rotating bush hydraulic reference point 16b. An important point here is the spacing problem between the moving bush hydraulic reference point 16a and the rotating bush hydraulic reference point 16b. Referring to the full load state diagram shown in FIG. 2 in detail, an interval between the moving bush hydraulic reference point 16a and the rotating bush hydraulic reference point 16b may be 1/100 to 1/10 degrees. Assuming starting, starting proceeds at 20 times more power and 1/20 speed than conventional automatic transmission, but at the same time, the transmission ratio is continuously changed and accelerated so that the engine starts smoothly without excessive force. The clutch slip does not occur at all. In the above description, the fuel economy which is unnecessaryly lost in the conventional transmission and the automatic transmission is greatly improved by employing the continuously variable automatic transmission of the present invention.

In the conventional automatic transmission, the hydraulic system of the automatic transmission and the loss due to torque, converter, clutch, etc., there is no way to avoid. The loss of the clutch is the same for automatic and manual transmissions. Especially when starting and shifting a car, a great loss is inevitable. Secondly, maintenance costs are high because parts are expensive. Third, in the case of friction type or belt type, in addition to losses, life problems due to wear loss are raised. Fourthly, in the case of chain type or belt type, metal belt or mixed belt type also have problems in noise, life and maintenance.

The problems described above are to be completely solved in the continuously variable automatic transmission of the present invention. In the present invention, the clutch is not required and can be started with a small amount of power. The service life of the parts due to friction is also not applicable due to the use of hydraulic pressure, and the noise is low and the maintenance cost is an advantage.

Claims (2)

In the present invention, the hydraulic reference point 16a of the rotary bush and the hydraulic reference point 16b of the movable bush, which are two hydraulic reference points on the same line as the contact surface of the rotary bush, coexist on one line, so that the vanes do not generate hydraulic pressure. In this state, the vehicle is considered to be in a stopped state. In order to move the movable bush in the pump chamber, the operating hydraulic cylinder 17 is mounted to move the movable bush 16-1 and 16-2 in the direction of the spring 19. Stepless automatic transmission characterized in that the rota and vanes pass through the inner surface of the rotary bush 15 to form a pump chamber, and the pump chamber is formed, and the hydraulic pressure is automatically changed according to the load change while starting slowly with the formed hydraulic pressure. . Operate the adjusting hydraulic cylinder 17 according to claim 1, but start, acceleration, deceleration, stop, etc. are basically manual, and at the same time, if the operating state is required such as slip, sharp curve, steep slope, etc. A continuously variable automatic transmission, characterized in that the operation of the cylinder (17) employs an electronic or servo-compensation.