JP2006105174A - Control device for continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce driving load by preventing the increase of an extra portion of line pressure in a V-belt type continuously variable transmission. <P>SOLUTION: A control device for the continuously variable transmission is provided with a processing part B1 obtaining supply oil pressure Ppri required for a primary pulley cylinder chamber according to input torque and a target variable speed ratio ip based on a map (PFMAPD); a processing part B2 obtaining a line pressure correction value according to the target variable speed ratio ip and the rotating speed Npri of a primary pulley based on a correction map; a processing part B3 determining whether predetermined operating conditions are met; and a processing part B4 outputting a value obtained by subtracting a line pressure correction value from a target line pressure PL in the case of determining that the predetermined operating conditions are met. The line pressure correction value for lowering the target line pressure PL with the decrease of the rotating speed Npri of the primary pulley is computed to lower the target line pressure PL with the line pressure correction value in the predetermined operating conditions. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an improvement in a hydraulic control device for a vehicle including a V-belt continuously variable transmission.

  In a V-belt type continuously variable transmission mounted on a vehicle, a V-belt is held between a primary pulley and a secondary pulley that variably control the groove width based on hydraulic pressure, and power is transmitted by the contact friction force. .

  For this reason, for example, as disclosed in Patent Document 1, the thrusts of the primary pulley and the secondary pulley are obtained according to the input torque and the gear ratio, and the thrust is converted into a hydraulic pressure based on a predetermined value such as a pressure receiving area. Hydraulic pressure is supplied to the transmission mechanism as the target line pressure. As the speed change mechanism, a servo link connecting the step motor, the speed change control valve, and the primary pulley is used to open the speed change control valve in accordance with the target speed ratio by driving the step motor, and the groove width of the primary pulley is set to the target speed change by speed change. When the ratio is reached, a mechanical feedback mechanism and a gear ratio control device are provided in which the gear shift control valve is closed according to the groove width of the primary pulley and the gear shift ends.

  In addition, this continuously variable transmission includes a hydraulic pressure control device that supplies line pressure to the secondary pulley, and supplies primary pressure with hydraulic pressure (primary pressure) that regulates the line pressure via the shift control valve. In addition, the pressure receiving area of the oil chamber of the primary pulley is set larger than the pressure receiving area of the oil chamber of the secondary pulley, and the primary pressure is changed in a range lower than the secondary pressure (line pressure) to change the speed.

  In the operation state where the accelerator pedal is depressed, the hydraulic control device is configured such that the primary pulley and the secondary pulley are determined by the hydraulic pressure determined by the input torque to the continuously variable transmission estimated based on the vehicle speed and the opening of the accelerator pedal. The gear ratio is changed by changing the contact radius with the V-belt, and the gear ratio according to the vehicle speed and the accelerator pedal opening is set.

  The target value of the line pressure is set in advance so that the secondary pressure balances the primary pressure according to the difference between the centrifugal thrust of the secondary pulley and the centrifugal thrust of the primary pulley in the high rotation speed region of the primary pulley.

On the other hand, the line pressure is corrected so as to be equal to or higher than a predetermined minimum value under the driving condition in which the accelerator pedal is released. The minimum value of the line pressure is changed according to the transmission ratio of the continuously variable transmission and the rotational speed of the primary pulley, and even when the input torque is reduced, the clamping hydraulic pressure of the V belt is secured and the Hi due to the centrifugal force of the V belt itself. Shifting to the side is prevented.
Japanese Patent No. 3183154

  However, the conventional hydraulic control device has a problem that it is difficult to accurately adjust the line pressure according to the rotation speed of the primary pulley.

  That is, in the low rotation speed range of the primary pulley where the accelerator opening is small and the gear ratio is shifted to the Hi side, the line pressure is reduced as the difference between the centrifugal thrust of the secondary pulley and the centrifugal thrust of the primary pulley decreases. There was a possibility that the surplus would increase and the driving load of the hydraulic pump would increase.

  Accordingly, the present invention has been made in view of the above problems, and an object of the present invention is to prevent an excessive amount of line pressure in a V-belt type continuously variable transmission and reduce a driving load.

  In the present invention, the primary pulley on the input side whose groove width changes according to the primary pressure, the secondary pulley on the output side whose groove width changes depending on the secondary pressure, the primary pulley and the secondary pulley are wound around, and the groove A belt whose pulley contact radius changes according to the width, a line pressure setting means for setting a target value of the line pressure corresponding to the centrifugal thrust of both the primary pulley and the secondary pulley in the high rotational speed region, and based on the operating state In a belt-type continuously variable transmission having a gear ratio control means for controlling a primary pressure and a secondary pressure by adjusting a line pressure so as to achieve a target gear ratio, the line is adjusted in accordance with a decrease in the rotational speed of the primary pulley. Line pressure correction value calculating means for calculating a line pressure correction value for reducing the target pressure value, and the line pressure correction value under a predetermined operating condition Therefore and a line pressure correcting means for decreasing the target value of the line pressure.

  According to the present invention, the centrifugal thrust of the secondary pulley and the centrifugal thrust of the primary pulley are reduced by reducing the target value of the line pressure in accordance with the decrease in the primary pulley rotation speed due to the line pressure correction value under a predetermined operating condition. Reflecting the reduction in the difference, the line pressure can be kept low, and the driving load of the hydraulic pump can be restrained to reduce fuel consumption.

  Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings.

  FIG. 1 is a schematic configuration diagram of a V-belt continuously variable transmission, and FIG. 2 is a conceptual diagram of a hydraulic control unit and a CVT control unit.

  In FIG. 1, the continuously variable transmission 5 is connected to the engine 1 via a torque converter 2 having a lock-up clutch on the input shaft side and a forward / reverse switching mechanism 4. The continuously variable transmission 5 includes a primary pulley 10 on the input shaft side and a secondary pulley 11 connected to the output shaft 13 as a pair of variable pulleys, and the pair of variable pulleys 10 and 11 are connected by a V belt 12. The output shaft 13 is connected to the differential gear 6 via an idler gear 14 and an idler shaft.

  The transmission ratio of the continuously variable transmission 5 and the contact friction force of the V belt are controlled by a hydraulic control unit 100 that responds to a command from the CVT control unit 20. The CVT control unit 20 determines and controls a target gear ratio and a contact friction force based on input torque information from an engine control unit 21 that controls the engine 1 and an output from a sensor or the like described later.

  A primary pulley 10 of the continuously variable transmission 5 includes a fixed conical plate 10b that rotates integrally with an input shaft, a V-shaped pulley groove that is disposed opposite to the fixed conical plate 10b, and a primary pulley cylinder chamber. The movable conical plate 10a can be displaced in the axial direction by hydraulic pressure (primary pressure) acting on 10c.

  The secondary pulley 11 is a fixed conical plate 11b that rotates integrally with the output shaft 13, and is disposed opposite to the fixed conical plate 11b to form a V-shaped pulley groove, and the hydraulic pressure acting on the secondary pulley cylinder chamber 11c. The movable conical plate 11a can be displaced in the axial direction according to (secondary pressure). The movable conical plate 11 a is also pressed against the V-belt 12 by the urging force of the spring 15.

  The driving torque input from the engine 1 is input to the continuously variable transmission 5 via the torque converter 2 and the forward / reverse switching mechanism 4 and transmitted from the primary pulley 10 to the secondary pulley 11 via the V belt 12. The movable conical plate 10a of the tenth and the movable conical plate 11a of the secondary pulley 11 are displaced in the axial direction to change the contact radius with the V-belt 12, thereby continuously changing the gear ratio between the primary pulley 10 and the secondary pulley 11. Can be changed.

  The transmission ratio of the continuously variable transmission 5 and the contact friction force of the V belt 12 are controlled by the hydraulic control unit 100.

  As shown in FIG. 2, the hydraulic control unit 100 includes a regulator valve 60 that controls the line pressure, a transmission control valve 30 that controls the hydraulic pressure in the primary pulley cylinder chamber 10c (hereinafter, primary pressure), and a secondary pulley cylinder chamber 11c. The pressure reducing valve 61 that controls the supply pressure (hereinafter referred to as secondary pressure) is mainly configured.

  The speed change control valve 30 is connected to a servo link 50 constituting a mechanical feedback mechanism, is driven by a step motor 40 connected to one end of the servo link 50, and is movable of the primary pulley 10 connected to the other end of the servo link 50. The groove width, that is, feedback of the actual gear ratio is received from the conical disk 10a.

  The line pressure control system is composed of a regulator valve 60 having a solenoid for regulating the pressure oil from the hydraulic pump 80, and is predetermined according to the operation state in accordance with a command (for example, a duty signal) from the CVT control unit 20. Regulate to the line pressure.

  The line pressure is supplied to a speed change control valve 30 that controls the primary pressure and a pressure reducing valve 61 that includes a solenoid that controls the secondary pressure.

  The gear ratio between the primary pulley 10 and the secondary pulley 11 is controlled by a step motor 40 driven in accordance with a shift command signal from the CVT control unit 20, and shift control is performed in accordance with the displacement of a servo link 50 that responds to the step motor 40. The spool 31 of the valve 30 is driven, the line pressure supplied to the speed change control valve 30 is adjusted and the primary pressure is supplied to the primary pulley 10, and the groove width is variably controlled and set to a predetermined speed ratio.

  The shift control valve 30 supplies and discharges hydraulic pressure to and from the primary pulley cylinder chamber 10c by displacement of the spool 31, and adjusts the primary pressure so that the target gear ratio commanded at the drive position of the step motor 40 is obtained. When the shifting is actually completed, the spool 31 is closed in response to the displacement from the servo link 50.

  Here, the CVT control unit 20 in FIG. 1 has a primary pulley speed sensor 26 that detects the rotational speed of the primary pulley 10 of the continuously variable transmission 5 and a secondary pulley speed that detects the rotational speed (or vehicle speed) of the secondary pulley 11. An operation amount sensor 24 corresponding to a sensor 27, a signal from a hydraulic pressure sensor 28 that detects a secondary pressure applied to the cylinder chamber 11c of the secondary pulley, a select position from the inhibitor switch 23, and an operation amount of an accelerator pedal operated by a driver. The target gear ratio and the contact friction force of the V-belt 12 are varied by reading the stroke (or the opening of the accelerator pedal), the oil temperature of the continuously variable transmission 5 from the oil temperature sensor 25, and the input torque information from the engine control unit. Control.

  The CVT control unit 20 determines the target gear ratio according to the vehicle speed and the stroke of the accelerator pedal in the driving state where the select position of the inhibitor switch 23 is in the D range, and drives the step motor 40 to drive the actual gear ratio. And the pulley pressure for controlling the thrust (contact frictional force) of the primary pulley 10 and the secondary pulley 11 according to the input torque, the gear ratio, the oil temperature, the gear shift speed, and the like. A (hydraulic pressure) control unit 202 is included.

  In the driving state in which the select position of the inhibitor switch 23 is set to the manual mode, the target gear ratio is fixed according to the shift position supported by the driver.

  The pulley pressure control unit 202 determines the target value of the line pressure from the input torque information, the gear ratio based on the primary pulley rotation speed and the secondary pulley rotation speed, and the oil temperature, and drives the solenoid of the regulator valve 60 to drive the line pressure. Control is performed, the target value of the secondary pressure is determined, the solenoid of the pressure reducing valve 61 is driven according to the detected value and the target value of the hydraulic sensor 28, and the secondary pressure is controlled by feedback control (closed loop control). .

  FIG. 3 shows a configuration in which the pulley pressure control unit 202 sets the target value PL of the line pressure corresponding to the centrifugal thrust of the primary pulley 10 and the secondary pulley 11 in the high rotational speed range.

  This control system includes a Psec determination section 220 that determines the thrust Psec of the secondary pulley 11 and a PL determination section 230 that determines the thrust of the primary pulley 10 in accordance with the thrust Psec and determines the target line pressure PL therefrom. .

  In the Psec determination section 220, first, the processing unit 221 calculates the Sec thrust (slip limit thrust) of the secondary pulley 11 from the target speed ratio ip and the input torque of the primary pulley 10.

  The processing unit 222 obtains a thrust A obtained by subtracting the centrifugal thrust of the secondary pulley 11 from the obtained Sec thrust. This centrifugal thrust is a thrust by which the secondary pulley 11 pushes the V belt 12 by the centrifugal force acting on the hydraulic oil interposed in the secondary pulley cylinder chamber 11c.

  The processing unit 225 reads a preset minimum hydraulic pressure Psecmin of the secondary pulley 11. Note that the minimum hydraulic pressure Psecmin indicates the minimum hydraulic pressure necessary to prevent the V belt 12 from slipping when reverse torque from the drive wheel side is input.

  The processing unit 226 multiplies the minimum hydraulic pressure Psecmin by the pressure receiving area of the primary pulley cylinder chamber 10c to obtain the thrust B.

  The processing unit 223 compares the thrust A and the thrust B, and outputs the larger value as MAX (AB).

  The processing unit 224 outputs a value obtained by adding the centrifugal thrust of the secondary pulley 11 to the thrust MAX (AB) as the thrust Psec of the secondary pulley 11 to the PL determination section 230.

  On the other hand, in the PL determination section 230, as will be described later, the processing unit 231 calculates the Pri thrust (slip limit thrust) of the primary pulley 10 from the thrust Psec of the secondary pulley 11, the target gear ratio ip, and the input torque of the primary pulley 10. It is obtained over the entire rotation speed range (Npri1-MAX).

  The processing unit 232 obtains a thrust obtained by subtracting the centrifugal thrust of the primary pulley 10 from the obtained Pri thrust over the entire rotation speed range (Npri1 to MAX). This centrifugal thrust is a thrust by which the primary pulley 10 pushes the V belt 12 by the centrifugal force acting on the hydraulic oil interposed in the primary pulley cylinder chamber 10c.

  The processing unit 233 divides the obtained thrust by the pressure receiving area of the primary pulley cylinder chamber 10c, and obtains the hydraulic pressure required for the primary pulley cylinder chamber 10c over the entire rotational speed range (Npri1 to MAX).

  The processing unit 234 outputs the maximum value from the hydraulic pressures in the obtained entire rotation speed range (Npri1 to MAX) as the required hydraulic pressure Ppri under the conditions of the target gear ratio ip and the input torque.

  The processing unit 235 converts each variation element of the secondary pressure, the solenoid, and the friction coefficient of the V-belt 12 into hydraulic pressure, and the processing unit 236 outputs the value added to the hydraulic pressure Ppri as the target line pressure PL.

4A and 4B show a method of calculating the target line pressure PL described above. This process is performed under the following conditions.
-The target gear ratio ip is on the Hi side (0.394).
-Input torque is smaller than a predetermined value, and the above-mentioned thrust A becomes smaller than thrust B.
The thrust Psec of the secondary pulley 11 is determined by the minimum hydraulic pressure Psecmin.

  FIG. 4A shows the Sec thrust (slip limit thrust) of the secondary pulley 11 obtained over the entire rotational speed range of the primary pulley 10. This Sec thrust is the sum of the thrust (constant value) by the spring 15, the thrust Psec (constant value) of the secondary pulley 11 obtained by the supply hydraulic pressure, and the centrifugal thrust of the secondary pulley 11. The centrifugal thrust of the secondary pulley 11 increases according to the rotational speed Npri of the primary pulley 10.

  FIG. 4B shows the Pri thrust (slip limit thrust) of the primary pulley 10 obtained over the entire rotational speed range of the primary pulley 10. This Sec thrust is the sum of the thrust Ppri of the primary pulley 10 obtained by the supply hydraulic pressure and the centrifugal thrust of the primary pulley 10. The thrust Ppri and the centrifugal thrust of the primary pulley 10 increase in accordance with the rotational speed Npri of the primary pulley 10, respectively.

  The target line pressure PL is determined so that the maximum value of the Sec thrust of the secondary pulley 11 matches the maximum value of the Pri thrust. That is, the maximum value of the hydraulic pressure Ppri supplied to the primary pulley cylinder chamber 10c is substantially the target line pressure PL.

  Thus, the target line pressure PL is determined based on the difference between the centrifugal thrust of the secondary pulley 11 and the centrifugal thrust of the primary pulley 10 in the maximum rotation speed range.

  For this reason, as shown in FIG. 4B, in the region where the rotational speed Npri of the primary pulley 10 is low, the target line pressure PL is significantly higher than the supply oil pressure Ppri required for the primary pulley cylinder chamber 10c. There is a reduction allowance for reducing the target line pressure PL.

  As the rotational speed Npri of the primary pulley 10 decreases, the difference between the centrifugal thrust of the secondary pulley 11 and the centrifugal thrust of the primary pulley 10 decreases, and the reduction cost of the target line pressure PL increases.

  Along with the shift ratio Hi side, there is a characteristic that the difference between the centrifugal thrust of the secondary pulley 11 and the centrifugal thrust of the primary pulley 10 increases, and the reduction amount of the target line pressure PL increases.

  The present invention has been made paying attention to this point, and calculates a line pressure correction value for decreasing the target line pressure PL in accordance with a decrease in the rotational speed Npri of the primary pulley 10, and predetermined operating conditions to be described later. The control for lowering the target line pressure PL by the line pressure correction value is performed.

  FIG. 5 shows the configuration of a control system for correcting the target line pressure PL in the CVT control unit 20. Hereinafter, this control system will be described.

  In the processing unit B1, a supply hydraulic pressure Ppri required for the primary pulley cylinder chamber 10c is obtained according to the input torque and the target gear ratio ip based on a map (PFMAPD) (not shown).

  In the processing unit B2, a line pressure correction value is obtained according to the target gear ratio ip and the rotation speed Npri of the primary pulley 10 based on the correction map shown in FIG.

  In the processing unit B3, it is determined whether or not a predetermined operation condition described later is satisfied. When it is determined that the predetermined operating condition is satisfied, the processing unit B4 outputs a value obtained by subtracting the line pressure correction value from the target line pressure PL. On the other hand, when it is determined that the predetermined operating condition is not satisfied, the processing unit B4 outputs the line pressure correction value as it is without subtracting it from the target line pressure PL.

  The CVT control unit 20 outputs a command (for example, a duty signal) according to the target line pressure PL to the regulator valve 60, and controls the line pressure supplied to the transmission control valve 30 and the pressure reducing valve 61, respectively.

  In the correction map shown in FIG. 6, the line pressure correction value has a characteristic that increases as the rotational speed Npri of the primary pulley 10 decreases.

  The line pressure correction value has a characteristic that increases as the target speed ratio ip decreases (Hi side).

  Next, an example of line pressure control performed by the pulley pressure control unit 202 of the CVT control unit 20 will be described in detail with reference to the flowchart of FIG. Note that the flowchart of FIG. 7 is executed every predetermined cycle, for example, every several tens of msec.

  First, in step S <b> 1, it is determined that the driving state is in which the D range is set at the select position of the inhibitor switch 23.

  Subsequently, in step S2, it is determined that the gear ratio is in an operating state where the gear ratio is smaller than a predetermined value (Hi side).

  In subsequent step S3, it is determined that the input torque is in an operating state larger than 0 and smaller than a predetermined value.

  If it is determined in steps S1 to S3 that all the conditions are satisfied, the process proceeds to step 4 to output a value obtained by subtracting the line pressure correction value from the target line pressure PL.

  On the other hand, if it is determined in steps S1 to S3 that at least one of the conditions is not satisfied, the process proceeds to step 5 where the line pressure correction value is not subtracted from the target line pressure PL and is output as it is.

  As described above, the line pressure correction value for reducing the target line pressure PL as the rotational speed Npri of the primary pulley 10 decreases is calculated, and the target line is calculated based on the line pressure correction value under predetermined operating conditions. By performing the control to reduce the pressure PL, the line pressure can be suppressed to reflect the reduction in the difference between the centrifugal thrust of the secondary pulley 11 and the centrifugal thrust of the primary pulley 10, and the driving load can be reduced.

  In the correction map shown in FIG. 6, the line pressure correction value corresponds to the line pressure corresponding to the difference between the centrifugal thrusts of the secondary pulley 11 and the primary pulley 10 decreasing as the rotational speed Npri of the primary pulley 10 decreases. It is possible to accurately reduce the surplus value of.

  Also, under the operating conditions in which the difference between the centrifugal thrust of the primary pulley 11 and the centrifugal thrust of the primary pulley 10 is reduced by performing the transmission gear ratio on the Hi side, which is smaller than the predetermined value, and the input torque being equal to or less than the predetermined value. Only the control for correcting the line pressure is performed. Under other operating conditions, the control for correcting the line pressure is not performed, and the control response of the line pressure is not impaired.

  The D range is put in the select position of the inhibitor switch 23, and the control for correcting the line pressure is performed in the operation mode for controlling the speed ratio according to the vehicle speed and the accelerator pedal opening, so that the vehicle speed and the stroke of the accelerator pedal are controlled. Accordingly, every time the target gear ratio shifts to the Hi side, there is a high possibility that the line pressure is reduced, and the effect of reducing fuel consumption is high.

  The present invention is not limited to the above-described embodiment, and it is obvious that various modifications can be made within the scope of the technical idea.

  The present invention can be applied to a control device for a continuously variable transmission mounted on a vehicle such as an automobile.

BRIEF DESCRIPTION OF THE DRAWINGS The schematic block diagram of the V belt type continuously variable transmission which shows one Embodiment of this invention. The schematic block diagram of a CVT control unit and a hydraulic control unit similarly. The block diagram which similarly shows the structure of the control system which calculates target line pressure PL. Explanatory drawing which similarly shows the method of calculating target line pressure PL. The block diagram which similarly shows the structure of the control system which correct | amends the target line pressure PL. A map with the target line pressure PL set. The flowchart which similarly shows the example of control which correct | amends target line pressure PL.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Engine 5 Continuously variable transmission 10 Primary pulley 11 Secondary pulley 12 V belt 21 Engine control unit 20 CVT control unit 28 Hydraulic sensor 30 Shift control valve 60 Regulator valve 61 Pressure reducing valve 100 Hydraulic control unit

Claims (5)

A primary pulley on the input side whose groove width changes according to the primary pressure;
A secondary pulley on the output side whose groove width changes according to the secondary pressure;
A belt that is wound around the primary pulley and the secondary pulley, and a pulley contact radius changes according to the groove width;
A line pressure setting means for setting a target value of the line pressure corresponding to the centrifugal thrust of both the primary pulley and the secondary pulley in a high rotational speed range;
In a belt-type continuously variable transmission comprising gear ratio control means for controlling the primary pressure and the secondary pressure by adjusting the line pressure so as to achieve a target gear ratio based on an operating state,
Line pressure correction value calculating means for calculating a line pressure correction value for decreasing the target value of the line pressure in response to a decrease in the rotational speed of the primary pulley;
A control device for a continuously variable transmission, comprising: a line pressure correction means for reducing a target value of the line pressure by the line pressure correction value under a predetermined operating condition.   2. The line pressure correction value according to claim 1, wherein the line pressure correction value increases as the rotation speed of the primary pulley decreases and increases as the target speed ratio decreases. Control device for continuously variable transmission.   3. The line pressure correction unit is configured to reduce a target value of the line pressure by the line pressure correction value under an operating condition in which a gear ratio is on a Hi side smaller than a predetermined value. Control device for continuously variable transmission.   The line pressure correcting means is configured to reduce a target value of the line pressure by the line pressure correction value under an operating condition in which the input torque of the primary pulley is smaller than a predetermined value. Control device for step transmission.   The line pressure correcting means is configured to reduce a target value of the line pressure by the line pressure correction value in an operation mode in which a gear ratio is controlled according to a vehicle speed and an accelerator pedal opening. The control device for a continuously variable transmission according to any one of claims 4 to 4.

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