JP3427700B2 - Transmission control device for continuously variable transmission - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a shift control device for a continuously variable transmission.

[0002]

2. Description of the Related Art As a continuously variable transmission used in a vehicle,
BACKGROUND ART V-belt type and toroidal type continuously variable transmissions have been conventionally known, and are disclosed in JP-A-58-54262 and JP-A-3.
A toroidal type continuously variable transmission as disclosed in Japanese Patent No. 288062 is known.

As shown in FIGS. 7 and 8, this is a pair of coaxially arranged input / output cone disks 1 and 2 and a pair of power transmissions by frictional engagement between the input / output cone disks 1 and 2. A so-called single-cavity toroidal transmission unit consisting of the power rollers 3, 3 of
In addition to the mechanical feedback system, the shift control device is provided with an electronic feedback system by PI control.

In the toroidal type continuously variable transmission 10, the power rollers 3 and 3 are sandwiched and pressed between the input / output cone disks 1 and 2, and the power roller 3 is an oil film between the input / output cone disks 1 and 2. The power is transmitted between the input and output cone discs 1 and 2 by the shearing of.

The rotation of the input cone disk 1 is transmitted to the power roller 3 by the shearing force of the oil film, and the rotation of the power roller 3 is transmitted to the output cone disk 2 by the shearing of the oil film, and vice versa. Power transmission from 2 to the input cone disk 1 is similarly performed via the power roller 3.

The shearing force of the oil film is the speed difference between the input / output cone disks 1 and 2 and the power roller 3 and the pressure acting on the oil film, that is, the input / output cone disks 1 and 2.
It is generated by the pressure pressing the power roller 3 between them.

Therefore, if the pressing pressure is strong,
Torque can be transmitted with a small speed difference, and if the pressing pressure is small, a large speed difference is required.

Further, since the torque is transmitted by the shear force of the oil film, when the speed difference exceeds a predetermined value, the oil film does not generate the shear force, and the input / output cone disk 1,
2 because the engagement relationship between the power roller 3 and the power roller 3 is broken,
It is desirable to apply a large pressing force, but since applying an unnecessary pressing force impairs the efficiency of power transmission, it is necessary to set the pressing force according to the transmission torque.

Therefore, as shown in FIG. 8, the mechanism for applying the pressing force is provided between the cam disk 22 disposed on the input shaft 20 connected to the engine and the back surface of the input cone disk 1. A loading cam 28 having a rotating shaft in the radial direction of the cam disk 22 is provided, and the input cone disk 1 having a predetermined slope on the back surface is rotatably supported by the input shaft 20.
Is also provided with a predetermined slope on the opposite surface of the input cone disk 1. When a rotational phase difference occurs between the cam disk 22 and the input cone disk 1, the slope formed on the back surface of the input cone disk 1 and the cam disk By rolling the loading cam 28 between the slopes of 22, the input cone disk 1 is pressed in the axial direction of the input shaft 20 (O ₂ axial direction) and is axially supported together with the output gear 29 via the bearing 30. The power roller 3 is pressed against the output cone disk 2 to generate a pressing force according to the transmission torque applied to the input shaft 20. The input shaft 20 is rotatably supported by the casing 19 via a bearing 31, and the output gear 29 is connected to driving wheels via an output shaft (not shown).

On the other hand, when the transmission torque of the continuously variable transmission 10 is very small, the loading cam 28 does not operate. Therefore, the disc spring 21 for urging the input shaft 20 in the axial direction is provided on the bearing 31 side, and is constantly set to a predetermined value. However, in order to improve the transmission efficiency and ensure the assembling ability, the urging force generated by the disc spring 21 cannot be significantly increased.

The gear ratio of the toroidal type continuously variable transmission 10 is determined according to the radius of contact between the power roller 3 and the input cone disk 1 and the output cone disk 2,
The change of the gear ratio is carried out by supporting the power rollers 3 and 3 respectively and driving the trunnions 41 and 41 which are displaceable in the O ₃ axis direction and the axis of FIG. The tilting motion of rotating the trunnion 41 around the axis according to the axial displacement of
The contact radius with the input / output cone disks 1 and 2 is continuously changed. The trunnion 41 pivotally supports the power roller 3 via the eccentric shaft 9.

The shift control device will now be described. As shown in FIG. 8, a hydraulic cylinder 6 having a piston 6a responsive to the hydraulic pressure supplied to the upper and lower oil chambers 6H and 6L is provided at the lower end of the trunnion 41. And these oil chambers 6H, 6
A shift control valve 5 for supplying hydraulic pressure to L, and a controller 52
The step motor 4 that drives the sleeve 5b of the shift control valve 5 in accordance with the command from the shift control valve 5 and the displacement of the trunnion 41 in the O ₃ axis direction (vertical direction in FIG. 8) and around the axis.
A mechanical feedback system is mainly composed of a recess cam 7 and a link cam 8 which feed back to the spool 5a.

The step motor 4 is rotated by being given a shift command value (step number) corresponding to the target gear ratio from the controller, and the sleeve 5b of the shift control valve 5 and the sleeve 5b of the spool 5a are rack-and-pinion. It is driven via a mechanism and is displaced from a predetermined neutral position relative to the spool 5a.

The shift control valve 5 has an input port 5d connected to a hydraulic pressure source 60, one communication port 5e is connected to the oil chamber 6L of the hydraulic cylinders 6 and 6, and the other communication port 5f is connected to the hydraulic cylinders 6 and 6. To communicate with the oil chambers 6H. Then, while the spool 5a is connected to the recess cam 7 via the link cam 8, the sleeve 5b which is slidable in the axial direction between the outer circumference of the spool 5a and the inner circumference of the valve body 5c,
It is driven by the step motor 4 via the rack and pinion.

A spool 5 driven by a step motor 4
Due to the displacement of a, both power rollers 3 and 3 move to the piston 6
The oil is displaced in the O ₃ axis direction according to the oil pressure applied to a. At this time, the oil pressure to each piston 6a is supplied so that the opposing power rollers 3 and 3 are displaced in opposite directions. If the power roller 3 of FIG. 3 moves up, the power roller 3 on the right side of the drawing moves down.

The opposing power rollers 3 and 3 are
The rotational axis O ₁ is synchronously offset from the neutral position as shown in the drawing where the rotational axis O 1 intersects the rotational axis O ₂ of the input / output cone disks 1 and ₂ in response to mutually opposite displacements of the trunnions 41.

Based on the offset amount in the O ₃ axis direction, both power rollers 3 and 3 are connected to the input / output cone disks 1 and 2.
By the component force from the power roller for the input / output cone discs 1 and 2 to perform a tilting motion to rotate around a swing axis O ₃ (= rotation axis of the trunnion 41) orthogonal to the own rotation axis O _1. By continuously changing the friction contact radii of 3 and 3, continuously variable transmission can be performed.

When the shift command value from the controller is achieved by such a continuously variable shift, the offset amount and tilt angle of the power roller 3 in the O ₃ axis direction are set to the trunnion 4.
1, feedback to the spool 5a of the shift control valve 5 via the precess cam 7 and the link cam 8
Is returned to the initial neutral position relative to the sleeve 5b and the suction and discharge of the hydraulic oil to the oil chambers 6H and 6L are blocked.
The trunnions 41, 41 return to the neutral position where the rotation axis O ₁ of the power rollers 3, 3 intersects with the rotation axis O ₂ of the input / output cone disks 1, ₂ to maintain the achievement of the shift command value. Of.

In such a continuously variable transmission 10, since the displacement of the trunnion 41 and the power roller 3 in the O ₃ axis direction is very small (for example, several mm), the trunnion constituting the feedback mechanism is constituted by the torque transmitted. Four
When part of 1 is deformed, there is a problem that an error occurs with respect to the target gear ratio.

That is, when the torque transmitted by the toroidal type continuously variable transmission increases rapidly, the power roller 3 receives a force in the O ₃ axis direction at the point of contact with the input / output cone disks 1 and 2, and this is applied to the piston. although supported by hydraulic pressure applied to 6a, the trunnion 41 that has received the stress causes elastic deformation, not completely support the power rollers 3, since the power rollers 3 move to O ₃ axially, the O ₃ axially offset The tilting motion is caused according to the amount, and the actual gear ratio changes with respect to the target gear ratio.

Further, in order to control this to a predetermined target gear ratio, a feedback mechanism by the precess cam 7 and the link cam 8 works, but as described above, the trunnion 41 is used.
When is deformed, the distance between the rotation center (axis O ₁ ) of the power roller 3 and the precess cam 7 changes, so that the gear ratio steadily shifts by this difference.

Such a shift in the gear ratio is called a so-called torque shift, and in order to eliminate this torque shift, an electronic feedback system based on the deviation between the target gear ratio and the actual gear ratio is added. The applicant of the present application is Japanese Patent Laid-Open No. 8
It is proposed as Japanese Patent Publication No. 2967222.

The applicant of the present application performs feedforward control in anticipation of delay in proportional-plus-integral control (hereinafter referred to as PI control) and deformation of the mechanical feedback system,
Japanese Patent Application Laid-Open No. 8-
It has been proposed as Japanese Patent No. 326887.

[0024]

The displacement amount of the sleeve 5b of the shift control valve 5 is, as shown in FIG. 10, a mechanical upper limit value and a lower limit value (Lo side and Hi side displacement limit positions). Therefore, it is necessary to limit the driving range of the step motor 4 as well.

Assuming that the drive range of the step motor 4 is limited by the step motor drive limit amount, the limit amount is taken into consideration as shown in FIG. 10 in consideration of mechanical errors such as dimensional tolerances and step out of the step motor 4. Further, it is desirable to set the displacement amount of the sleeve 5b smaller than the upper limit value and the lower limit value.

However, since the above-mentioned restrictions are provided, in the above-mentioned Japanese Patent Laid-Open No. 8-326887, the PI
By the control, a command value is issued to the step motor 4 so that the target speed ratio and the actual speed ratio match, and when the command value reaches the step motor drive limit amount, the driving of the step motor 4 is stopped. However, at this time, if there is a deviation between the target gear ratio and the actual gear ratio, the integral value of the integral control is accumulated, and when the step motor 4 is driven in the reverse direction, the accumulated integral value causes the command value to be changed. However, there is a problem in that the start of change of the shift control is delayed and the followability of the shift control is deteriorated. For example, as shown in FIG. 9, when the command value of the step motor reaches the lower limit value and is no longer driven, the integral value by the PI control reaches the integral upper limit value, so that the step motor command from the time when the target gear ratio decreases. By the time the value starts to change, there is a delay and the followability deteriorates.

This phenomenon occurs when the integral limit value (upper limit or lower limit) of the continuously variable transmission, which is pointed out in Japanese Patent Laid-Open No. 3-244943, is reached unless the integral is stopped. Although it is similar to the phenomenon that the following value is deteriorated due to an abnormal value, in JP-A-3-249463, since the continuously variable transmission that directly PI-controls the opening amount of the hydraulic valve is a control target, the integrated value of Abnormal accumulation occurs only after the mechanically inherent gear ratio limit of the continuously variable transmission is reached.

On the other hand, the above-mentioned JP-A-8-32688 is used.
In the conventional example of Japanese Patent Publication No. 7 or the like, the step motor 4 as an actuator is driven to displace the sleeve 5b of the shift control valve 5, thereby changing the valve opening amount and starting the change of the gear ratio. The spool 5a, which is relatively displaced according to the change of the ratio, closes the sleeve 5b to maintain the gear ratio corresponding to the drive amount of the step motor 4,
It has a so-called follow-up control type mechanical feedback system. Therefore, the step motor drive limit amount based on the displacement limit position of the sleeve 5b is reached before the gear ratio of the continuously variable transmission reaches the inherent gear ratio limit.
Despite the fact that the value of the actual gear ratio has a margin with respect to the inherent gear ratio limit, the integral value is accumulated by stopping the driving of the step motor, and there is a problem that the followability deteriorates as described above. .

Further, as shown in FIG. 10, when the step motor 4 goes out of step and the original drive limit amount moves as shown by the wavy line in the figure, the gear ratio limit peculiar to the continuously variable transmission is met. Even if there is a margin, there is a problem that the step motor drive limit amount is reached and the followability is deteriorated due to the accumulation of the integrated value as in the above case.

Therefore, the present invention has been made in view of the above problems, and it is an object of the present invention to suppress the deterioration of the followability due to the increase of the integral value.

[0031]

SUMMARY OF THE INVENTION The first invention Mechanica to maintain the gear ratio corresponding to the driving position of the actuator
Has a speed change mechanism having a le feedback system, the accession
A continuously variable transmission that continuously changes the gear ratio by driving a chutator, and a target gear ratio of the continuously variable transmission that is calculated according to operating conditions, and a deviation between the actual gear ratio and the target gear ratio is calculated. Feedback control means for driving the actuator so that the actual gear ratio matches the target gear ratio, and a drive amount for restricting the drive amount of the actuator so as not to exceed a predetermined drive range. In a shift control device for a continuously variable transmission including a regulating means, the drive amount of the actuator is regulated by the drive amount.
And an integration operation stopping means for stopping the integration operation of the integration means while the driving range of the means is at the upper limit value or the lower limit value.

Further, the second invention, a mechanical feed to maintain the gear ratio corresponding to the drive <br/> turned position of the actuator
The actuator having a speed change mechanism including a back system,
Is operated to continuously change the gear ratio, and the target gear ratio of the continuously variable transmission is calculated according to the operating state, and the deviation between the actual gear ratio and the target gear ratio is integrated. Feedback control means for driving the actuator so that the actual speed ratio matches the target speed ratio, and the drive amount of the actuator so that the position of the speed change mechanism does not exceed a predetermined displacement range. In a shift control device for a continuously variable transmission equipped with a drive amount regulating means for regulating, a means for detecting a displacement amount of the speed change mechanism, and the displacement amount is a predetermined upper limit value or a lower limit value in the drive amount regulating means. During a certain period, it is provided with an integral operation stopping means for stopping the integral operation of the integrating means.

[0033]

Therefore, according to the first aspect of the invention, when electronic feedback control including integral control is performed, the drive amount of the actuator is restricted within a predetermined drive range.
It is possible to prevent deformation of the speed change mechanism driven by the actuator, for example, the speed change control valve. Further, when the drive amount of the actuator is at the upper limit value or the lower limit value of these drive ranges, the integral operation of the feedback means is performed. Since the suspension is temporarily stopped, it is possible to suppress the deterioration of the followability due to the increase of the integral value as in the conventional example, and further improve the control accuracy of the shift control. When adopted, displacement of the speed change mechanism with respect to the control amount due to step-out, etc., for example,
Even if the valve position continues to be set to the upper limit value or the lower limit value due to deviation of the relationship with the valve opening amount, the integral operation is stopped during this period, preventing an excessive increase in the integral value and preventing deterioration of the followability. You can

The second aspect of the invention detects the amount of displacement of the speed change mechanism driven by the actuator, for example, the stroke of the speed change control valve, and so long as the amount of displacement is at a predetermined upper limit value or lower limit value, Since the actuator driving and the integral operation stop, the transmission mechanism driven by the actuator, for example, the deformation of the shift control valve is prevented, and the integral operation of the feedback means is temporarily stopped. As described above, it is possible to suppress a decrease in followability due to an increase in the integral value.When a step motor is used as the actuator, the drive is performed based on the amount of displacement of the speed change mechanism even if a step-out occurs. It is possible to prevent the shift of the range and further improve the stability of the shift control.

[0035]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the accompanying drawings.

FIG. 1 shows an example in which, as the continuously variable transmission 10, a toroidal type of single cavity type similar to the conventional example is adopted, and the present invention is applied to a shift control controller 52 of the continuously variable transmission 10.

The continuously variable transmission 10 is connected to the engine 11 via a torque converter 12 having a lockup mechanism L / U on the input shaft 20 side, while the output shaft side (output cone disc 2 side) is illustrated. Not connected to the drive wheel,
The transmission mechanism and the mechanical feedback mechanism of the toroidal type continuously variable transmission 10 are shown in FIGS.
The same configuration as that of the conventional example is used, and the step motor 4 (actuator) drives the shift control valve 5 in response to a command from the shift control controller 52 to shift gears. Will be attached and redundant description will be omitted.

The shift control controller 52 is mainly composed of a microcomputer, and includes a throttle opening TVO detected by the throttle opening sensor 53 and a vehicle speed sensor 54 arranged on the output shaft side of the continuously variable transmission 10. The target speed ratio corresponding to the operating state of the vehicle is calculated based on the vehicle speed VSP and the rotation speed Ni of the input shaft 20 of the continuously variable transmission 10 detected by the input shaft rotation sensor 55, and the continuously variable transmission 10 is actually operated. The stepped motor 4 is instructed to control the control amount STP such that the gear ratio of 1 matches the target gear ratio. The vehicle speed sensor 54 outputs a value obtained by multiplying the output shaft speed No of the continuously variable transmission 10 by a predetermined constant as the vehicle speed VSP.

An outline of the shift control of the shift control controller 52 is, as shown in FIG. 2, a target tilt angle calculation unit 73 for calculating a target gear ratio according to a throttle opening TVO and a vehicle speed VSP, and a vehicle speed VSP ( ∝ Output shaft rotation speed No) and input shaft rotation speed Ni to obtain the actual gear ratio Tilt angle calculation unit 7
1. Based on the deviation between the target gear ratio and the actual gear ratio,
Electronic feedback control by integral control using an observer is performed to send the control amount STP to the step motor 4. The state estimation observer unit 72, the integrator 74,
The step conversion unit 75 is mainly used for multiplication of various gains and addition / subtraction of various signals.

Here, electronic feedback control by integral control using an observer is performed as follows.

The target tilt angle calculator 73 calculates the target tilt angle from the throttle opening TVO and the vehicle speed VSP based on a preset map (not shown).

When the characteristic of the toroidal type continuously variable transmission 10 is expressed as shown in FIG.
4 can be configured, and in this case, a and f in FIG. 3 are constants indicating the characteristic relating to the tilt angle φ, b and g are constants indicating the characteristic of the axial displacement y of the trunnion 41, and The constant can be identified from the input / output characteristics of the toroidal type continuously variable transmission 10.

In FIG. 4, ω is a predetermined constant indicating the pole of the observer, K1 and K2 are observer gains, input A is a command value, and input B is an actual gear ratio.

In addition to the above, the state estimation observer unit 72 may be configured in the same manner as in Japanese Patent Application No. 7-71495.

On the other hand, a deviation e is calculated from the target gear ratio from the target tilt angle calculation unit 73 and the actual gear ratio from the tilt angle calculation unit 71, and this deviation e is input to the integrator 74. Then, after adding the value obtained by multiplying the output of the integrator 74 by the predetermined gain C ₀ and the person obtained by multiplying the deviation e by the predetermined gain C ₁ , the output of the state estimation observer unit 72 is subtracted and the command value is obtained. To calculate.

Then, the step conversion section 75 is obtained by adding the output of the cam cancellation feedback section 70 to this command value.
To enter. As disclosed in Japanese Patent Application Laid-Open No. 8-296722, the cam offset feedback unit 70 provides a valve displacement amount equal to the mechanical feedback amount by driving the step motor 4 to offset the mechanical feedback amount. .

In the step conversion section 75, the control output value according to the command value, specifically, the step number STP of the step motor 4 is calculated based on the map shown in FIG. At this time, the step converter 75 outputs the control output value S
TP is limited between a predetermined lower limit value Lowlim and upper limit value Hilim so as not to exceed the displacement limit of the sleeve 5b of the shift control valve 5 shown in FIGS. 8 and 10.

Further, in the step conversion unit 75, when the command value or the control output value STP corresponding to the command value is attempted to be less than a predetermined lower limit value (Lowmax or Lowlim) or more than an upper limit value (Himax or Hilim), the integration is performed. The integration stop command is sent to the integrator 74, and the integrator 74 stops its integration operation while the integration stop command is issued. That is, when the command value U is between the predetermined lower limit value Lowmax and the upper limit value Himax, the integrator 74 performs the integration operation, while the command value U is less than the predetermined lower limit value Lowmax or exceeds the upper limit value Himax. The integration operation is temporarily stopped while the STP reaches the lower limit value Lowlim or the upper limit value Hilim.

Therefore, according to the present invention, as shown by the solid line in FIG. 6, the shift output is controlled by setting the control output value to the step motor 4 from the time Time = 0 to the upper limit value or the lower limit value (lim in the figure). After increasing the opening amount of the valve 5 to start the speed change quickly and then decreasing the opening amount by moving the shift control valve 5 to a predetermined gear ratio, the upper limit value or the lower limit value is maintained until Time = 0.4. Then, when the target value is changed so that it is within the drive range of the step motor 4, the integral operation is stopped while the control output value is the upper limit value or the lower limit value, so that the integral value increases regardless of the deviation e. Therefore, Time = immediately after changing the command value so that it is within the drive range.
From 0.5, the control output STP is within the drive range, the opening amount of the shift control valve 5 is changed, and the speed can be changed quickly, and in a continuously variable transmission equipped with a follow-up control type mechanical feedback system, Therefore, it becomes possible to suppress the deterioration of the followability due to the increase of the integral value.

On the other hand, in the above-mentioned conventional example, as shown by the one-dot chain line in the figure, since the integration operation is continued while the control output value STP is at the upper limit value or the lower limit value (lim in the figure), accumulation of the integrated value is carried out. Becomes too large and the command value changes from Time = 0.4, the control output value actually starts to change due to the excessive integration value after Time = 0.9, and It is greatly reduced.

Further, in the case where the control output value is not limited, as shown by the broken line in FIG. 6, the response is improved, but the sleeve 5b of the shift control valve 5 exceeds the limit value lim, so the shift control valve 5 It has an adverse effect such as deforming the.

As described above, in the continuously variable transmission provided with the follow-up control type mechanical feedback system, when electronic feedback control including integral control is performed, the control output value STP of the step motor 4 is set to the upper limit value Hilim and In addition to preventing the shift control valve 5 from being deformed by setting the lower limit value Lowlim, the integration operation is temporarily stopped when the control output value STP is at the upper limit value or the lower limit value. As in the prior art example, it is possible to suppress the deterioration of the followability due to the increase of the integral value and further improve the control accuracy of the shift control.

Further, even if the relationship between the valve opening amount and the control output value is deviated due to step-out of the step motor 4 or the like, and the control output value is continuously set to the upper limit value Hilim or the lower limit value Lowlim, the integral operation is stopped during this period. Therefore, it is possible to prevent the integral value from excessively increasing and prevent the followability from deteriorating.

In the above embodiment, the sleeve 5b of the shift control valve 5 is calculated from the control output value to the step motor 4.
Although the position of the sleeve 5b has been estimated, the position of the sleeve 5b may be detected by a stroke sensor or the like and the actuator such as the step motor 4 may be driven based on this position information. Is the most Lo
Alternatively, when the maximum Hi is reached, the driving of the actuator is stopped, and at the same time, if the integration operation is stopped, the same operation as described above,
In addition to the effect, it is possible to prevent the deviation of the driving range even when the actuator such as the step motor is out of step.

Further, in the above-mentioned embodiment, the shift control controller 52 performs integral control, but although not shown, the present invention is applied to one which performs PI control or PID control as in the conventional example. Good.

Further, in the above embodiment, an example in which the toroidal type is adopted as the continuously variable transmission is shown, but the same effect can be obtained even if the present invention is applied to the V belt type continuously variable transmission. .

[Brief description of drawings]

FIG. 1 is a conceptual diagram of a shift control device for a continuously variable transmission according to an embodiment of the present invention.

FIG. 2 is a block diagram of a shift control controller.

FIG. 3 is a model of a toroidal continuously variable transmission which is also used in the observer.

FIG. 4 is a model showing an example of an observer.

FIG. 5 is a map showing a relationship between a command value and a control output value.

FIG. 6 is a graph showing the operation, showing the relationship between the valve displacement amount, the gear ratio, the integral value, and time; the solid line represents the present invention, the dashed line represents a conventional example, and the broken line does not limit the step motor drive amount. Indicate the case.

FIG. 7 is a cross-sectional view of the toroidal type continuously variable transmission and shift control valve.

FIG. 8 is a vertical sectional view of the toroidal continuously variable transmission.

FIG. 9 is a graph showing the relationship between the integrated value, the number of steps, the gear ratio, and time by the conventional control.

FIG. 10 is a conceptual diagram showing a relationship between a displacement range of a sleeve of a shift control valve and a drive range of a step motor, showing a conventional example.

[Explanation of symbols]

1 input cone disc 2 output cone disc 3 power rollers 4 step motor 5 shift control valve 5a spool 5b sleeve 6 hydraulic cylinder 7 Precessum 8 link cams 10 continuously variable transmission 20 input axis 41 trunnion 52 Shift control controller 53 Throttle opening sensor 54 vehicle speed sensor 55 Input shaft rotation sensor 71 Tilt angle calculation unit 72 State estimation observer section 73 Target tilt angle calculation unit 74 integrator 75 step converter

Continuation of front page (56) Reference JP-A-3-249464 (JP, A) JP-A-60-249759 (JP, A) JP-A-64-49760 (JP, A) JP-A-8-338491 (JP , A) JP-A-2-283957 (JP, A) JP-A 64-74132 (JP, A) JP-A 9-14415 (JP, A) (58) Fields investigated (Int.Cl. ⁷ , DB) (Name) F16H 59/00-61/12 F16H 61/16-61/24 F16H 63/40-63/48

Claims (2)

(57) [Claims] 1. A shift corresponding to the driving position of the actuator
A continuously variable transmission having a speed change mechanism having a mechanical feedback system for maintaining the ratio, and continuously changing the speed change ratio by driving the actuator; A feedback for driving the actuator so that the actual gear ratio matches the target gear ratio by providing an integrating means for calculating the target gear ratio of the automatic transmission and integrating the deviation between the actual gear ratio and the target gear ratio. A shift control device for a continuously variable transmission, comprising: a control unit; and a drive amount regulation unit that regulates a drive amount of the actuator so as not to exceed a predetermined drive range, wherein the drive amount of the actuator is the drive amount regulation unit. To
Kicking While in upper or lower limit of the driving range, the continuously variable transmission shift control device characterized by comprising an integration operation stopping means for stopping the integral operation of the integration means. 2. A shift corresponding to the driving position of the actuator
A continuously variable transmission having a speed change mechanism having a mechanical feedback system for maintaining the ratio, and continuously changing the speed change ratio by driving the actuator; A feedback for driving the actuator so that the actual gear ratio matches the target gear ratio by providing an integrating means for calculating the target gear ratio of the automatic transmission and integrating the deviation between the actual gear ratio and the target gear ratio. A shift control device for a continuously variable transmission, comprising: a control unit; and a drive amount regulation unit that regulates a drive amount of an actuator so that the position of the transmission mechanism does not exceed a predetermined displacement range. means for detecting a, while the amount of displacement is within a predetermined upper limit value or lower limit value in the driving amount controlling means, Bei an integration operation stopping means for stopping the integral operation of the integration means The shift control device for a continuously variable transmission, characterized in that the.