JP3312271B2 - Control device for hydraulically operated transmission for vehicles - Google Patents

Abstract

PROBLEM TO BE SOLVED: To perform upshifting for a short time without generating shock by decreasing releasing pressure to a specified low value at a specified timing after connection preparation completion signal is output. SOLUTION: OFF pressure is feedback-controlled in a subtraction mode such that an input/output speed ratio of a transmission Gratio is a target value YG(N)S, for generating certain sliding in a releasing side hydraulic clutch. ON pressure is controlled in an addition mode under such a state, so that the speed ratio Gratio is sensitively varied according to connection force of the connection side of the hydraulic clutch. Completion timing of the connection preparation of the connection side hydraulic clutch is sensed through increasing of the speed ratio Gratio to a specified value YGCONOK. The OFF pressure is abruptly decreased by switching to a bottom-raising mode after a specified time YTMUP8 passes. A transmission state can be shifted to an inertial phase in an initial time while preventing blow-up of an engine.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a control apparatus for a hydraulically operated transmission for a vehicle having a plurality of shift speeds established by a selection operation of a plurality of hydraulic coupling elements.

[0002]

2. Description of the Related Art Conventionally, as this type of control device, the hydraulic pressure (release pressure) of a release hydraulic connection element and the hydraulic pressure (connection pressure) of a connection hydraulic connection element during gear shifting are electronically controlled using an electromagnetic proportional valve. Control, detecting the input / output speed ratio (output shaft rotation speed / input shaft rotation speed) of the transmission, discriminating the progress of the shift from the input / output speed ratio, and controlling the release pressure and the connection pressure. Known to do so.

In such a control device, in order to prevent the engine from blowing up during an upshift,
A predetermined connection region in which the slippage of the release hydraulic connection element does not occur, that is, the input / output speed ratio of the transmission is set on the basis of the gear ratio of the shift speed established by the connection of the release hydraulic connection element. The coupling pressure is gradually increased while controlling the release pressure so that it falls within the range. It is known that when the speed is increased, the shift state is determined to have shifted from the torque phase to the inertia phase, and the connection pressure is increased to a predetermined high pressure and the release pressure is reduced to a predetermined low pressure.

[0004]

In the above-described conventional upshift control, if the rate of gradually increasing the connection pressure in the torque phase is increased, the connection force of the connection side hydraulic connection element during the transition to the inertia phase becomes excessive, and a shock occurs. The connection pressure is relatively gently increased because it easily occurs, and as a result, it takes time to shift to the inertia phase, and the time required for the upshift becomes longer. In view of the above, an object of the present invention is to provide a control device capable of performing an upshift in a short time without causing a shock.

[0005]

Means for Solving the Problems In order to solve the above problems,
The present invention provides a control device for a hydraulically operated transmission for a vehicle having a plurality of shift speeds established by a selection operation of a plurality of hydraulic connection elements. The input / output speed ratio of the transmission at the time of the upshift is determined based on the gear ratio of the gear position established by the connection of the release-side hydraulic connection element, using the hydraulic pressure of the connection-side hydraulic connection element connected at the time of the upshift as the connection pressure. In such a manner that the input / output speed ratio is maintained at a predetermined ratio lower than a predetermined connection region set in a range in which the input / output speed ratio falls when no slippage of the release-side hydraulic connection element occurs.
Means for controlling the release pressure to decrease, means for gradually increasing the connection pressure, and outputting a connection preparation completion signal when the input / output speed ratio of the transmission falls below the connection region and then rises again to the connection region. It is characterized by comprising a connection preparation determining means, and means for reducing the release pressure to a predetermined low pressure at a predetermined time after the output of the connection preparation completion signal.

According to the present invention, the connection pressure is gradually increased in a state in which the release side hydraulic connection element slightly slips, so that the input / output speed ratio of the transmission is sensitive according to the connection force of the connection side hydraulic clutch. The completion of the connection preparation of the connection-side hydraulic connection element can be detected by the re-rise of the input / output speed ratio to the connection region, and at this time, a connection preparation completion signal is output. Then, at a predetermined time after the output, the release pressure is reduced, and the shift state is shifted to the inertia phase. At this point, the coupling force of the coupling-side hydraulic coupling element has risen to an extent that prevents the engine from blowing up. Thus, the shift state is quickly shifted to the inertia phase while preventing the engine from blowing up. Therefore, the time required for the upshift can be reduced.

[0007] The predetermined time can be set to a point in time when a predetermined time has elapsed from the output of the connection preparation completion signal. However, when the vehicle speed increases, the pressure drop of the release-side hydraulic connection element is delayed due to the effect of the centrifugal force. In this case, if the predetermined time is variably set according to the vehicle speed so as to become shorter with an increase in the vehicle speed, the release pressure decreases at a high vehicle speed, and the release-side hydraulic connection element at a high vehicle speed is increased. The occurrence of a shock due to an increase in co-biting due to a delay in pressure drop is prevented. When the hydraulic pressure detecting means for detecting the connection pressure is provided, the predetermined time may be set at a time when the detected value of the connection pressure exceeds a predetermined value.

It is desirable that the transition to the inertia phase be accelerated by increasing the gradually increasing rate of the coupling pressure after the output of the coupling preparation completion signal. The second from the output of the completion signal
It is desirable to provide means for increasing the connection pressure to a predetermined high pressure after a predetermined time has elapsed. Furthermore, if the second predetermined time is variably set according to the vehicle speed so as to be longer as the vehicle speed increases, it is possible to more effectively prevent the occurrence of a shock due to an increase in co-meshing at a high vehicle speed.

Incidentally, the degree of change in the output torque of the engine due to the throttle opening increases in the low throttle opening region. When the throttle opening decreases to a low opening, the engine torque decreases significantly, and the release side hydraulic coupling element The slip may decrease and the input / output speed ratio of the transmission may again rise to the coupling range even though the coupling hydraulic coupling element has not begun to have coupling force. Therefore, when the throttle opening, that is, the engine load is equal to or less than a predetermined value, the connection preparation completion signal is not output even if the input / output speed ratio rises again to the connection region, and the connection-side hydraulic connection element is not ready for connection. It is desirable to prevent the connection preparation completion signal from being output when it is not completed.

In the embodiment described later, the "means for controlling the release pressure to decrease" corresponds to S10 in FIG.
-5-3, S10-5-4, YG
(N) S is the predetermined ratio. The "means for gradually increasing the connection pressure" corresponds to the step of S18 in FIG. 7, and the step of increasing the connection pressure gradually after the output of the connection preparation completion signal is the step of S18 ". The time is YTMUP8, which is variably set in accordance with the vehicle speed as described above in step S10-12 in Fig. 9. The second predetermined time is YTMUP3, which is determined according to the vehicle speed. The variable setting as described above is performed in S2 of FIG.
This is the sixth step. The connection preparation determining means corresponds to the step of S14 in FIG. 7, that is, S14- in FIG.
1 to S14-9, where FCONOK = 1
Is a connection preparation completion signal, and the step of S14-6 is to prevent the connection preparation completion signal from being output when the engine load is equal to or less than a predetermined value. YG (N) L is the lower limit value of the connection area, YGCONOK is a determination reference value for determining whether the input / output speed ratio Gratio has risen to the connection area, and the input / output speed ratio is determined in step S14-2. It is determined whether or not the input / output speed ratio has fallen below the connection area, and it is determined in step S14-7 whether or not the input / output speed ratio has increased to the connection area. Although YGCONOK may be set to a value equal to YG (N) L, the detected value of the input / output speed ratio may be temporarily changed due to noise or the like in a state where the connection preparation of the connection side hydraulic connection element is not completed. In consideration of the possibility that YGCONN may exceed YG (N) L, YGCONOK is set to a value slightly higher than YG (N) L in the embodiment described later.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring to FIG. 1, reference numeral 1 denotes a hydraulically operated transmission for performing four forward speeds and one reverse speed, and the transmission 1 is connected to an engine via a fluid torque converter 2. The output of the input shaft 3, the intermediate shaft 5 constantly connected to the input shaft 3 via the gear train 4, and the shaft end meshing with the final gear 6 a on the differential gear 6 connected to the driving wheels of the vehicle An output shaft 7 having a gear 7a. Note that the final gear 6a and the output gear 7a are separated from each other in the drawing because the drawing is an exploded view.
7a are in mesh with each other.

Between the intermediate shaft 5 and the output shaft 7, there are first speed and second speed.
Speed transmission systems G1 and G2 are arranged side by side, and the input shaft 3 and the output shaft 7
Between them, transmission systems G3, G4 for the third and fourth speeds and a reverse transmission system GR are arranged in parallel. Then, on the intermediate shaft 5, 1
The first and second speed hydraulic clutches C1 and C2, which are hydraulic connection elements interposed in the first and second speed transmission systems G1 and G2, respectively, and the third and fourth speed transmission systems G3 and G3 are provided on the input shaft 3. G3 is provided with hydraulic clutches C3 and C4 for the third speed and the fourth speed, which are the hydraulic connection elements interposed, respectively.
3 and C4, each corresponding transmission system G1, G
2, G3, and G4 are selectively established.
The reverse transmission system GR is configured to share the fourth-speed transmission system G4 and the fourth-speed hydraulic clutch C4. The gear 8 is shifted by the switching operation of the fourth speed transmission system G4 and the reverse transmission system GR.
The fourth speed transmission system G4 and the reverse transmission system GR are selectively established by meshing with the driven gears G4a and GRa. It should be noted that an idle gear (not shown) is interposed in the reverse drive transmission system GR. In the figure, reference numeral 9 denotes a parking gear provided on the output shaft 7.

The supply and discharge of the hydraulic clutches C1 to C4 are controlled by a hydraulic circuit shown in FIG. The hydraulic circuit comprises a hydraulic source 10 composed of a gear pump driven by the engine through the casing of the fluid torque converter 2.
A manual valve 11 that is switched in conjunction with a select lever in the vehicle compartment, a shift valve unit 12, a switching valve 13 on the upstream side of the shift valve unit 12, and first and second valves connected to the switching valve 13. A pair of pressure regulating valves 14 ₁ , 14 ₂ , a forward / backward switching servo valve 15 connected to a fork 8 a connected to the selector gear 8, and a first control for switching the shift valve unit 12 and the switching valve 13. To the third three solenoid valves 16 ₁ , 16 ₂ , 16 ₃ and the first and second pressure regulating valves 14 ₁ , 1
4 first performing pressure regulation control of the ₂ solenoid proportional valve of the second 1-one
7 ₁ , 17 ₂ . In the figure, A1 to A4 are accumulators provided to buffer a sudden change in hydraulic pressure of each of the hydraulic clutches C1 to C4.

The manual valve 11 has a parking position "P", a reverse position "R", a neutral position "N", and a first to fourth speed automatic shift position "D ₄ ".
When a serving automatic shift position of the first speed through third speed "D _3", the third speeds, a second speed retaining position "2", which is freely switchable to a total of 7 positions of the serving first speed retaining position "1".

At the "D ₄ " position of the manual valve 11, the first oil passage L1 connected to the hydraulic pressure source 10 is connected to the second oil passage L1 connected to the switching valve 13.
The pressure oil, which is connected to the oil passage L2 and adjusted to a constant line pressure by the regulator 18 from the first oil passage L1 to the second oil passage L2, is supplied to the switching valve 13 and the shift valve unit 12 And first to fourth speed hydraulic clutches C1 to C4
, And automatic transmission of the first to fourth speeds is performed. Referring to FIG. 3, the shift valve unit 12, the changeover valve 13, pressure regulating valves 14 _1, 14 ₂ will be described in detail.

The shift valve unit 12, first to third three shift valves 12 _1, 12 _2, 12 ₃ is constituted by a third of the first shift valve 12 ₁ in the switching valve 13 4th 2
Through two oil passages L3 and L4, and the second shift valve 12
_{2 is connected} to the switching valve 13 via the fifth and sixth oil passages L5 and L6. The first and second shift valves 12 ₁ ,
12 ₂ is connected through the seventh to ninth three oil passages L7, L8, L9, and also, the third shift valve 12 _3, the first 10 to the first shift valve 12 ₁ 11 Two oil Road L10, L
Is connected via the 11, it is connected to the second shift valve 12 ₂ via No. 12 oil passage L12.

The first speed hydraulic clutch C1 is connected to a thirteenth oil passage L13.
And the second-speed hydraulic clutch C2 is connected to the first shift valve 12 ₂ via the fourteenth oil passage L14.
₁ and the third speed hydraulic clutch C3 is connected to the fifteenth oil passage L1.
5 is connected to the second shift valve 12 ₂ via a fourth speed hydraulic clutch C4 is No. 16 oil passage L1 leading to the clutch C4
6 of the manual valve 11 the "D _4", "D _3", "2", "1" first shift valve via No. 17 oil passage L17 which is connected in position 1
Connected to 2 ₁ .

The first shift valve 12 _1, while being urged to the right position by a spring 12 ₁ a, is urged to the left position by the hydraulic pressure in No. 18 oil passage L18 which is controlled by the first solenoid valve 16 _1, Second
The shift valve 12 ₂ is pressed to the right by a spring 12 ₂ a and is controlled by a second solenoid valve 16 _2.
9 is pressed to the left position. Third shift valve 12 ₃
Is pressed rightward by the spring 12 ₃ a and pressed leftward by the hydraulic pressure of the 21st oil passage L21 connected to the first oil passage L1 at a position other than “2” and “1” of the manual valve 11. And
At the “D ₄ ” position of the manual valve 11, it is held at the left position by the line pressure input via the 21st oil passage L 21,
No. 10 oil passage L10 and the third shift valve 12 ₃ of the oil discharge port 1
Is connected to the 2 ₃ b, and No. 11 oil passage L11 12
The oil passage L12 is connected.

1 at the position "D ₄ " of the manual valve 11
When fast traveling, the first shift valve 12 ₁ to the left side position, in which switching the second shift valve 12 ₂ in the right position, according to this, No. 13 oil passage L13 for the first speed hydraulic clutch C1 is a 2
Via the shift valve 12 ₂ and the eighth oil passage L8 and the first shift valve 12 ₁ is connected to the second connecting oil channel serving No. 4 oil passage L4 for the switching valve 13. At this time, No. 14 oil passage L14 for the second speed hydraulic clutch C2, the first shift valve 12 ₁ and through the No. 10 oil passage L10, the oil discharge port 12 ₃ of the oil discharge passage serving the third shift valve 12 ₃ b, the third speed hydraulic clutch C3
The fifteenth oil passage L15 for the second shift valve 12 is an oil discharge passage.
It is connected to the _second oil discharge port 12 ₂ b, 4-speed hydraulic clutch C
No. 16 oil passage L16 for 4, a No. 17 oil passage L17 first shift valve 12 ₁ and No. 11 oil passage L11 and the third shift valve 12 ₃ and No. 12 oil passage L12 and the second shift valve 12 ₂ Through the connection, the switching valve 13 is connected to a sixth oil passage L6 which is a fourth connection oil passage.

The time of the second speed running, which switches the first shift valve 12 ₁ while holding the second shift valve 12 ₂ in the right position to the right position, according to this, for the second speed hydraulic clutch C2 No. 14 oil passage L14 is first shift valve 12 ₁ No. 9 oil passage L
9 and via the second shift valve 12 ₂ is connected to the third connecting oil channel serving No. 5 oil passage L5 for the switching valve 13, No. 13 oil passage L13 for the first speed hydraulic clutch C1 and the second
Via the shift valve 12 ₂ and the eighth oil passage L8 and the first shift valve 12 ₁ is connected to No. 3 oil passage L3 serving first connecting oil passage for the changeover valve 13. At this time, No. 15 oil passage L15 for the third speed hydraulic clutch C3 is connected to the second shift valve 12 ₂ of the oil discharge port 12 ₂ b as with the first speed running, first for 4-speed hydraulic clutch C4 16 oil passage L16 is oil discharge passage serving the first shift valve via No. 17 oil passage L17 12 ₁ of the oil discharge port 12 ₁
b.

The time of the third speed running, which switches the second shift valve 12 ₂ while holding the first shift valve 12 ₁ in the right position to the left position, according to this, for the third speed hydraulic clutch C3 No. 15 oil passage L15 and the second shift valve 12 _2, No. 7 oil passage L
7 and is connected to the first shift valve 12 ₁ and No. 4 oil passage L4 via the, No. 14 oil passage L for the second speed hydraulic clutch C2
14 is connected to No. 6 oil passage L6 via the first shift valve 12 _1, No. 9 oil passage L9 and the second shift valve 12 _2. At this time, the thirteenth oil passage L13 for the first-speed hydraulic clutch C1 is
Is connected to the shift valve 12 ₂ of the oil discharge port 12 ₂ b, 4-speed No. 16 oil passage for the hydraulic clutch C4 L16 12 ₁ of the first shift valve via a similarly at the time of the second speed running No. 17 oil passage L17 It is connected to the drain port 12 ₁ b.

[0022] During the fourth speed running, those for switching the second shift valve 12 ₂ of the first shift valve 12 ₁ while holding the left position to the left position, according to this, the four-speed hydraulic clutch C4 The 16th oil passage L16 is connected to the 17th oil passage L17 and the first shift valve 1
2 ₁ and No. 11 oil passage L11 and the third shift valve 12 ₃ and No. 5 oil passage L5 via a No. 12 oil passage L12 and the second shift valve 12 ₂
And the fifteenth gear for the third speed hydraulic clutch C3.
Oil passage L15 and the second shift valve 12 ₂ and the seventh oil passage L7 first
Via the shift valve 12 ₁ is connected to No. 3 oil passage L3.
At this time, first gear 13 oil passage for the hydraulic clutch C1 L13 is the third speed running time as in the second shift valve 12 ₂ the oil discharge port 1
Is connected to the 2 ₂ b, 2-speed No. 14 oil passage L14 for the hydraulic clutch C2 is 1 speed running time as well as of the first shift valve 12 ₁ and No. 10 oil passage L10 and the third shift valve 12 ₃ via the It is connected to the oil drain port 12 ₃ b.

The switching valve 13 includes the second oil passage L2 as a line pressure oil passage, the third to sixth oil passages L3, L4, L5 and L6 as first to fourth connection oil passages, 1 pressure regulating valve 14
Serving first regulated oil passage which pressure is regulated by ₁ No. 22 oil passage L22
When a second regulated oil passage serving No. 23 oil passage L23 which is pressure regulated by the second pressure regulating valve 14 ₂ is connected. The switching valve 13
A right switching position as a first switching position by a constant oil pressure (hereinafter, referred to as a modulator pressure) lower than the line pressure, which is output to a twenty-fourth oil passage L24 downstream of the modulator valve 19 connected to the first oil passage L1. a is pressed, the spring 13a and the third solenoid valve 16 ₃ hydraulically second No. 20 oil passage L20 which is controlled by
Is pressed to the left position which is the switching position.

When the switching valve 13 is at the right position, the third oil passage L3 is connected to the twenty-second oil passage L22, and the fifth oil passage L5 is connected to the twenty-third oil passage L23. And the fifth hydraulic passages L3 and L5 can be regulated by the _first and _second pressure regulating valves 141 and 142, respectively. At this time, the fourth oil passage L
4 is connected to the second oil passage L2, and the sixth oil passage L6 is connected to the oil discharge port 13b of the switching valve 13, which is an oil discharge passage.

When the switching valve 13 is in the left position, the fourth oil passage L4 is connected to the twenty-second oil passage L22, the sixth oil passage L6 is connected to the twenty-third oil passage L23, and the fourth oil passage L6 is connected to the fourth oil passage L23. Sixth
Oil passages L4, L6 by hydraulic pressure of the respective first and second respective pressure regulating valve 14 _1, and 14 ₂ can pressure regulation in. At this time, the third oil passage L3
Is connected to an oil discharge port 13c of the switching valve 13, which is an oil discharge passage, and the fifth oil passage L5 is connected to the second oil passage L2.

The first shift valve 12 ₁ to the left side position, the second shift valve 12 ₂ as the right position when the first speed to connect the first speed hydraulic clutch C1 to the fourth oil passage L4 is the changeover valve 13 is right The fourth oil passage L4 is connected to the second oil passage L2 while being switched and held at the first position. Thus, the hydraulic pressure of the first-speed hydraulic clutch C1 (hereinafter referred to as first-speed pressure) becomes the line pressure, and the clutch C1
, The first speed transmission system G1 is established.

With the first and second shift valves 12 ₁ and 12 ₂ at the right position, the first-speed hydraulic clutch C1 is connected to the third oil passage L3,
2 to connect the second speed hydraulic clutch C2 to the fifth oil passage L5
At the time of speed, the switching valve 13 is switched to the left position,
The oil passage L3 is connected to the oil drain port 13c,
The second oil passage L2 is connected to the oil passage L5. Thus, the first speed pressure drops to the atmospheric pressure and the connection of the first speed hydraulic clutch C1 is released, while the hydraulic pressure of the second speed hydraulic clutch C2 (hereinafter referred to as the second speed pressure) becomes the line pressure, and the clutch C2 , The second speed transmission system G2 is established.

In upshifting from the first speed to the second speed, first, both the first and second shift valves 12 ₁ , 12 ₁ are maintained while the switching valve 13 is held at the position for the first speed, that is, the right position. _Two
Is switched to the state of the second speed. In this case, the third and fifth oil passages L3, L5 connected to the first and second speed hydraulic clutches C1, C2 are connected to the 22nd and 23rd oil passages L22, L23, respectively. Therefore, it becomes possible to control the pressure drop characteristics of the first pressure regulating valve 14 ₁ by one speed pressure by the second pressure regulating valve 14 ₂ 2
It is possible to control the boost characteristic of the speed, and to perform a smooth upshift from the first speed to the second speed. Then, the switching valve 13 after the shift completion switched to the left position, the oil is discharged without passing through the first speed hydraulic clutch C1 through the first pressure regulating valve 14 _1, the second speed hydraulic clutch C2 through the second pressure regulating valve 14 ₂ Supply pressure oil at line pressure.

At the time of the downshift from the second speed to the first speed, first, the switching valve 13 is set to the second speed while keeping both the first and second shift valves 12 ₁ and 12 ₂ in the state of the second speed. The position is shifted from the position to the position at the first speed, that is, from the left position to the right position. According to this, similarly to the case of the upshift from the first speed to the second speed, the first and second speed hydraulic clutches C1 and C2
And the twenty-third oil passages L22 and L23. Therefore, it becomes possible to control the pressure rise characteristics of the first pressure regulating valve 14 ₁ by one speed pressure by the second pressure regulating valve 14 ₂ can control the pressure drop characteristics of the second speed pressure, smooth down from the second speed to the first speed A shift is obtained. After the shift is completed, the first and second gears
The two shift valves 12 ₁ and 12 ₂ are switched to the state of the first speed, and
The high speed hydraulic clutch C2 is connected to the oil discharge port 12 ₃ b of the third shift valve 12 ₃ , and the second pressure regulating valve 1
4 oil is discharged without passing through the _2, first speed hydraulic clutch C1
Supplied with the pressurized oil at the line pressure without passing through the first pressure regulating valve 14 ₁ like at the time of the first speed to.

The first shift valve 12 ₁ is moved to the right position, the second shift valve 12 ₂ as the left position, the second speed hydraulic clutch C2 to No. 6 oil passage L6,3 speed hydraulic clutch C3 to the fourth oil passage L4 At the time of the third speed, respectively, the switching valve 13 is switched to the right position, and the sixth oil passage L6 is connected to the oil discharge port 13b and the fourth oil passage L4 is connected at the same time as in the first speed. Second oil passage L
2 is connected. Thus, the second speed pressure drops to atmospheric pressure and
The connection of the high-speed hydraulic clutch C2 is released, while the hydraulic pressure of the third-speed hydraulic clutch C3 (hereinafter, referred to as the third-speed pressure) becomes the line pressure, and the connection of the clutch C3 establishes the third-speed transmission system G3.

In upshifting from the second speed to the third speed, first, both the first and second shift valves 12 ₁ , 12 ₁ are held while the switching valve 13 is held at the position for the second speed, ie, the left position. _Two
Is switched to the state of the third speed. In this case, the fourth and sixth oil passages L4 and L6 respectively connected to the third and second speed hydraulic clutches C3 and C2 are connected to the 22nd and 23rd oil passages L22 and L23. Therefore, it becomes possible to control the pressure rise characteristics of the first pressure regulating valve 14 ₁ by 3 speed pressure by the second pressure regulating valve 14 ₂ 2
The step-down characteristic of the high speed can be controlled, and a smooth upshift from the second speed to the third speed can be performed. Then, switching to the right position the switching valve 13 after the shift completion, the second speed hydraulic clutch C2 oil is discharged without passing through the second pressure regulating valve 14 _2, passing through the first pressure regulating valve 14 ₁ in the third speed hydraulic clutch C3 Supply pressure oil at line pressure.

When downshifting from the third speed to the second speed, first, the switching valve 13 is set to the third speed while the first and second shift valves 12 ₁ and 12 ₂ are maintained at the third speed. The position is switched from the position to the position at the second speed, that is, from the right position to the left position. According to this, similarly to the upshift from the second speed to the third speed, the third and second speed hydraulic clutches C3 and C2
And the twenty-third oil passages L22 and L23. Therefore, it becomes possible to control the pressure drop characteristics of the first pressure regulating valve 14 ₁ by 3 speed pressure by the second pressure regulating valve 14 ₂ can control the pressure rise characteristics of the second speed pressure, smooth down from the third speed to the second speed A shift is obtained. After the shift is completed, the first and second gears
The two shift valves 12 ₁ and 12 ₂ are switched to the state of the second speed,
The high-speed hydraulic clutch C3 is connected to the oil discharge port 12 ₂ b of the second shift valve 12 ₂ , and the first pressure regulating valve 1
41 Drain oil without going through ₁ and the 2nd speed hydraulic clutch C2
Supplied with the pressurized oil at the line pressure without passing through the second pressure regulating valve 14 ₂ in the same manner as in the second speed to.

With the first and second shift valves 12 ₁ and 12 ₂ at the left position, the third-speed hydraulic clutch C3 is connected to the third oil passage L3,
The fourth speed hydraulic clutch C4 is connected to the fifth oil passage L5.
At the time of speed, the switching valve 13 is switched to the left position and, as in the case of the second speed, the third oil passage L3 is connected to the oil discharge port 13c and the second oil passage L5 is connected to the fifth oil passage L5. L2 is connected. Thus, the third-speed hydraulic pressure drops to the atmospheric pressure and the connection of the third-speed hydraulic clutch C3 is released, while the fourth-speed hydraulic clutch C4 is released.
(Hereinafter referred to as the fourth speed pressure) becomes the line pressure, and the connection of the clutch C4 establishes the fourth speed transmission system G4.

In upshifting from the third speed to the fourth speed, first, the first and second shift valves 12 ₁ , 12 ₁ are maintained while the switching valve 13 is held at the third speed position, that is, the right position. _Two
Is switched to the state of the fourth speed. In this case, the third and fifth oil passages L3, L5 connected to the third and fourth speed hydraulic clutches C3, C4 are connected to the 22nd and 23rd oil passages L22, L23, respectively. Therefore, it becomes possible to control the pressure drop of the first pressure regulating valve 14 ₁ by 3 speed pressure by the second pressure regulating valve 14 ₂ and to control the pressure rise of 4 speed pressure, a smooth upshifting from the third speed to the fourth speed Can be obtained. Then, the switching valve 13 after the shift completion switched to the left position, the oil is discharged from the third speed hydraulic clutch C3 without passing through the first pressure regulating valve 14 _1, the fourth speed hydraulic clutch C4 passing through the second pressure regulating valve 14 ₂ Supply pressure oil at line pressure.

When downshifting from fourth speed to third speed, first, the switching valve 13 is set to the fourth speed while the first and second shift valves 12 ₁ and 12 ₂ are maintained at the fourth speed. The position is changed from the position to the position at the third speed, that is, from the left position to the right position. According to this, similarly to the upshift from the third speed to the fourth speed, the third and fourth speed hydraulic clutches C3 and C4
And the twenty-third oil passages L22 and L23. Therefore, it becomes possible to control the pressure rise characteristics of the first pressure regulating valve 14 ₁ by 3 speed pressure by the second pressure regulating valve 14 ₂ can control the pressure drop characteristics of the fourth speed pressure, smooth down from 4th speed to 3rd speed A shift is obtained. After the shift is completed, the first and second gears
Switch both the shift valves 12 ₁ and 12 ₂ to the state at the third speed.
The speed hydraulic clutch C4 is connected to the first shift valve 12 ₁ of the oil discharge port 12 ₁ b, oil is discharged without passing through the four-speed hydraulic clutch C4 second pressure regulating valve 14 _2, the third speed hydraulic clutch C3 supplied with the pressurized oil at the line pressure without passing through the first pressure regulating valve 14 _1.

The first and second pressure regulating valves 14 ₁ and 14 ₂ are connected to the respective springs 14 ₁ a and 14 ₂ a and the 22nd and 23rd oil passages L2.
2, L23 by the hydraulic pressure of the press to the oil discharge side of the rightward to connect the respective oil passages L22, L23, each oil discharge port 14 ₁ b, 14 ₂ b, also first and second respective solenoid proportional Valve 17 ₁ ,
17 ₂ on the output side of the first 25 and second 26 oil passages of L25, L2
And the second and third oil passages L22, L2
3 is pressed to the left oil supply side connecting the second oil passage L2,
Thus, the hydraulic pressure of each of the 22nd and 23rd oil passages L22 and L23 is increased or decreased in proportion to the output pressure of each of the electromagnetic proportional valves 17 ₁ and 17 ₂ . By the way, in order to reduce the shift shock, delicate hydraulic control in a transition region of connection between the disengagement side hydraulic clutch and the connection side hydraulic clutch is required. Since this embodiment, supplied to and discharged from the oil without passing through after shifting to the coupling hydraulic clutch tone side and release-side valve 14 _1, 14 _2, pressure regulating valve 1
4 _1, 14 ₂ is relatively well be shared only hydraulic control in the low pressure connection transition region of increasing the resolution of the hydraulic pressure control, pressure drop characteristics of the step-up characteristics and the release-side hydraulic clutch of the hydraulic clutch on the engaging side at the time of shifting Delicate control in the connection transition region can be performed with high accuracy.

A modulator pressure is input to the first and second solenoid proportional valves 17 ₁ and 17 ₂ via a twenty-fourth oil passage L24. Here, the first solenoid proportional valve 17 ₁ is not energized. sometimes used as the output pressure becomes maximum (modulator pressure), the second solenoid proportional valve 17 ₂ is used as the output pressure at the time of non-energization becomes minimum (atmospheric pressure).

The first solenoid valve 16 ₁ is connected to the twenty-fourth oil passage L
The eighteenth oil passage L1 connected to the pump 24 via a throttle 16 ₁ a
8 is opened to the atmosphere, and is closed when not energized to increase the oil pressure in the eighteenth oil passage L18 to a high pressure (modulator pressure).
To

Each of the second and third solenoid valves 16 ₂ and 16 ₃ is connected to an oil supply position for connecting the nineteenth and twentieth oil passages L19 and L20 on the output side thereof to the twenty-fourth oil passage L24, and the connection thereof. And the respective oil passages L19, L20 are connected to the respective oil discharge ports 16 ₂ a, 1
6 ₃ consists of oil discharge position and the switching freely three-way valve to connect to a, is switched to the oil supply position by first 19 and a high pressure second 20 oil passages L19, L20 oil pressure of the (modulator pressure) To

[0040] Incidentally, it is conceivable to constitute the second and third solenoid valves 16 _2, 16 ₃ of the first solenoid valve 16 ₁ and the same two-way valve. However, the two-way valve has a large leak amount when the valve is opened, and a residual pressure is generated even when the valve is opened at a low temperature, so that control responsiveness is deteriorated. Here, at the time of slowing down or stopping at the 1st speed where the engine speed decreases, the amount of oil discharged from the hydraulic pressure source 10 decreases, so that it is necessary to reduce the leak amount. Then, when the first speed, the first 19 to the second shift valve 12 ₂ and the changeover valve 13 in the right position the 20 oil passages L19, L20
Must be set to atmospheric pressure, and the second and third solenoid valves 1
6 _2, 16 ₃ the amount of leakage than is constituted by two-way valve becomes excessive. With this in mind, also consider making the switching control of a good response it is necessary to switch the changeover valve 13 in the third solenoid valve 16 _3, in this embodiment, the second,
The third solenoid valve 16 _2, 16 ₃ constitute three-way valve, constitute only the first solenoid valve 16 ₁ in consideration of the space in the two-way valve compact.

The first to third solenoid valves 16 at the first to fourth speeds and each shift at the "D ₄ " position of the manual valve 11
_1, 16 _2, 16 and ₃ energized state, first, the second shift valve 1
2 ₁ , 12 ₂ and the position of the switching valve 13 and the output pressures of the first and second pressure regulating valves 14 ₁ , 14 ₂ (the 22nd and 23rd oil passages L22, L22
23) is as shown in the table below.

[0042] (○ ... energized, × ... deenergized) In the present embodiment, functions as the first and the oil supply pressure regulating valve for boosting the hydraulic pressure of the hydraulic clutch on the engaging side upon previous shift of the second of the two pressure regulating valves 14 _1, 14 ₂ Those that functioned as oil discharge pressure regulators that reduce the hydraulic pressure of the disengagement side hydraulic clutch during the next shift, and those that functioned as oil discharge pressure regulators during the previous shift as oil supply pressure regulators during the next shift to function, it is possible to prepare for the next shift to hold the output pressure of the post-shift each of the pressure regulating valves 14 _1, 14 ₂ to the exact value. On the other hand, if one of the first and second pressure regulating valves 14 ₁ and 14 ₂ is dedicated to refueling and the other is dedicated to draining, the output pressure of the refueling pressure regulating valve, which has been increased during gear shifting, is reduced and the gear shifting is performed during gear shifting. It is necessary to increase the output pressure of the reduced oil discharge pressure regulating valve to prepare for the next shift. In this case, if the next shift is performed in a short time at a low temperature, the shift is started before the output pressure of the oil supply pressure regulating valve or the output pressure of the oil discharge pressure adjustment valve is sufficiently increased. Of the hydraulic control of the vehicle, and shift shock is likely to occur. Therefore, as in the present embodiment, it is desirable to selectively use alternately for oil supplying and for oil discharging each pressure regulating valve 14 _1, 14 ₂ each time shift.

The first to third solenoid valves 16 ₁ , 16 ₂ , 16 ₃
When the first and second solenoid proportional valves 17 _1, 17 _2, together with the fourth solenoid valve 16 ₄ for a lockup clutch which is described later,
It is controlled by an electronic control circuit 20 composed of a microcomputer shown in FIG.

The electronic control circuit (ECU) 20 has a signal from an engine sensor 21 for detecting the engine speed Ne, the throttle opening θ and the coolant temperature TW, and a signal from a vehicle speed sensor 22 for detecting the vehicle speed V. A signal from a speed sensor 23 for detecting the rotation speed Nin of the input shaft 3 of the transmission, a signal from a speed sensor 24 for detecting the rotation speed Nout of the output shaft 7 of the transmission, and a position sensor 25 of the select lever. And the signal from.

At the "D ₄ " position, a gear position suitable for the current throttle opening .theta. To 4th speed automatic shifting.

At the “D ₃ ” position, the same oil passage configuration as that at the “D ₄ ” position is obtained.
The first to third speed automatic shifts are performed based on the third speed shift map.

At the "2" and "1" positions, a stepwise downshift to the second speed or the first speed is performed based on the second speed map or the first speed map stored in the ECU 20. Is held. In addition, at the “2” and “1” positions,
No. 21 oil passage L21 is opened to the atmosphere, the third shift valve 12 ₃ can thus become switchable to the right position that was connected to the "D _4", "D _3" first oil passage L1 at a position.

[0048] When the third shift valve 12 ₃ is switched to the right position, No. 10 oil passage L10 that was connected to the oil discharge port 12 ₃ b at the left position is connected to No. 12 oil passage L12, the left No. 11 oil passage L11 that was connected to No. 12 oil passage L12 is connected to No. 2 oil discharge port 12 ₃ c of the third shift valve 12 ₃ in position. Tenth and eleventh oil passages L
10, 11 not connected with the oil passage for any hydraulic clutch in the right position of the first shift valve 12 _1, when the first shift valve 12 ₁ in the right position, the "D _4" position a first shift valve 12 ₁ the oil circuit arrangement will become the same when the right position in, therefore, both the first and the second shift valves 1
2 ₁ , 12 ₂ at the right position ("D ₄ " position at 2nd speed)
To the second speed transmission train G2 is speed hydraulic clutch C2 is established when the first shift valve 12 ₁ is moved to the right position,
When the second shift valve 12 ₂ in the left position (the "D _4" condition of the third speed position), third speed transmission train G3 is established oil is supplied to the third speed hydraulic clutch C3.

Meanwhile, when the first shift valve 12 ₁ to the left position, No. 14 oil passage L14 for the second speed hydraulic clutch C2
Are the tenth oil passage L10 and the seventeenth oil passage for the four-speed hydraulic clutch C4.
Since the oil passages L17 are respectively connected to the eleventh oil passage L11,
This is different from the oil passage configuration at the “D ₄ ” position. Then, the first shift valve 12 ₁ to the left side position, when the second shift valve 12 ₂ is moved to the right position (the "D _4" state of the first speed position), for the first speed hydraulic clutch C1 13 Oil passage L1
3 is connected to the fourth oil passage L4 (this connection is "D
₄ "same position), the second speed hydraulic clutch No. 14 oil passage L14 for the C2 is connected to No. 6 oil passage L6 (the" D ₄ "No. 17 oil passage for the fourth speed hydraulic clutch C4 in the position L17 sixth Connected to the oil passage), the first and second shift valves 12 ₁ , 12 ₂
To the left position (the state at the fourth speed at the “D ₄ ” position), the fifteenth oil passage L15 for the third speed hydraulic clutch C3 is in the third position.
It is connected to the oil passage L3 (this connection is the same as the "D _4" position), for the second speed hydraulic clutch C2 No. 14 oil passage L14
Is connected to the fifth oil passage L5 (at the “D ₄ ” position, the seventeenth oil passage L17 for the fourth-speed hydraulic clutch C4 is connected to the fifth oil passage L5), and no oil is supplied to the fourth-speed hydraulic clutch C4 .

[0050] Here, the third shift valve 12 ₃ is adapted to be urged to the left by the output pressure of the second solenoid proportional valve 17 ₂ to be inputted via No. 26 oil passage L26, a blown fuse The first to third solenoid valves 16 when the system goes down due to
_1, 16 _2, 16 ₃ and the first and second solenoid proportional valves 17 _1, 17
₂ is stopped, the first and second shift valves 1 and 2 are turned off.
With a 2 _1, 12 ₂ and the changeover valve 13 is switched to the left position, the output pressure of the second solenoid proportional valve 17 ₂ becomes the atmospheric pressure, the third shift valve 12 ₃ is "2", "1" position It is switched to the right position in, the "D _4", "D _3" second at position
The position is switched to the left position by the line pressure from one oil passage L21. Therefore, at the “1” and “2” positions, the second speed transmission system G
2, the "D _4", "D _3" fourth speed transmission train G4 is established, respectively position, and the second speed even during system down 4
Running at high speed can be obtained.

At the "R" position of the manual valve 11, the second oil passage L2 is opened to the atmosphere, and the first oil passage L1 is connected to the 27th oil passage L.
27, and the first servo control valve 27 is connected to the oil passage L27.
The oil is supplied to the first oil chamber 15a at the left end of the servo valve 15 via a twenty-eighth oil passage L28 connected through the oil passage. According to this, the servo valve 15 is pushed to the right reverse position, the selector gear 8 is switched to the reverse side, and the twenty-eighth oil passage L28
Shaft hole 15b of the servo valve 15 communicating with the first oil chamber 15a
Is connected to the twenty-ninth oil passage L29. The oil passage L29
Is connected to a sixteenth oil passage L16 connected to the fourth-speed hydraulic clutch C4 at the "R" position of the manual valve 11,
Thus, the reverse transmission system GR is established by refueling the fourth speed hydraulic clutch C4 and switching the selector gear 8 to the reverse side.

The first servo control valve 27 is connected to the third solenoid valve 16
By the _third output side of the No. 20 oil passage L20 hydraulics and a second 25 hydraulic pressure in the oil passage L25 of the first solenoid proportional valve 17 ₁ of the output side, the left to connect with No. 27 oil passage L27 and No. 28 oil passage L28 And the spring 27a and the second oil passage L2
And the oil pressure of the twenty-ninth oil passage L29, the connection between the twenty-seventh oil passage L27 and the twenty-eighth oil passage L28 is cut off, and the twenty-eighth oil passage L28 is pressed to the right closing side to be connected to the oil discharge port 27b. Is done. In the “D ₄ ”, “D ₃ ”, “2” and “1” positions, the second
The line pressure is input via the oil passage L2, the first servo control valve 27 the third solenoid valve 16 ₃ and the first solenoid proportional valve 17 ₁
Even if both the output pressures are increased, the oil pressure is held at the right position, the oil supply to the 28th oil passage L28 is prevented, the servo valve 15 is held at the left forward position by the locking member 15c, and the reverse transmission is performed. The establishment of the system GR is prevented.

When the manual valve 11 is switched to the "R" position during forward running at a predetermined vehicle speed or higher, the third solenoid valve 1
6 ₃ and the output pressure of the first electromagnetic proportional valve 17 ₁ are both set to the atmospheric pressure, and the first servo control valve 27 is held at the right position.
Oil supply to the oil passage L28, that is, establishment of the reverse drive transmission system GR is prevented.

[0054] When the manual valve 11 is switched to a predetermined speed below the "R" position, the first servo control valve 27 to the leftward open side in increased gradually the first output pressure of the solenoid proportional valve 17 ₁ As described above, the 28th oil passage L28, the servo valve 15 and the second
Lubricate the fourth speed hydraulic clutch C4 via the 9 oil passage L29, to function the control valve 27 as a pressure regulating valve to thereby control the boosting of the hydraulic pressure in the fourth speed hydraulic clutch C4, from then on the third solenoid valve 16 ₃ By outputting the modulator pressure, the control valve 27 is pushed to the left position, and the hydraulic pressure of the fourth-speed hydraulic clutch C4 is maintained at the line pressure. Even if the output pressure third solenoid valve 16 ₃ is turned on failure remains at atmospheric pressure, the hydraulic pressure required for connecting the fourth speed hydraulic clutch C4 with the first output pressure of the solenoid proportional valve 17 ₁ Guaranteed Is done.

The manual valve 11 is moved from the "R" position to "D ₄ ".
"D _3", "2", "1" when switching the position, No. 30 oil passage L30 from the second servo control valve 28 connected to the first oil passage L1 similarly to the second oil passage L2 at these locations The line pressure is input to the second oil chamber 15d in the middle of the servo valve 15 through the and the 31st oil passage L31, and the servo valve 15 moves to the left to switch to the forward position.

The second servo control valve 28 is connected to the thirteenth oil passage L1.
And 1 speed pressure to 3 via the input, the output pressure of the second solenoid valve 16 ₂ to be inputted via No. 19 oil passage L19, the second pressure regulating valve 14 to be inputted via No. 23 oil passage L23 Due to the output pressure of ₂ , the spring 28a and the 27th oil passage L
27, the 30th and 31st oil passages L30, L30,
The connection of L31 is cut off and the 31st oil passage L31 is connected to the drain port 2
8b.

Thus, at the "R" position, the second servo control valve 28 is reliably switched to the right position by the line pressure from the 27th oil passage L27, and the "D ₄ ", "D ₃ ", "2", "1" The control valve 28 is held at the right position until the 1st speed pressure rises to a predetermined value after the switching to the "" position, input of line pressure to the second oil chamber 15d is blocked, and the servo valve 15 is engaged. It is held at the reverse position by the stopper 15c. Then, when the first speed pressure becomes equal to or higher than a predetermined value, the second servo control valve 28 is switched to the left position, the line pressure is input to the second oil chamber 15d, and the servo valve 15 is switched to the forward position. Therefore, even if the manual valve 11 is switched from the “R” position to the “D ₄ ”, “D ₃ ”, “2”, or “1” position with the accelerator pedal depressed,
At the time of switching of the servo valve 15, the rotation of the output shaft 7 in the reverse direction is stopped by the torque transmission in the normal direction via the first speed transmission system G1 due to the increase in the first speed pressure. The driven gear G4a of the four-speed transmission system G4 smoothly meshes with each other without causing a large relative rotation.
Wear of the meshing portion 4a is prevented.

By the way, even if the second servo control valve 28 is locked at the right position due to foreign matter biting in, or the control valve 28 is switched to the left position, the servo valve 15 is locked at the reverse position. When causing abnormal as or, the "D _4" the manual valve 11 from the "R" position "D _3", "2", "1"
Even when the selector gear 8 is switched to the position, the selector gear 8 remains on the reverse side, and when the fourth speed hydraulic clutch C4 is refueled, the reverse transmission system GR is established. Therefore, in this embodiment, provided with a No. 32 oil passage L32 which is in communication with the left end oil chamber of the third shift valve 12 _3, the reverse position of the servo valve 15 to the second oil chamber 15d of the valve 15 a notched groove 15e 33rd connected via
An oil passage L33 is provided so that the 32nd oil passage L32 is connected to the 30th oil passage L30 at the right position of the second servo control valve 28 and to the 33rd oil passage L33 at the left position of the control valve 28, respectively. ing. According to this, the the abnormality occurs, left line pressure through No. 32 oil passage L32 to the oil chamber of the third shift valve 12 ₃ is input, a third pressing the shift valve 12 ₃ is this leftward Regardless of the oil pressure in the 21st oil passage L21 or the 26th oil passage L26, the position is switched to the right position, and oil supply to the fourth-speed hydraulic clutch C4 is prevented.

Once the second servo control valve 28 is switched to the left position, the 30th oil passage L30 and the 31st oil passage L31
Is held at the left position by the self-locking force generated by the pressure receiving area difference between the left and right lands of the annular groove 28c connecting the oil pressure groove 28c.
For example, when the hydraulic pressure is temporarily stopped, the second servo control valve 28 is switched to the right position by the force of the spring 28a. In this case, if the second servo control valve 28 is configured to be pressed to the left position only by the first speed pressure, the second servo control valve 28 will be left Cannot return to position. Therefore, in this embodiment, the second pressure regulating valve 14 ₂ of the output pressure to be higher during the second speed and at the time of the fourth speed, 3
By a fast time and increases in the fourth speed second solenoid valve 16 ₂ of the output pressure presses the second servo control valve 28 to the left position. Incidentally, 1 time speed through the third speed, the second servo control valve 28 does not return to the left position, No. 32 oil passage third shift valve 12 ₃ at the input of the line pressure from the L32 is switched to the right position This does not affect the oil supply / discharge of each of the hydraulic clutches C1 to C4. However, at the time of the fourth speed, the oil is supplied to the second speed hydraulic clutch C2 and the downshift is performed from the fourth speed to the second speed. Therefore, when the fourth speed, the second pressure regulating valve 14 ₂ of the output pressure and the second servo control valve 28 and the second solenoid valve 16 ₂ of the output pressure is urged to the left, normal one output pressure after the hydraulic recovery Even if the value does not increase, the second servo control valve 28 is reliably switched to the left position.

At the "N" position of the manual valve 11, the second oil passage L2, the sixteenth oil passage L16, the seventeenth oil passage L17,
The oil passage L27, the twenty-ninth oil passage L29, and the thirtieth oil passage L30 are all opened to the atmosphere, and all the hydraulic clutches C1 to C4 are disconnected. Further, at the “P” position, the 27th oil passage L27 is connected to the first oil passage L1, and the servo valve 15 moves backward by inputting the line pressure via the first servo control valve 27 and the 28th oil passage L28. Position, but in the "P" position, the 16th
When the connection between the oil passage L16 and the 29th oil passage L29 is disconnected, the first
Since the six oil passages L16 are opened to the atmosphere, the reverse transmission system GR is not established.

The fluid torque converter 2 incorporates a lock-up clutch 2a, and controls the operation of the lock-up clutch 2a in a hydraulic circuit using oil supplied from the regulator 18 via the 34th oil passage L34 as operating oil. A lock-up control unit 29 is provided.

The control unit 29 includes a lock-up clutch 2
a switch valve 30 for controlling the on / off control of the lock-up clutch 2a, a switching valve 31 for switching the connection state when the lock-up clutch 2a is on to a lock-up state where no slip occurs and a slip state, and a control for increasing / decreasing the connection force in the slip state. And a pressure valve 32.

The shift valve 30 is connected to a thirty-fifth oil passage L3 connecting the thirty-fourth oil passage L34 to the back pressure chamber of the lock-up clutch 2a.
5 and a thirty-sixth oil passage L3 connected to an internal space of the fluid torque converter 2 and a thirty-seventh oil passage L3
7 through the throttle 30a, and
The oil passage L34 is connected to the thirty-eighth oil passage L38 connected to the switching valve 31, and the thirty-sixth oil passage L3 is connected via the throttle part 30a.
Connect to 6, further it is freely switched to the left position to be connected to No. 39 oil passage L39 continuing the No. 35 oil passage L35 to the pressure regulating valve 32 is switching control by the fourth solenoid valve 16 _4. The fourth solenoid valve 16 ₄ is connected to the second side of the output side of the modulator valve 19.
The fortieth oil passage connected to the fourth oil passage L24 via the throttle 16 ₄ a.
It is configured by a two-way valve that opens the oil passage L40 to the atmosphere.
Then, the shift valve 30 is pressed to the left position by the hydraulic pressure of the twenty-fourth oil passage L24, that is, the modulator pressure,
And urged to the right position by a spring 30b and the hydraulic pressure in No. 40 oil passage L40, No. 40 oil passage L4 and closing the fourth solenoid valve 16 ₄
When the hydraulic pressure of 0 is increased to the modulator pressure, the shift valve 30
There is switched to the right position, the fourth shift valve 30 when the hydraulic pressure in No. 40 oil passage L40 to open the solenoid valve 16 ₄ is lowered to the atmospheric pressure is to be switched to the left position.

The switching valve 31 has a right position connecting the 41st oil passage L41 connected to the internal space of the fluid torque converter 2 to a 42nd oil passage L42 connected to the oil chamber at the left end of the pressure regulating valve 32, and a 42nd oil passage. L42 is opened to the atmosphere, and the thirty-eighth oil passage L38 can be freely switched to a left position connecting to the thirty-sixth oil passage L36. The oil pressure of the 43rd oil passage L43 is pressed to the left.

The pressure regulating valve 32 connects the thirty-ninth oil passage L39 to the thirty-fourth oil passage L39.
The oil passage L34 is connected to the oil passage L34, the right position where the oil passage L41 is connected to the oil passage L37 via the throttle 32a, and the connection between the oil passage L39 and the oil passage L34 is cut off. The 39th oil passage L39 is connected to the oil discharge port 32b with a throttle, and the 41st oil passage L41 and the 37th oil passage L37 are connected.
Between the left side and the left side where the connection with the hydraulic circuit is disconnected, and is pressed rightward by the spring 32c and the hydraulic pressure of the 42nd hydraulic path L42, and the hydraulic pressure of the 39th hydraulic path L39 and the hydraulic pressure of the 43rd hydraulic path L43. Is pressed to the left. Here, the 39th oil passage L39
Both the pressure receiving area for the hydraulic pressure and the pressure receiving area for the hydraulic pressure of the 42nd hydraulic path L42 are s1, the pressure receiving area for the hydraulic pressure of the 43rd hydraulic path L43 is s2, and the 39th hydraulic path L39, the 42nd hydraulic path L42, and the 43rd hydraulic path. The hydraulic pressure with L43 is Pa, Pb,
Assuming that the urging force of the Pc and the spring 32c is F, s1 · Pb + F = s1 · Pa + s2 · Pc Pb−Pa = (s2 · Pc−F) / s1. Is increased or decreased according to the oil pressure of the 43rd oil passage L43.

[0066] No. 43 oil passage L43 is No. 25 oil passage of the first solenoid proportional valve 17 ₁ of the output side right position of the changeover valve 13 L25
Is connected to the second electromagnetic proportional valve 1 at the left position of the switching valve 13.
7 ₂ on the output side is connected to No. 26 oil passage L26. Thus, the first and third speeds when the switching valve 13 is in the right position are the first speeds.
At the 2nd speed and 4th speed when the electromagnetic proportional valve 17 ₁ and the switching valve 13 are in the left position, the second electromagnetic proportional valve 17 ₂ switches the switching valve 31 respectively.
And the pressure regulating valve 32 is controlled.

When the shift valve 30 is at the right position,
The operating oil from the 34th oil passage L34 is
Oil is supplied to the back pressure chamber of the lock-up clutch 2a via the oil passage L35, and the internal space of the fluid torque converter 2 is formed via the 41st oil passage L41 and the pressure regulating valve 32, and the 36th oil passage. L36 and the throttle portion 30a of the shift valve 30 are connected to the thirty-seventh oil passage L37, respectively, and the internal pressure of the inner space is reduced by oil drainage from the inner space through the thirty-seventh oil passage L37, so that the lock-up clutch 2a is in an off state, that is, a disconnection state.

When the shift valve 30 is switched to the left position, the back pressure chamber of the lock-up clutch 2a is connected to the thirty-ninth oil passage L39 via the thirty-fifth oil passage L35 and the shift valve 30.
While the switching valve 31 is in the right position, the internal gap of the fluid torque converter 2 is connected to the thirty-fourth oil passage L34 via the thirty-sixth oil passage L36 and the throttle part 30a of the shift valve 30. A 43rd oil passage L43 which is connected to the 42nd oil passage L42 via the 41st oil passage L41 and the switching valve 31 and which inputs the differential pressure between the internal pressure of the internal gap and the internal pressure of the back pressure chamber to the pressure regulating valve 32. Increase / decrease control can be performed by hydraulic pressure. Thus, the lock-up clutch 2a is connected, in a slipping condition, with an engaging force in response to the _second output pressure first solenoid proportional valve 17 ₁ or the second solenoid proportional valve 17.

When the oil pressure in the 43rd oil passage L43 becomes a predetermined value or more and the switching valve 31 is switched to the left position, the 42nd oil passage L42 is opened to the atmosphere, and the pressure regulating valve 32 is switched and held in the left position. The back pressure chamber of the lock-up clutch 2a is 35th
The oil passage L35, the shift valve 30, and the thirty-ninth oil passage L39 remain connected to the oil discharge port 32b of the pressure regulating valve 32, while the shift valve 30 and the thirty-eighth oil passage are connected through the thirty-fourth oil passage L34.
Oil is supplied to the internal space of the fluid torque converter 2 via the oil passage L38, the switching valve 31, and the thirty-sixth oil passage L36.
Since the connection between the 41st oil passage L41 and the 37th oil passage L37 is disconnected by switching the pressure regulating valve 32 to the left position, the internal pressure of the internal space is set by the check valve 33 connected to the 41st oil passage L41. Is maintained at a relatively high pressure, and the lock-up clutch 2a is engaged in a lock-up state.

In the figure, reference numeral 34 denotes an oil cooler provided in the 37th oil passage L37, 35 denotes a check valve for the oil cooler, 36
Is a regulator 18 on the lubrication part of each shaft 3, 5 and 7 of the transmission.
This is a throttle member interposed in a lubricating oil passage LB for supplying leak oil from the cylinder.

Next, control of the first and second electromagnetic proportional valves 17 ₁ and 17 ₂ during shifting will be described. In the following description, the output pressure of an electromagnetic proportional valve that controls the hydraulic pressure of a coupling hydraulic clutch that is connected during gear shifting is set to ON pressure, and the output of an electromagnetic proportional valve that controls the hydraulic pressure of a release hydraulic clutch that is released during gear shifting. The pressure is set to the OFF pressure. The shift control is mainly composed of upshift control, downshift control, and in-gear control at the beginning of switching from the [P] [N] range to the “D ₄ ”, “D ₃ ”, “2”, “1”, and “R” range. is another, they control, as shown in FIG. 5 the first solenoid proportional valve 17 ₁ and the control mode in the magnitude relation and gear control of the second solenoid proportional valve 17 ₂ output pressure
FIG. 5B shows a proportional valve monitor value MAT represented as shown in FIG. 5A, and an ON pressure control mode and an OFF pressure control mode during an upshift as shown in FIG.
The control mode of the ON pressure and the control mode of the OFF pressure at the time of the downshift are performed as follows using the downshift monitor value MDN shown in FIG. 5C.

The upshift control is performed according to the procedure shown in FIG.
OFF pressure, transmission input / output speed ratio Gratio (Nou
t / Nin) will be described with reference to FIG. Although the ratio slightly fluctuates due to the pulsation of the speed detection pulse, noise, and the like, if the hydraulic clutch is completely connected, a predetermined upper limit value YG (N) H based on the gear ratio of each shift speed and a lower limit value are set. It falls between the value YG (N) L.

In the upshift control, the gear position designating signal SH for designating the gear position to be established is switched to a signal designating a gear stage G (N + 1) higher than the currently established gear stage G (N). When it starts. In the upshift control, first, in step S1, the MAT is set to “A, B”. When the MAT is set in this way the first,
The second shift valves 12 ₁ and 12 ₂ are switched to a state in which an upshift is performed. Next, in step S2, it is determined whether or not the value on the MUP ON side (MUP (ON)) is "0". M
UP is initially set to “0,0”, and is determined to be “YES” in step S2, and proceeds to step S3.
Here, the remaining time TM of the subtraction timer built in the electronic control circuit 20 is set to a predetermined initial value TMST, and S
In step 4, initial settings of various values used for calculating the ON pressure and the OFF pressure are performed. Next, in step S5, MUP (O
N) = 1, and further, in step S6, the reference value QUPONA in the response pressure mode of the ON pressure is calculated (S6).
6). The response pressure mode is a control mode for removing the play of the piston of the connection side hydraulic clutch so as to increase the clutch pressure thereafter with good responsiveness.
It is set to an appropriate value according to the vehicle speed and the throttle opening, and decreases over time.

Next, the process proceeds to step S7, and is set to "1" at the time of manual shifting, that is, at the time of shifting by range switching, or at the time of shifting by lever operation in a transmission capable of shifting to the first gear by lever operation. The value of the flag FTIP to be executed. If FTIP = 0, the process proceeds to step S8 to perform a process of setting the ON pressure command value QUPON to QUAPONA. A process is performed for setting the value QUAPONX to the added value.
After the processing in steps S8 and S9, the process proceeds to step S10, in which an OFF pressure command value QUPOFF, which will be described in detail later, is calculated. Then, the process proceeds to step S11, where the first and second electromagnetic proportional valves are operated. 17 _1, 17 of the _two, and a command value of the output pressure of the solenoid proportional valve which controls the hydraulic pressure of the hydraulic clutch on the engaging side in this shift with QUPON, the output pressure of the solenoid proportional valve which controls the oil pressure of the disengagement side hydraulic clutch Command value is QUPOFF
Is performed, and the first upshift control process is completed.

In the next upshift control processing,
Since MUP (ON) = 1 was previously set in step S5, "NO" is determined in step S2. In this case, the process proceeds to step S12, and it is determined whether or not the elapsed time (TMST-TM) from the start of the upshift has reached a predetermined time YTMUP1. YTMUP1
Is set longer than the normal time required for the upshift, and when TMST-TM ≧ YTMUP1, it is determined that the upshift control is malfunctioning, the process proceeds to step S13, and the MAT is set to “A, 0 "(at the time of 2nd → 3rd speed upshift) or" 0, B "(at the time of upshift other than 2nd speed → 3rd speed), MUP is set to" 0, 0 ", and TM is further set. An upshift completion process for resetting to zero is performed. When the MAT is set to “A, 0” or “0, B” in this process, the switching valve 13 is switched to a position different from the current position, and the hydraulic pressure of the connecting hydraulic clutch is changed to the line pressure and the release hydraulic clutch. Oil pressure becomes atmospheric pressure.

If TMST-TM <YTMUP1,
Proceeding to step S14, a preparation judgment of the connection side hydraulic clutch (ON clutch) is performed. The details of this processing are as shown in FIG. 8. First, in step S14-1, it is determined whether the MUP is "1, 1" or "1, 2", and if the determination result is "YES". For example, the process proceeds to step S14-2, in which the ratio of the clutch is determined based on the gear ratio of the established gear before the shift, and the lower limit value YG (N) of the clutch connection determination.
L is determined, and Gratio <YG
(N) If L, proceed to step S14-3,
Flag FCOF reset to "0" in step 4
Set FS to "1". Next, in step S14-4, it is determined whether or not the MUP is "2, 2". If the determination result is "YES", the flow proceeds to step S14-5 to determine whether FCOFFS = 1. FCOFFS
If = 1, it is determined in step S14-6 whether or not the throttle opening .theta. Exceeds a predetermined value Y.theta.CONOK. It is determined whether or not a predetermined value YGCONOK set slightly larger than L is exceeded. If Gratio> YGCONOK, the process proceeds to step S14-8, where the flag FCONOK reset to “0” in step S4 is set to “1”, and θ ≦ YθCONOK or Gratio ≦
In the case of YGCONOK, the process proceeds to step S14-9, where FCONOK is reset to "0".

When MUP is "1, 1" or "1, 2", G
The ratio <YG (N) L occurs when slippage of the release hydraulic clutch occurs due to the control in the subtraction mode described later in the OFF pressure, and when the MUP is "2, 2", the ratio is ratio> The state becomes YGCONOK when the connection-side hydraulic clutch starts to have a connection force due to the control in the addition mode described later, that is, when the connection preparation of the connection-side hydraulic clutch is completed. MUP is "1,
If “Gratio <YG (N) L” does not hold when “1” or “1, 2”, FCOFFS = 1 does not hold, and in this case MOFF
When UP is "2,2", Ratio> YGCONO
Even if it becomes K, FCONOK = 0 remains. By the way, the degree of change of the engine output torque due to the throttle opening is large in the low throttle opening region, and when the throttle opening is low, the output torque is greatly reduced, and the slippage of the release hydraulic clutch is reduced. Gratio> YGC
It may be ONOK. Therefore, θ ≦ YθCONO
In the low throttle opening region where K is set, FCONOK = 0, and only in the middle and high throttle opening regions where the output torque does not fluctuate greatly, the FCONOK is set based on the ratio, and the connection preparation of the connection side hydraulic clutch is not completed. However, it is prevented that FCONOK = 1 is set.

When the preparation judgment processing of the connection side hydraulic clutch is performed as described above, MUP (ON) is performed in step S15.
= 1 is determined. In the second upshift control process, since MUP (ON) = 1, it is determined to be "YES" in the step S15, and the process proceeds to the step S16, where the elapsed time from the start of the upshift (TMST-T
It is determined whether or not M) has reached the predetermined time YTMUP2. If TMST-TM <YTMUP2, the process proceeds to steps S5 and below. If TMST-TM ≧ YTMUP2, the process proceeds to step S17 to set the MUP ON-side value to “2”. Next, in step S18 ', △ Q
UPONA is set to a relatively small value, and the process proceeds to step S18, where an addition process is performed in which QUPONA is a value obtained by adding △ UPONA to the previous value, and the process proceeds to S7 and subsequent steps. Thus, the control in the addition mode in which the ON pressure is increased stepwise is started.

When MUP (ON) = 2 is set in step S17, S1 is set in the next upshift control processing.
It is determined "NO" in the step 5 and MUP (ON)
= 2, the process proceeds to step S19, where "YES" is determined, the process proceeds to step S20, and Gr
It is determined whether or not atio has reached or exceeded the upper limit value YG (N) H of the clutch engagement determination set based on the gear ratio of the established gear before the shift. And Gratio <YG
If (N) H, proceed to step S21 to FCON
It is determined whether or not OK = 1, and if FCONOK = 0, S is determined.
Proceeding to steps 17 and below, control in the addition mode is continued.

If FCONOK = 1, the value of TM at that time is stored as TMSTA in step S22, and then the MUP is set to "3, 3" in step S23, and then the following steps from S25 are performed. move on. In the next upshift control process, "NO" is determined in the step S19, and the process proceeds to a step S24 in which it is determined whether or not MUP (ON) = 3, where "YES" is determined. In this case, YTMUP is performed in step S25.
3 is set, and then the process proceeds to step S26, where FCON is set.
It is determined whether or not OK = 1, that is, whether or not the elapsed time (TMSTA-TM) from the completion of connection preparation of the connection side hydraulic clutch has reached YTMUP3. In addition, YTMU
P3 is set to a table value using the vehicle speed V as a parameter so as to increase as the vehicle speed increases. TMST
In the case of A-TM <YTMUP3, it is necessary to set $ QUPONA to a relatively large value in step S18 ", and then to set S1
Proceed to steps 8 and below to continue the control in the addition mode.

When TMSTA-TM ≧ YTMUP3, the process proceeds to step S27 to determine whether or not FTIP = 1, and when FTIP = 0, the process proceeds to step S28.
QUP the reference value QUPONB in the ON pressure bottom-up mode
The final value of ONA is set to a value obtained by adding the value QUPONB0 obtained according to the vehicle speed and the throttle opening to the FTI.
If P = 1, the process proceeds to step S29, and QUAPONB
Is set to a value obtained by further adding a predetermined boosting correction value QUPONY to the above value. Note that QUPONY is set to a value smaller than the boost correction value QUPONX added in step S9. QUPON in steps S28 and S29
When the setting process of B is completed, the process proceeds to step S30 and the MU is set.
P (ON) = 4 is set, and then Q is set in step S31.
UPON is set to QUPONB, and control in the ON pressure raising mode is started. It should be noted that Gra at the step of S20
When it is determined that tio> YG (N) H, the MUP is set to "3, 3" in step S32, and the process directly proceeds to step S27.

In the next upshift control processing,
Since MUP (ON) is set to 4 in step S30, “NO” is determined in step S24,
The process proceeds to the step of S33 for determining whether or not MUP (ON) = 4, where "YES" is determined. In this case, S
Proceeding to step 34, it is determined whether or not the elapsed time (TMST-TM) from the start of the upshift has reached a predetermined time YTMUP4. When TMST-TM ≧ YTMUP4, the ratio is set to the predetermined value YGUP at step S35.
It is determined whether or not the ratio has exceeded T, and Gratio <YGU
In the case of PT, the process proceeds to steps after S27 to continue the control in the bottom-up mode.

When Grad ≧ YGUPT, the flow advances to step S36 to set MUP to “5,5”, and then to step S37, where T
The value of M is stored as TMSTB, then the process proceeds to step S38, where QUPON is set to the final value of QUPONB.
Set to the value obtained by adding PONC. QUAPONC has been reset to zero in step S4, and QUAPON
= QUPONB, and control in the bottom-up mode is continued.

In the next upshift control processing,
Since the MUP is set to “5, 5” in step S36, “NO” is determined in step S33,
The process proceeds to the step of S39 for determining whether or not MUP (ON) = 5, where "YES" is determined. In this case, S
In step 40, it is determined whether or not the elapsed time (TMST-TM) from the start of the upshift has reached a predetermined time YTMUP5. If TMST-TM ≧ YTMUP5, the process proceeds to step S41 and the ratio is changed after the gear shift. It is determined whether or not the clutch engagement determination lower limit value YG (N + 1) L which is set based on the gear ratio of the established gear stage is equal to or more than
TMST-TM <YTMUP5 or Ratio <YG
If (N + 1) L, the process proceeds to S36 and subsequent steps, and control in the bottom-up mode is continued.

When Grad ≧ YG (N + 1) L, the MUP is set to “7, 7” in step S42, and then the process proceeds to step S43, where QUPONC is set to a value obtained by adding a predetermined value △ QUPONC to the previous value. And then S
In a step 44, it is determined whether or not the ratio is between the lower limit value YG (N + 1) L and the upper limit value YG (N + 1) H of the clutch engagement determination set based on the gear ratio of the established gear after the shift. Is determined. The determination result is "NO"
If so, the process proceeds to S37 and subsequent steps. In this case, S4
In the calculation in step 3, QUAPONC becomes △ QUAPONC
QUP calculated in step S38 to increase the address
ON also gradually increases, and control in the ON pressure end mode is started.

In the next upshift control processing,
Since the MUP is set to “7, 7” in the step S42, “NO” is determined in the step S39 and S
Go to step 42 and below. In this case, YG (N + 1)
If L ≦ Gratio ≦ YG (N + 1) H, ie,
If the connection-side clutch is in the connection completed state, the process proceeds to step S45 and the duration of the connection completed state (TMSTB-T
It is determined whether or not M) has reached a predetermined time YTMUP6. If TMSTB-TM <YTMUP6, the process proceeds to step S38 to continue the control in the end mode, and
When TB-TM ≧ YTMUP6, the process proceeds to step S13 to perform an upshift completion process.

The details of the calculation processing of the QUAPOFF in the step S10 are as shown in FIG.
In the step, the value QU in the OFF pressure lowering mode
Set POFFB to an appropriate value according to the throttle opening,
Next, in step S10-2, it is determined whether or not the MUP OFF value (MUP (OFF)) is “0”. In the first upshift control process, since MUP (OFF) = 0, it is determined to be “YES” in the step S10-2, and the process proceeds to the step S10-3 to execute the MUP (OF).
F) = 1 is set. Next, the process proceeds to step S10-4, where the reference value QUP in the OFF pressure initial pressure mode is set.
OFFA is set to an appropriate value according to the throttle opening and the speed ratio of the fluid torque converter 2, and a process of calculating a value in the OFF pressure subtraction mode is performed in step S10-5. Details of this processing are as shown in FIG. 10. First, in step S10-5-1, MUP (OFF) = 1
It is determined whether or not MUP (OFF) = 1, S1
In step 0-5-2, the subtraction value ΔQUPOFF and the feedback correction value QWP are both reset to zero, and the MUP
If (OFF) ≠ 1, ΔQUPOFF is set to a predetermined value in step S10-5-3, and the lower limit value YG of the clutch engagement determination set based on the gear ratio of the established shift stage before shifting is set. (N) The clutch slip target value YG (N) S set slightly lower than L and the current ratio
QWP is calculated by a function operation from the deviation from. Then, in step S10-5-4, QUAPOFFA is set to S1.
A process is performed in which the value of △ QUPOFF-QWP is subtracted from the value of QUPOFFA set in step 0-4, and finally QUPOFFA sets QUPOFFB by the process in steps S10-5-5 and S10-5-6. Do not drop below.

When the processing of step S10-5 is completed as described above, the processing of setting QUPOFF to QUPOFFA is performed in step S10-6, and the calculation processing of QUPOFF in the first upshift control processing is completed. . In the second upshift control process, the previous
Since MUP (OFF) = 1 is set in step S-3, "NO" is determined in step S10-2, and it is determined whether MUP (OFF) = 1 or not S10-7.
The process proceeds to the step (1), where "YES" is determined. At this time, the process proceeds to step S10-8, and the elapsed time (TMST-TM) from the start of the upshift is set to the predetermined time YT
It is determined whether or not MUP7 has been reached. TMST-TM <
If YTMUP7, the process proceeds to S10-3 and subsequent steps. In this case, QUPOFF becomes equal to the value of QUPOFFA obtained in step S10-4, and control in the initial pressure mode is performed.

When TMST-TM ≧ YTMUP7,
In step S10-9, MUP (OFF) is set to 2 and the process proceeds to step S10-4 and subsequent steps. in this case,
QUPOFF is a value obtained by subtracting $ QUPOFF-QWP from QUPOFFA obtained from the map in step S10-4, and control in the subtraction mode is started. In the next upshift control process, since MUP (OFF) = 2 was previously set in step S10-9, “NO” is determined in step S10-7, and
The process proceeds to step S10-10 to determine whether or not UP (OFF) = 2, where "YES" is determined and step S10-
The process proceeds to steps 9 and below, and control in the subtraction mode is continued. In the subtraction mode, QUPOFF decreases in order, and the disengagement side hydraulic clutch starts to slip and the ratio becomes YG (N).
L is less than L, but when Gratio <YG (N) S, Q
When WP> 0, the subtraction width of QUPOFFA becomes smaller, and feedback control is performed so that Grati = YG (N) S.

In the above-described steps S23 and S32, the MU
When P is set to "3,3", "NO" is determined in the step S10-10, and the process proceeds to a step S10-11 in which it is determined whether or not MUP (OFF) = 3. Is determined. At this time, YTMUP8 is set in step S10-12, and then the process proceeds to step S10-13, where the elapsed time (TMSTA-TM) from the completion of connection preparation of the connection side hydraulic clutch is set to YTMUP8.
Is determined. It should be noted that YTMUP8 is set to a table value using the vehicle speed V as a parameter so that it becomes shorter as the vehicle speed increases. TMSTA-TM <YTM
In UP8, the process proceeds to S10-4 and subsequent steps to continue the control in the subtraction mode, and TMSTA-TM ≧ YTMU
When P8 is reached, MUP is performed in step S10-14.
(OFF) = 4 before proceeding to step S10-15, where QUPOFF is set to QUPOFFB,
Start the control in the bottom lowering mode. In the next upshift control process, the MUP was performed in the previous step S10-14.
(OFF) = 4, so S10-11
Is determined as "NO" in the step of "MUP (OFF)".
= 4, the process proceeds to step S10-16 to determine
Here, it is determined as "YES", and the process proceeds to S10-14 and the subsequent steps, and the control in the bottom-down mode is continued.

If the MUP is set to "5, 5" in the step S36, "NO" is determined in the step S10-16, and it is determined whether or not MUP (OFF) = 5. Proceed to step 17 where "Y
ES ”. In this case, the process proceeds to step S10-18, where QUPOFF is changed from GUPOFFB to Grat.
The control in the tail mode is performed by setting a value QUPOFFC that gradually decreases in accordance with io. When the MUP is set to “7, 7” in step S42, S1 is set.
In the step of 0-17, “NO” is determined, and S10-1
Proceeding to step 9, control is performed in an end mode for setting QUPOFF to zero.

In the upshift control described above, the ratio is set to YG by the control in the OFF pressure subtraction mode.
(N) The OFF pressure is feedback-controlled so as to be S, and a slight slippage occurs in the release hydraulic clutch. In this state, the control in the ON pressure addition mode is performed. The ratio changes sensitively in response to the time, and the completion point of the connection preparation of the connection side hydraulic clutch is determined by G.
The ratio can be detected by rising to YGCONOK.
Conventionally, in order to prevent the engine from blowing up, the release-side hydraulic clutch is prevented from slipping, that is, Grat.
The ON pressure is gradually increased while controlling the OFF pressure so that io falls between YG (N) L and YG (N) H, and the input shaft rotation speed due to co-meshing of the release hydraulic clutch and the connection hydraulic clutch. When the ratio exceeds YG (N) H due to the decrease in the pressure, it is determined that the shift state has shifted to the inertia phase, and the OFF pressure is rapidly decreased and the ON pressure is rapidly increased. Is increased, the connecting force of the connecting side hydraulic clutch at the time of the shift to the inertia phase becomes excessive, and a shock occurs.Therefore, the gradually increasing rate of the ON pressure cannot be increased as far to the left. It takes time and the time required for shifting becomes longer. On the other hand, in this embodiment, the completion of the connection preparation of the connection-side hydraulic clutch is detected as described above, and the OFF pressure is rapidly reduced by switching to the bottom-down mode after YTMUP8 from the completion of the connection preparation. The gear shift state is quickly changed to the inertia phase (Gratio> Y) while preventing
G (N) H state) to reduce the time required for shifting. Furthermore, in the present embodiment, the transition to the inertia phase is further accelerated because the gradually increasing rate in the ON pressure addition mode is increased from the completion of the connection preparation.

By the way, when the vehicle speed increases, the decrease in the hydraulic pressure of the release hydraulic clutch is delayed due to the effect of the centrifugal force.
In this embodiment, since the YTMUP8 is set to be shorter as the vehicle speed increases, the switching timing of the OFF pressure to the lowering mode is advanced at a high vehicle speed, and the pressure of the release hydraulic clutch decreases at a high vehicle speed. The occurrence of a shock due to an increase in co-biting due to the delay of the time is prevented. Further, in the present embodiment, in order to promote the shift after the shift to the inertia phase, the YTMUP3
Later, the ON pressure is suddenly increased by switching to the bottom-up mode, but since the YTMUP3 is set to be longer as the vehicle speed increases, the occurrence of shock due to an increase in co-meshing at high vehicle speeds is reliably prevented. Is done.

If the control in the OFF pressure subtraction mode is malfunctioning, the oil pressure in the OFF-side hydraulic clutch does not slip without causing slippage.
Ratio> YG (N) H due to co-biting due to increase in N pressure
It may be. In this case, it is determined that the phase has shifted to the inertia phase, and the control mode for the OFF pressure and the control mode for the ON pressure are immediately switched to the bottom-down mode and the bottom-up mode, respectively.

At the time of a manual shift at which FTIP = 1, it is desired that the shift time be shorter than at the time of an automatic shift. Therefore, in the present embodiment, the ON pressure is corrected to be increased during the manual shift to reduce the shift time. ing. Further, in the present embodiment, the boosting correction value QUPONX in the response pressure mode and the addition mode before the transition to the inertia phase is set relatively large, so that the time required for the transition to the inertia phase is shortened. The boost correction value QUAPONY in the bottom-up mode is set relatively small to prevent an increase in shock.

In the above embodiment, the OFF pressure control mode is switched to the bottom-down mode after a lapse of the predetermined time YTMUP8 from the completion of the connection preparation. However, as shown by the phantom line in FIG. To 4th speed hydraulic clutch C
When the hydraulic pressure detecting means 26 ₁ to 263 composed of hydraulic switches and the like for detecting the hydraulic pressures of 2 to C ₄ are provided, the output signals of these detecting means are inputted to the electronic control circuit 20 to detect the hydraulic pressure of the connection side hydraulic clutch. OFF when the value exceeds the specified value
The pressure control mode may be switched to the bottom-down mode. For example, when a hydraulic pressure detecting means 26 ₁ to 26 ₃ hydraulic switch which is turned on when the hydraulic pressure exceeds a predetermined value, S in FIG. 9
In step 10-13, it is determined whether or not the hydraulic switch for the connection side hydraulic clutch is on. If it is on, the process proceeds to step S10-14, and if it is off, the process proceeds to step S10-4. Let go.

The downshift control is performed according to the procedure shown in FIG.
A description will be given with reference to FIG. 11 schematically showing changes in the pressure, the OFF pressure, and the ratio. In the downshift control, the gear stage G (N) for which the gear stage designation signal SH is currently established.
The process is started when the signal is switched to a signal designating a lower gear G (N-1). In the downshift control, first, in step S101, the MAT is set to “A, B”. When the MAT is set in this manner, the switching valve 13 is switched to a position different from the current position. Next, S10
MDN ON value (MDN (ON)) in step 2
Is determined to be “0”. Since MDN is initially set to “0,0”, “YE” is set in step S102.
S ”and proceeds to step S103 to set TM to T
Set to MST and turn on in step S104
Initialization of various values used for calculation of pressure and OFF pressure is performed.
Next, through steps of S104 'described in detail later, S10
Proceed to step 5 and set MDN (ON) = 1,
Further, in step S106, the value QDNONA in the response pressure mode of the ON pressure is set to an appropriate value according to the vehicle speed and the throttle opening. Note that QDNONA decreases with time.
Next, in step S107, the ON pressure command value QDNON
Is set to QDNONA, an OFF pressure command value QDNOFF calculation process, which will be described in detail later, is performed in step S108, and then the process proceeds to step S109, where the first and second commands are performed.
Of the two electromagnetic proportional valves 17 ₁ and 17 ₂ , the command value of the output pressure of the electromagnetic proportional valve that controls the hydraulic pressure of the connecting hydraulic clutch in this shift is QDNON, and the electromagnetic proportional valve that controls the hydraulic pressure of the release hydraulic clutch. A proportional valve selection process for setting the command value of the valve output pressure to QDNOFF is performed, and the first downshift control process is completed.

In the next downshift control processing,
Since MDN (ON) = 1 was set in the previous step S105, "NO" is determined in the step S102. At this time, the process proceeds to step S110, and it is determined whether or not the elapsed time (TMST-TM) from the start of the downshift has reached a predetermined time YTMDN1. YTM
DN1 is set slightly longer than the normal time required for downshifting. When TMST-TM ≧ YTMDN1, it is determined that downshift control is malfunctioning, the process proceeds to step S111, and the MAT is set to “1”. 0, B "(3
Set to "A, 0" (for downshifts other than 3rd to 2nd gear) or "MD" to "0, 0" and TM to zero. Downshift completion processing. When the MAT is set to “0, B” or “A, 0” in this process, the positions of the _first and second shift valves 12 ₁ and 12 ₂ are switched to a state in which downshifting is performed, and the connection side hydraulic clutch Becomes the line pressure, and the oil pressure of the release hydraulic clutch becomes the atmospheric pressure.

If TMST-TM <YTMDN1,
Proceeding to the step of S112, it is determined whether or not MDN (ON) = 1. MDN in the second downshift control process
Since (ON) = 1, “YE” is determined in step S112.
S ”and proceeds to the step of S113,
It is determined whether or not io exceeds a predetermined value YGDDNS. If Gratio> YGDDNS, the process proceeds to step S114, and the elapsed time (T) from the start of the downshift
MST-TM) has reached a predetermined time YTMDN2 or not, and if TMST-TM <YTMDN2, S1
Proceeding to steps 05 and below, control is performed in the ON pressure response pressure mode.

Gratio ≦ YGDDNS or TMST-T
If M ≧ YTMDN2, the process proceeds to step S115 to set MDN (ON) = 2, and then proceeds to step S116, where the value QDNON of the ON pressure in the low pressure correction mode is set.
B is set to an appropriate value according to the vehicle speed and the throttle opening,
In step S117, a smoothing process for gradually changing QDNNNB from QDNONA to the value set as described above is performed, and then in step S118, QDNON is changed to QDN.
The control is set to ONB, and control in the ON pressure low pressure correction mode is started.

In the next downshift control processing,
Since MDN (ON) = 2 is set in step S115, “NO” is determined in step S112, and the process proceeds to step S119 in which it is determined whether MDN (ON) = 2. It is determined as “YES”. In this case, the process proceeds to step S120, and the ratio is set to YG.
It is determined whether or not it exceeds DNS. Gratio
If> YGDDNS, the process proceeds to step S121 to determine whether or not the elapsed time (TMST-TM) from the start of the downshift has reached a predetermined value YTMDN3. If TMST-TM <YTMDN3, S115
Proceeding to the following steps, control in the low pressure correction mode is continued.

If Grat ≦ YGDNS, S1
After setting the MDN to “3, 3” in the step 22, the process proceeds to the step S 123, and the relation of Gratio> YG
If TMST-TM ≧ YTMDN3 in DNS, the process directly proceeds to step S123, and MDN (ON) = 3 is set. Next, in step S124, the reference value QDNONC in the ON-pressure synchro mode is set to an appropriate value according to the vehicle speed and the throttle opening, and in step S125, QDNONC is not gradually changed from QDNNNB to the above value. Performing the processing. Next, proceeding to step S126, the value of the flag FTBD set to "1" when the gear position designating signal SH is switched to a signal designating a lower speed gear stage G (N-2) during downshift control. I see.
When FTBD = 0, the process proceeds to step S127, where QDNON is set to a value obtained by adding QDNND to QDNNC. QDNND is initially set to zero, so that QDNON = QDNNC, and control in the ON-pressure synchro mode is started.

In the next downshift control processing,
Since MDN (ON) = 3 is set in step S123, “NO” is determined in step S119, and the process advances to step S128 to determine whether MDN (ON) = 3. YES is determined. At this time, the process proceeds to step S129, and the elapsed time (TMST-TM) from the start of the downshift is set to the predetermined time YTMDN.
4 to determine whether TMST-TM <YTMD
If it is N4, the process proceeds to the steps after S123, and the control in the synchro mode is continued.

If TMST-TM ≧ YTMDN4, then
Proceeding to step S130, it is determined whether or not the ratio of the ratio of the clutch is equal to or less than an upper limit value YG (N-1) H of the clutch engagement determination set based on the gear ratio of the established shift stage after the speed change. (N-1) When it becomes H
Proceed to step 131, and as described later,
By using the timer value TMSTC set to the value of TM at the time when YG (N−1) H is reached, Grat ≦ YG
(N-1) Elapsed time (TMSTC)
-TM) has reached a predetermined time YTMDN5. Then, Gratio> YG (N-1) H or T
If MSTC-TM <YTMDN5, the process proceeds to steps after S123 to continue the control in the synchro mode.
When MSTC-TM ≧ YTMDN5, S132
Step FTBD = 1 to determine whether or not FTBD = 1.
If BD = 0, MDN (O
N) = 4, and then QDN in step S134
The ONC is set to an appropriate value according to the vehicle speed and the throttle opening, and in step S135, QDNND is set to a value obtained by adding △ QDNND to the previous value. Next, S
In step 136, the ratio is between the upper limit YG (N-1) H and the lower limit YG (N-1) L of the clutch engagement determination set based on the gear ratio of the established gear after the shift. Is determined, and the determination result is “NO”.
If so, in step S137, TMSTD is set to the current value of TM, and the process proceeds to step S127. In this case, in the calculation in S135, QDNAND becomes △ QD
Since the value increases to NON, the QDNON obtained in step S127 also gradually increases, and control in the ON pressure termination mode is started.

In the next downshift control processing,
Since MDN (ON) is set to 4 in the step S133, “NO” is determined in the step S128, and the process directly proceeds to the steps S132 and subsequent steps to continue the control in the end mode. Then, in step S136, “YE
S ”, the process proceeds to step S138, and
The time during which the ratio continuously enters between YG (N-1) H and YG (N-1) L, that is, the duration (TMSTD-TM) of the connection completion state of the connection side hydraulic clutch is a predetermined time. It is determined whether or not YTMDN6 has been reached, and TMST
When D-TM ≧ YTMDN6, the process proceeds to step S111 to perform a downshift completion process. Also, S12
When it is determined that FTBD = 1 in step S6 or S132, the process directly proceeds to step S111 to perform downshift completion processing. The setting process of the FTBD is as shown in FIG. 27. During the downshift control to the first-speed lower speed G (N-1), the lower-speed speed G (N-
When a downshift command to 2) is issued (S120)
1, S1202), and set FTBD = 1 (S120
3) Otherwise, reset FTBD = 0 (S1204).

According to the above control, Gratio ≦ YG
The ON pressure rises in the transition to the synchro mode when the DNS is reached.
There is a response delay until the ON clutch pressure increases). This response delay is short at high vehicle speeds and long at low vehicle speeds due to the effect of centrifugal force. Therefore, as shown in FIG. 13A, YGDNS is set relatively high at low vehicle speeds and relatively low at high vehicle speeds in consideration of the difference between the response delay a at low vehicle speeds and the response delay b at high vehicle speeds. And Gratio is Y
When the vehicle enters the synchro region between G (N-1) H and YG (N-1) L, the ON clutch pressure is increased to a predetermined pressure which does not cause clutch slip, regardless of the vehicle speed. ing. When the engine temperature is low, the output torque of the engine increases due to idle-up, and the rate of decrease in the ratio during downshifting is greater than at high temperatures as shown in FIG. Therefore, the engine temperature, that is, the engine cooling water temperature TW is detected, and the YGDDNS
Is set higher at a low water temperature than at a high water temperature, so that the ON clutch pressure is increased to a predetermined pressure at which the clutch does not slip when the ratio enters the synchro region even at the low water temperature. The ON clutch pressure boost response delay a
Is constant regardless of engine temperature, but O
In the present embodiment, in order to cope with the difference in the pressure rise response delay of the N clutch pressure, the YGDNS is calculated from, for example, a map using the vehicle speed and the cooling water temperature as parameters in step S104 '.

The QD in step S108 described above
Details of the NOFF calculation process are as shown in FIG.
First, in step S108-1, MDN (OFF) = 0.
It is determined whether or not. Since MDN is set to “0, 0” in the first downshift control processing, S108
It is determined to be "YES" in the step S-1 and the step S108-2 is executed.
Then, the initial value QDNOFFA of the OFF pressure in the initial pressure mode is set to an appropriate value according to the vehicle speed and the throttle opening. Next, MDN (OFF) is set to 1 in the step of S108-3, and S108-
In step 4, the speed ratio etr of the fluid torque converter 2 at that time (etr rotation speed / engine rotation speed)
Is stored as etrm, and then the process proceeds to step S108-5, where a boost correction value QDNOFFZ corresponding to the shift progress degree of the engine rotation speed at the start of the downshift due to the increase of the engine rotation speed due to the slippage of the fluid torque converter 2 is set. Calculate. QDNOFFZ is calculated by multiplying a reference value QDNOFFZO corresponding to the throttle opening by a shift progress coefficient K obtained by a function operation using etrm as a parameter. The coefficient K will be described later in detail. After calculating QDNOFFZ, the process proceeds to step S108-6, where the value QDN of the OFF pressure in the low pressure holding mode is set.
OFFB is a reference value QDNOFF corresponding to the throttle opening.
BO is set to a value obtained by adding QDNOFFZ, and then S1
In step 08-7, QDNOFFB is changed to QDNOFFA.
, A smoothing process for gradually decreasing the value to the value set as described above is performed, and then QDNOF is performed in step S108-8.
Set F to QDNOFFB. Thus, the OFF pressure is Q
Control in the initial pressure mode gradually decreasing from DNOFFA is started.

In the next downshift control processing,
Since MDN (OFF) is set to 1 in step S108-3, “NO” is determined in step S108-1.
Then, the process proceeds to step S108-9 for determining whether or not MDN (OFF) = 1, where "YES" is determined. In this case, the process proceeds to step S108-10, where the ratio of the clutch is determined based on the gear ratio of the established gear before the shift, and the lower limit value YG (N) of the clutch engagement determination is set.
L is determined to be less than or equal to Gratio> YG
If (N) L, in step S108-11, it is determined whether or not the elapsed time (TMST-TM) from the start of the downshift has reached a predetermined time YTMDN7.
If TM <YTMDN7, the process proceeds to S108-3 and the subsequent steps to continue the control in the initial pressure mode. Then, Gratio ≦ YG (N) L or TMST-TM ≧
When YTMDN7 is reached, MDN (OFF) is set to 2 in step S108-12, and then S108-5.
Proceeding to the following steps, the control in the OFF pressure low pressure holding mode is started.

In the next downshift control processing,
Since MDN (OFF) is set to 2 in step S108-12, “N” is set in step S108-9.
O ”, the process proceeds to step S108-13 to determine whether or not MDN (OFF) = 2.
S ”is determined. In this case, the process proceeds to step S108-14, where it is determined whether or not the ratio is equal to or smaller than a predetermined value YGDNT. TM) is a predetermined time YTMDN
8 to determine whether TMST-TM <YTMD
In N8, the process proceeds to S108-12 and the subsequent steps to continue the control in the low pressure holding mode. And Grati
When o ≦ YGDNT or TMST-TM ≧ YTMDN8, MDN (OFF) in step S108-16.
= 3, the process proceeds to step S108-17, and the value QDNOFFC of the OFF pressure in the tail mode is set to an appropriate value according to the throttle opening.
In step 18, QDNOFF is set to QDNOFFC, and control in the tail mode in which the OFF pressure is maintained at a lower pressure than in the low pressure holding mode is started.

In the next downshift control processing,
Since MDN (OFF) is set to 3 in step S108-16, “N” is set in step S108-13.
O ”, the process proceeds to step S108-19 for determining whether or not MDN (OFF) = 3.
S ”is determined. In this case, the process proceeds to step S108-20, where the time elapsed from the start of the downshift (TMS
T-TM) has reached a predetermined time YTMDN4, and if TMST-TM ≧ YTMDN4, S108.
Going to step -21, Gratio changes to YG (N-
1) It is determined whether or not H is less than H, and TMST-TM <
If YTMDN4 or Gratio> YG (N-1) H, the process proceeds to S108-16 and subsequent steps to continue the control in the tail mode. And TMST-TM ≧ YTM
When DN4 and Gratio≤YG (N-1) H, the process proceeds to step S108-22, and the value of TM at that time is set to TMSTC used in the time measurement process in step S131. Next, in step S108-23, MDN (OFF) = 4 is set, and
In step 108-24, the value QDNOFFD in the OFF pressure termination mode is set to a value that gradually decreases from QDNOFFC, and in step S108-25, QDNOFF is set to QDNOFFD, and control in the OFF pressure termination mode is performed. Do.

The shift progress coefficient K is defined as the fluid at the start of the downshift with respect to the amount of change in the engine rotation speed when the downshift is performed while the speed ratio etr of the fluid torque converter 2 is maintained at the reference value Yetr. It represents the ratio of the amount of increase in the engine speed due to slippage of the torque converter 2. Here, assuming that the gear ratio (Nin / Nout) of the established gear before the downshift is YG (N) and the gear ratio of the established gear after the downshift is YG (N−1), et
If the downshift is performed with r = Yetr, the engine speed NeG (N) before the downshift and the engine speed NeG (N−1) after the downshift are the rotation speed of the output shaft 7 of the transmission. Where Nout (constant), NeG (N) = Nout · YG (N) / Yetr (1) NeG (N−1) = Nout · YG (N−1) / Yetr (2) The actual etr at the start of the downshift is etrm
Then, the engine rotation speed Ne at that time is as follows: Ne = Nout · YG (N) / etrm (3) The shift progress coefficient K is represented by the following equation: K = (Ne−NeG (N)) / (NeG (N−1) −NeG (N)) (4) By substituting the equations (2) and (3), K = {(Yet / etrm-1)} / {(YG (N-1) / YG (N))-1} (5)

When the accelerator pedal is depressed slowly,
If the vehicle speed does not change, only the engine rotational speed increases due to slippage of the fluid torque converter 2, and the engine rotational speed may rise above NeG (N) at the start of the downshift. In this case, when the disengagement side hydraulic clutch slips after the start of the downshift, the rotation speed of the input shaft 3 rapidly increases to approach the previously increased engine rotation speed, and Gr
The ratio decreases, and the ratio enters the synchro region before the ON clutch pressure is sufficiently increased, so that the connecting side hydraulic clutch cannot be connected at the time of the synchro. Therefore, in the present embodiment, etrm
Is used as a parameter to calculate the boost correction value QDNOFFZ using the shift progress coefficient K obtained from the equation (5), add QDNOFFB by the calculated value, and suppress the decrease in the ratio by the coupling force of the disengagement-side hydraulic clutch to reduce the synchronization. Thus, the connection side hydraulic clutch is sufficiently connected. Since the value of etr at the time of completion of the shift changes delicately in accordance with the engine operating condition, it is desirable to change the value of Yetr to be substituted into the above equation (5) in accordance with the engine operating condition.

In this embodiment, G (N) changes to G (N).
(S-1) during downshift control to (N-1)
When H is switched to a signal designating a further lower gear G (N-2) and FTBD is set to 1, when the control in the ON-pressure low-pressure correction mode ends (in the ON-pressure synchronization mode). If FTBD = 1 is set during the control of (1), the control in the synchro mode is ended), the downshift completion processing is performed, and G (N-1) to G (N-
Downshift control to 2) is started. In this way, the downshift control from G (N) to G (N-1) is completed early, so that the time required for downshifting from G (N) to G (N-2) is reduced, Drivability is improved.

By the way, during downshift control from G (N) to G (N-1), the gear position designating signal SH is switched to a signal designating G (N), or from G (N) to G (N +).
During the upshift control to 1), the gear position designation signal SH becomes G
It may be switched to a signal designating (N). In such a case, even if the positions of the first and second shift valves 12 ₁ and 12 ₂ and the switching valve 13 are not switched, the hydraulic pressure of the hydraulic clutch involved in the shift can be changed by the first and second electromagnetic proportional valves 17 ₁ and 17. ₂ can be controlled. Therefore, when the gear position designation signal SH is switched to a signal designating G (N) during downshift control from G (N) to G (N-1), the downshift control is stopped halfway. A transfer upshift is performed in which the upshift control is switched from G (N-1) to G (N), and during the upshift control from G (N) to G (N + 1), the gear position designation signal SH becomes G (N). When the signal is switched to a signal designating G, the upshift control is stopped halfway, and a transfer downshift is performed to switch the downshift control from G (N + 1) to G (N).

The details of the transfer upshift control are as shown in FIG. 16 and will be described with reference to FIG. 15 which schematically shows changes in the ON pressure, the OFF pressure, and the ratio. First, in step S201, MUP is set to "4,4" and MDN is reset to "0,0".
In step 02, TM is set to TMST, and then S2
In step 03, it is determined whether or not the elapsed time (TMST-TM) from the start of the upshift has reached a predetermined time YTMUP1, and if TMST-TM ≧ YTMUP1, the process proceeds to step S204 to perform the upshift completion processing. Do. The content of this process is the same as the process in step S13 shown in FIG.

If TMST-TM <YTMUP1,
In step S205, the value QUPONB of the ON pressure in the upshift in the bottom-up mode is calculated.
It is determined whether or not MUP (ON) = 4 in the step. 1
In the second processing, “YES” is determined in the step of S206, and the process proceeds to the step of S207, where the ratio of YG
It is determined whether or not UPT has been reached. Gratio <
If it is YGUPT, QUPON in step S208
B is gradually changed from the final value of QDNOFF in the immediately preceding downshift control to the value of QUPONB obtained in step S205, and after setting QUPON to QUPONB in step S209, the process proceeds to step S210. The calculation processing of QUPOFF is performed, and then S21
In step 1, a proportional valve selection process is performed. The calculation processing of QUPOFF is performed in the same manner as the processing in steps S10-16 to S10-19 in FIG. Fig. 7 shows the proportional valve selection process.
Is the same as the process in step S11.

When Grad ≧ YGUPT, S2
In step 12, MUP is set to "5,5", and in step S213, TMSTB is set to T
M is set to the value of M, and then QUAPO
N is set to a value obtained by adding QUPONC to QUPONB. The initial value of QUPONC is zero, and QUPON = Q
The control becomes UPONB and the control in the ON pressure bottom-up mode is performed.

In the next process, since MUP was set to “5, 5” in the previous step of S212,
It is determined as “NO” in step 06, and MUP (O
N) = 5, proceed to step S215 to determine
Here, "YES" is determined. At this time, it is determined in step S216 whether or not the ratio is greater than or equal to YG (N) L.
Proceeding to step 212 and subsequent steps, control in the ON pressure bottom-up mode is continued. When Grad ≧ YG (N) L, the MUP is set to “7, 7” in step S217, and the process proceeds to step S218 and subsequent steps. Therefore, in the next process, “NO” is determined in the step S215, and the process directly proceeds to the step S217. In step S218, processing is performed to set QUAPONC to a value obtained by adding △ QUAPONC to its previous value. Next, in step S219, it is determined whether or not the ratio is between YG (N) L and YG (N) H, and the determination result is “NO”.
If so, the process proceeds to steps after S213. In this case, S
By the calculation in step 218, QUAPONC is $ QUAPO
Since the number increases to the NC, the QUPON obtained in step S214 also gradually increases, and the control in the ON pressure termination mode is performed. If YG (N) L ≦ Gratio ≦ YG (N) H, that is, if the connection-side hydraulic clutch is in the connection completed state, the continuation time (TMSTB-TM) of the connection completed state is set to the predetermined time YTMUP6 in step S220. Is determined, and when TMSTB-TM ≧ YTMUP6, the process proceeds to step S204 to perform an upshift completion process.

The details of the transfer downshift are as shown in FIG. 18, and will be described with reference to FIG. 17 which schematically shows changes in the ON pressure, the OFF pressure, and the ratio. First,
After resetting the MUP to “0, 0” and setting the MDN to “2, 2” in step S301, the process proceeds to step S302.
Is set to TMST in the step of
The time elapsed since the start of the downshift (TM)
ST-TM) has reached a predetermined time YTMDN1 or not, and if TMST-TM ≧ YTMDN1, S30 is reached.
The process proceeds to step 4 to perform a downshift completion process. The content of this process is the same as the process in step S111 shown in FIG.

If TMST-TM <YTMDN1,
In step S305, it is determined whether or not MDN (ON) = 2. In the first processing, “YE
S ”and proceeds to the step of S306,
It is determined whether or not io exceeds YGDDNS, and Gr is determined.
If atio> YGDDNS, Q in step S307
DNNNB is calculated, and in step S308, QDNON
B is gradually changed from the final value of QUPOFF in the immediately preceding upshift control to the value of QDNNNB obtained in step S307, and QDNON is set to QDNNNB in step S309, and then, in step S310. QDNOFF arithmetic processing is performed, and then S31
In step 1, a proportional valve selection process is performed. ON by this
The control is performed in the pressure low-pressure correction mode. In addition, QDNO
The calculation processing of the FF is performed in S108-15 and S108 in FIG.
The process is performed in the same manner as the steps from S108-13 onward in which the step of -20 is omitted. Fig. 1 shows the proportional valve selection process.
The processing is the same as the processing in step S109 of No. 2.

When Grati ≦ YGDNS, S3
After setting MDN to "3,3" in step 12,
QDNONC is calculated in step S313, and S314
In step (3), a smoothing process for gradually changing QDNONC from the final value of QDNONNB to the value obtained in step S312 is performed, and then in step S315, QDNON is set to a value obtained by adding QDNON to QDNONC.
The initial value of QDNND is zero, and QDNON = QDN
The control becomes ONC and the control in the sync mode of ON pressure is started.

In the next process, since the MDN was set to “3, 3” in the previous step of S312,
05 is determined to be “NO” and MDN (O
N) = 3, proceed to step S316 to determine whether
Here, "YES" is determined. In this case, it is determined in step S317 whether or not the ratio of Grati is equal to or less than YG (N) H. If Grati ≦ YG (N) H, S is determined.
Proceeding to step 318, Gratio ≦ YG (N) H
It is determined whether or not the elapsed time (TMSTC-TM) from the time when the time has reached the predetermined time YTMDN5 is determined.
io> YG (N) H or TMSTC-TM <YTMDN5
In the case of, control proceeds to the steps after S313 to continue control in the synchro mode.

When TMSTC-TM ≧ YTMDN5, MDN (ON) = 4 is set in step S319,
Next, in step S320, QDNONC is calculated, and in step S321, QDNND is set to a value obtained by adding $ QDND to its previous value.
It is determined whether or not it is in between. If the determination result is "NO", TMSTD is set to the value of TM at that time in step S323, and the process proceeds to step S315. In this case, Q in the calculation in the step of S321
Since DNOND increases to $ QDNOND, S315
Is gradually increased, and the control in the ON pressure termination mode is performed. If “YES” is determined in the step of S322, the continuation time (TMSTD) of the connection completion state of the connection-side hydraulic clutch is determined in a step of S324.
-TM) has reached a predetermined time YTMDN6, and T
When MSTD-TM ≧ YTMDN6, the process proceeds to step S304 to perform downshift completion processing.

As described above, in the transfer change-up shift control and the transfer change-down shift control, the determination based on the elapsed time (TMST-TM) from the shift start time is made based on YTMUP1 and YTMDN1 which are the criteria for determining the shift time.
Only when it is determined whether or not has been reached. this is,
This is because the shift change is started in the middle of the immediately preceding shift, and the progress of the shift cannot be determined based on the elapsed time from the start of the shift. Therefore, the progress state of the shift has to be determined only by the ratio. If the ratio cannot be accurately detected due to a sensor failure or the like, it becomes impossible to appropriately control the ON pressure and the OFF pressure according to the progress of the shift. So, Grat
A flag FGFAIL that is set to “1” when io cannot be detected accurately is used, and when FGFAIL = 1, a transfer change speed is prohibited. Also,
In the forward range such as “D ₄ ” or “D ₃ ”, the vehicle shifts according to a shift map set using the vehicle speed and the throttle opening as parameters. However, the vehicle speed sensor 22 does not detect the ground speed but the rotational speed of the wheels. Therefore, when a tire lock occurs due to braking on a low μ road or the like, the vehicle speed V detected by the vehicle speed sensor 22 decreases to almost zero even though the actual vehicle speed hardly changes. Then, a downshift is performed according to the shift map, and an upshift is performed according to the vehicle speed after the tire grip is recovered, resulting in useless shifting. Also, in the manual shift state in which the gear is shifted to the first gear by operating the lever, the vehicle is automatically downshifted to the first gear when the vehicle speed becomes extremely low so that the vehicle can be restarted at the first gear after the vehicle stops. Upshift is performed. Therefore, when the vehicle is downshifted to the first gear due to a tire lock, the first gear remains established even after the tire grip is recovered, forcing the driver to perform an upshift operation to a gear suitable for the vehicle speed. Will be. In order to solve such a problem, the vehicle speed sensor 22
Is set to a predetermined time "1" when the vehicle speed detected in step (1) is rapidly decelerated by the tire lock, that is, when the vehicle speed decreases at a deceleration equal to or more than a predetermined value.
When FLOCK = 1, downshifting is prohibited.

FIG. 19 shows a shift selection process using FGFAIL and FLOCK. In this process, first, in step S401, it is determined whether or not the gear G (SH) designated by the gear designation signal SH is the same as the gear G (SHO) designated up to then. (S
H) When G (SHO), G in step S402
(SH) is higher than G (SHO), and if G (SH)> G (SHO), the upshift flag FUP is set to “1” in step S403,
If G (SH) <G (SHO), it is determined in step S404 whether or not FLOCK = 1, and when FLOCK = 0, FUP is reset to "0" in step S405. Next, in step S406, it is determined whether or not the MAT is set to "A, B", that is, whether or not the shift control is being performed. If MAT = A, B, the transfer shift flag FCS is determined in step S407. Is set to “1” and MAT ≠
If it is A or B, the FCS is reset to "0" in step S408. Then, in step S409, FCS =
1 is determined, and if FCS = 0, it is determined whether or not FUP = 1 in step S410. If FUP = 1, the process proceeds to step S411 to perform upshift control.
If FUP = 0, the process proceeds to step S412 to perform downshift control. If FCS = 1, it is determined in step S413 whether or not FGFAIL = 1, and FGFAIL is determined.
If L = 0, it is determined whether or not FUP = 1 in step S414. If FUP = 1, transfer upshift control is performed in step S415. If FUP = 0, SUP is performed.
At step 416, transfer downshift control is performed. When FGFAIL = 1, the process is terminated as it is to inhibit a shift change, and the FLOC is determined in step S404.
When it is determined that K = 1, the process is terminated as it is, and downshifting is prohibited. Since the FLOCK is reset to “0” after a predetermined time, the downshift is prohibited during a predetermined time after the tire lock is generated.
After that, downshift is permitted in preparation for stopping.

In the setting process of the FGFAIL, when the gear is not being shifted, the gear ratio G at which the gear is established at that time is set.
A timer value TMG (N) that counts the time between the lower limit value YG (N) L and the upper limit value YG (N) H of the clutch engagement determination set based on the gear ratio of (N) is used. .
20. TMG (N) is prepared for each shift speed.
As shown in (A), first, in step S1100, MA
It is determined whether or not T is set to "A, 0" or "0, B", that is, whether or not the gear is not shifting. If the gear is not shifting, the gear is shifted to the first gear in step S1101. It is determined whether the value falls within the range between the upper and lower limit values YG (1) L and YG (1) H, and if the value falls within this range, S
In step 1102, the timer value TMG for the first speed stage (1)
Is added, and if it is out of this range, TMG (1) is subtracted in the step of S1103. The same process is performed in the second gear at the steps S1104, S1105, and S1106, the third gear at the steps S1107, S1108, and S1109, the fourth gear at the steps S1110, S1111, and S1112, and the steps at S1113, S1114, and S1115. The timer value TMG (2), TMG (3), TMG for the second speed stage to the reverse stage is executed for the reverse gear.
(4) Addition / subtraction of TMG (R) is performed. Therefore, the timer values TMG (1) to TMG (R) for each of these gears are
Upper and lower limit values YG (1) L, YG corresponding to Gratio
(1) The difference is the difference between the cumulative time of the time in the range between H and YG (R) L and YG (R) H and the cumulative time of the time out of this range. If the detection of Gratio is accurate, the timer value TMG (N) for the gear G (N) established before the shift immediately before the transfer shift becomes a sufficiently large value. Therefore, as shown in FIG. 20B, TMG (N) is compared with a predetermined threshold value YTMG in step S1116, and when TMG (N)> YTMG, FGFAIL = 0 and TMG ( N) When ≤YTMG, FGFAIL = 1 is set in step S1118.

As shown in FIG. 21 (A), the FLOCK is a value obtained by setting the vehicle speed V detected by the vehicle speed sensor 22 to a relatively low value from a first predetermined vehicle speed YVH (for example, 40 km / h) which is set relatively high. 2 predetermined vehicle speed YVL (for example, 1
0 km / h) is measured, and when this time t falls below a predetermined value, it is set to "1" for a predetermined time. This predetermined value is, for example, (YVH-YV
L) / t is set to be about 1 G (gravitational acceleration). Details of the FLOCK setting process are as shown in FIG. 21B. First, it is determined whether or not the vehicle speed V has fallen below YVH in step S1001, and if V ≧ YVH, the flow proceeds to step S1002. The remaining time tm of an arithmetic expression timer different from the shift control timer is set to an initial value tmst.
, And then in step S1003, FLOCK =
Reset to zero. If V <YVH, it is determined in step S1004 whether the vehicle speed V has fallen below YVL.
If V ≧ YVL, the process proceeds to step S1003. When V <YVL, the process proceeds to step S1005 to determine whether FLOCK = 1 or not, and FLOCK = 0.
If so, the vehicle speed V changes from YVH to Y in step S1006.
Time t (tmst-t) required to decrease to VL
It is determined whether or not m) has become equal to or less than a predetermined time Ytmlock. If tmst-tm ≦ Ytmlock, S
Whether or not tm has become zero in step 1007 (V <Y
It is determined whether or not tmst has elapsed since VH, and if tm ≠ 0, FLOC is determined in step S1008.
Set K = 1. From the next time, as long as V <VHL, the process proceeds from step S1005 to step S1008, and a predetermined time (tmst-Yt) until tm = 0 is reached.
mlock) FLOCK = 1 is held. Note that the predetermined time is set to be slightly longer than the braking time when performing temporary braking that is not intended to stop, and is set to, for example, about 10 seconds.

The details of the in-gear control are as shown in FIG. 23. This will be described with reference to FIG. 22 which schematically shows changes in the ON pressure and the ratio during in-gear. In the in-gear control, first, in step S501, the MAT is set to “2,
It is determined whether any one of "0", "4,0" and "6,0" is set. In the first process, “NO” is determined in the step S501, and the TM is determined in the step S502.
Is set to TMST, and the value QINGA in the response pressure mode of the ON pressure is set to an appropriate value according to the throttle opening in step S503. Note that QINGA decreases with time. Next, after the MAT is set to “2, 0” in the step S504, the command value QING of the ON pressure in the in-gear control is set to QINGA in the step S505, and the process proceeds to the step S506. The command value of the output pressure of one of the second electromagnetic proportional valves, which controls the hydraulic pressure of the hydraulic clutch connected during in-gear among the second electromagnetic proportional valves 17 ₁ and 17 ₂ , is QING, and the command value of the output pressure of the other electromagnetic proportional valve is QING. A proportional valve selection process for setting the atmospheric pressure is performed.

In the next process, since the MAT was previously set to “2, 0” in the step of S504,
01 is determined to be “YES”, the process proceeds to step S507, and the time (TM) elapsed from the in-gear start time is set.
ST-TM) has reached a limit value YTMING1 for abnormality determination, and TMST-TM ≧ YTMING
When it becomes 1, the process proceeds to step S508, and the MAT is set to "A, 0" (when the gear is shifted to the first gear, the third gear, or the reverse gear).
Or "0, B" (at the time of in-gear to the 2nd speed) and performs in-gear completion processing for resetting TM to zero.
If TMST-TM <YTMING1, it is determined whether or not MAT is set to "2,0" S50.
The process proceeds to step 9, where "YES" is determined.
At this time, the process proceeds to step S510, where it is determined whether or not the elapsed time from the in-gear start time has reached a predetermined time YTMING2. Control is performed.

If TMST-TM ≧ YTMING2, the flow advances to step S511 to set MAT to "4, 0". Then, in step S512, it is determined whether or not the ratio has exceeded a predetermined value YGINGS. Gr
If atio <YGINGS, the flag FING is set to “1” in step S513, and at step S514
In step (5), the value of TM at that time is stored as TMD, and then in step S515, $ QINGX is set to a relatively large value. When the hydraulic clutch begins to engage Gr
If atio ≧ YGINGS, it is determined in step S516 whether FING = 1 or not. If FING = 0, S is determined.
Proceed to step 515, and if FING = 1, S51
Go to step 7 and start from in-gear
Time required until o ≧ YGINGS (TMST-
It is determined whether or not (TMD) is equal to or longer than a predetermined time YTMING3. And TMST-TMD <YTMING
If it is 3, △ QINGX is set to a relatively small value in step S518, and TMST-TMD ≧ YTMING
If it is 3, $ QINGX is set to a medium value in step S519. When △ QINGX is set in this way, the process proceeds to step S520, where QINGX is set to a value obtained by adding △ QINGX to its previous value, and then S
In step 521, the value QING in the ON pressure addition mode
B is set to a value obtained by adding QINGX to the final value of QINGA, and QING is set to QINGB in step S522. In the next process, since the MAT was previously set to “4, 0” in the step of S511, S509
Is determined to be "NO" in the step of
The process proceeds to step S523 for determining whether or not the value is set to “0”, where “YES” is determined. At this time, the process proceeds to step S524, and it is determined whether or not the ratio is equal to or more than the lower limit YG (N) L of the clutch connection determination set based on the gear ratio of the gear established at the time of in-gear. In the case of Gratio <YG (N) L, the process proceeds to S511 and subsequent steps, and control in the addition mode is performed.

When Gratio ≧ YG (N) L, the flow advances to step S525 to set MAT to “6,0”. From the next time, “NO” is determined in the step S523, and the process directly proceeds to the step S525. Next, S5
Proceeding to step 26, it is determined whether or not Gratio ≧ YG (N) L, and if Gratio <YG (N) L,
In step S527, the value of TM at that time is set to TMST.
E, and the process proceeds to step S528.
If io ≧ YG (N) L, the process directly proceeds to step S528. In step S528, QINGC is set to a value obtained by adding $ QINGC to the previous value. Next, S5
Proceeding to step 29, the state of Gratio ≧ YG (N) L, that is, the duration (TM
STE-TM) has reached a predetermined time YTMING4. And TMSTE-TM <YTMIN
In G4, the process proceeds to step S530, where QING is changed to Q
The final value of INGB is set to a value obtained by adding QINGC, and the control in the ON pressure end mode is performed.
When TM ≧ YTMING4, the process proceeds to step S508 to perform in-gear completion processing.

According to the above control, in the addition mode, △ QING is maintained until Gratio ≧ YGINGS.
Since X is set to a large value, the speed of increasing the ON pressure increases, and thereafter, the speed of increasing the ON pressure decreases. Therefore, the time lag at the time of in-gear can be reduced, and the occurrence of in-gear shock can be prevented. Also, under conditions such as high temperature where the hydraulic pressure is apt to decrease, it takes time to start the engagement of the clutch. Under these conditions, Gra
If the speed of increasing the ON pressure after tio ≧ YGINGS is reduced, it takes time to complete the engagement of the clutch, and the time lag increases. On the other hand, in the present embodiment, if it takes time until the clutch engagement starts, TM
ST-TMD ≧ YTMING3, then
Is set to a medium value, Gratio ≧ YG
Even after INGS, the speed of increasing the ON pressure does not decrease to the left, and the time lag can be reduced.

Further, during the reverse running in the "R" range, "D"
₄ ", etc., the Gratio will change to YG
May remain above INGS. The reason is as follows. Although the ratio is obtained by Nout / Nin, the rotational speed of the output shaft 7 is zero during a stop, and
If the output shaft rotation speed is set to Nout as it is, even if Nin decreases due to a decrease in engine rotation speed during in-gear, G
The ratio remains at zero. Therefore, Nout is set to a value obtained by adding a predetermined raised value to the output shaft rotation speed, and Nout is set.
The ratio is made to increase as the in decreases.
When the range is switched from the "R" range to the forward range, the output shaft 7 is switched from the reverse rotation state to the normal rotation state, and the output shaft rotation speed temporarily becomes zero in the middle thereof, but Nout is raised as described above. Gratio ≧ YGINGS may remain. When switching from the "R" range to the forward range, it is desired to increase the ON pressure quickly to quickly switch the output shaft 7 to the forward rotation state. In the present embodiment,
If Grat ≧ YGINGS, FING =
It becomes 0, and △ QINGX is held at a large value, which satisfies the above demand.

During high speed running in the "R" range, "D"
₄₎ , the transmission torque to the output shaft 7 is reduced when a high gear corresponding to a high vehicle speed is established according to the shift map, so that by the time the rotation direction of the output shaft 7 is switched, It takes time, during which time the clutch keeps slipping and the durability deteriorates. In this case, it is determined whether the traveling direction of the vehicle is forward or reverse by providing a vehicle speed sensor capable of determining the rotation direction of the wheels, and when it is determined that the vehicle is traveling backward in the forward range, the shift speed is lower than normal. By establishing the above, the above-mentioned problem can be solved. FIG. 24 shows the control for this. If it is determined in step S601 that the vehicle is in the forward range, it is determined in step S602 whether or not the vehicle is in reverse. If the determination result is "NO", the process proceeds to step S603. In step S1, a normal shift map is selected as the shift map. If the vehicle is traveling in reverse, a shift map for countermeasures against reverse is selected as the shift map. The reverse gear shift map is set, for example, to establish the second gear and the first gear at the vehicle speed at which the third gear and the second gear are established in the normal map, for example.

It should be noted that providing forward / backward detection means such as a vehicle speed sensor with a function of discriminating the rotation direction increases the cost,
By using the following control without using a special sensor,
A shift map may be selected when switching from the “R” range to the forward range. This control includes
This is performed using a flag FREV that is set and maintained at “1” when the vehicle speed exceeds a predetermined value in the “R” range and does not fall below the predetermined value in the “N” range. The details are
As shown in FIG. 25A, if it is determined in step S701 that the vehicle is in the forward range, it is determined in step S702 whether or not FREV = 1, and if FREV = 0, the gear is shifted in step S703. Select a normal shift map as the map. If FREV = 1, in step S704, the same reverse shift map as described above is selected as the shift map. Then, in step S705, the MAT
Is set to any of "2, 0", "4, 0", and "6, 0", and when the result of the determination is "NO", that is, when the in-gear control is completed , S70
In step 6, FREV is reset to "0", and a normal shift map is selected from the next time. Details of the FREV setting process are as shown in FIG.
When it is determined that the range is the "R" range in step S802,
In step S803, it is determined whether or not the reverse gear GR has been established. If so, it is determined in step S803 whether or not the vehicle speed V exceeds a predetermined value YVa (for example, 10 km / h). When V> YVa, FREV is set to "1" in step S804. And S80
If it is determined in step 5 that the range is the "N" range, S80
At step 6, it is determined whether or not the vehicle speed V has fallen below a predetermined value YVa. When V <YVa, FREV is reset to "0" at step S807. According to this,
When V> YVa in the “R” range and FREV is set to “1”, FREV = 1 remains unless V <YVa in the “N” range. Therefore, when the range is switched from the “R” range to the forward range through the “N” range, if FREV = 1, it can be determined that the vehicle is moving backward. Therefore, during reverse travel in the forward range, the shift map for countermeasures against reverse is selected, and switching from the reverse state to the forward state can be accelerated to improve the durability of the clutch. When switching from the forward range to the “R” range, as described above, when the reverse gear GR is established when the vehicle speed falls below the predetermined value, V> YVa in the “R” range. However, it is not immediately possible to say that the vehicle is moving backward. Therefore, in this embodiment, FREV = 1 is set only when V> YVa in the state where the reverse gear GR is established in the “R” range, and the reverse gear GR is established in the reverse range. FRE when not done
V is not set to 1 to prevent erroneous determination.

By the way, the electronic control circuit (ECU) 20 may temporarily go down due to a voltage drop during traveling. When the voltage rises, the ECU 20 performs an initialization operation and restarts. While the ECU 20 is down, the power supply to all the solenoid valves is stopped, and the first and second shift valves 12 ₁ and 12 ₂ and the switching valve 13 are switched to the left position to establish the fourth speed. Further, even if the ECU 20 is restarted, during the initialization of the ECU 20, it is not possible to read the values of the parameters such as the vehicle speed and the throttle opening, so that it is not possible to specify the shift speed according to the shift map. During the shift, a high gear is established (to prevent overspeeding of the engine due to the establishment of the low gear during the high-speed running), and after the initialization is completed, the gear is shifted to the gear according to the shift map. In this method, if the ECU 20 goes down during traveling in the low gear, the engine rotational speed decreases due to the establishment of the high gear until the end of initialization, and the engine rotational speed is significantly increased when downshifting to the low gear after the end of initialization. , The downshift takes time, and the recovery of the driving force is delayed.

[0137] Here, the hydraulic circuit of the present embodiment, even when the manual valve 11 is switched to the running range position such as "R" the "D _4", "D _3", "2", "1", the transmission It is configured to be in a neutral state. In other words, the first and second shift valves 12 ₁ and 12 ₂ and the switching valve 13 are set to the state at the time of shifting, and the first and second electromagnetic proportional valves 17 ₁ and 1
If both atmospheric 7 ₂ output pressure, hydraulic pressure of either hydraulic clutch C1~C4 also becomes the atmospheric pressure, the transmission is in the neutral state. Therefore, when the ECU 20 is started, as shown in FIG. 26, it is determined whether or not the initialization has been completed in a step S901. During the initialization, a neutral signal is output in a step S902, and in a step S903, The flag FINT is set to "1". The neutral signal indicates a state in which the first and second shift valves 12 ₁ and 12 ₂ and the switching valve 13 are shifted, for example, the first and second shift valves 12 ₁ and 12 ₂ are set to the left position, and the switching valve 13 is set to the left position. This signal is a signal for setting the right position to the state at the time of shifting from third gear to fourth gear and setting the output pressure of the first and second electromagnetic proportional valves 17 ₁ and 17 ₂ to atmospheric pressure. become. Upon completion of the initialization, the flow advances to step S904 to determine whether FINT = 1. Immediately after the end of the initialization, FINT = 1, so that “YES” is determined in the step of S904. At this time, the process proceeds to step S905 to determine whether or not the vehicle is in the travel range. If it is not the driving range, that is, if it is in the “N” or “P” range, FINT is executed in step S906.
Is reset to "0", and the process proceeds to step S907 to perform normal control. ECU 20 by key switch on
The processing at the time of starting is performed by this route. If it is in the travel range, the process proceeds to step S908 to start in-gear control for establishing a shift speed according to the shift map,
Next, in step S909, the MAT is "2, 0", "4,
0, "6, 0" is determined, and when the determination result is "NO", that is, when the in-gear control is completed, FI at step S910.
Reset NT to "0". Thus, after the in-gear control is completed, “NO” is determined in the step of S904, and normal control is performed. According to this, even if the fourth gear is established due to the down of the ECU 20 during traveling at the low gear, the ECU 2
When 0 is restarted, the engine will be in a neutral state until initialization ends, during which the engine speed will increase,
The in-gear to the low-speed stage after the end of the initialization is performed with good responsiveness, and the driving force recovers early.

[0138]

As is apparent from the above description, the claims
According to the second aspect, the shift state can be shifted to the inertia phase early while preventing the engine from blowing up, and the upshift can be performed smoothly and quickly. According to the first aspect of the invention, it is possible to prevent the occurrence of a shock due to an increase in co-engagement caused by a delay in pressure drop of the release-side hydraulic connection element at a high vehicle speed. According to the third aspect of the invention, the shift to the inertia phase can be accelerated, and according to the fourth aspect of the invention, the progress of the shift after the shift to the inertia phase can be accelerated, and the time required for upshifting Can be further reduced. According to the fifth aspect of the present invention, it is possible to more reliably prevent the occurrence of a shock due to an increase in co-meshing at a high vehicle speed. According to the invention of claim 6 , erroneous determination of connection preparation due to fluctuations in engine output can be prevented, and it is possible to accurately detect whether connection preparation has been completed.

[Brief description of the drawings]

FIG. 1 is a sectional view of an example of a transmission to which the present invention is applied.

FIG. 2 is a diagram showing a hydraulic circuit of a transmission.

FIG. 3 is an enlarged view of a main part of a hydraulic circuit.

FIG. 4 is a block circuit diagram of a control system of an electromagnetic valve provided in a hydraulic circuit.

5A, 5B, and 5C are diagrams showing a relationship between various monitor values used for shift control and a control mode.

FIG. 6: ON pressure, OFF pressure, and Gra during upshifting
Time chart showing changes in tio

FIG. 7 is a flowchart showing upshift control.

FIG. 8 is a flowchart showing control contents in step S14 of FIG. 7;

FIG. 9 is a flowchart showing control contents in step S10 of FIG. 7;

FIG. 10 is a flowchart showing control contents in step S10-5 of FIG. 9;

FIG. 11: ON pressure, OFF pressure, and Gr during downshifting
Time chart showing changes in atio

FIG. 12 is a flowchart showing downshift control.

FIG. 13 (A) Ratio in downshift control
A graph showing the setting according to the vehicle speed of the determination value YGDDNS of the shift progress state according to the vehicle speed;

FIG. 14 is a flowchart showing control contents in step S108 of FIG. 12;

FIG. 15: ON pressure and OFF during transfer upshift
Time chart showing changes in pressure and ratio

FIG. 16 is a flowchart showing transfer upshift control;

FIG. 17: ON pressure and OFF during a transfer downshift
Time chart showing changes in pressure and ratio

FIG. 18 is a flowchart showing transfer downshift control.

FIG. 19 is a flowchart showing shift selection control.

20A shows a flag FGF used in the control of FIG.
Flow chart showing the counting processing of the timer value TMG (N) used in the AIL setting processing, and (B) flow chart showing the FGFAIL setting processing

FIG. 21A shows a flag FLO used in the control of FIG.
Graph showing the principle of setting CK, (B) Flow chart showing processing of setting FLOCK

FIG. 22 is a time chart showing changes in ON pressure and ratio during in-gear.

FIG. 23 is a flowchart of in-gear control.

FIG. 24 is a flowchart showing an example of a shift map selection process.

25A is a flowchart illustrating another example of the shift map selection process, and FIG. 25B is a flowchart illustrating a flag F used in the process of FIG. 25A.
Flow chart showing REV setting processing

FIG. 26 is a flowchart showing control during and after initialization of the ECU.

FIG. 27 is a flowchart showing a process of setting a flag FTBD used in the control of FIG. 12;

[Explanation of symbols]

C1 to C4 1st to 4th speed hydraulic clutch (hydraulic connection element) G1 to G4 1st to 4th speed transmission system (gear stage) 20 Electronic control circuit 26 _{1 to} 26 ₃ Oil pressure detecting means S14 Step of making ON clutch preparation determination ( Connection preparation judging means) FCONOK flag (FCONOK = 1 is connection preparation completion signal) YTMUP8 predetermined time YTMUP3 second predetermined time

──────────────────────────────────────────────────続 き Continuing from the front page (72) Inventor Hiromitsu Ishibashi 1-4-1 Chuo, Wako-shi, Saitama Prefecture Inside of Honda R & D Co., Ltd. (72) Kazuo Okada 1-4-1 Chuo, Wako-shi, Saitama Stock (56) References JP-A-4-175567 (JP, A) JP-A-4-15357 (JP, A) JP-A-5-296323 (JP, A) JP-A-6-294465 ( JP, A) (58) Fields investigated (Int. Cl. ⁷ , DB name) F16H 61/00-61/24

Claims (6)

(57) [Claims] In a control device for a hydraulically operated transmission for a vehicle having a plurality of shift speeds established by a selection operation of a plurality of hydraulic connection elements, a hydraulic pressure of a release side hydraulic connection element released during an upshift is released. Pressure, the input / output speed ratio of the transmission at the time of the upshift, and the gear ratio of the shift speed established by the connection of the release-side hydraulic connection element. On the basis of the reference, the input / output speed ratio is reduced and maintained at a predetermined ratio lower than a predetermined connection region which is set in a range in which the input / output speed ratio falls when no slippage of the release-side hydraulic connection element occurs. Means for decreasing the release pressure; means for gradually increasing the connection pressure; and outputting a connection ready signal when the input / output speed ratio of the transmission falls below the connection area and then rises again to the connection area. A connection standby determination means for, a predetermined time has elapsed after the output point of the coupling ready signal
And means for decreasing said release pressure at a predetermined low pressure at the time, the predetermined time is to be shorter with increasing vehicle speed,
A control device for a hydraulically operated transmission for a vehicle , which is variably set according to a vehicle speed. 2. A control device for a hydraulically operated transmission for a vehicle having a plurality of shift speeds established by a selection operation of a plurality of hydraulic connection elements, wherein a hydraulic pressure of a release side hydraulic connection element released during an upshift is released. Pressure, the input / output speed ratio of the transmission at the time of the upshift, and the gear ratio of the shift speed established by the connection of the release-side hydraulic connection element. On the basis of the reference, the input / output speed ratio is reduced and maintained at a predetermined ratio lower than a predetermined connection region which is set in a range in which the input / output speed ratio falls when no slippage of the release-side hydraulic connection element occurs. Means for controlling the release pressure to decrease, means for gradually increasing the connection pressure, oil pressure detection means for detecting the connection pressure, and after the input / output speed ratio of the transmission falls below the connection area, returns to the connection area again. A connection standby judging means for outputting the connection standby completion signal upon rising, the detection value of the connected pressure after the output of the coupling ready signal is given
Means for reducing the release pressure to a predetermined low pressure when the value exceeds a value, the control device for a hydraulically operated transmission for a vehicle. 3. After the connection preparation completion signal is output, the connection is completed.
The gradual increase rate of the consolidation pressure is larger than before the connection ready signal is output.
The control device for a hydraulically operated transmission for a vehicle according to claim 1 or 2, wherein the control device comprises: 4. The method according to claim 1, further comprising the step of:
2. After a predetermined time elapses, the connection pressure is increased to a predetermined high pressure.
That means control apparatus for a hydraulically operated vehicular transmission according to any one of claims 1 to 3, characterized in that it comprises a. 5. The method according to claim 1, wherein the second predetermined time is set as the vehicle speed increases.
The control device for a hydraulically operated transmission for a vehicle according to claim 4, wherein the control device is variably set according to the vehicle speed so as to be longer . 6. The engine according to claim 1, wherein said connection preparation determining means includes an engine load.
Will not output the connection preparation completion signal when
The control device for a hydraulically operated transmission for a vehicle according to any one of claims 1 to 5 , wherein the control device is configured as follows.