KR20070113450A - Control device of pulley ratio for cvt - Google Patents

Abstract

A pulley ratio control device for a continuously variable transmission is provided to improve the fuel ratio and power transmission performance by controlling a pulley ratio in a mechanical rack/pinion manner or screw gear manner. A driving pulley(30) and a driven pulley(40) are supported by a driving shaft(80) and a driven shaft(90), and rotation power of the driving pulley is transmitted to the driven pulley by a metal belt. Control motors(20) are disposed on upper and lower portions of movable sheaves(34,44), and are forwardly or reversely rotated according to a command of stroke amount of a transmission control unit or hybrid control unit(10). The rotation power of the control motor is transmitted to the movable sheaves through a transmission member of rack and pinion type.

Description

Pulley ratio control device of continuously variable transmission {Control Device of Pulley Ratio for CVT}

1 is a block diagram of a pulley ratio control apparatus according to an embodiment of the present invention,

2 is a view showing a part of another application example of FIG. 1;

3 is a block diagram of a pulley ratio control apparatus according to another embodiment of the present invention;

FIG. 4 shows a part of another application of FIG. 3. FIG.

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

10: TCU (or HCU) 20: control motor

30: driven pulley 40: driven pulley

50: metal belt 60: pinion

70: ball detent 80: drive shaft

90: driven shaft 100: fixing bracket

110: driven stroker 120: driven stroker

130: metal bearing 140: bearing thrust

150: fastening member 160: ball bearing

170: reduction shaft 180: control motor shaft

190: support bearing

The present invention relates to a pulley ratio control apparatus for a continuously variable transmission, and more particularly, to a continuously variable transmission having a great advantage in terms of fuel economy, power transmission performance, and weight by compensating for disadvantages of the continuously variable transmission using hydraulic pressure.

For example, the transmission of the vehicle has a function of transmitting the rotational force of the engine to the drive wheels. The transmission includes a manual transmission in which the driver directly selects a shift stage at the driver's will, and an automatic transmission in which the transmission is automatically made according to the driving conditions of the vehicle. And are continuously divided into a continuously variable transmission in which continuously continuous shifts are made without a specific shift region between each shift stage.

In such a continuously variable transmission, the driving and driven pulleys consist of a fixed sheave and a moving sheave so that the moving sheave exerts thrust on the side of the metal belt to a level suitable for the driving torque by the hydraulic pressure acting on the hydraulic chamber formed at the rear side of the moving sheave. The stepless speed change is made according to the diameter conversion of these pulleys.

However, in the hydraulic control system of the continuously variable transmission as described above, the transmission is made by varying the diameter of the pulley. Since the high pressure is used in comparison with the general automatic transmission, the loss in the oil pump is relatively 30 ~ 30% of the total continuously variable transmission loss. It is known to account for 40%.

As such, the loss of power occupied by the oil pump is advantageous as the pump capacity is reduced, but there is a problem that it is very difficult to reduce the capacity of the oil pump because a large flow rate may be required depending on the operating conditions.

In other words, in a normal driving condition, the capacity of the oil pump is rather low, but a large capacity oil pump must be used for kickdown and emergency brake situations requiring a large flow rate. The problem is that the fuel economy is reduced, the weight is increased, and the configuration is complicated.

The present invention has been made in view of the above-mentioned problems, and the object of the present invention is to provide a pulley ratio control apparatus for a continuously variable transmission that has great advantages in terms of fuel economy, power transmission performance, and weight by supplementing the disadvantages of the continuously variable transmission using hydraulic pressure. .

Pulley ratio control apparatus for a continuously variable transmission according to an embodiment of the present invention for achieving the above object, the drive pulley and the driven pulley each consisting of a fixed sheave and a mobile sheave is axially supported on the drive shaft and the driven shaft by a metal belt In the pulley ratio control device that the rotational force of the drive pulley is transmitted to the driven pulley, the pulley ratio is controlled by the diameter conversion of the pulley according to the movement of the movable sheave,

The moving sheave is arranged side by side up and down and the control motor for forward and backward rotation by the stroke amount command of the TCU or HCU in front or rear of the moving sheave is located, the rotational force of the control motor to the rack and pinion power transmission means It is transmitted to the mobile sheave by the mobile sheave is characterized in that the movement in the opposite direction.

In addition, in the pulley ratio control apparatus of the continuously variable transmission according to another embodiment of the present invention, the driving pulley and the driven pulley each consisting of a fixed sheave and a moving sheave are axially supported by the drive shaft and the driven shaft, and the rotational force of the drive pulley is driven by the metal belt. In the pulley ratio control device is transmitted to the driven pulley, the pulley ratio is controlled by the diameter conversion of the pulley according to the movement of the movable sheave,

The moving sheave is arranged in a diagonal direction up and down, and the control motor for forward and reverse rotation by the stroke amount command of the TCU or HCU is located on one side of the fixed sheave and the mobile sheave, the rotational force of the control motor is a screw gear type power transmission It is transmitted to the moving sheave by means, characterized in that the moving sheave is moved in the same direction with each other.

Hereinafter, the configuration and operation of the present invention will be described with reference to the accompanying drawings.

1 is a block diagram showing a pulley ratio control apparatus according to an embodiment of the present invention.

As shown in FIG. 1, the driving pulley 30 and the driven pulley 40 which are axially supported by the driving shaft 80 and the driven shaft 90 move right and left fixed sheaves 32 and 42 and the left upper and lower sides. Sheaves 34 and 44, and the metal belt 50 is wound between the two pulleys 30 and 40 so that the rotational force of the driving pulley 30 is transmitted to the driven pulley 40 by the metal belt 50 and driven. The pulley 40 rotates.

At this time, the moving sheaves 34 and 44 apply thrust to the side of the metal belt 50 at a level appropriate to the driving torque, and by the diameter conversion of the pulleys 30 and 40 according to the movement of these moving sheaves 34 and 44. Stepless speed change is achieved.

A plurality of ball bearings 160 are inserted between the moving shaft 34 of the drive shaft 80 and the driving pulley 30 and between the moving shaft 44 of the driven shaft 90 and the driven pulley 40 to move the ball. Smooth movement in the axial direction when the sheaves 34 and 44 move along the axes 80 and 90.

Transmission Control Unit (TCU) or Hybrid Control Unit (HCU) 10 receives signals from various sensors such as Throttle Position Sensor (TPS), Speedometer, Engine Speed, and Brake Switch. The timing and stroke amount are determined and the stroke amount is commanded to the control motor 20.

The control motor 20 is located in front of or behind the pulleys 30 and 40 in the opposite direction to the shafts 80 and 90 and rotates forward and backward according to the stroke amount commanded by the TCU (or HCU) 10.

The pinion 60, which is axially supported by the control motor 20, has a gear 62 formed on an outer circumference thereof to serve as a gear rack within the movable sheaves 34 and 44. Gears 112 and 122 formed on the rocker 120 are engaged to move in opposite directions.

Therefore, when the pinion 60 rotates in the clockwise direction, the drive stroker 110 moves to the right in the drawing, and the driven stroker 120 moves to the left, and the drive stroker 110 when rotated in the counterclockwise direction. ) Moves to the left and driven stroker 120 moves to the right.

The moving sheaves 34 and 44 and the strokers 110 and 120 are separated from power. The separated structure is installed between the moving sheaves 34 and 44 and the strokers 110 and 120 to reduce the frictional force so that the moving sheave ( It consists of a metal bearing 130 to support the smooth rotation of the 34,44.

A fastening member 150 such as a nut supporting one side of the strokers 110 and 120 is fastened to the movable sheaves 34 and 44 to couple the movable sheaves 34 and 44 to the strokers 110 and 120. Both sides of the 110 and 120 are provided with a bearing thrust 140 for reducing friction when the strokers 110 and 120 pressurize the fastening member 150 or the moving sheaves 34 and 44.

In addition, between the gears 62 formed on the pinion 60, a ball detent 70, which is a shift step locking mechanism, is interposed, and the pinion 60 is locked and rotated if the control motor 20 does not rotate. You will not.

In the above configuration, the drive pulley 30 and the driven pulley 40 are connected by the metal belt 50 to the stroke amount command of the TCU (or HCU) 10 for the transmission ratio control suitable for the engine and vehicle conditions while rotating. This results in a continuously variable shift.

That is, when the TCU (or HCU) 10 commands the stroke amount to the control motor 20 according to the vehicle condition, and the control motor 20 rotates forward and backward according to the commanded stroke amount, the pinion 60 is also forward and reverse. Rotation, the movement of the sheave (34, 44) or the fastening member 150 to move the movement sheave (34, 44) of the stroker (110,120) engaged with the pinion (60) in accordance with the forward and reverse rotation of the pinion (60) Press to one side.

When the fastening members 150 coupled to the movable sheaves 34 and 44 or the movable sheaves 34 and 44 are pressurized, the movable sheaves 34 and 44 are formed along the shafts 80 and 90 with the ball bearings 160 interposed therebetween. Will move in the opposite direction.

At this time, the driving pulley 30 and the driven pulley 40 is in a rotating state, but the rotational force transmission is separated by the metal bearing 130, so that the strokers 110 and 120 do not rotate.

When the pinion 60 rotates in the clockwise direction, the upper movable sheave 34 moves to the right and the lower movable sheave 44 moves to the left, so that the diameter of the driving pulley 30 increases and the driven pulley 40 The diameter of) decreases to have a pulley ratio that is slowed down.

On the contrary, when the pinion 60 rotates counterclockwise, the upper movable sheave 34 moves to the left, and the lower movable sheave 44 moves to the right, so that the diameter of the driving pulley 30 decreases and the driven pulley is reduced. The diameter of 40 has a pulley ratio which is accelerated by increasing.

In the case of the decelerated or accelerated pulley ratio, the metal belt 50 transmits rotational force in a state in which the upper and lower sides are slightly inclined, but the inclination angle is insignificant and the frictional force does not change, which greatly affects the transmission of the rotational force. You will not receive.

Since the control of the pulley ratio as described above is continuously made while the driving pulley 30 and the driven pulley 40 rotate, it is possible to continuously vary the speed.

FIG. 2 is a diagram showing a part of another application example of FIG. 1.

Reduction gear 172 to reduce the rotation of the control motor 20 to transmit to the pinion 60 to secure the driving force of the control motor 20 without directly supporting the pinion 60 to the control motor 20. It is also possible to axially support the deceleration shaft 170 having a control motor 20.

3 is a block diagram of a pulley ratio control apparatus according to another embodiment of the present invention.

As shown in FIG. 3, the driving pulley 30 and the driven pulley 40 axially supported by the driving shaft 80 and the driven shaft 90 are fixed sheaves 32a and 42a which are formed to face in a diagonal direction. The movable sheaves 34a and 44a, the metal belt 50 is wound between the two pulleys (30, 40) and the rotational force of the driving pulley (30) is transmitted to the driven pulley (40) by the metal belt (50) The driven pulley 40 rotates.

At this time, the moving sheaves 34a and 44a exert thrust on the side of the metal belt 50 at a level appropriate to the driving torque, and the pulleys 30 and 40 of the pulleys 30 and 40 according to the movement of the moving sheaves 34a and 44a formed in the diagonal direction. Stepless speed change is achieved by the diameter conversion.

A plurality of ball bearings 160a are inserted between the moving shaft 34a of the drive shaft 80 and the driving pulley 30 and between the fixed sheave 42a of the driven shaft 90 and the driven pulley 40 to move the moving sheave. When the 34a, 44a moves along the axes 80, 90, the movement in the axial direction is smoothed.

The TCU (or HCU) 10 receives signals input from various sensors such as TPS, speedometer, engine speed, brake switch, etc. and determines the timing and stroke amount to shift according to the vehicle condition. Command in 20a).

The control motor 20a is located on one side of the pulleys 30 and 40 in the axial directions 80 and 90 to rotate forward and backward according to the stroke amount commanded by the TCU (or HCU) 10.

The control motor shaft 180 which is axially supported by the control motor 20a is supported by the support bearing 190 so as to be smoothly rotated, and a screw gear 182 is formed in the middle of the outer circumference, so that the inside of the movable sheave 34a is formed. The screw gear 114 formed on the driving stroker 110a and the driven shaft 90 are engaged with the screw gear 124 formed on the driven stroker 120a extending in the fixed sheave 42a.

Accordingly, the driving stroker 110a and the driven stroker 120a are moved together left or right according to the rotation direction of the control motor shaft 180.

The moving sheaves 34a and 44a and the strokers 110a and 120a are separated from the rotational force. First, a configuration in which the driving pulley 30 is separated between the movable sheaves 34a and the driving stroker 110a is installed. It consists of a metal bearing 130a for supporting the rotation of the movable sheave 34a.

A fastening member 150a, such as a nut supporting one side of the drive stroker 110a, is fastened to the mover sheave 34a to couple the mover sheave 34a and the drive streaker 110a to the drive stroker 110a. Bearing thrust 140a for reducing friction when the driving stroker 110a presses and moves the fastening member 150a or the moving sheave 34a is installed at both sides.

Next, the configuration in which the rotational force of the driven pulley 40 side is separated is formed between the driven shaft 90 and the driven stroker 120a and is formed of a metal bearing 130b supporting the rotation of the driven shaft 90.

A fastening member 150b, such as a nut supporting both sides of the driven stroker 120a, is fastened in the middle of the driven shaft 90 to couple the driven shaft 90 and the driven stroker 120a and the driven stroker ( On both sides of the 120a, a bearing thrust 140b for reducing friction when the driven stroker 120a presses the fastening member 150b to move the driven shaft 90 is provided.

In addition, when the movable sheave 44a of the driven pulley 40 moves and rotates, the fixing sheave 42a is fixed to the vehicle body not shown to rotate in place without the fixed sheave 42a moving. A metal bearing 130c is installed at one side of the 42a and supports the rotation of the fixed sheave 42a between the fixed bracket 100 and the fixed sheave 42a.

In the above-described configuration, the drive pulley 30 and the driven pulley 40 are connected to the metal belt 50 while the stroke amount command of the TCU (or HCU) 10 is applied to the transmission ratio control suitable for the engine and vehicle conditions while rotating. This results in a continuously variable shift.

When the TCU (or HCU) 10 commands the stroke amount to the control motor 20a according to the vehicle condition, and the control motor 20a rotates forward and backward according to the commanded stroke amount, the control motor shaft 180 accordingly. The forward and reverse rotation of the control motor shaft 180 in accordance with the forward and reverse rotation of the stroke motor (110a, 120a) coupled to the control motor shaft 180 by pressing the moving sheave 34a or fastening members (150a, 150b) The moving sheaves 34a and 44a formed in diagonal directions with each other are moved in the same direction.

At this time, the driving pulley 30 and the driven shaft 90 is in a state of rotating, but the rotational force transmission is separated by the metal bearings (130a, 130b) and the stroker (110a, 120a) is not rotated.

Pulleys that are decelerated by increasing the diameter of the driving pulley 30 and decreasing the diameter of the driven pulley 40 when both of the moving sheaves 34a and 44a move to the right while the fixed sheaves 32a and 42a are fixed. Will have rain.

On the contrary, when the movable sheaves 34a and 44a both move to the left, the diameter of the driving pulley 30 is reduced and the diameter of the driven pulley 40 is increased to have the pulley ratio accelerated.

Since the control of the pulley ratio as described above is continuously made while the driving pulley 30 and the driven pulley 40 rotate, it is possible to continuously vary the speed.

4 is a diagram illustrating a part of another application example of FIG. 3.

In order to secure the driving force of the control motor 20a without supporting the control motor shaft 180 directly on the control motor 20a, the rotation of the control motor 20a is reduced to reduce the gears on the control motor shaft 180. 194a and 194b may be axially supported by the control motor 20a to be connected to the control motor shaft 180.

As described above, by controlling the pulley ratio by the rack / pinion or the screw gear method, the shift control accuracy can be more accurate and excellent than the conventional hydraulic control, and there is no hydraulic loss, so the efficiency of the continuously variable transmission can be improved. .

As described above, according to the present invention, it is possible to improve the fuel efficiency and power transmission performance by controlling the pulley ratio by a mechanical rack / pinion or screw gear method by supplementing the disadvantage of the continuously variable transmission using hydraulic pressure. Since it does not need to be used, the cost and weight can be reduced.

Claims (11)

The driving pulley 30 and the driven pulley 40 each consisting of the fixed sheaves 32 and 42 and the moving sheaves 34 and 44 are axially supported by the driving shaft 80 and the driven shaft 90 to be attached to the metal belt 50. By the rotational force of the drive pulley 30 is transmitted to the driven pulley 40, the pulley ratio is controlled by the pulley ratio by changing the diameter of the pulley (30, 40) according to the movement of the movable sheave (34, 44) In The moving sheaves 34 and 44 are arranged side by side up and down, and the control motor 20 for forward and reverse rotation by the stroke amount command of the TCU or HCU 10 is located in front or rear of the moving sheaves 34 and 44. The CVT is characterized in that the rotational force of the control motor 20 is transmitted to the movable sheaves 34 and 44 by the rack and the pinion type power transmission means so that the movable sheaves 34 and 44 are moved in opposite directions to each other. Pulley ratio control. The method of claim 1, A plurality of ball bearings 160 are inserted between the drive shaft 80 and the movable sheave 34 and between the driven shaft 90 and the movable sheave 44 so that the movable sheaves 34 and 44 are rotated by the shafts 80 and 90. Pulley ratio control device of a continuously variable transmission, characterized in that the smooth movement along). The method according to claim 1 or 2, The power transmission means is supported by the control motor 20, the pinion 60, the gear 62 is formed on the outer periphery, and the gear sheaves inside the movable sheave (34, 44) and the gear ( 62 is provided between the driving stroker 110 and the driven stroker 120 having the gears 112 and 122 engaged with the 62, and the inner side of the movable sheaves 34 and 44 and the strokers 110 and 120. Pulley ratio control device of a continuously variable transmission, characterized in that made of a metal bearing 130 to support the smooth rotation of 44. The method of claim 3, wherein Reducing the rotation of the control motor 20 to the pinion 60 by supporting the deceleration shaft 170 having a reduction gear 172 for transmitting to the pinion 60 to the pinion 60, characterized in that the fitting. Pulley ratio control of continuously variable transmission. The method of claim 3, wherein A fastening member 150 supporting one side of the strokers 110 and 120 and fastened to the movable sheaves 34 and 44 to couple the movable sheaves 34 and 44 to the strokers 110 and 120, and the strokers 110 and 120. Is installed on both sides of the throttle (110, 120) of the continuously variable transmission characterized in that the bearing thrust 140 is further provided to reduce the friction when the fastening member 150 or the moving sheave (34, 44) to move Pulley Ratio Control. The method of claim 5, Ball detent 70 is interposed between the gears 62 formed on the pinion 60, the pinion 60 is locked when the control motor 20 does not rotate, pulley ratio control device of a continuously variable transmission. . The driving pulley 30 and the driven pulley 40 each consisting of the fixed sheaves 32a and 42a and the movable sheaves 34a and 44a are axially supported by the drive shaft 80 and the driven shaft 90 to be attached to the metal belt 50. By the rotational force of the drive pulley 30 is transmitted to the driven pulley 40, to the pulley ratio control device that the pulley ratio is controlled by the diameter conversion of the pulley (30, 40) according to the movement of the movable sheave (34a, 44a). In The control motor 20a which the movable sheaves 34a and 44a are arranged up and down in a diagonal direction and is rotated forward and backward by the stroke amount command of the TCU or the HCU 10 on one side of the fixed sheave 42a and the movable sheave 34a. ) Is positioned, the rotational force of the control motor (20a) is transmitted to the moving sheave (34a, 44a) by the power transmission means of the screw gear type, characterized in that the moving sheave (34a, 44a) is moved in the same direction with each other. Pulley ratio control of continuously variable transmission. The method of claim 7, wherein A plurality of ball bearings 160a are inserted between the drive shaft 80 and the movable sheave 34a and between the driven shaft 90 and the fixed sheave 42a so that the movable sheaves 34a and 44a are rotated by the shafts 80 and 90. Pulley ratio control device of a continuously variable transmission, characterized in that the smooth movement along). The method according to claim 7 or 8, The power transmission means is axially supported by the control motor (20a) and the control motor shaft 180, the screw gear 182 is formed in the middle of the outer periphery, and is located inside the movable sheave (34a) and the screw gear 182 and A driving stroker 110a having a screw gear 114 to be engaged therewith, and a screw gear 124 fixed to the middle of the driven shaft 90 to extend into the fixed sheave 42a and engaged with the screw gear 182 are provided. A formed driven stroker 120a, a metal bearing 130a installed between the moving sheave 34a and the driving stroker 110a to support rotation of the moving sheave 34a, and the driven shaft 90 And a driven roller (120a) is installed between the pulley ratio control device of a continuously variable transmission, characterized in that made of a metal bearing (130b) for supporting the rotation of the driven shaft (90). The method of claim 9, Reduction gears (194a, 194b) for reducing the rotation of the control motor (20a) to be transmitted to the control motor shaft 180, the shaft is supported by the control motor (20a) and is fitted to the control motor shaft (180) Pulley ratio control for continuously variable transmission. The method of claim 9, A fastening member 150a supporting one side of the driving stroker 110a and fastened to the movable sheave 34a to couple the movable sheave 34a and the driving stroker 110a to the driving stroker 110a. It is installed on both sides to support the bearing thrust 140a to reduce friction when the driving stroker 110a presses and moves the fastening member 150a or the movable sheave 34a, and both sides of the driven stroker 120a. And a fastening member 150b which is coupled in the middle of the driven shaft 90 to couple the driven shaft 90 and the driven stroker 120a, and installed on both sides of the driven stroker 120a. The apparatus for controlling the pulley ratio of the continuously variable transmission further comprises a bearing thrust (140b) which reduces friction when the driven member (90b) presses the fastening member (150b).

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