JPH04151061A - Hydraulic control device for automatic transmission - Google Patents

Abstract

PURPOSE:To commonly use a control means for a plurality of pressure regulating mechanisms and to perform accurate and simple simultaneous control of a plurality of hydraulic servoes by providing the two pressure regulating mechanisms with a control means to output a pressure signal, which two pressure regulating mechanisms are communicated respectively to two hydraulic servoes. CONSTITUTION:When a command for a 2-3 shift is received, a linear solenoid valve 45 feeds a signal oil pressure for regulation of a pressure is fed to a drain control valve 220 of a second clutch, and an oil pressure in a servo 12S is drained to dring the second clutch into a slight slip state. In this case, when the feed on an oil pressure to a servo 13S of a third clutch is not completed and the third clutch does not start transmission of torque yet, the number of input revolutions is about to increase. In which case, a linear solenoid valve 45 controls a signal oil pressure as a change in the number of revolutions is monitored to hold the slip state of a second clutch. When the third clutch states transmission of torgue, a shift to a third speed is started, and the number of input revolutions is about to decrease. Through detection of the change in the number of revolutions, the second clutch is rapidly released to complete a shift to a third speed.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a hydraulic control device installed in an automatic transmission of an automobile.

[Prior Art] Automobile automatic transmissions are equipped with a gear train using a plurality of rows of planetary gear sets, and each element of the planetary gear set is selectively engaged or kept stationary to achieve multiple gear stages. Achieve.

Among the frictional engagement elements used to engage and release each element,
The clutch and brake are equipped with a hydraulic servo, and a hydraulic control device controls the supply and removal of hydraulic pressure to the hydraulic servo to achieve the necessary engagement and release.

Conventionally, one hydraulic servo is provided with two pressure regulating mechanisms, such as an accumulator that controls the engagement hydraulic pressure when engaged and a pressure regulating valve that controls the drain speed when released. A control means such as a solenoid valve that controls the pressure regulating mechanism controls the operation and drain of the hydraulic servo, and controls the engagement and release of the frictional engagement element provided with the hydraulic servo. In this case, for example, when one pressure regulating mechanism such as a drain control valve is operating, the pressure change of said one pressure regulating mechanism interferes with the other pressure regulating mechanism such as an accumulator, and the other pressure regulating mechanism Pressure fluctuations may occur.

In order to solve this problem, the inventors have proposed a means for cutting off the oil passage between the hydraulic servo and the other pressure regulating mechanism when one pressure regulating mechanism is operating (patent application 1
-288182).

Furthermore, in an automatic transmission with a small number of gears, simultaneous control of two or more frictional engagement elements is avoided as much as possible, and the hydraulic control device is designed to prevent the gear train from being in a neutral state or an interlock state during gear shifting.

[Problems to be Solved by the Invention] If an attempt is made to further increase the number of gear stages of an automatic transmission to make it multi-stage, simultaneous control of a plurality of frictional engagement elements becomes necessary.

For example, if it is necessary to control so that one of two frictional engagement elements is released and many of them are engaged at the same time,
Two pressure regulating mechanisms are required for each friction engagement element and one control means for each pressure regulating mechanism, which not only increases the number of parts but also requires one of the plurality of control means. When a failure occurs, it is difficult to avoid an interlock state or a neutral state of the automatic transmission gear train.

Therefore, the control means for the same type of pressure regulating mechanism attached to each hydraulic servo is made common, and the two hydraulic servos are controlled by control means such as two solenoid valves to release and engage the two frictional engagement elements. It is conceivable to simultaneously control both gears, but by sharing the control means, a problem arises in that even the pressure regulating mechanism, which is not used during gear shifting, operates.

Therefore, the present invention provides a hydraulic control device for an automatic transmission equipped with a plurality of hydraulic servos to which the two pressure regulating mechanisms are attached, in which a control means for controlling the plurality of pressure regulating mechanisms is shared, and the plurality of pressure regulating mechanisms are provided in common. An object of the present invention is to provide a hydraulic control device that can accurately and easily control hydraulic servos simultaneously.

[Means for Solving the Problem] A transmission having a plurality of rows of planetary gear sets, and a friction engagement element that achieves engagement and disengagement of elements of the planetary gear set;
A hydraulic control device for an automatic transmission comprising: a hydraulic servo for operating the friction engagement element; and means for controlling pressure oil supplied to the hydraulic servo; first and second hydraulic servos; a first communication means for selectively communicating the first hydraulic servo with the hydraulic power source; a second communication means for selectively communicating the second hydraulic servo with the hydraulic power source; and the first and second hydraulic pressures. The third part connects both servos to a hydraulic power source.
a first position that is disposed between the first hydraulic servo and the shift control means and allows the first hydraulic servo to communicate with the shift control means; , a first adjustment mechanism including a spool that is movable between a second position that communicates the first hydraulic servo with a drain passage; and between the second hydraulic servo and the shift control means. and the second
a first hydraulic servo connected to the shift control means;
and a second position in which the second hydraulic servo is communicated with the drain passage. a second pressure regulating mechanism communicated with the second hydraulic servo; a second pressure regulating mechanism communicated with the first and second regulating mechanisms, respectively; outputting a hydraulic signal to the first and second adjustment mechanisms to bias the respective spools of the first and second adjustment mechanisms in the direction of positioning them at the first positions when the communication means is switched to the communication means of the first and second adjustment mechanisms; At the same time, when the shift control means is switched to the third communication means,
In synchronization with this, an adjustable pressure signal is outputted to the first and second adjustment mechanisms to bias the respective spools of the first and second adjustment mechanisms in the direction of respectively positioning the spools in the second positions. a first control means; a communication position that is disposed between the first hydraulic servo and the first pressure regulating mechanism and allows the first hydraulic servo to communicate with the first pressure regulating mechanism; a switching valve configured to switch to a closed position in which communication is cut off and a communication passage from the hydraulic servo to the pressure regulating mechanism is closed; the switching valve is connected to the second adjusting mechanism; when the first and second communication means output a signal to set the switching valve to the communication position, and when the shift control means is switched to the third communication means;
It is characterized by comprising a second control means that outputs a signal for switching the switching valve to the cutoff position and a signal for holding the spool of the second adjustment mechanism at the first position in synchronization with this. That is.

[Function] According to the present invention, when the shift control means is in the first communication means, the pressure oil of the hydraulic source is sent from the shift control means to the first adjustment mechanism, while the first control means is in the first communication means. Since the spool of the first adjustment mechanism is positioned at the first position, the first hydraulic servo is energized with pressure oil from the hydraulic source via the first adjustment mechanism, and the first hydraulic servo is equipped with the first hydraulic servo. The frictional engagement elements are engaged. At this time, the second hydraulic servo is cut off from the hydraulic power source. Further, since the second control means has the switching valve in the communication position, the first hydraulic servo communicates with the first pressure regulating mechanism, and the pressure increase is appropriately controlled.

Next, when the shift control means is in the second communication means, the shift control means isolates the first hydraulic servo from the hydraulic pressure source and communicates the second adjustment mechanism with the hydraulic pressure source. Since the second control means biases the spool of the second adjustment mechanism to the first position, the second hydraulic servo is communicated with the hydraulic source via the second adjustment mechanism and biased. Since the frictional engagement element having the second hydraulic servo is engaged, the second hydraulic servo is communicated with the second pressure regulating mechanism, and the pressure increase is appropriately controlled.

The shift control means has a third communication means between the first communication means and the second communication means for communicating both the first and second hydraulic servos with a hydraulic power source, and the first communication means When the communication means is switched to the third communication means, the first control means applies an adjustable pressure that biases the spools of the first and second adjustment mechanisms in the direction of respectively positioning the spools in the second position. A signal is output to the first and second adjustment mechanisms, and a hydraulic signal that is biasing the spools of the first and second adjustment mechanisms in a direction to position them in the first position is drained. Further, the second control means switches the switching valve to the cutoff position, closes the communication path of the first hydraulic servo to the first pressure regulating mechanism by the switching valve, and simultaneously controls the second regulating mechanism. Holding the spool of the mechanism in the first position.

Therefore, the pressure oil from the hydraulic source is supplied to the second hydraulic servo via the shift control means switched to the third communication means and the second adjustment mechanism in which the spool is held in the first position. flow to and bias the second hydraulic servo, and in the first adjustment mechanism, the spool is biased to the second position by an adjustable pressure signal of the first control means. The internal pressure drop of the first hydraulic servo is adjusted based on the relationship between the pressure oil that is about to be discharged from the first hydraulic servo into the drain passage and the pressure oil that is supplied from the shift control means and input to the first hydraulic servo. be done.

[Example code] Hereinafter, the present invention will be explained in detail based on the drawings.

FIG. 3 shows a skeleton of the automatic transmission of the present invention, and first, an overview of the whole will be explained with reference to FIG.

The automatic transmission 1 includes a starting device 2 and a transmission 3 having a planetary gear device, but the starting device 2 includes, in addition to the torque converter shown in this embodiment, a fluid coupling, an electromagnetic clutch,
Appropriate means such as a multi-plate clutch, a centrifugal clutch, etc. can be selected.

The transmission 3 houses a planetary gear train and a frictional engagement element in a case, and includes a three-row simple planetary gear set 61, 62, 63 as the planetary gear train.

The carrier of the first simple planetary gear set 61 is connected to the ring gear of the third simple planetary gear set 63 via the first intermediate shaft, and the carrier of the third simple planetary gear set 63 is connected to the second simple planetary gear set 62. It is connected to the ring gear of the motor and the output shaft. The sun gear of the third simple planetary gear set 63 is connected to the carrier of the second simple planetary gear set 62 and is connected to the first simple planetary gear set 61 via a frictional engagement element.
Connects to the sun gear.

The frictional engagement elements are 4 clutches, 2 brakes, 2
The system is equipped with two one-sided clutches, and the connection relationship between the frictional engagement elements and each element of the planetary gear train is as follows.

The input shaft of the transmission 3 is connected to the drum of the first clutch 11 and the third clutch.
The clutch 13 is connected to the drum of the clutch 13. first clutch 1
1 hub is the first simple planetary gear set 61
The hub of the third clutch 13 is connected to the sun gear of the first simple planetary gear set 61. The hub of the third clutch 13 is connected to the second clutch 1
It is also connected to the second drum, and further connected to the hub of the fourth clutch 14 and the outer race of the first one-way clutch 31.

The hub of the second clutch 12 is connected to the third clutch via the second intermediate shaft.
The second simple planetary gear set 6 is connected to the sun gear of the second simple planetary gear set 63.
Connect to the second carrier.

This carrier is further connected to the outer race of a second one-way clutch 32 which also serves as the hub of the second brake 22. The inner race of the second one-sided clutch 32 is attached to a case, which is a stationary member.

The drum of the fourth clutch 14 also serves as the drum of the first brake 21, and is connected to the sun gear of the second simple planetary gear set 62 via the inner race of the first one-sided clutch 31 and the third intermediate shaft. .

A first rotation sensor 71 is provided outside the third clutch 13 directly connected to the input shaft to obtain rotation information of the input shaft. A second rotation sensor 72 is also provided outside the output shaft to obtain rotation information of the output shaft.

(Drowning Table 1 Table 1 Squeal) 4th speed *marked: C-2, C-3 small and large piston engagement Table 2 This automatic transmission operates by engaging and disengaging each frictional engagement element. It is possible to achieve eight forward speeds and one reverse speed.

Table 1 shows the engagement/disengagement state of each friction engagement element to achieve eight forward speeds and one reverse speed.

The eight forward speeds are 1st, 2nd, and 2.5th.

The terms 3rd speed, 3.2nd speed, 3.5th speed, 4th speed, and 5th speed are:
Depends on the gear ratio achieved by each gear shown in Table 2.

Table 2 shows the gear ratio and torque distribution borne by the frictional engagement elements for each gear stage.

In the automatic transmission of the present invention, the relationship between each gear and gear ratio as a reference shift pattern is 1st gear, 3rd gear, and 3rd gear.
．． 1 2nd speed 2.0 3rd speed 1.4 4th speed 1.0 5th speed 0.7 Quick speed 2.5 Therefore, five forward speeds with a good gear ratio can be achieved as a basic shift pattern.

And between the 2nd and 4th gears of the basic shift pattern,
By setting three gear stages, it is possible to obtain a more appropriate shift pattern corresponding to driving and acceleration conditions.

FIG. 4 shows a circuit configuration of a control device for an automatic transmission according to the present invention.

The hydraulic servos of the frictional engagement elements to be controlled are four clutch servos 11, 12, 13°14 and two brakes 21, 22. The second clutch 12 among the four clutches includes a small servo 12s with a small piston and a large servo 12L with a large piston as hydraulic servos. The third clutch 13 similarly includes a small servo 13S with a small piston and a large servo 13L with a large piston.

As is clear from Tables 1 and 2, the second clutch 12 is engaged in 2nd, 3.2nd, and 4th gears, and remains engaged in 4th gear in 5th gear. .

The torque to be borne is the 2nd gear which is in the engaged state.

3. It is small in 2nd and 4th gears, but maintains the engaged state 5
It becomes large at high speed. Therefore, in the present invention, the small servo 12S is controlled in 4th speed and below where locking and releasing are performed, achieving control with good responsiveness, and in S speed, where the torque burden is large, both servos 12S are controlled.

Use 12L to obtain sufficient locking torque.

The third clutch 13 also has a similar configuration and operation.

The first brake 21 is a band brake and needs to exhibit various functions. In order to handle this variety of control, the servo of the first brake 21 includes a first servo 2LA and a second servo 21B on the apply side of the servo, and a servo that supplies hydraulic pressure to the return side of the servo. It has 21R. Only this first brake 21 is directly controlled using a linear solenoid valve 46.

As is clear from Table 2, the second brake 22 is
Since the torque to be borne varies depending on the gear stage, a first servo 22A and a second servo 22B are provided.

The accumulators for adjusting the servo pressure include an accumulator 51 for the first clutch, an accumulator 52 for the second clutch, and an accumulator 53 for the third clutch.

Four solenoid valves 4 are used as means to control the hydraulic circuit.
1, 42, 43, 44 and 4 near solenoid valves 45
, 46, 47.48. Second solenoid valve 41
is a normally open valve, which communicates with the drain when off and communicates with the corresponding circuit when on. Third solenoid valve 4
2 is a normally closed valve, which communicates with the drain when it is on and communicates with the corresponding circuit when it is off. The first solenoid valve 43 is a normally closed valve, and the fourth solenoid valve 44 is a normally open valve.

A total of 29 valves are equipped as oil passage switching valves and pressure regulating valves. List the signs and pillars of polyverbs.

100...Manual valve 110...1-2 shift valve 120...2-3 shift valve 130...3-4 shift valve 140... ... 4-5 shift valve 160 ... Reverse control valve 210 ... Orifice control valve 220 of first clutch 11 ... Drain control valve 230 of second clutch 12 ...Accumulator relay first valve 240 of second clutch 12...Accumulator relay second valve O of second clutch 12...Second. Control valve O of third clutch 12.13...Drain control valve 0 of third clutch I3
...Accumulator relay first valve 0 of third clutch 13 ...Accumulator relay second valve 0 of third clutch 13 ...Modulator valve of fourth clutch 14 0
...Large piston relay valve 0...Control first valve 0 of the first brake 21...
... Control second valve 0 of the first brake 21 ...
・Release relay valve 20 of the first brake 2I...Relay valve 0 of the first brake 21...
...Modulator valve 0 of the second brake 22...
...Solenoid relay valve 0...Primary regulator valve 0...
・Secondary regulator valve 0...Lock-up relay valve O...Accumulator control valve 450...Lock-up control valve 470...
. . . Cutback valve 480 . . . Solenoid modulator valve The present invention achieves eight forward speeds as described above.

In the basic shift pattern of 1st speed → 2nd speed → 3rd speed → 4th speed → 5th speed, simultaneous switching of two clutches occurs between 2nd speed and 3rd speed.

In other words, when upshifting from 2nd to 3rd gear,
The second clutch 12 is released and the third clutch 13 is engaged. In downshifting from third speed to second speed, third clutch 13 is released and second clutch 12 is engaged.

As mentioned above, the second clutch 12 has a small servo 123.
and a large servo 12L, and a small servo 12 for 2nd gear engagement.
The response is improved by using only S. Similarly,
The third clutch 13 also has a small servo 13S and a large servo 13L.
, and only the small servo 13S is energized for third-speed engagement.

In order to smoothly achieve simultaneous switching of these two clutches, the hydraulic control device of the present invention includes a drain control valve, which is an adjustment mechanism, for each clutch to be simultaneously switched;
It includes a hydraulic servo, an accumulator that is a pressure regulating mechanism thereof, and an accumulator relay first valve that is a switching valve that controls connection and disconnection between the hydraulic servo and the accumulator.

Drain control of the servo hydraulic pressure of both clutches is then achieved using a single linear solenoid valve.

To configure this control device, when one linear solenoid valve is controlling the hydraulic servo drain control valve of one clutch, it is necessary to stop the operation of the servo drain control valve of the other clutch. Therefore, an accumulator relay second valve is provided, which is a switching valve that operates one accumulator relay first valve and stops the other drain control valve.

FIG. 1 shows the details of the main parts of the device of the present invention, and also shows the operation of the multiple valves and the flow of pressure oil when the device is in second gear.

The small servo 12S of the second clutch 12 is connected to the oil passage 1120.
．． 1100 to the drain control valve 220 (first adjustment mechanism) of the second clutch 12, and the accumulator relay first valve 230 (switching valve) of the second clutch 12 via oil passages 1120, 1140. It will be communicated to.

Accumulator relay first valve 23 of second clutch 12
0 communicates with the accumulator relay second valve 240 (second control means) of the second clutch 12 via oil passages 34, 20, and 3400.

The small servo 13S of the third clutch 13 is connected to the oil path 1340.
．． It communicates with the drain control valve 260 (second adjustment mechanism) of the third clutch 13 via 1320, and communicates with the accumulator relay first valve 270 of the third clutch 13 via oil passages 1340, 1360. The accumulator relay first valve 270 of the third clutch 13 is connected to the oil path 3
It communicates with the accumulator relay second valve 280 of the third clutch 13 via 380° and 3350°.

The accumulator relay second valve 240 of the second clutch 12 communicates with the drain control valve 260 of the third Claratier 3 via oil passages 3400 and 3440, and the accumulator relay second valve 280 of the third clutch 13 communicates with the drain control valve 220 of the second clutch 12 via oil passages 3350 and 3360.

The drain control valve 220 of the second clutch 12 is connected to the oil passage 1
040, and the drain control valve 260 of the third clutch 13 communicates with the 2-3 shift valves 120 via oil passages 1300, respectively, and the 2-3 shift valves 120 communicate with the oil passages 1020, 1030, and 1000, respectively. It is connected to a manual valve 1°O shown in FIG. 4 via.

The back pressure chamber of the accumulator 52 of the second clutch 12 and the back pressure chamber of the accumulator 53 of the third clutch 13 are connected to the accumulator control valve shown in FIG. 440.

The solenoid valve 45 has oil passages 4500, 4550°451
0 through the drain control valve 220 of the second clutch 12
The oil passages 4500 and 4 communicate with the upper oil chamber of the
550.4520 to the upper oil chamber of the drain control valve 260 of the third clutch 13.

The solenoid valve 41 communicates with the upper oil chamber of the second accumulator relay valve 240 of the second clutch 12 via an oil passage 4100.

The solenoid valve 42 communicates with the upper oil chamber of the 3-4 shift valve 130 via an oil passage 4200.

The solenoid valve 43 communicates with the upper oil chamber of the 2-3 shift valve 120 via oil passages 4300 and 4310, and
It communicates with the upper oil chamber of the second accumulator relay valve 280 of the third clutch 13 via an oil passage 4320.

The 3-4 shift valve 130 connects to the 2-3 shift valve 120 via the oil passage 3000 and via the oil passages 3020 and 3010.
The accumulator relay second valve 24 of the second clutch 12 communicates with the second clutch 12 via oil passages 3300 and 3320.
0 and the second accumulator relay valve 280 of the third clutch 13 via oil passages 3300 and 3330, respectively.

As shown in Table 1, in 2nd speed, solenoid valve 4
1 is on, solenoid valve 42 is on, solenoid valve 43
is off, and the solenoid valve 45 is off.

In this state, a hydraulic signal is output from the normally open solenoid valve 41 to the oil passage 4100 marked with an
Set the spool of the second accumulator relay valve 240 of No. 2 to the right position shown by diagonal lines. Further, the upper oil chamber of the accumulator relay first valve 230 of the second clutch 12 is connected to the oil chamber 3.
420° 3400 to the accumulator relay second valve 240 of the second clutch 12, but is drained because the spool of the accumulator relay second valve 240 is in the right position. Therefore, the spool of the first valve 230 of the accumulator relay of the second clutch 12 is brought to the left position indicated by diagonal lines due to the force of a spring (not shown) disposed in the lower oil chamber.

From the normally closed solenoid valve 43 there is an oil path 4300 marked with an
Since a hydraulic signal is output to the upper oil chamber of the 2-3 shift valve 120 via the oil passage 4310, it overcomes the force of a spring (not shown) disposed in the lower oil chamber and shifts the 2-3 shift valve. 120 to the right position indicated by the diagonal line. The second accumulator relay of the third clutch 13 is connected via the oil passage 4320.
The signal sent to valve 280 overcomes the force of a spring (not shown) disposed in the lower oil chamber to move the spool to the right position shown by diagonal lines.

The linear solenoid valve 45 (first control means) is turned off in 2nd speed and does not output oil pressure to the oil passage 4500, but communicates with the second gear via the oil passage 4530. Since hydraulic pressure is not supplied to the upper oil chamber of the control valve 250 of the third clutch 12.13, the spool of the drain control valve 220.260 of the second and third clutches 12.13 is arranged in the lower oil chamber. The left position shown by diagonal lines is achieved by the force of a provided spring (not shown).

Then, the line pressure input from the oil passage 2510 becomes
．． Output to the oil passage 2520 through the intermediate oil chamber of the control valve 250 of the third clutch 12.13, and input to the lower oil chamber of the drain control valve 220 of the second clutch 12 via the oil passage 253o. As a result, the spool of the drain control valve 220 of the second clutch 12 is held at the left position shown by diagonal lines.

Similarly, line pressure is input to the lower oil chamber of the drain control valve 260 of the third clutch 13 through the oil passage 2540, so that the spool of the drain control valve 260 of the third clutch 13 is connected to the spool shown by diagonal lines. It is held in the left position.

Next, the flow of hydraulic pressure supplied to the servo will be explained.

For D range oil pressure, the line pressure is oil line 1000 marked with O.
Pass through, oil passages 1020, 1030G, - branch 2 -
Since the spool of the 3-shift valve 120 is in the right position indicated by diagonal lines, the input to the oil passages 10 and 20 is from the oil passage 1o4 marked O.
0 and the drain control valve 2 of the second clutch 12
Enter into 20. drain control of the second clutch 12;
Since the spool of the valve 220 is in the left position indicated by diagonal lines, the input hydraulic pressure is output to the oil passage 1100 marked with an O mark, and is transmitted to the small servo 12 of the second clutch 12 via the oil passage 1120.
energize s. This oil pressure is applied to the second
input to the first valve 230 of the clutch's accumulator relay. Second clutch accumulator relay first valve 2
Since the spool 30 is in the left position, the input hydraulic pressure is sent to the accumulator 52 for the second clutch via the oil path 1200, and the accumulator control shown in FIG. By controlling the back pressure by the valve 440, it is controlled to have an appropriate pressure increase characteristic.

Since the spool is in the right position, the hydraulic pressure input to the 2-3 shift valve 120 via the oil passage 1030 is not output to the oil passage 1300, and therefore the small servo 13S of the third clutch 13 is not energized. .

Due to the above action, the second clutch 12 is engaged and the second clutch 12 is engaged.
speed is achieved. Note that in the second speed, the first clutch 11 is also engaged, but a description of its operation will be omitted.

Third gear is achieved by releasing the second clutch 12 and engaging the third clutch 13, so in 2-3 gear shifting, the second clutch 12 is released and the third clutch is engaged. It is necessary to switch the engagements of 13 at the same time.

Next, the operation during the 2-3 gear shift will be explained with reference to FIG.

As shown in Table 1, in the 2-3 gear shift state, the solenoid valve 41 is turned off, the solenoid valve 42 is turned off, and the solenoid valve 43 is turned on.

When the solenoid valve 41 is turned off, the output of the signal hydraulic pressure to the oil passage 410o is cut off, and the spool of the accumulator relay second valve 240 of the second clutch 12 is activated by the force of a spring (not shown) disposed in the lower oil chamber. This results in the left position shown by diagonal lines. 3-4 from the solenoid valve 42 through the oil passage 4200 marked with 0 in order to turn off the solenoid valve 42.
Since a signal is output to the upper oil chamber of the shift valve 130, 3
The spool of the -4 shift valve 130 overcomes the force of a spring (not shown) provided in the lower oil chamber and assumes the right position indicated by diagonal lines.

Then, the line pressure input from the oil passage 3000 marked with Δ is output to the oil passage 3010 through the 3-4 shift valve 130, and is output to the oil passage 3010 through the furnace passages 3300 and 3320 to the accumulator relay No. 1 of the second clutch 12. 2 valve 240.

Accumulator relay second valve 24 of second clutch 12
The line pressure input to 0 is oil line 3 marked with Δ.
400 and input to the accumulator relay first valve 230 of the second clutch 12 via the oil path 3420,
Overcoming the force of a spring (not shown) installed in the lower oil chamber, the spool is moved to the right position shown by diagonal lines. By changing the position of the spool, the small servo 1 of the second clutch 12
The oil passage 120o leading to the accumulator 52 for the second clutch 12 is cut off from the oil passage 1140 of the 2S,
The oil passage 1140 is closed by the spool of the valve 230 and the pressure within the accumulator 52 is drained.

Accumulator relay second valve 24 of second clutch 12
The hydraulic pressure output from 0 to the oil path 3400 is input to the drain control valve 260 of the third clutch 13 via the oil path 3440 marked with Δ, and the spool is input to the oil path 132 indicated by diagonal lines.
0 is in a locked state at the position where it communicates with the oil passage 1300, and the function as a pressure regulating valve is stopped.

When the solenoid valve 43 is turned on, the output of the signal hydraulic pressure to the oil passage 4300 is cut off. 2-3 due to the loss of input of the signal oil pressure sent via the oil path 4310.
The spool of the shift valve 120 is moved to the left position indicated by diagonal lines by the force of a spring (not shown) disposed in the lower oil chamber. Then, the oil pressure in the oil passage 1000 is output to the oil passage 3000 through the 2-3 shift valve 120 and input to the 3-4 shift valve 130. The input oil pressure is output to the oil passage 3010, returns to the 2-3 shift valve 120 via the oil passage 3020, and is output to the oil passage 1040 marked with Δ.

The oil pressure in the oil passage 1040 is input to the drain control valve 220 of the second clutch 12. Similarly, since the signal oil pressure input to the oil passage 4320 is no longer input, the spool of the second clutch accumulator relay valve 280 is moved to the left position shown by diagonal lines by the force of a spring (not shown) disposed in the lower oil chamber. Become.

During the 2-3 gear shift, the solenoid valve 45 functions as a duty-controlled linear solenoid valve, and outputs the controlled signal oil pressure to the oil path 4500 marked with an X. This signal oil pressure is transmitted to the second oil pressure via the oil passage 4530. is input to the upper oil chamber of the control valve 250 of the third clutch, and the control valve 250
The spool is moved to the right position shown by diagonal lines by overcoming the force of a spring (not shown) installed in the lower oil chamber.

Then, the line pressure that has been input into the lower oil chambers of the drain control valve 220 of the second clutch 12 and the drain control valve 260 of the third clutch 13 is drained via the oil passages 2520, 2530, and 2540. In addition, the signal oil pressure output from the linear solenoid valve 45 is transmitted through the oil path 4550,
4510 to the control valve 220 of the second clutch 12, and adjust this valve by moving the spool of the control valve 220 of the second clutch 12 to any position between the left position and the right position shown by diagonal lines. Function as a pressure valve. Note that a spring (not shown) is disposed between the spool of the drain control valve 220 of the second clutch 12 and the plunger. As a result, the hydraulic pressure is drained and controlled by the near solenoid valve 45 that energizes the small servo 12S of the second clutch 12 via the oil passages 1100 and 1120 marked with black circles. At this time, the accumulator relay first valve 230 of the second clutch 12 disposed between the oil passage 114o and the oil passage 1200 is in a cutoff state, and the accumulator relay 5
The oil passage 1200 from 2 leads to the drain, and the oil passage 11
40 is closed by the spool of the first valve 230 of the accumulator relay.

On the other hand, the oil passages 1000 and 1030 marked with O are
The D range oil pressure input to the -3 shift valve 120 is output to an oil path 1300 marked with an O mark, and is sent to the drain control valve 260 of the third clutch 13. The oil pressure that has passed through the drain control valve 260 of the third clutch 13 in the locked state energizes the small servo 13S of the third clutch 13 via the oil passage 1320. This oil pressure is applied to the accumulator relay first valve 2 of the third clutch 13 via an oil passage 1360.
70, and the hydraulic pressure that has passed through this valve is sent to the accumulator 53 for the third clutch 13 via an oil passage 1380, and is controlled to have an appropriate pressure increase characteristic.

Next, the control action will be explained.

When receiving the 2-3 speed change command, the linear solenoid valve 45
sends a signal hydraulic pressure for pressure regulation to the drain control valve 220 of the second clutch 12, drains the hydraulic pressure of the servo 12S, and puts the second clutch 12 into a slight slip state. At this time, if the hydraulic pressure supply to the servo 13 of the third clutch 13 is not completed and the third clutch 13 has not started torque transmission, both the second clutch 12 and the third clutch 13 will be in the disengaged side. The state is as follows. When both clutches are released, the engine returns to 1st gear, so the input rotational speed tends to increase.

Therefore, while monitoring this rotation speed change, the linear solenoid valve 45 controls the signal oil pressure to maintain the slip state of the second clutch 12.

When the third clutch 13 starts transmitting torque, a shift to third gear begins, and the input rotational speed tends to decrease. This rotational change is detected and the second clutch is rapidly released to
The shift to the next speed is completed.

In the present invention, the clutch on the release side is directly controlled by the linear solenoid valve 45 so as to tilt to the far side, thereby achieving smooth and simultaneous switching of the latch.

When shifting from 3rd speed to 2nd speed, the second clutch 12 is on the engagement side, the third clutch 13 is on the release side, and the accumulator relay first valve 270 drains the pressure in the accumulator 52. The other control means are the same as those for the 2-3 speed shift, so the explanation will be omitted.

[Effects of the Invention] According to the present invention, the shift control means
, the first control means controls the spools of the first and second adjustment mechanisms disposed between the shift control means and the first and second hydraulic servos, respectively, using a hydraulic signal. Since the hydraulic servo and the second hydraulic servo selected by the shift control means are respectively positioned at the first position, the hydraulic power source communicates with only one of the first hydraulic servo and the second hydraulic servo selected by the shift control means, and selectively connects both hydraulic servos. and selectively engages the frictional engagement element provided with the hydraulic servo.

Therefore, when an automatic transmission shifts up, for example, when the gear is at a lower speed, the frictional engagement element equipped with the first hydraulic servo is engaged, and when the gear is shifted to a higher gear, the friction engagement element equipped with the second hydraulic servo is engaged. Accurate gear shifting occurs when the first hydraulic servo is drained by engaging the friction engagement device.

In the present invention, the shift control means includes a third communication means for communicating both the first and second hydraulic servos with the hydraulic power source, and the first communication means is switched to the third communication means. When the first control means is switched, the first control means outputs a pressure signal to the first and second adjustment mechanisms in synchronization with this switching to bias the spools of these mechanisms in a direction to position the spools of these mechanisms in the second position. In addition, the second control means outputs a signal for switching the switching valve to the cutoff position and a signal for holding the spool of the second adjustment mechanism in the first position in synchronization with the switching, thereby controlling the second adjustment. a spool of the mechanism is held in the first position against a pressure signal from the first control means, thereby causing a second hydraulic servo to communicate with a hydraulic source to reduce the internal pressure of the second hydraulic servo; The pressure is increased quickly, and the communication path between the first hydraulic servo and the first pressure regulating mechanism is blocked by blocking it, and the regulated pressure signal output from the first control means is applied. The pressure oil in the blocked first hydraulic servo is drained into the drain passage through the spool, while the pressure oil supplied from the hydraulic source through the shift control valve is drained through the spool into the first hydraulic servo. The pressure drop within the first hydraulic servo is controlled by a regulated pressure signal output from the first control means.

Therefore, the engagement of the frictional engagement element with the second hydraulic servo takes place quickly, and the release of the frictional engagement element with the first hydraulic servo is effected by an adjustable pressure signal of the first control means. Since the adjustment is performed in a controlled manner, it is possible to avoid an interlock state or a neutral state of the gear train of the automatic transmission, and the first hydraulic servo is closed by a switching valve and isolated from the first pressure regulating mechanism. Therefore, pressure changes within the first hydraulic servo do not interfere with or affect the pressure of the second pressure regulating mechanism or hydraulic control device circuit attached to the second hydraulic servo.

Moreover, according to the present invention, one first control means can extremely smoothly engage one of the two frictional engagement elements and release the other at the same time. Particularly in multi-speed automatic transmissions with five or more speeds, the need for simultaneous control of multiple frictional engagement devices increases, so the number of parts can be reduced and control can be performed easily. This has great effects.

Therefore, according to the present invention, a hydraulic control device for an automatic transmission that achieves multiple gears of five or more gears can be configured compactly and lightweight.

[Brief explanation of drawings]

FIG. 1 shows the main parts of the hydraulic control device of the present invention, and 2
2 is a circuit diagram showing the flow of oil pressure when the speed is 2-3. FIG. 3 is an explanatory diagram showing the skeleton of an automatic transmission implementing the present invention. FIG. 4 is a circuit diagram showing the entire hydraulic control device of the present invention. 11...First clutch (first clutch hydraulic servo) 12...Second clutch 12S...Second clutch small servo 12L.
...Second clutch large servo 13...
Third clutch 13S...Third clutch small servo 13L.
...Third clutch large servo 14...
Fourth clutch (hydraulic servo of the fourth clutch) 21...First brake 21A...First servo 21 of the first brake
B... Second servo 21R of the first brake.
...First brake return servo...
-First one-way clutch 2...Second one-way latch...Second solenoid valve 2...Third solenoid valve 3... First solenoid valve 4...Fourth solenoid valve 5...For linear solenoid valve) 6...For linear solenoid valve control) oO...Manual valve 10...1-2 Shift valve 20...2-3 Shift valve 30...3-4 Shift valve 40...4-5 Shift valve 6o. ... Reverse control valve 10 ... First clutch 1 valve (orifice control of first brake control (lockup control 220 ... Drain control valve 230 of second clutch 12) ...Accumulator relay first valve 240 of second clutch 12 ...Accumulator relay second valve 250 of second clutch 12 ...Second and third clutches 12 .13 control valve 260... Drain control valve 270 of third clutch 13... Accumulator relay first valve 280 of third clutch 13... Third clutch 13 accumulator relay second valve 290...Fourth clutch 14 modulator valve 300...Large piston relay valve 310...
...Control first valve 320 of the first brake 21...
...Control second valve 330 for the first brake 21...
・Release relay valve 340 of the first brake 21...Relay valve 35 of the first brake 21
0...Modulator valve O of the second brake 22
... Solenoid relay valve O ... Primary regulator valve O ...
・Secondary regulator valve O...Lock-up relay valve 0...Accumulator control valve 0...Lock-up control valve 0...Cutback valve

Claims (1)

[Scope of Claims] A transmission having a plurality of rows of planetary gear sets, a frictional engagement element that achieves engagement and disengagement of elements of the planetary gearset, and a hydraulic servo that operates the frictional engagement element. A hydraulic control device for an automatic transmission having means for controlling pressure oil supplied to the hydraulic servo, comprising first and second hydraulic servos, and a first hydraulic servo that selectively connects the first hydraulic servo to a hydraulic power source. a second communication means for selectively communicating the second hydraulic servo with a hydraulic power source; and a third communication means for communicating both the first and second hydraulic servos with a hydraulic power source. a first position that is disposed between the first hydraulic servo and the shift control means and communicates the first hydraulic servo with the shift control means; a first adjustment mechanism provided with a spool that is movable between a second position for communicating the hydraulic servo with the drain passage; and a first adjustment mechanism disposed between the second hydraulic servo and the shift control means. , a spool that is movable between a first position where the second hydraulic servo is communicated with the shift control means and a second position where the second hydraulic servo is communicated with the drain passage. a first pressure regulation mechanism communicated with the first hydraulic servo; a second pressure regulation mechanism communicated with the second hydraulic servo; and the first and second adjustment mechanisms. the respective spools of the first and second adjustment mechanisms in a direction to position the respective spools of the first and second adjustment mechanisms in respective first positions when the shift control means is switched to the first and second communication means; A hydraulic signal for energizing is output to the first and second adjustment mechanisms, and when the shift control means is switched to the third communication means, the first and second adjustment mechanisms are synchronously a first control means for outputting an adjustable pressure signal to the first and second adjustment mechanisms to bias each spool in a second position; and the first hydraulic servo. a communication position disposed between the first pressure regulating mechanism and the first hydraulic servo communicating with the first pressure regulating mechanism, and a communication position disposed between the first hydraulic servo and the first pressure regulating mechanism; and a communication position disposed between the first hydraulic servo and the first pressure regulating mechanism; a switching valve that is connected to the switching valve and the second adjustment mechanism, and when the shift control means is the first and second communication means; outputting a signal to set the switching valve to the communication position, and when the shift control means is switched to the third communication means, a signal for switching the switching valve to the cutoff position in synchronization with the switching, and a signal for switching the switching valve to the blocking position; A hydraulic control device for an automatic transmission, comprising a second control means for outputting a signal for holding a spool of the mechanism at the first position.