JP4636431B2 - Automatic transmission control device - Google Patents

Description

  The present invention relates to an automatic transmission control device.

  2. Description of the Related Art Conventionally, two spool valves that respectively adjust output pressures to two types of friction elements are one type of automatic transmission control device that outputs fluid pressure to a plurality of friction elements of an automatic transmission to control the automatic transmission. Are driven by the command pressure of one solenoid valve (see, for example, Patent Documents 1 and 2). In such an automatic transmission control device, since one electromagnetic valve is shared to drive two spool valves, the number of electromagnetic valves is reduced, thereby reducing the size and cost of the device. .

JP-A-6-26568 JP-A-6-341541

  However, when a common command pressure is directly applied to the two spool valves as in the automatic transmission control device disclosed in Patent Document 1, not only the spool valve that outputs the engagement pressure to the friction element but also the friction element. The spool valve that outputs the release pressure is also driven by the command pressure. Therefore, in the electromagnetic valve, since the flow rate of the working fluid is excessively consumed by driving the latter spool valve, the command pressure varies. As a result, in the former spool valve, the engagement pressure output to the friction element changes, and the engagement state of the friction element changes accordingly, so that the control accuracy of the automatic transmission decreases. .

  Further, as in the automatic transmission control device disclosed in Patent Document 2, when a common command pressure is applied to two spool valves via an electromagnetic relay valve, only one spool valve is caused by the flow path switching action of the electromagnetic valve. It is possible to suppress the command pressure fluctuation of the electromagnetic valve by stopping the operation. However, since an electromagnetic relay valve is used, the size reduction and cost reduction effects are reduced accordingly.

The present invention has been made in view of the above problems, and an object thereof is to provide an automatic transmission control device that improves the control accuracy of an automatic transmission.
Another object of the present invention is to provide an automatic transmission control device that achieves downsizing and cost reduction.

According to the invention of claim 1, adjusting at least one Der of the plurality of spool valves is, the output pressure of the specific spool valve that share the electromagnetic valve between said pressure control valve to release pressure of the friction element In this case, a counter force opposite to the force by the command pressure is applied to the spool of the specific spool valve, and the spool is locked by the spool hole of the specific spool valve. Therefore, when adjusting the output pressure of the specific spool valve to the release pressure, the operation of the specific spool valve is surely stopped by the spool being locked by the spool hole. Variation is suppressed. Therefore, when the specific spool valve adjusts its output pressure to the release pressure, other spool valves that adjust the output pressure to the friction element engagement pressure are prevented from changing the engagement pressure due to the command pressure fluctuation of the solenoid valve. As a result, the control accuracy of the automatic transmission is improved. In addition, such an improvement in control accuracy can be realized by directly driving a plurality of spool valves with a common command pressure, thereby reducing the size and cost of the apparatus.

  According to the second aspect of the present invention, when adjusting the output pressure of the specific spool valve to the engagement pressure of the friction element, the opposing force is reduced compared to when adjusting the output pressure to the release pressure, and the spool of the specific spool valve Can be moved to a position corresponding to the command pressure. Therefore, the release and engagement of the friction element can be reliably switched by the output pressure of the specific spool valve.

According to the third aspect of the present invention, when adjusting the output pressure of the specific spool valve to the release pressure, the force generated by the output pressure of the manual valve adjusted to the first pressure is applied to the spool of the specific spool valve as an opposing force. . On the other hand, when adjusting the output pressure of the specific spool valve to the engagement pressure, the force by the output pressure of the manual valve adjusted to the second pressure lower than the first pressure is applied to the spool of the specific spool valve as an opposing force. . Therefore, it becomes possible to drive the specific spool valve by using the existing manual valve that switches the range of the automatic transmission by adjusting the output pressure that is the source pressure of the plurality of spool valves. A reduction in cost effect can be avoided.
In the first to third aspects of the invention, as the specific spool valve, for example, as in the fourth aspect of the invention, at least one of the switching valve and the pressure control valve can be used.

Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings.
(First embodiment)
FIG. 1 shows an automatic transmission control device 10 according to a first embodiment of the present invention. The automatic transmission control device 10 is attached to the vehicle automatic transmission 2 and electronically controls the automatic transmission 2.

  The automatic transmission 2 includes clutches C1, C2 and the like as a plurality of friction elements that are engaged or released according to the hydraulic pressure of the hydraulic oil output from the automatic transmission control device 10. Here, the clutch C1 is engaged when the drive (D) range is selected as the range of the automatic transmission 2, and is released when the reverse (R) range is selected. Conversely, the clutch C2 is released when the D range is selected, and is engaged when the R range is selected. In addition to the D and R ranges, the automatic transmission 2 is provided with a parking (P) range and a neutral (N) range.

The automatic transmission control device 10 includes a manual valve 12, a solenoid valve 14, a pressure control valve 16, and a switching valve 18.
The manual valve 12 is a 4-port spool valve that is substantially the same as an existing manual valve. The input side of the manual valve 12 is connected to a drain pressure drain 20 opened to the atmosphere and a line pressure flow path 24 connected to a line pressure generation circuit 22. Here, the line pressure is a hydraulic pressure adjusted to be higher than the drain pressure by the line pressure generation circuit 22. The output side of the manual valve 12 is connected to a flow path 26 connected to the pressure control valve 16 and the switching valve 18 and a flow path 28 connected to the switching valve 18. The spool of the manual valve 12 is mechanically or electrically connected to a shift lever 30 as a range selector.

The manual valve 12 moves the spool to a position that realizes one of the ranges of D, R, P, and N selected by the shift lever 30 by the user of the vehicle, and outputs the output pressure to each of the flow paths 26 and 28. Adjust between pressure and lower drain pressure.
Specifically, when the D range is selected, the manual valve 12 adjusts the output pressure to the flow path 26 to the line pressure and adjusts the output pressure to the flow path 28 to the drain pressure. When the R range is selected, the manual valve 12 adjusts the output pressure to the flow path 26 to the drain pressure and adjusts the output pressure to the flow path 28 to the line pressure. Furthermore, when the P or N range is selected, the manual valve 12 adjusts the output pressure to each of the flow paths 26 and 28 to the drain pressure.

  The solenoid valve 14 is constituted by a solenoid / spring-driven 4-port spool valve. The input side of the electromagnetic valve 14 is connected to a modulated pressure flow path 36 connected to the modulated pressure generating circuit 32. Here, the modulation pressure is a hydraulic pressure that is adjusted to be higher than the drain pressure and not to exceed the line pressure by the modulation pressure generation circuit 32 using the line pressure as the original pressure. The output side of the electromagnetic valve 14 is connected to a flow path 34 connected to the pressure control valve 16 and the switching valve 18. The electromagnetic valve 14 is electrically connected to an electronic control unit (ECU) (not shown). The electromagnetic valve 14 adjusts the command pressure given to the pressure control valve 16 and the switching valve 18 in common to the pressure control valve 16 and the switching valve 18 by being output to the flow path 34 to a hydraulic pressure according to the command value of the ECU using the modulation pressure as a source pressure.

  The pressure control valve 16 is a spring-driven 6-port spool valve. The flow path 34 connected to the electromagnetic valve 14 branches into two in the middle, and the input side of the pressure control valve 16 is connected to one branch flow path 34a. Further, the flow path 26 connected to the manual valve 12 is branched into two in the middle, and the input side of the pressure control valve 16 is connected to one branch flow path 26a. The output side of the pressure control valve 16 is connected to a flow path 38 connected to the clutch C1 and the input side of the pressure control valve 16 itself. Here, the flow path 38 is bifurcated in the middle, one branch flow path 38a is connected to the clutch C1, and the other branch flow path 38b is connected to the input side of the pressure control valve 16. Yes.

As shown in FIG. 2, in the pressure control valve 16, the force F _c1 due to the output pressure to the clutch C1 input from the branch flow path 38b and the force F _s1 due to the compression spring 40 are input from the branch flow path 34a. The spool 42 acts on the spool 42 in the opposite direction to the force F _e generated by the command pressure of the valve 14. Thus the pressure control valve 16 moves the spool 42 in response to the balance of forces _{F c1, F s1, F e} , to adjust the output pressure to the clutch C1.

During selection of the specific D-range, the pressure control valve 16 to the source pressure line pressure to be input from the branch passage 26a is command pressure of the solenoid valve 14 as shown in FIG. 3 is a predetermined pressure P _th or more and In this case, the output pressure to the clutch C1 is linearly increased or decreased according to the increase or decrease of the command pressure. The output pressure of the pressure control valve 16 at this time, when a predetermined pressure P _b above shown in FIG. 3, the engagement pressure for engaging the clutch C1. In addition, when the R range is selected, the pressure control valve 16 to which the drain pressure is input from the branch flow path 26a adjusts the output pressure to the clutch C1 to the drain pressure without depending on the command pressure of the electromagnetic valve 14. In addition, the drain pressure which is the output pressure of the pressure control valve 16 at this time becomes a release pressure for releasing the clutch C1.

  As shown in FIG. 1, the switching valve 18 is constituted by a spring-driven 5-port spool valve. The input side of the switching valve 18 includes a branch channel 34b on the other side of the channel 34 connected to the electromagnetic valve 14, a branch channel 26b on the other side of the channel 26 connected to the manual valve 12, and a manual valve. 12 is connected to a flow path 28 connected to 12. The output side of the switching valve 18 is connected to a flow path 44 connected to the clutch C2.

In the switching valve 18 as shown in FIG. 4 (A), the force F _s2 by the force F _m and the compression spring 46 by the hydraulic pressure supplied from the branch passage 26b is, the electromagnetic valve 14 is inputted from the branch flow path 34b acting on the spool 48 in a direction opposite to the force F _e due to the command pressure. Thus the switching valve 18 moves the spool 48 in response to the balance of forces _{F m, F s2, F e} , to adjust the output pressure to the clutch C2.

Specifically, when the D range is selected, the switching valve 18 receives the line pressure from the branch flow path 26b and the drain pressure from the flow path 28, whereby the maximum values F of the forces F _m and F _s2 and the force F _e are obtained. _emax satisfies F _m + F _s2 > F _emax . Therefore, in the switching valve 18 when the D range is selected, the spool 48 is locked in the spool hole 50 and positioned at a position where the output pressure to the clutch C2 is adjusted to the drain pressure as shown in FIG. In addition, the drain pressure which is the output pressure of the switching valve 18 at this time becomes a release pressure for releasing the clutch C2. When the R range is selected, the switching valve 18 is supplied with drain pressure from the branch flow path 26b and line pressure from the flow path 28, whereby the maximum values F _emax of the forces F _m , F _s2 and force F _e are _{obtained. Satisfies} F _m + F _s2 <F _emax . Therefore, in the switching valve 18 when the R range is selected, when the command pressure of the electromagnetic valve 14 is equal to or higher than a predetermined pressure, the spool 48 changes the output pressure to the clutch C2 to the original line pressure as shown in FIG. Position at the position to be adjusted. Note that the line pressure that is the output pressure of the switching valve 18 at this time is the engagement pressure for engaging the clutch C2.

In such an automatic transmission control device 10, when the D range is selected, the pressure control valve 16 adjusts the output pressure to the clutch C1 to the engagement pressure or the like according to the command pressure of the electromagnetic valve 14. In this case the switching valve 18, the force F _e by the force F _m is the command pressure by the line pressure by a spool 48 that acts in the opposite direction the spool hole 50 is engaged, the output pressure release pressure to the clutches C2 Adjusted. Therefore, when the output pressure to the clutch C1 is adjusted to the engagement pressure or the like according to the command pressure, the operation of the spool 48 of the switching valve 18 is surely stopped so that the command pressure fluctuation of the electromagnetic valve 14 is suppressed. Therefore, the output pressure to the clutch C1 becomes difficult to change.

When the R range is selected, the pressure control valve 16 adjusts the output pressure to the clutch C2 to the release pressure. In this case the switching valve 18, by the hydraulic pressure in the branch passage 26b is switched from the line pressure at the time of D range selection drain pressure, the force F _m of the opposite direction to the force F _e due to the command pressure than during the D range selection And the spool 48 moves to a position corresponding to the command pressure, and the output pressure to the clutch C2 is adjusted to the engagement pressure or the like. In the switching valve 18 in which the rate of change of the output pressure with respect to the input pressure is generally reduced, even if the spool 42 of the pressure control valve 16 vibrates and the command pressure of the electromagnetic valve 14 fluctuates when the R range is selected, the fluctuation occurs. Is almost unaffected. For this reason, the output pressure to the clutch C2 is unlikely to fluctuate.

  As described above, in the automatic transmission control device 10, fluctuations in the hydraulic pressure output to the clutch C <b> 1 or C <b> 2 on the engagement side can be suppressed, so that the control accuracy of the automatic transmission 2 is improved. Moreover, such an improvement in control accuracy can be realized by driving the pressure control valve 16 and the switching valve 18 with a common command pressure and the output pressure of the manual valve 12 having substantially the same configuration as the existing one. Miniaturization and cost reduction are achieved.

As described above, in the first embodiment, the set of the pressure control valve 16 and the switching valve 18 corresponds to “a plurality of spool valves” recited in the claims, and the switching valve 18 is the “specific spool” recited in the claims. Corresponds to “valve”. The line pressure of the hydraulic pressure output from the manual valve 12 to the flow path 26 and input to the switching valve 18 corresponds to the “first pressure” recited in the claims, and the drain pressure of the hydraulic pressure is patented. This corresponds to the “second pressure” recited in the claims, and the force F _m generated by the hydraulic pressure (line pressure and drain pressure) corresponds to the “opposing force”.

(Second embodiment)
As shown in FIG. 5, the second embodiment of the present invention is a modification of the first embodiment, and the description of the components that are substantially the same as those of the first embodiment will be omitted by attaching the same reference numerals. .
The automatic transmission control device 100 according to the second embodiment includes a first pressure control valve 102 having a configuration different from that of the pressure control valve 16 according to the first embodiment, and is replaced with a first pressure control valve 102 according to the first embodiment. A two-pressure control valve 104 is provided.

  The first pressure control valve 102 is a spring-driven 6-port spool valve. The input side of the first pressure control valve 102 is connected to the branch channel 34 a of the channel 34 connected to the electromagnetic valve 14 and the branch channel 26 a of the channel 26 connected to the manual valve 12. Further, the flow path 28 of the present embodiment connected to the manual valve 12 is branched into two in the middle, and the input side of the first pressure control valve 102 is also connected to one of the branched flow paths 28a. . The output side of the first pressure control valve 102 is connected to a flow path 38 connected to the clutch C1 and the input side of the first pressure control valve 102 itself, as in the case of the pressure control valve 16 of the first embodiment. ing.

As shown in FIG. 6A, in the first pressure control valve 102, the force F _m1 due to the line pressure or drain pressure inputted from the branch flow path 28a, the force F _c1 due to the output pressure to the clutch C1, and the compression spring 106 are used. The force F _s1 acts on the spool 108 in the opposite direction to the force F _e caused by the command pressure of the electromagnetic valve 14. Thus the first pressure control valve 102 moves the spool 108 in response to the balance of forces _{F m1, F c1, F s1} , F e, to adjust the output pressure to the clutch C1.

Specifically, when the D range is selected, the first pressure control valve 102 receives the drain pressure from the branch flow path 28a and the line pressure from the branch flow path 26a, whereby the forces F _m1 , F _c1 , F _s1 and The maximum value F _emax of the force F _e satisfies F _m1 + F _c1 + F _s1 <F _emax . Therefore, in the first pressure control valve 102 when the D range is selected, when the command pressure of the electromagnetic valve 14 is equal to or higher than a predetermined pressure, the output pressure to the clutch C1 is linearly increased or decreased according to the increase or decrease of the command pressure. Note that the output pressure of the first pressure control valve 102 at this time becomes the engagement pressure of the clutch C1 when the pressure exceeds a predetermined pressure. Further, when the R range is selected, the first pressure control valve 102 receives line pressure from the branch flow path 28a and drain pressure from the branch flow path 26a, whereby the forces F _m1 , F _c1 , F _s1 and force The maximum value F _{emax of} F _e satisfies F _m1 + F _c1 + F _s1 > F _emax . Therefore, in the first pressure control valve 102 when the R range is selected, the spool 108 is locked to the spool hole 110 and positioned at a position where the output pressure to the clutch C1 is adjusted to the drain pressure as shown in FIG. 6B. . The drain pressure that is the output pressure of the first pressure control valve 102 at this time becomes the release pressure of the clutch C1.

  As shown in FIG. 5, the second pressure control valve 104 is constituted by a spring-driven 6-port spool valve. The input side of the second pressure control valve 104 is connected to the branch channel 34 b of the channel 34 connected to the electromagnetic valve 14 and the branch channel 26 b of the channel 26 connected to the manual valve 12. Further, the input side of the second pressure control valve 104 is also connected to the branch flow path 28 b on the other side of the flow path 28 connected to the manual valve 12. The output side of the first pressure control valve 102 is connected to a flow path 112 connected to the clutch C2 and the input side of the second pressure control valve 104 itself. Here, the flow path 112 is branched into two in the middle, and one of the branch flow paths 112a is connected to the clutch C2 and the other branch flow path 112b is connected to the input side of the second pressure control valve 104. Has been.

As shown in FIG. 7A, in the second pressure control valve 104, a force F _m2 due to the hydraulic pressure input from the branch flow path 26b, a force F _c2 due to the output pressure to the clutch C2, and a force F _s2 due to the compression spring 114 are obtained. but it acts on the spool 116 in a direction opposite to force F _e by command pressure of the solenoid valve 14. Thus the second pressure control valve 104 moves the spool 116 in response to the balance of forces _{F m2, F c2, F s2} , F e, to adjust the output pressure to the clutch C2.

Specifically, when the D range is selected, the second pressure control valve 104 is supplied with the line pressure from the branch flow path 26b and the drain pressure from the branch flow path 28b, whereby the forces _Fm2 , _Fc2 , _Fs2 and The maximum value F _emax of the force F _e satisfies F _m2 + F _c2 + F _s2 > F _emax . Therefore, in the first pressure control valve 102 when the D range is selected, the spool 116 is locked by the spool hole 118 and positioned at a position where the output pressure to the clutch C2 is adjusted to the drain pressure as shown in FIG. 7B. . The drain pressure that is the output pressure of the second pressure control valve 104 at this time is the release pressure of the clutch C2. Further, when the R range is selected, the second pressure control valve 104 is supplied with drain pressure from the branch flow path 26b and line pressure from the branch flow path 28b, whereby forces _Fm2 , _Fc2 , _Fs2 and force The maximum value F _{emax of} F _e satisfies F _m2 + F _c2 + F _s2 <F _emax . Therefore, in the second pressure control valve 104 when the R range is selected, the output pressure to the clutch C2 is linearly increased / decreased according to the increase / decrease of the command pressure when the command pressure of the electromagnetic valve 14 is equal to or higher than a predetermined pressure. Note that the output pressure of the second pressure control valve 104 at this time becomes the engagement pressure of the clutch C2 when the pressure exceeds a predetermined pressure.

In such an automatic transmission control device 100, when the D range is selected, the first pressure control valve 102 adjusts the output pressure to the clutch C1 to the engagement pressure or the like according to the command pressure of the electromagnetic valve 14. In this case the second pressure control valve 104, the force F _e force F _{m @ 2} by the line pressure according to command pressure by a spool 116 which acts in the opposite direction the spool hole 118 is engaged, the output pressure to the clutch C2 Adjusted to the release pressure. Therefore, when the output pressure to the clutch C1 is adjusted to the engagement pressure or the like according to the command pressure, the operation of the spool 116 of the second pressure control valve 104 is surely stopped, and the command pressure fluctuation of the electromagnetic valve 14 is suppressed. As a result, the output pressure to the clutch C1 is less likely to fluctuate.

When the R range is selected, the second pressure control valve 104 adjusts the output pressure to the clutch C2 to the engagement pressure or the like according to the command pressure of the electromagnetic valve 14. In this case the first pressure control valve 102, the force F _e force F _m1 by the line pressure according to command pressure by a spool 108 which acts in the opposite direction the spool hole 110 is engaged, the output pressure to the clutch C1 Adjusted to the release pressure. Therefore, when the output pressure to the clutch C2 is adjusted to the engagement pressure or the like according to the command pressure, the operation of the spool 108 of the first pressure control valve 102 is surely stopped, and the command pressure fluctuation of the electromagnetic valve 14 is suppressed. As a result, the output pressure to the clutch C2 is unlikely to fluctuate.

  Thus, the automatic transmission control device 100 can also suppress fluctuations in the hydraulic pressure output to the clutch C1 or C2 on the engagement side, and can control the first and second pressure control valves 102 and 104 with a common command pressure, It can be driven by the output pressure of the manual valve 12 that has substantially the same configuration as the existing one. Therefore, it is possible to reduce the size and cost of the apparatus 100 while improving the control accuracy of the automatic transmission 2.

As described above, in the second embodiment, the set of the first and second pressure control valves 102 and 104 corresponds to the “plurality of spool valves” recited in the claims, and the first and second pressure control valves 102 and 104. Are equivalent to “specific spool valves” described in the claims. The line pressure of the hydraulic pressure output from the manual valve 12 to the flow path 28 and input to the first pressure control valve 102 corresponds to the “first pressure” recited in the claims, and the drain pressure of the hydraulic pressure is the drain pressure. The pressure corresponds to the “second pressure” recited in the claims, and the force F _m1 due to the hydraulic pressure corresponds to the “opposing force”. Furthermore, the line pressure of the hydraulic pressure output from the manual valve 12 to the flow path 26 and input to the second pressure control valve 104 corresponds to the “first pressure” recited in the claims. The drain pressure corresponds to the “second pressure” recited in the claims, and the force F _m2 due to the hydraulic pressure corresponds to the “opposing force”.

In the above description, a plurality of embodiments of the present invention have been described. However, the present invention should not be construed as being limited to these embodiments.
For example, in the first embodiment, the example in which the present invention is applied to the switching valve 18 that adjusts the output pressure to the clutch C2 that is engaged in the R range and released in the D range has been described. In the second embodiment, the first pressure control valve 102 that adjusts the output pressure to the clutch C1 that is engaged in the D range and released in the R range, and the clutch that is engaged in the R range and released in the D range The example which applied this invention to the 2nd pressure control valve 104 which adjusts the output pressure to C2 was demonstrated. In the present invention, not only the spool valve that adjusts the output pressure to the friction element having the same engagement / release configuration as C1 and C2 but also the output to the friction element having the engagement / release configuration different from C1 and C2. It can also be applied to a spool valve that adjusts the pressure. In any case, the present invention may be applied to one or two spool valves as in the above-described embodiment, or the present invention may be applied to an appropriate number of spool valves. Also good.

1 is a hydraulic circuit diagram showing an automatic transmission control device according to a first embodiment. It is a schematic diagram for demonstrating the action | operation of the pressure control valve by 1st embodiment. It is a characteristic view for demonstrating the action | operation of the pressure control valve by 1st embodiment. It is a schematic diagram for demonstrating the action | operation of the switching valve by 1st embodiment. It is a hydraulic circuit diagram which shows the automatic transmission control apparatus by 2nd embodiment. It is a schematic diagram for demonstrating the action | operation of the 1st pressure control valve by 2nd embodiment. It is a schematic diagram for demonstrating the action | operation of the 2nd pressure control valve by 2nd embodiment.

Explanation of symbols

2 automatic transmission, 10, 100 automatic transmission control device, 12 manual valve, 14 solenoid valve, 16 pressure control valve (spool valve), 18 switching valve (spool valve, specific spool valve), 48, 108, 116 spool, 50, 110, 118 Spool hole, 102 First pressure control valve (spool valve, specific spool valve), 104 Second pressure control valve (spool valve, specific spool valve)

Claims (4)

A plurality of spool valves including a specific spool valve and a pressure control valve, respectively adjusting output pressures to the plurality of friction elements according to the command pressure;
An electromagnetic valve that applies the command pressure common to the specific spool valve and the pressure control valve;
It said pressure control valve, when said command pressure of the solenoid valve is on a predetermined pressure or more, the output pressure of the friction element is linearly increased or decreased in accordance with increase or decrease of the command pressure,
When adjusting the output pressure of the specific spool valve to the release pressure of the friction element, a counter force opposite to the force by the command pressure is applied to the spool of the specific spool valve so that the spool is An automatic transmission control device that is locked by a spool hole.   When adjusting the output pressure of the specific spool valve to the engagement pressure of the friction element, the counter force is reduced compared to when adjusting the output pressure to the release pressure, and the spool of the specific spool valve is set to the command pressure. The automatic transmission control device according to claim 1, wherein the automatic transmission control device is moved to a corresponding position. A manual valve that switches a range of the automatic transmission by adjusting an output pressure, which is an original pressure of the plurality of spool valves, between a first pressure and a second pressure lower than the first pressure;
When adjusting the output pressure of the specific spool valve to the release pressure, the force by the output pressure of the manual valve adjusted to the first pressure is applied to the spool of the specific spool valve as the opposing force,
When adjusting the output pressure of the specific spool valve to the engagement pressure, a force generated by the output pressure of the manual valve adjusted to the second pressure is applied to the spool of the specific spool valve as the opposing force. The automatic transmission control device according to claim 2. The automatic transmission control device according to any one of claims 1 to 3, wherein the specific spool valve includes any one of a switching valve and a pressure control valve.

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