JP2000097302A - Speed change control device for automatic transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To correct a speed change time constant so that a gear shifting speed is decreased when it is decided that operation of a select lever by a driver is performed. SOLUTION: An arrival change gear ratio calculating part 73 researches a given map from a throttle opening and a car speed to calculate an arrival change gear ratio i*. A target change gear ratio calculating part 75 calculates a target change gear ratio Ratio 0 to realize the arrival change gear ratio i*. A speed change time constant calculating part calculates a deviation between the arrival change gear ratio i* and the target change gear ratio Ratio 0 and through comparison of the deviation with a preset value, a time constant calculation mode responding to a speed? change demand by a driver is set, and based on a time constant calculation mode and the presence of operation of a select lever, responsiveness of a speed change to the arrival change gear ratio 1* is decided and first and second speed change time constants Tg1 and Tg2 to set a gear shifting speed are calculated.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention includes a continuously variable transmission in which a target speed ratio is set such that an actual speed ratio approaches a speed ratio set in accordance with an operation state, and a speed change control is performed. The present invention relates to a shift control device for an automatic transmission.

[0002]

2. Description of the Related Art An automatic transmission including a continuously variable transmission such as a V-belt type continuously variable transmission and a toroidal type continuously variable transmission is described in, for example, Japanese Patent Application Laid-Open No. 5-126239. In this way, the target gear ratio is usually determined from the running conditions such as the required engine load and the vehicle speed, and the gear ratio is controlled so that the actual gear ratio reaches the target gear ratio with a predetermined response.

[0003] Therefore, in the case of a continuously variable transmission, the target gear ratio is changed so as to increase (become a low-speed gear ratio) when the driver depresses the accelerator pedal to accelerate the load required by the engine. The continuously variable transmission is continuously downshifted toward the target gear ratio thus increased. On the other hand, when the load is low such that the driver releases the accelerator pedal to reduce the required engine load, the target gear ratio is changed to be smaller (to be a higher gear ratio). Upshifting is performed steplessly toward the target gear ratio reduced in this way. In performing such a shift control, a shift time constant for determining a shift responsiveness to an attained speed ratio and setting a shift speed is calculated to mitigate a shock during shifting.

[0004]

The object of the invention is to, however, the driver, such as the switching of the change in the range occurs perform the select lever operation or the like of the automatic transmission from (forward normal driving range D to the forward sports driving range D _s select In addition to switching the lever, it also includes shifting in the D range.)
The attained gear ratio changes stepwise. If the gear is shifted without changing the shift time constant in such a case, the shift may be too fast depending on the driving condition, and the driver may feel uncomfortable. Therefore, it is preferable to correct the shift time constant according to whether or not the select lever is operated.

SUMMARY OF THE INVENTION It is an object of the present invention to calculate a shift time constant according to whether or not a lect lever is operated.

[0006]

According to a first aspect of the present invention, there is provided a shift control device for an automatic transmission, wherein the first shift ratio is set based on an operation state of a driver and / or a running state of a vehicle. Means, target gear ratio setting means for setting the target gear ratio such that the actual gear ratio changes at a predetermined gear speed with respect to the attained gear ratio, and a gear time constant for determining the gear speed of the target gear ratio. An operation determining means for determining whether or not the driver has operated the select lever in a shift control device for an automatic transmission having a time constant setting means for setting and controlling the actual gear ratio to be the ultimate gear ratio; Time constant correction means for correcting the shift time constant set by the time constant setting means so that the shift speed becomes slower when the operation determination means determines that the operation of the select lever has been performed. It is characterized in that the.

[0007]

According to the shift control device for an automatic transmission according to the first aspect of the present invention, when the operation determining means determines that the operation of the select lever has been performed, the time constant correcting means includes: The shift time constant set by the time constant setting means is corrected so that the shift speed becomes slow. By correcting the shift time constant in accordance with the presence or absence of the operation of the select lever in this manner, there is no possibility that the shift is too fast depending on the driving state and gives the driver an uncomfortable feeling.

[0008]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A shift control device for an automatic transmission according to the present invention will be described in detail with reference to the drawings. 1 and 2 show a toroidal type continuously variable transmission provided with a shift control device for an automatic transmission according to the present invention. FIG. 1 is a longitudinal side view of the toroidal type continuously variable transmission, and FIG. It is a front view.

First, a toroidal transmission unit, which is a main part of a continuously variable transmission, will be described. The transmission unit includes an input shaft 20 to which rotation from an engine (not shown) is transmitted. This input shaft is clearly shown in FIG. As described above, the end remote from the engine is rotatably supported in the transmission case 21 via the bearing 22, and the center portion is rotated in the intermediate wall 23 of the transmission case 21 via the bearing 24 and the hollow output shaft 25. Support freely.
The input and output cone disks 1 and 2 are rotatably supported on the input shaft 20, and these input and output cone disks are
The toroidal curved surfaces 1a and 2a are arranged so as to face each other. A pair of power rollers 3 disposed on both sides of the input shaft 20 with the input shaft 20 interposed therebetween are interposed between the opposed toroid curved surfaces of the input and output cone disks 1 and 2, and these power rollers are interposed between the input and output cone disks 1 and 2. To pinch,
The following configuration is adopted.

That is, a loading nut 26 is screwed into the end of the bearing (22) of the input shaft 20, and a cam disk 27 which is prevented from coming off by this loading nut and is rotationally engaged with the input shaft 20; Loading cam 2 between the toroidal surface 1a and the end surface far from the toroidal surface 1a
The rotation from the input shaft 20 to the cam disk 27 is transmitted to the input cone disk 1 via the loading cam. Here, the rotation of the input cone disk 1 is transmitted to the output cone disk 2 via the rotation of both power rollers 3, and during this transmission, the loading cam 28 generates a thrust proportional to the transmission torque, and inputs and outputs the power roller 3. Press between the cone disks 1 and 2,
The above power transmission is enabled.

The output cone disk 2 is wedge-mounted on an output shaft 25, and an output gear 29 is fitted on the output shaft 25 so as to rotate integrally therewith. The output shaft 25 is further rotatably supported in an end cover 31 of the transmission case 21 via a radial and thrust bearing 30, and a radial and thrust bearing 3 is separately provided in the end cover 31.
2, the input shaft 20 is rotatably supported. here,
The radial and thrust bearings 30 and 32 butt against each other via a spacer 33 so that they cannot approach each other, and the corresponding output gear 29 and the input shaft 20 have an axial line so that they cannot be displaced relative to each other. Make contact in the direction.
Thus, the thrust acting between the input and output cone disks 1 and 2 by the loading cam 28 becomes an internal force that sandwiches the spacer 33 and does not act on the transmission case 21.

Each power roller 3 is, as shown in FIG.
The trunnions 41 are rotatably supported by trunnions 41. Each of the trunnions is rotatable and swingable at both ends of an upper link 43 by a spherical joint 42, and a spherical joint 44 is a lower end thereof.
Thus, the lower link 45 is rotatably and swingably connected to both ends. Then, the upper link 43 and the lower link 4
The transmission case 21 is provided with spherical joints 46 and 47 at the center.
The two trunnions 41 can be vertically moved synchronously in opposite directions.

A shift control device for shifting gears by moving the two trunnions 41 up and down in synchronization with each other in the opposite direction will be described with reference to FIG. Each trunnion 41
Are provided with pistons 6 for individually moving them vertically, and upper chambers 51 and 52 and lower chambers 53 and 54 are defined on both sides of both pistons 6, respectively. In order to control the strokes of the pistons 6 in opposite directions, the shift control valve 5 is installed. Here, the shift control valve 5 includes a spool-type inner valve element 5a and a sleeve-type outer valve element 5b which are slidably fitted to each other, and the outer valve element 5b is connected to the valve outer casing 5.
c so as to be slidably fitted.

The transmission control valve 5 has an input port 5d connected to a pressure source 55, one communication port 5e connected to the piston chambers 51 and 54, and the other communication port 5f connected to the piston chambers 52 and 53, respectively. . And the inner valve body 5a is
Precess cam 7 fixed to the lower end of one trunnion 41
And the outer valve body 5b is driven and engaged with the step motor 4 as a shift actuator in a rack-and-pinion type.

An operation command for the shift control valve 5 is given by an actuator (step motor) 4 responding to an actuator drive position command Asstep (step position command) as a stroke to the outer valve body 5b via a rack and pinion. By this operation command, the outer valve body 5b of the transmission control valve 5
When the shift control valve 5 is opened by displacing the shift control valve 5 from the neutral position to the position shown in FIG. 2 with respect to the inner valve body 5a, the fluid pressure (line pressure P _L ) from the pressure source 55 is supplied to the chambers 52 and 53. On the other hand, when the other chambers 51 and 54 are drained, and the outer valve body 5b of the transmission control valve 5 is displaced in the opposite direction from the neutral position relative to the inner valve body 5a to open the transmission control valve 5. The fluid pressure from the pressure source 55 is supplied to the chambers 51 and 54, while the other chambers 52 and 53 are drained, and the two trunnions 41 are mutually moved in the corresponding vertical direction through the piston 6 by the fluid pressure. It shall be displaced in the opposite direction. As a result, both power rollers 3 have their rotation axis O ₁
Is offset (offset amount y) from the illustrated position intersecting the rotation axis O ₂ of the power roller 3. Tilt (tilt angle φ) around the swing axis O ₃ that is orthogonal to ₁ enables a continuously variable transmission.

During such a gear shift, one trunnion 41
The precess cam 7 coupled to the lower end of the transmission gear 8 mechanically transmits the above-described vertical movement (offset amount y) and tilt angle φ of the trunnion 41 and the power roller 3 to the inner valve body 5 a of the transmission control valve 5 via the transmission link 8. Is fed back as indicated by x. Then, when the speed ratio command value corresponding to the actuator drive position command Asstep to the step motor 4 is achieved by the stepless speed change, the mechanical feedback via the precess cam 7 is applied to the inner valve body 5a of the speed change control valve 5.
The was, is returned to a relatively initial neutral position with respect to the outer valve member 5b, at the same time, both the power roller 3, the rotation axis O ₁ intersects the rotation axis O ₂ of the input and output cone discs 1 and 2 shown By returning to the position, the state of achievement of the speed ratio command value can be maintained.

Since the aim of the control is to make the power roller tilt angle φ a value corresponding to the gear ratio command value, the precess cam 7 basically has to feed back only the power roller tilt angle φ. However, the reason why the power roller offset amount y is also fed back here is to provide a damping effect for preventing the shift control from becoming oscillating, thereby avoiding the hunting phenomenon of the shift control.

The actuator drive position command Asstep to the step motor 4 is determined by the controller 61. For this purpose, as shown in FIG. 2, a signal from a throttle opening sensor 62 for detecting an engine throttle opening TVO, a signal from a vehicle speed sensor 63 for detecting a vehicle speed VSP, and a rotation speed of the input cone disk 1 are provided to the controller 61 as shown in FIG. N _i signal from the output rotation sensor 65 that detects signals from an input rotation sensor 64 for detecting (or may be the engine speed N _e), the rotational speed N _o of the output cone disc 2,
Signal from an oil temperature sensor 66 for detecting a transmission working oil temperature TMP, detects the line pressure P _L from the hydraulic source 55 (typically, internal signals of the controller 61 from controlling the line pressure P _L by the controller 61 signal from the detection to) the line pressure sensor 67, a signal from an engine speed sensor 68 for detecting an engine speed N _e, the signal of the range information from the inhibitor switch 60, UP / DO
A signal for UP / DOWN information from the WN switch 69, a selection mode signal from the mode selection switch 70,
A torque down permission signal from the engine control device 310,
ABS from Anti-Skid Controller (ABS) 320
Control signal, traction control device (TCS) 3
30 and the ASCD cruise signal from the constant speed traveling device 340, respectively.

The controller 61 determines an actuator drive position command Astep (shift command value) for the step motor 4 by the following calculation based on the above various input information. For this reason, in the present embodiment, the controller 61 is configured as shown in FIG. 3, and first, the shift map selecting unit 71 detects the oil temperature TM detected by the sensor 66 in FIG.
The shift map is selected in accordance with various conditions such as P and whether or not the exhaust purification catalyst is being activated.

The case where the shift map selected in this way is, for example, as shown in FIG. 4 will be described.
From the throttle opening TVO and the vehicle speed VSP detected at 63, respectively, based on the shift map corresponding to the shift diagram in the same figure, the reached input speed to be the steady target input speed in the current operating state Search for and find _Ni ^* . Attained gear ratio calculation unit 73, by dividing by reaching the input rotational speed N _i ^* a transmission output rotational speed detected by the sensor 65 of FIG. 2 N _o, a constant corresponding to the arrival input rotation speed N _i ^* A target speed ratio i ^* , which is a target speed ratio, is determined.

The shift time constant calculating section 74 calculates a selected range (forward normal running range D, forward sports running range D _S ),
Vehicle speed VSP, throttle opening TVO, engine speed N
_e , an accelerator pedal operation speed, a signal relating to the amount of torque reduction from a torque down control device (not shown) and a torque down permission signal, an anti-skid control signal, a traction control signal, a low-speed running signal, and a target gear ratio Ratio0 described later. The first speed constant Tg1 and the second speed constant Tg2 of the speed change control are determined according to various conditions such as the speed ratio deviation RtoERR of the speed change, and the ultimate speed ratio i
^* To calculate the deviation E _ip of the target gear ratio Ratio0.
Here, the first speed change time constant Tg1 and the second speed change time constant Tg2 determined to correspond to the secondary delay system of the toroidal-type continuously variable transmission determine the response of the speed change to the attained speed ratio i ^* . The target speed ratio calculating section 75 calculates the target speed ratio i ^* as a first speed time constant Tg.
The target gear ratio Rati at each transitional time and moment for realizing with the gear shift response determined by the first and second gear time constants Tg2
o0 and the intermediate gear ratio Ratio00, respectively,
Only the target gear ratio Ratio0 is output.

The input torque calculating section 76 is for determining the transmission input torque T _i by known method, first determine the engine output torque from the throttle opening TVO and the engine speed N _e, then the input and output of the torque converter The torque ratio t of the torque converter is determined from the speed ratio, which is the ratio of the rotation speeds ( _Ne , _Ni ), and finally, the transmission input torque _Ti is calculated by multiplying the engine output torque by the torque ratio t.
The torque shift compensating speed ratio calculating unit 77 uses the transient target speed ratio Ratio0 and the transmission input torque T _i to eliminate a torque shift (incorrect speed ratio) peculiar to a toroidal-type continuously variable transmission. Shift compensation gear ratio T
Calculate Srto.

Here, the torque shift of the toroidal type continuously variable transmission will be additionally described. During transmission of the toroidal type continuously variable transmission, the power roller 3 is connected between the input and output cone disks 1 and 2 as described above. The trunnion 41 is deformed due to the pinching, and the position of the precess cam 7 at the lower end of the trunnion changes, thereby causing a change in the path length of the mechanical feedback system including the precess cam 7 and the speed change link 8. This causes the torque shift to occur. Therefore, the torque shift of the toroidal type continuously variable transmission differs depending on the target speed ratio Ratio0 and the transmission input torque T _i , and the torque shift compensation speed ratio calculation unit 77 calculates the torque shift compensation speed ratio TSrto from these two-dimensional maps. Ask by search.

The actual transmission ratio calculating section 78 calculates the transmission output rotation speed N _i detected by the sensor 65 in FIG.
_By dividing by _o , the actual gear ratio Ratio is calculated. The gear ratio deviation calculator 79 calculates the target gear ratio Rat.
The actual gear ratio Ratio is subtracted from io0, and the gear ratio deviation RtoERR (= Ratio0-Ra) between the two.
tio).

The first feedback (FB) gain calculating section 80 is a well-known PID corresponding to the speed ratio deviation RtoERR.
Control (P is a proportional control, I is an integral control, D is a differential control) is used when calculating the speed ratio feedback correction amount by, among feedback gain of each control, the transmission input rotational speed N _i and the vehicle speed VSP First proportional control feedback gain fbpDATA to be determined accordingly
1. Feedback gain fbiDATA for integral control
1, and feedback gain fbdDAT for differential control
Find A1. These first feedback gains fb
pDATA1, fbiDATA1, fbdDATA1
It is set in advance as a two-dimensional map of the transmission input rotational speed N _i and the vehicle speed VSP, and request the search from the transmission input rotational speed N _i and the vehicle speed VSP based on this map.

The second feedback (FB) gain calculation unit 81, among the feedback gain used when calculating the speed ratio feedback correction amount by the PID control, be determined in accordance with the transmission hydraulic oil temperature TMP and the line pressure P _L Power feedback gain fbp for the second proportional control
DATA2, feedback gain fbiD for integral control
ATA2 and differential control feedback gain fbd
DATA2, respectively, and these second feedback gains fbpDATA2, fbiDATA2, fbd
DATA2 is set in advance as a two-dimensional map of the working oil temperature TMP and the line pressure P _L, and request the search from the working oil temperature TMP and the line pressure P _L based on this map.

The feedback gain calculator 83 multiplies the first feedback gain and the second feedback gain by the corresponding ones, and obtains the feedback gain fbpDATA for proportional control (= fbpDATA).
1 × fbpDATA2), feedback gain fbiDATA for integration control (= fbiDATA1 × fbiDA)
TA2) and feedback gain fbd for differential control
DATA (= fbdDATA1 × fbdDATA2) is obtained.

The PID control unit 84 uses the feedback gain obtained as described above to change the speed ratio deviation RtoE.
In order to calculate the gear ratio feedback correction amount FBrto by the PID control according to the RR, first, the gear ratio feedback correction amount by the proportional control is calculated by RtoERR × fbpD.
ATA, a speed ratio feedback correction amount by integral control is obtained by ∫RtoERR × fbiDATA, a speed ratio feedback correction amount by differential control is further obtained by (d / dt) RtoERR × fbdDATA, and finally a sum of these three values is obtained. Is the gear ratio feedback correction amount FBrto (= RtoERR × f) by the PID control.
bpDATA + @ RtoERR × fbiDATA + (d /
dt) RtoERR × fbdDATA).

The target gear ratio corrector 85 calculates the target gear ratio Ra
tio0 is corrected by the torque shift compensation speed ratio TSrto and the speed ratio feedback correction amount FBrto, and the corrected target speed ratio DsrRTO (= Ratio0 + TSrt)
o + FBrto). The target step number (actuator target drive position) calculation unit 86 obtains a target step number (actuator target drive position) DsrSTP of the step motor (actuator) 4 for realizing the corrected target gear ratio DsrRTO by searching a map.

Step motor drive position command calculator 87
If the step motor 4 cannot be displaced to the target step number DsrSTP during one control cycle even at the limit drive speed of the step motor 4 determined by the step motor drive speed determination unit 88 based on the transmission operating oil temperature TMP, etc. If the achievable limit position achievable at the limit drive speed of the motor 4 is set as a drive position command Astep to the step motor 4, and the step motor 4 can be displaced to the target step number DsrSTP in one control cycle, The target step number DsrSTP is used as it is as the drive position command Asstep for the step motor 4. Therefore, the drive position command Asstep can always be regarded as the actual drive position of the step motor 4.

The step motor 4 has a drive position command Ast
The outer valve body 5b of the transmission control valve 5 is displaced in the direction and position corresponding to ep through the rack and pinion, and the toroidal-type continuously variable transmission can be shifted in a predetermined manner as described above. When a gear ratio command value corresponding to the drive position command Asstep is achieved by this shift, mechanical feedback via the precess cam 7 causes the inner valve element 5a of the shift control valve 5 to move relative to the outer valve element 5b. is returned to the initial neutral position, at the same time, both the power roller 3, the rotation axis O ₁ is output cone discs 1,
By returning to the illustrated position intersecting the _second rotation axis O2, the state of achieving the above-mentioned speed ratio command value can be maintained.

In the present embodiment, a step motor follow-up determination section 89 is additionally provided. The step motor follow-up determination section 89 determines whether or not the step motor 4 can follow the target step number (actuator target drive position) DsrSTP corresponding to the corrected target gear ratio DsrRTO as follows.

That is, the determination unit 89 first obtains a step number deviation (actuator driving position deviation) ΔSTP between a target step number (actuator target driving position) DsrSTP and a driving position command Asstep which can be regarded as an actual driving position. . Then, the determination unit 89 determines the step number deviation (actuator drive position) at which the step motor 4 cannot be eliminated during one control cycle even at the limit drive speed of the step motor 4 determined as described above by the step motor drive speed determination unit 88. Deviation) lower limit value ΔSTP
_{When the} step number deviation (actuator drive position deviation) ΔSTP is smaller than _LIM (ΔSTP <ΔSTP _LIM ),
The target number of steps corresponding to the corrected target speed ratio DsrRTO of the step motor 4 (actuator target drive position)
It is determined that DsrSTP can be followed, and ΔSTP
When ≧ ΔSTP _LIM, it is determined that the step motor 4 cannot follow the target step number (actuator target drive position) DsrSTP.

When the discriminating section 89 determines that the step motor 4 can follow the target step number (actuator target driving position) DsrSTP corresponding to the corrected target gear ratio DsrRTO, the PID control section 84 has already explained. The calculation of the gear ratio feedback correction amount FBrto by the same PID control is continued. In this manner, when it is determined that the step motor 4 cannot follow the target step number (actuator target drive position) DsrSTP, the gear ratio feedback correction amount ΔRt by the integral control is determined.
The PID control unit 84 is instructed to hold oERR × fbiDATA at the value at the time of the determination.

Further, in the present embodiment, when the step motor drive position command calculation section 87 cannot displace the target step number DsrSTP in one control cycle even at the limit drive speed of the step motor 4, the step motor 4 is set as a drive position command Astep to the step motor 4, and the drive position command Astep is set as an actual drive position of the step motor 4 by the determination unit 89 to follow the step motor. The actual drive position of the step motor 4 required for performing such a follow-up determination is detected by the drive position command Astep from the speed change control device to the step motor 4, as described above. Inexpensive for follow-up determination without relying on actual measurement of the actual drive position of the step motor 4 It can be carried out.

In this embodiment, the stepping motor
In the compliance determination unit 89, the target step number (actuator
Eta target drive position) DsrSTP and the actual drive position (drive
Moving position command) Step number deviation from Asstep
(Actuator drive position deviation) ΔSTP
Follow-up judgment standard deviation determined for each limit drive speed of motor 4
ΔSTP_LIMSmaller than (ΔSTP <ΔST
P_LIM), When the stepper motor 4 has the corrected target speed ratio Dsr
Target number of steps corresponding to RTO (actuator target
Driving position) It is determined that DsrSTP can be followed.
ΔSTP ≧ ΔSTP _LIMWhen step motor 4
Is the target step number (actuator target drive position) Ds
oil temperature TMP to determine that it is impossible to follow rSTP
Limit driving speed of the stepping motor 4 that varies in various ways
The stepping motor 4 can be determined to follow regardless of the
I can.

When the controller 61 shown in FIG. 2 is constituted by a microcomputer, the shift control described with reference to FIG. 3 is executed by the programs shown in FIGS. FIG. 5 shows the entire shift control.
Executed every ms. First, in step 91,
The shift time constant 74 (FIG. 3) is determined by the vehicle speed VSP detected by the vehicle speed sensor 63 (FIG. 2) and the engine rotation sensor 68.
Engine speed detected by (2) N _e, the input rotation sensor 64 transmission input rotational speed detected by the (2) N _i, the throttle opening detected by the throttle opening sensor 62 (FIG. 2) The range information (automatic shift (D) range, sports running (S) range, etc.) from the TVO and the inhibitor switch 60 (FIG. 2) is read.

[0038] Then, in step 92, it reaches the input rotation speed calculating unit 72 (FIG. 3), by dividing the transmission output speed N _o an input rotational speed N _i, and calculates the actual gear ratio Ratio. Next, at step 93, the reached input rotational speed N _i ^* is searched and obtained from the throttle opening TVO and the vehicle speed based on the shift map as shown in FIG.

Next, at step 94 as the attained speed ratio setting means, the attained speed ratio calculating section 73 (FIG. 3)
The attained speed ratio i ^* is calculated by dividing the attained input speed N _i ^* by the transmission output speed N _o . Next, in step 95, the shift time constant calculation unit 74 (FIG. 3) subtracts the target gear ratio Ratio0 calculated in the previous routine (this is calculated in later step 99) from the attained gear ratio i ^* . To calculate the deviation _Eip .

Next, at step 96, it is determined whether or not there is a stepped shift by mode switching and manual shift (hereinafter referred to as "switch shift"). Specifically, in response to a selection mode signal from the mode selection switch 70 (FIG. 2), the presence or absence of switching between the power mode and the snow mode is detected, and a manual range signal is output from the inhibitor switch 60 (FIG. 2). UP / DO while detecting
It is determined whether a signal for UP / DOWN information has been detected from the WN switch 69 (FIG. 2). Next, in step 97, step 98, and step 99 as the target gear ratio setting means, the shift time constant calculating section 74 (FIG. 3)
Is the time constant calculation mode and the first and second shift time constants Tg
1 and Tg2, and a target speed ratio Ratio0 and an intermediate speed ratio Ratio00, respectively. Note that these time constant calculation modes, the first and second shift time constants Tg1 and Tg2, the target speed ratio Ratio0 and the intermediate speed ratio R
The calculation of atio00 will be described in detail with reference to the flowcharts of FIGS.

Thereafter, in step 100, the torque shift compensation speed ratio calculating section 77 (FIG. 3) determines the target speed ratio R
The torque shift compensating speed ratio TSrto is calculated from a map relating to atio and the transmission input torque T _i . Next, in step 101, the PID control unit 84 (FIG. 3) calculates the gear ratio feedback correction amount FBrto by PID control. Next, in step 102, the target gear ratio correction unit 85 (FIG. 3) outputs the target gear ratio R
The corrected target speed ratio DsrRTO is calculated by adding the torque shift compensation speed ratio TSrto and the speed ratio feedback correction amount FBrto to atio0. Next, in step 103, a drive position command Asep to the step motor 4 (FIG. 2) is calculated, and this routine ends.

FIG. 6 is a flowchart showing the time constant calculation mode setting process in the shift control program. This process is executed by the shift time constant calculation unit 74 (FIG. 3). First, at step 104, the vehicle speed sensor 63 (FIG. 2) is used to determine whether the vehicle is stopped or slowing down. It is determined whether or not the vehicle speed VSP detected in the step S) is equal to or higher than a predetermined value VSPA.

[0043] When the vehicle speed VSP is equal to or greater than a predetermined value VPSA, for example, in step 105, the deviation E _ip is determined whether 0 or more. If the deviation _Eip is equal to or greater than 0, it is determined that the driver is depressing the accelerator pedal and the vehicle is in a downshift direction, and the UP / DOWN flag is set to D.
The flag is set to OWN, and the rapid return flag and the return flag for setting the time constant calculation mode are cleared (step 106).

Next, at step 107, the deviation E
It is determined whether or not the absolute value of _ip is less than a predetermined value RPEIP1. If the absolute value of the deviation E _ip is a predetermined value RPEIP1 above, in step 108, the absolute value of the deviation E _ip determines whether less than a predetermined value RPEIP2 (RPEIP2> RPEIP1). The absolute value of the deviation _Eip is a predetermined value R
If PEIP2 or more, in step 109,
The absolute value of the deviation E _ip predetermined value RPEIP3 (RPEIP3
> RPEIP2) is determined. Deviation E _ip
Is greater than or equal to the predetermined value RPEIP3, it is determined that the time constant calculation mode is the rapid depression mode of the accelerator pedal, the rapid depression flag and the depression flag are set (step 110), and the routine ends. . On the other hand, the absolute value of the deviation _Eip is equal to the predetermined value RPE.
If it is less than IP3, it is determined that the time constant calculation mode is the normal depression mode of the accelerator pedal, the depression flag is set (step 111), and this routine ends.

Further, when the absolute value of the deviation E _ip is determined to be smaller than the predetermined value RPEIP1 in step 107, the time constant calculation mode, sudden depression mode of the accelerator pedal, the normal depression mode of the accelerator pedal, the accelerator pedal Is determined to be a mode other than the rapid return mode (this will be described later) and the accelerator pedal return mode (this will also be described later), and the stepping flag and the rapid stepping flag are cleared. Then, this routine ends. Further, in step 108, if the absolute value of the deviation E _ip is smaller than the predetermined value RPEIP2, the present routine ends, to maintain the constant calculation mode when set in the previous routine.

If it is determined in step 105 that the deviation _Eip is greater than 0, for example, it is determined that the driver is returning to the accelerator pedal to perform an upshift.
The UP / DOWN flag is set to UP, and the depression flag and the rapid depression flag for setting the time constant calculation mode are cleared (step 11).
3).

Next, at step 114, the deviation E
It is determined whether or not the absolute value of _ip is less than a predetermined value RSEIP1. If the absolute value of the deviation E _ip is a predetermined value RSEIP1 above, in step 115, the absolute value of the deviation E _ip determines whether less than a predetermined value RSEIP2 (RSEIP2> RSEIP1). The absolute value of the deviation _Eip is a predetermined value R
If SEIP2 or more, in step 116,
The absolute value of the deviation E _ip predetermined value RSEIP3 (RSEIP3
> RSEIP2). Deviation E _ip
Is greater than or equal to the predetermined value RSEIP3, it is determined that the time constant calculation mode is the rapid return mode of the accelerator pedal, and the rapid return flag and the return flag are set (step 117). To end.
In contrast, given the absolute value of the deviation E _ip is value RSEIP3
If it is less than this, it is determined that the time constant calculation mode is the normal foot return mode of the accelerator pedal, a foot return flag is set (step 118), and this routine ends.

[0048] Also, when the absolute value of the deviation E _ip is determined to be smaller than the predetermined value RSEIP1 in step 114, the time constant calculation mode, sudden depression mode of the accelerator pedal, the normal depression mode of the accelerator pedal, the accelerator pedal Is determined to be a mode other than the rapid return mode and the accelerator pedal return mode, the foot return flag and the rapid return flag are cleared (step 119),
This routine ends. Further, in step 115, if the absolute value of the deviation E _ip is smaller than the predetermined value RSEIP2, the present routine ends, to maintain the constant calculation mode when set in the previous routine.

If the vehicle speed VSP is less than the predetermined value VSPA in step 104, the quick return flag, the return flag, the stepping flag, and the sudden step flag are all cleared. (Step 120). The predetermined value RPEIP
1, RPEIP2, RPEIP3, RSEIP1, RS
Let EIP2 and RSEIP3 be experimental values given according to the vehicle.

FIG. 7 is a flowchart showing a time constant calculation process in the shift control program. This processing is also executed by the shift time constant calculation unit 74 (FIG. 3). First, in step 121, the first basic time constant calculated based on the map selected according to the time constant calculation mode TG1 and the second basic time constant TG2 are calculated.
The detailed calculation process of the first basic time constant TG1 and the second basic time constant TG2 will be described later with reference to the flowchart of FIG.

Next, in step 122 as a time constant correcting means, the first set according to the change of the range.
Shift correction coefficient KO_1 and second shift correction coefficient KO_
2 are calculated respectively. The detailed calculation processing of the first shift correction coefficient KO_1 and the second shift correction coefficient KO_2 will be described later with reference to the flowchart of FIG.

Next, in step 123 as time constant setting means, the first shift time constant Tg1 is calculated by multiplying the first basic time constant TG1 and the first shift correction coefficient KO_1, and the second shift time constant Tg1 is calculated. Tg2
With the second basic time constant TG2 and the second shift correction coefficient KO
_2, and the routine ends.

FIG. 8 is a flowchart showing the intermediate speed ratio and target speed ratio calculation processing in the speed change control program. This process is also executed by the shift time constant calculation section 74 (FIG. 3). In step 128, the difference between the attained speed ratio i ^* and the intermediate speed ratio Ratio00 calculated in the immediately preceding routine is set to the first value. The intermediate speed ratio Rat calculated by multiplying the speed change time constant Tg1 by the previous routine.
io00, the current intermediate gear ratio R
atio00 and at the same time multiplying the difference between the intermediate speed ratio Ratio00 calculated in the immediately preceding routine and the target speed ratio Ratio0 calculated in the immediately preceding routine by the second speed constant Tg2 one time earlier. The current target gear ratio Ratio0 is calculated by adding the target gear ratio Ratio0 calculated in the routine (2), and this routine ends.

FIG. 9 is a flowchart showing the first and second basic time constant calculation processing in the shift control program.
This process is also executed by the shift time constant calculation unit 74 (FIG. 3).
It is determined whether or not a switch shift has occurred. In the case where the switch shift is not performed, that is, in the case of the normal shift mode, it is determined in step 130 whether the mode selection switch 70 (FIG. 2) is turned on. If the mode selection switch 70 (FIG. 2) is not turned on, in step 131, the UP / DO
It is determined whether the WN flag is UP or DOWN.

When the UP / DOWN flag is UP,
In step 132, it is determined whether the rapid return flag is set, that is, whether the time constant calculation mode is the rapid return mode of the accelerator pedal. If it is determined that the quick return flag is not set, it is determined in step 133 whether the return flag is set, that is, whether the time constant calculation mode is the accelerator return mode of the accelerator pedal. . If the return flag is not set, the table TgTBL1 is selected (step 134). If the return flag is set, the table TgTBL2 is selected (step 135). If it is determined in step 132 that the quick return flag is set, the table TgTBL3
Is selected (step 136).

If it is determined in step 131 that the UP / DOWN flag is DOWN, in step 137, it is determined whether or not the rapid depression flag is set, that is, the time constant calculation mode is the rapid depression mode of the accelerator pedal. It is determined whether or not. If it is determined that the sudden depression flag is not set, it is determined in step 138 whether the depression flag is set, that is, whether the time constant calculation mode is the accelerator pedal depression mode. If the stepping flag is not set, the table TgTBL4 is selected (step 139), and if the stepping flag is set, the table TgTBL5 is selected (step 14).
0). If it is determined in step 137 that the sudden depression flag is set, the table TgTBL6 is selected (step 141).

If it is determined in step 130 that the mode selection switch 70 (FIG. 2) has been turned on,
In steps 42 and thereafter, steps 131 to 141
The tables TgTBL7 to TgTBL12 are selected in the same manner as described above.
Further, when it is determined in step 129 that the switch shift has been performed, in step 143 and subsequent steps,
In the steps after step 143, step 13
Tables TgTBL13-2 in the same manner as 1-142
Select 4. In addition, the tables TgTBL13 to 24
Is a table related to the throttle opening TVO, the idle state, the first basic time constant TG1, and the second basic time constant TG2.

Steps 134-136, 139-141
After selecting one of the tables TgTBL1 to TgTBL24 by, for example, the first basic time constant TG1 and the second basic time constant TG2 are respectively determined in step 144 based on the throttle opening TVO and the idle state from the selected table. Calculate and end this routine. It should be noted that the first basic time constant TG1 and the second basic time constant TG2 obtained in this manner increase as the operation speed of the accelerator pedal increases, when the throttle opening and the idling determination state are the same. It is set as follows. Therefore, the first basic time constant TG1 and the second basic time constant TG2 are respectively larger in the case of the rapid stepping mode and the rapid step return mode than in the case of the normal stepping mode or the normal step return mode. Is set to

FIG. 10 is a flowchart showing the first and second shift correction coefficient calculation processing in the shift control program. This process is also executed by the shift time constant calculating section 74 (FIG. 3). First, at step 145 as operation determining means, the inhibitor switch 60
Based on the signal for range information from FIG.
Select whether the range has been switched or not. If the range has been switched, it is determined in step 146 whether the rapid depression flag or the depression flag is set. If neither the rapid depression flag nor the depression flag is set, it is determined in step 147 whether the rapid return flag or the return flag is set. If neither the rapid return flag nor the return flag is set, the first shift correction coefficient and the second shift correction coefficient are set to KOTBL1 in step 148, respectively.
When this routine is completed by setting [1] and KOTBL1 [2], and the rapid return flag or the return flag is set, the first shift correction coefficient and the second shift correction coefficient are set to KOTBL2 in step 149, respectively. [1] and KOTBL2 [2] are set, and this routine ends.

If the rapid depression flag or the depression flag is set in step 146, the first shift correction coefficient and the second shift correction coefficient are set in step 150 to KOTBL3 [1] and KOTB, respectively.
L3 [2] is set and this routine is terminated.
If it is determined at 45 that there is no range switching,
In step 151, the first shift correction coefficient and the second shift correction coefficient are each set to 1, that is, the present routine ends without performing the correction relating to the change in the range.
The first shift correction coefficient is set such that KOTBL1 [1]> KOTBL3 [1] KOTBL1 [1]> KOTBL2 [1], and the second shift correction coefficient is KOTBL1 [2]> KOTBL3 [ 2] Set so that KOTBL1 [2]> KOTBL2 [2]. As a result, as the change in the range becomes larger, the shift time constant is made smaller so that the shift speed becomes slower, whereby good shift control is performed for the driver.

According to the present embodiment, when it is determined that the operation of the select lever has been performed, the shift time constant is corrected so that the shift speed becomes slower, so that there is no possibility that the driver will feel uncomfortable. .

The present invention is not limited to the above-described embodiment, and many modifications and variations are possible. For example, in the above-described embodiment, a case has been described in which the shift control device for an automatic transmission according to the present invention is applied to a toroidal-type continuously variable transmission. The present invention can be applied to an automatic transmission and a stepped automatic transmission. However, when the present invention is applied to a stepped automatic transmission, the operating oil pressure values of the shifting friction elements such as a hydraulic clutch and a hydraulic brake are directly controlled individually to shift from the pre-shift speed to the post-shift speed. In the meantime, the shift control device for an automatic transmission according to the present invention can be applied when the execution gear ratio represented by the transmission input rotation ratio is transiently controlled with a predetermined shift time constant.

The shift time constant is calculated based on the throttle opening and the basic time constant relating to the idling determination state, but the shift time constant is calculated using only one of the throttle opening and the idling determination state. You can also.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional side view of a toroidal type continuously variable transmission including a shift control device for an automatic transmission according to the present invention.

FIG. 2 is a longitudinal sectional front view showing the toroidal-type continuously variable transmission of FIG. 1 together with a shift control system thereof.

FIG. 3 is a functional block diagram of a shift control executed by a controller of FIG. 2;

FIG. 4 is a shift diagram illustrating a shift pattern of the continuously variable transmission.

FIG. 5 is a flowchart showing an entire shift control program of a shift control device for an automatic transmission according to the present invention.

FIG. 6 is a flowchart showing a time constant calculation mode setting process in a shift control program.

FIG. 7 is a flowchart showing a time constant calculation process in a shift control program.

FIG. 8 is a flowchart showing an intermediate speed ratio and a target speed ratio calculation process in the speed change control program.

FIG. 9 is a flowchart showing a first and a second basic time constant calculation process in the shift control program.

FIG. 10 is a flowchart showing first and second shift correction coefficient calculation processes in a shift control program.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Input cone disk 2 Output cone disk 3 Power roller 4 Step motor (transmission actuator) 5 Transmission control valve 6 Piston 7 Precess cam 8 Transmission link 20 Input shaft 28 Loading cam 41 Trunnion 43 Upper link 45 Lower link 60 Inhibitor switch 61 Controller 62 Throttle Openness sensor 63 Vehicle speed sensor 64 Input rotation sensor 65 Output rotation sensor 66 Oil temperature sensor 67 Line pressure sensor 68 Engine rotation sensor 69 UP / DOWN switch 70 Mode selection switch 71 Shift map selection unit 72 Reached input rotation speed calculation unit 73 Reached speed change Ratio calculation unit 74 Shift time constant calculation unit 75 Target gear ratio calculation unit 310 Engine control switch 320 Anti-skid control device 330 Traction control device 34 0 Constant speed traveling device

 ────────────────────────────────────────────────── ─── Continued on the front page (72) Inventor Tetsu Takizawa 2 Takara-cho, Kanagawa-ku, Yokohama-shi, Kanagawa Nissan Motor Co., Ltd. (72) Inventor Masato Koga 2 Takara-cho, Kanagawa-ku, Yokohama-shi, Kanagawa Nissan Motor ( 72) Inventor Mitsuru Watanabe F-term (reference) 3J052 AA04 CA22 FB31 GC01 GC03 GC13 GC23 GC46 GD11 HA11 HA13 KA01 LA01 2 Takara-cho, Kanagawa-ku, Yokohama-shi, Kanagawa Prefecture

Claims (1)

[Claims] An attained gear ratio setting means for setting an attained gear ratio based on an operating state of a driver and / or a running state of a vehicle, wherein an actual gear ratio changes at a predetermined gear speed with respect to the attained gear ratio. Target speed ratio setting means for setting a target speed ratio, and time constant setting means for setting a speed time constant for determining a shift speed of the target speed ratio, so that the actual speed ratio becomes the attained speed ratio. An operation determining means for determining whether or not the driver has operated the select lever; and determining that the operation of the select lever has been performed by the operation determining means. A shift control device for an automatic transmission, comprising: a time constant correction unit that corrects a shift time constant set by a constant setting unit so that a shift speed is reduced.