JPS61286665A - Direct-coupled mechanism controlling method of hydraulic power transmission device in automatic transmission for vehicles - Google Patents

Abstract

PURPOSE:To make a comfortable drive feeling securable, by comparing the measured value of a parameter showing slippage in an input-output member of a hydraulic power transmission device with a reference range value at every specified period, which controlling the transmission capacity of direct coupling clutch at the next specified period. CONSTITUTION:A velocity ratio (e) or a parameter showing relative slippage in an input-output member of a hydraulic power transmission system is measured at every specified period and compared with each of discriminating values e1-e4 conformed to a driving mode. When a fact that the velocity ratio (e) exists in what zone in regard to the transmission capacity of a direct coupling clutch is discriminated, the transmission capacity of the direct coupling clutch is increased at every specified period as much as the increment set at the zone. At this time,the increment of the transmission capacity per specified time is reducing as it approaching to a reference range value, so that the transmission capacity of the direct coupling clutch comes to be approximated to the reference range value stably and speedily in consequence, thus a comfortable drive feeling is securable.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a method for controlling a direct coupling mechanism of a fluid power transmission device for an automatic transmission for a vehicle.

(Prior art and its problems) In general, vehicles equipped with automatic transmissions use a fluid power transmission device, such as a fluid torque converter, to provide sufficient driving force and a smooth and easy driving feeling with a small number of gears. On the other hand, practical fuel efficiency is poor due to fluid immersion loss in the torque converter, and the engine rotational speed increases due to the fluid slippage, making the operation louder and less quiet.

For this reason, when it is no longer possible to expect the torque amplification function of a torque converter, the torque converter
A direct-coupling clutch mechanism (hereinafter referred to as a "direct-coupling mechanism") called a so-called lock-up mechanism that mechanically couples output members to improve power transmission efficiency has been developed and has already been put into practical use. Since favorable effects can be obtained from improvements in power transmission characteristics and fuel efficiency, it is desirable to operate the direct coupling mechanism from as low a speed as possible. However, if the torque converter is completely directly connected in the low-speed operating range where the engine speed is also low, there are drawbacks such as large fluctuations in engine torque, which may cause vibration and noise in the vehicle body, or deteriorate driving performance. .

Therefore, instead of directly connecting the torque converter in such a low-speed operating range, for example, the rotational speed of the input member and output member of the torque converter should be Calculate the ratio e or slip ratio (=1-〇), etc., and in the above low-speed operation range, the rotation speed ratio e is 1 or the slip ratio is O.
The transmission capacity of the direct coupling mechanism is controlled by adopting the optimum transmission capacity from among the plurality of transmission capacities (engaging forces) of the direct coupling mechanism while feeding back the actual measured value of the rotational speed ratio e or slip ratio so as to avoid this. It is possible that

However, when such a control method is implemented, the following problems occur. That is, for example, in an embodiment of the present invention to be described later, the transmission capacity is the maximum capacity of the control system when the electromagnetic valve that controls the transmission capacity is off, that is, when the valve is closed.

) is set relatively weakly, the control is performed smoothly and no vibration or noise is generated in the vehicle body, but fuel efficiency deteriorates.On the other hand, in order to improve fuel efficiency, the transmission capacity is set relatively weakly. When set relatively strongly, the rotation speed ratio e sometimes becomes 1.
, or the slip ratio approaches O, or the rotational speed ratio e=1 or the slip ratio becomes -0, causing vibrations and noise in the vehicle body.

This is because no matter how electronic control technology is used, calculating the rotational speed ratio e or slip ratio takes a certain amount of time, including data sampling time, and the feedback system includes mechanical parts such as hydraulic equipment. , there is a physical limit to the response time of the control system that cannot be accelerated beyond a certain value, but if the transmission capacity is set to be strong, the transition to the direction of direct coupling (increasing the transmission capacity) is possible. As the speed increases, there is a delay in control and the rotational speed ratio e or slip ratio exceeds the standard range value, and in order to reflect this result and return it to the standard range value, the transmission capacity is increased more than necessary. Since control is started to decrease the rotational speed ratio e or the slip ratio, the rotational speed ratio e or the slip ratio decreases again to be below the reference range value, which is repeated, and in the worst case, it diverges.

Note that if the response time of the entire control system is shortened, there is no risk of the above-mentioned problem occurring even when the transmission capacity is set to be strong, but in reality, there is a limit to the shortening of the response time.

(Object of the Invention) The present invention has been made in view of the above circumstances, and is an operating range in which it is necessary to accurately control the transmission capacity without causing divergence even when the transmission capacity of the direct coupling mechanism is set to be strong. We control this to the optimum value to suppress vehicle body vibration and noise, as well as improve fuel efficiency and power transmission characteristics.
Another object of the present invention is to provide a direct-coupling mechanism control method for a fluid power transmission device of an automatic transmission for a vehicle, which allows an extremely smooth and comfortable driving feeling to be obtained.

(Means for Solving the Problems) In order to solve the above-mentioned problems, in the present invention, predetermined values of predetermined parameter values representing the relative slip amounts of the output member and the output member of the hydraulic power transmission device are set in advance. The transmission capacity of the direct coupling mechanism for a predetermined period to be implemented from now on is determined based on the comparison result.

(Example) An embodiment of the present invention will be described in detail below with reference to the accompanying drawings.

FIG. 1 shows an outline of a vehicle automatic transmission to which the present invention can be applied, in which the output of the engine E is transmitted from its crankshaft 1 to a torque converter T as a fluid power transmission device, an auxiliary transmission M, and a differential device Df. The diameter of the left and right drive wheels w, w'
and drive them.

The torque converter T includes a pump impeller 2 which is an input member connected to a crankshaft 1, a turbine impeller 4 which is an output member connected to an input shaft 3 of an auxiliary transmission M, and a rotatable member on the input shaft 3. The stator wheel 5 is connected to a stator shaft 5a supported by a stator shaft 5a via a one-way clutch 6. The torque transmitted from the crankshaft 1 to the pump wheel 2 is hydrodynamically transmitted to the turbine wheel 4, and when the torque is amplified during this time, the stator wheel 5 acts as a reaction force. bear the burden.

A pump drive gear 7 for driving the hydraulic pump P shown in FIG. 2 is provided at the right end of the pump impeller 2, and a stator shaft 5a
A stator arm 5b that controls the regulator valve Vr shown in FIG. 2 is fixed to the right end of the stator arm 5b.

A roller-type direct coupling clutch Cd is provided between the pump impeller 2 and the turbine impeller 4 as a direct coupling mechanism capable of mechanically coupling these. To explain this in detail with reference to FIGS. 2 and 3, an annular drive member 9 having a drive conical surface 8 on the inner circumference is spline-fitted to the inner peripheral wall 2a of the pump impeller 2.

Further, an annular driven member 11 having a driven conical surface 10 facing parallel to the driving conical surface 8 on its outer periphery is spline-fitted to the inner circumferential wall 4a of the turbine impeller 4 so as to be slidable in the axial direction. . A piston 12 is integrally formed at one end of this driven member 11, and this piston 12 is slidably engaged with a hydraulic cylinder 13 provided on the inner circumferential wall 4a of the tarpit wheel 4.
The internal pressure of the cylinder 13 and the internal pressure of the torque converter T are simultaneously received on both left and right end surfaces.

A cylindrical clutch roller 14 is interposed between the driving and driven sickle surfaces 8 and 10, and this clutch roller 14
As shown in the figure, the annular glue retainer 15 is arranged so that its central axis 0 is inclined at a constant angle θ with respect to the generatrix g of the virtual conical surface 1c (see FIG. 2) passing through the center between the hundred conical surfaces 8 and 10. Retained.

Therefore, when a hydraulic pressure higher than the internal pressure of the torque converter T is introduced into the hydraulic cylinder 13 at a stage when the torque amplification function of the torque converter T is no longer required, the piston 12, that is, the driven member 11 is pushed toward the drive member 9. Ru. As a result, the clutch roller 14 is pressed against both conical surfaces 8 and 10. At this time, when the driving member 9 is rotated in the X direction in FIG. 3 with respect to the driven member 11 by the output torque of the engine E, the clutch roller 14 rotates. Since 0 is tilted as described above, its rotation imparts a relative axial displacement to both members 9.11 that brings them closer together. As a result, the clutch roller 14 has a hundred conical surfaces 8, 10
It bites in between the two members 9 and 11, that is, the pump wheel 2 and the turbine wheel 4 to be mechanically connected. Even during such operation of the direct coupling clutch Cd, if the output torque of the engine E exceeds the coupling force and is applied between the wing wheels 2 and 4, the clutch roller 14 will slip against each conical surface 8.10. The above torque is divided into two parts, and a part of the torque is transmitted mechanically through the direct coupling clutch Cd, and the remaining torque is transmitted hydrodynamically from the pump wheel 2 to the turbine wheel 4. , the ratio of the former torque to the latter torque changes depending on the degree of slippage of the clutch roller 14.

If a reverse load is applied to the torque converter T in the operating state of the direct coupling clutch Cd, the rotational speed of the driven member 11 becomes greater than the rotational speed of the driving member 9, so that the driving member 9 relatively On the other hand, the clutch roller 14 rotates in the Y direction in FIG. 3, and as a result, the clutch roller 14 rotates in the opposite direction to the previous direction, giving a relative axial displacement to both members 9 and 11 to separate them from each other. . the result,
The clutch roller 14 is released from being wedged between the 100-conical surfaces 8 and 10 and enters an idling state. The transmission of the reverse load from the turbine wheel 4 to the pump wheel 2 therefore takes place only hydrodynamically.

When the hydraulic pressure of the hydraulic cylinder 13 is released, the piston 12 receives the internal pressure of the torque converter T and retreats to its initial position, so that the direct coupling clutch Cd becomes inactive.

In FIG. 1 again, the auxiliary speed change vIAM is parallel to each other, and between the output shafts 3 and 16 are the first speed gear train G1, the second speed gear train G2, the third speed gear train G3, and the fourth speed gear train. G4 and reverse gear train Gr are provided in parallel. 1st speed gear train G1
A drive gear 17 is connected to the input shaft 3 via a first speed clutch C1, and a one-way latch C is meshed with the gear 17 and attached to the output shaft 16.

and a driven gear 18 that can be connected via. The second speed gear train G2 consists of a driving gear 19 that can be connected to the input shaft 3 via a second speed clutch C2, and a driven gear 20 that is fixed to the output shaft 16 and meshes with the gear 19. The third speed gear train G3 consists of a driving gear 21 fixed to the input shaft 3, and a driven gear 22 connected to the output shaft 16 via a third speed clutch C3 and capable of meshing with the gear 21. Also the fourth
The speed gear train G4 is connected to the input shaft 3 via the fourth speed clutch C4.
The drive gear 24 is connected to the output shaft 16 via a switching clutch Cs and meshes with the gear 23. Further, the reverse gear train Gr includes a driving gear 25 provided integrally with the driving gear 23 of the fourth speed gear train G4, a driven gear 26 connected to the output shaft 16 via the switching clutch Cs, and both gears 25. .26 and an idle gear 27 that meshes with the gear. The switching clutch Cs is
By shifting the selector sleeve S of the clutch Cs, which is provided between the driven gear 24 and the idle gear 27 of the fourth speed gear train G4, to the forward position on the left or the reverse position on the right in FIG. Driven gear 24 and idle gear 27
can be selectively coupled to the output shaft 16. One-way clutch Co transmits only drive torque from engine E to drive wheels w, w', and does not transmit torque in the opposite direction.

Thus, when the selector sleeve S is held in the forward position as shown in FIG. A gear train G1 is established, and torque is transmitted from the input shaft 3 to the output shaft 16 via this gear train G1. Next, the first
While the speed clutch C1 remains connected, the second speed clutch C2
When connected, the drive gear 19 is connected to the input shaft 3 to establish the second speed gear train G2, and torque is transmitted from the input shaft 3 to the output shaft 16 via this gear train G2. At this time, the first speed clutch C1 is also engaged, but due to the action of the one-way clutch Co, the first speed is not established, but the second speed gear train G2 is established, which is connected to the third and fourth speeds. The same goes for when. Release the second gear clutch C2 and apply the third gear clutch C3.
When the driven gear 22 is connected to the output shaft 16, the third speed gear train G3 is established, and when the third speed clutch C3 is released and the fourth speed clutch C4 is connected, the driven gear 22 is connected to the output shaft 16 and the third speed gear train G3 is established. 23 is connected to the input shaft 3 and the fourth speed gear train G4
is established. Furthermore, if the selector sleeve S of the switching clutch Cs is moved to the right in FIG. The reverse gear train Gr is established, and the input shaft 3 is connected to the output shaft 1 via this gear train Gr.
Reverse torque is transmitted to 6.

The torque transmitted to the output shaft 16 is transmitted from the output gear 28 provided at the end of the shaft 16 to the large diameter gear DG of the differential device Df. One end of a speedometer cable 30 is fixed to the gear 29 meshing with the gear Ds fixed to the gear DG, and the speedometer 3 is connected to the other end of the speedometer cable 30 via a magnet 31a of a vehicle speed detector 31.
2 is connected, and the speedometer 32 is connected to the gear Ds, 29
and a cable 30 to display the vehicle speed.

The vehicle speed detector 31 includes the magnet 31a and a reed switch 31b, for example, which is driven by the magnet 31a.
1b is opened and closed, and on and off signals accompanying this opening and closing are supplied to an electronic control device 33, which will be described later.

FIG. 2 shows a hydraulic control circuit for a vehicle automatic transmission to which the present invention is applied.

In the figure, a hydraulic pump P whose suction port is connected to an oil tank R is connected via an oil path 300 to an inlet boat 60a of a regulator valve Vr, a pilot pressure introduction port 60b, and a boat 70 of a manual shift valve (hereinafter simply referred to as a manual valve) Vm.
b and the inlet boat 80a of the governor valve Vg, respectively. The boats 70a and 70c of the manual valve Vm are connected to the boats 9 of the servo piston 90 via oil passages 301 and 302, respectively.
0c.

90b, the boat 70c is further connected to the boat 70d of the manual valve Vm and the inlet boat of the pressure reducing valve 270 via the oil passage 303).
270a and the boat 100a of the throttle valve Vt, and the boat 70e is connected to the boat 70g of the manual valve Vm, the boat 210d of the timing valve 210, the boat 170a of the first accumulator 170, and the second speed clutch C2 via an oil path 304, respectively. Connected. Also, manual valve Vm
The boat 70f is connected to the boat 130b of the second shift valve 2 via an oil passage 305 in which a throttle 350 and a one-way valve 380 are connected in parallel, and the boat 70h is connected to a throttle 3 in the middle.
59 and a one-way valve 383 are respectively connected to the first speed clutch C1 via oil passages 313 provided in parallel. nuclear oil road 3
Two inlet boats 400a and 400b of a flow rate regulating valve 400 are connected to 13 via an oil passage 307 provided with a throttle 369, and one outlet boat 400 of the flow rate regulating valve 400 is connected to
d is the bow of the first shift valve v1 via the oil passage 307a)
120b. A throttle 370 is interposed between the first inlet port 400a of the flow rate regulating valve 400 and the oil passage 307.

The boat 70i of the manual valve Vm is connected to the boat 90a of the servo piston 90 via an oil path 308, and the boat 70 of the timing valve 210 is connected to the boat 90a of the timing valve 210 via an oil path 309.
, the boat 70m is connected to the boat 190a of the second accumulator 190 and the fourth speed clutch C4 via the oil passage 310 to the port 70n1 of the manual valve Vm and the second shift valve V2.
boat 13Qd, and boat 13Qd of the first control valve 160)
60b, respectively. A throttle 356 and a one-way valve 381 are arranged in parallel with each other between the oil passage 310 and the boat 130d of the second shift valve v2.

Boat 100b with throttle opening response valve V.t.

and 100C are connected to each of the first to third accumulators 170, 190, and 180 via the oil passage 311) 170b,
190b, 180b, boat 2 of modulator valve 220
20f, boat 230c of on-off valve 230, boat 400c of flow rate regulating valve 400).

A throttle 352 is connected to the boat 160a of the first control valve 160 and the boat 200a of the second control valve 200, and is interposed between the boat 100b of the throttle opening responsive valve Vt and the oil passage 311. be done. Throttle opening response valve Vt
The boat 100d is connected to the boat 130g of the second shift valve v2 and the drain EX through an oil passage 312, and a throttle 353 is interposed between the oil passage 312 and the drain EX. The bow 110a of the third control valve 110 is the oil passage 3
15 to the bow) 120a of the first shift valve v1 and the drain EX, respectively, and the oil passage 315 and the drain EX
A diaphragm 354 is interposed between the two.

Boats 120c, 120 of first shift valve v1
d are connected to the second shift valve v via oil passages 316 and 317, respectively.
The boat 120e is connected to the second boat 130a, 130c through the oil passage 318 to the boat 160c of the first control valve 160.
and a drain EX, and a throttle 355 is interposed between the oil passage 318 and the drain EX. The boat 130e of the second shift valve v2 is connected to the boat 200c of the second control valve 200 and the drain EX via an oil passage 319, and a throttle 357 is connected between the oil passage 319 and the drain EX.
is interposed. The boat 130f of the second shift valve v2 is connected to the boat 20 of the second control valve 200 via an oil passage 320 in which a throttle 358 and a one-way valve 382 are connected in parallel.
0 b, baud of third accumulator 180) 180a
and third speed clutch C3. In addition, the second
A throttle 356a is interposed in one of the two EX ports of the shift valve (2).

The bow) 120f of the first shift valve v1 is connected to the inlet port) 140a of the first solenoid valve 140 via an oil passage 340, and the oil passage 340 is connected to the pressure reducing valve 270 via an oil passage 341 provided with a throttle 361. output bow) 270b. The second shift valve ■2 boat 130h has an oil passage 322a
The oil passage 322a is connected to the inlet port 150a of the second solenoid valve 150 through the throttle 362, and the oil passage 322 is connected to the outlet boat 80b of the governor valve Vg. Ru.

Each valve body 1'41 of the first and second solenoid valves 140, 150
, 151 are pressed by the spring force of springs 143 and 153 when the solenoids 142 and 152 are deenergized (off) to close the large openings 140a and 150a, and when the solenoids 142 and 152 are energized (on), the spring force is applied. 140a.

150a is opened. Hit, first and second solenoid valve 14
0 and 150 are closed when the solenoids 142 and 152 are deenergized, and opened when the solenoids are energized.

The outlet boat 60C of the regulator valve Vr is connected to the boat 210a of the timing valve 210 and the on-board via the oil passage 325.
They are connected to the boats 230d of the off valves 230, respectively. The boat 210b of the timing valve 210 has a throttle 371 in the middle.
The boat 210c is connected to the boat 220a of the modulator valve 220 via an oil path 327, and the boat 210c is connected to the boat 220a of the modulator valve 220 via an oil path 327.
Of is connected to the oil passage 501 through an oil passage 501a provided with a throttle 375 in the middle. Boat 1-220b of the modulator valve 220 is connected to the oil passage 326 via an oil passage 326a provided with a throttle 372 in the middle, and the boat 220
c is the flow of the on-off valve 230 through the oil passage 353 with a throttle 373 in the middle;
e are connected to oil passages 322 each having a throttle 366a in the middle. The boat 230a of the on-off valve 230 is connected to the oil line 3
26, the boat 230e is connected to the oil passage 334 via an oil passage 501 having a throttle 374 in the middle.

The third solenoid valve 2400Å mouth boat 240a has an orifice 367
It is connected to the oil passage 326 via. This third solenoid valve 2
When the solenoid 242 is deenergized (off), the valve body 241 of 40 is pressed by the spring force of the spring 243, and the valve body 241 of the inlet boat 2
40a is closed, and when the solenoid 242 is energized (on), it is attracted against the spring force and opens the inlet port 240a. That is, the third solenoid valve 240 is closed when the solenoid 242 is deenergized, and opened when the solenoid 242 is energized.

The boat Ta of the torque converter T is connected to the oil passage 325 through the oil passage 334 provided with the throttle 368, the boat Tb is connected to the oil passage 326, and the boat Tc is connected to the pressure holding valve 2 through the oil passage 335.
50 inlet bow) 250a. This pressure holding valve 2
The 50 pilot pressure introduction boats 250b are connected to the upstream side of the throttle 366a of the oil passage 322 via the oil passage 336, and the outlet boat 250c is connected to the drain EX via the oil passage 337 and the oil cooler 260, respectively. Each drain EX is connected to an oil tank R, respectively.

Each solenoid 142, 152, 242 of the first to third solenoid valves 140, 150, 240 is connected to a signal line 142a, 1
It is connected to the electronic control device 33 via 52a and 242a, respectively. The electronic control device 33 operates in accordance with a predetermined shift map based on input signals from a vehicle speed detector 31, an engine speed detector 34, a gear position detector 35, etc.
Then, the second solenoid valves 140 and 150 are controlled to control the engagement and disengagement (disengagement) of the first to fourth gear clutches C1 to C4, thereby controlling the speed change. Further, the electronic control device 33 actually measures a predetermined parameter value representing the relative slip amount of the output member of the torque converter T, for example, the speed ratio e, and compares the measured value e with a predetermined reference value, Based on the comparison result, the engagement force (transmission capacity) of the direct coupling clutch CdO is determined and the third solenoid valve 240 is controlled to control the direct coupling clutch CdO.
O Controls the engagement force.

The operation of the above-mentioned hydraulic circuit will be explained below.

The hydraulic pump P sucks and pressurizes the hydraulic oil in the oil tank R, regulates the pressure to a predetermined pressure (hereinafter referred to as line pressure pz) with the regulator valve Vr, and then pumps it to the oil path 300. The stator arm 5b (see Fig. 1) is in contact with the spring receiver 61 of the regulator valve Vr, and when the reaction force of the stator wheel 5 of the torque converter T exceeds a predetermined value, the spring 62 is compressed and the hydraulic pump P Increase the discharge pressure. Such hydraulic control is detailed in Japanese Patent Publication No. 45-30861. A part of the hydraulic oil whose pressure is regulated by the regulator valve Vr is sent into the torque converter T through an inlet oil passage 334 having a throttle 368, and after pressurizing the inside of the torque converter T to prevent cavitation. The oil is returned to tank R via pressure valve 250 and oil cooler 260. In the pressure holding valve 250, as the vehicle speed U increases, the spool 251 moves to the right in the figure against the spring 252 due to the governor pressure Pc, and the internal pressure of the torque converter T is released to the oil tank R. That is, the pressure holding valve 250 works to lower the internal pressure of the torque converter T in proportion to the vehicle speed U, and since its spool 251 is operated by the differential pressure with the governor pressure Pc, the transmission capacity of the direct coupling clutch Cd increases. The maximum value of the transmission capacity of the direct coupling clutch Cd is increased on the high speed side.

The manual valve Vm is switched by manual switching operation of the shift lever, and is set to P (parking), R (reverse), N (neutral), D4 (4-speed forward automatic transmission), I)l (3-speed forward automatic transmission except TOP). ), 2 (2ND hold), and an operation mode corresponding to each shift position can be arbitrarily selected.

When the spool 71 of the manual valve Vm is in the illustrated N position, the boat 7ob connected to the oil passage 300 is blocked by the spool 71 of the manual valve Vm, and the other ports 70a, 70c to 70n are all connected to the drain EX. The four clutches C1 to C4 of the first to fourth speeds are all disengaged, so that the engine torque is not transmitted to the drive shafts W, W" (see FIG. 1).

When the spool 71 of the manual valve Vm moves one frame to the left from the illustrated position and is at the D4 position, both the oil passages 302 and 313 communicate with the oil passage 300, and pressure oil is supplied to the oil passage 30.
5,304 communicate with each other. Further, the oil passage 309 is communicated with the oil passage 310, but is isolated from the drain EX and the oil passage 308, respectively, and the oil passage 301 continues to communicate with the drain EX. As a result, in the D4 position (range), the servo piston 90 for moving the selector sleeve S (see Fig. 1) receives the line pressure PR in its spring chamber 92, and the spool 91 also receives the line pressure PR as shown in the figure. The selector sleeve S is held in the position shown in FIG. 1 by a shift shear 39 fixed to one end of the spool 91. As a result, the fourth speed driven gear 24 is switched to the switching clutch C.
3, the reverse driven gear 26 is rotatably placed.

From this state, even if the spool 7e of the manual valve Vm moves one frame to the left and is placed at the D3 position, the oil passage 310 is connected to the port 70m, ? The connection relationships of the respective oil passages connected to the manual valve Vm do not change except that they are connected to the drain EX via the On. These 2. D3. At the D4 position, pressure oil is sent to the throttle opening responsive valve Vt via the oil passage 303.

The throttle opening response valve Vt is a parameter representing the load of the engine E, and is proportional to the amount of depression of the throttle pedal (not shown), that is, the valve opening of the throttle valve (not shown) provided in the intake system of the engine E. The left spool 101 is moved to the left by receiving the displacement of the cam 104 which rotates counterclockwise from the illustrated position via the spring 103, and the port 10 is moved to the left.
0a to the open side, and the discharge pressure of its output port 100c,
Spool 1 in addition to boat 100b via aperture 352
01 to the right) 100a to the closing side, and generates a pressure (hereinafter referred to as throttle pressure pt) in the output oil passage 311 that is proportional to the opening degree of the throttle valve. In addition, the counterclockwise rotation of the cam 104 moves the right spool 102 to the left, continuously restricts the communication between the port 100d and the drain EX, and kicks down from 3rd speed (3RD) to 2nd speed (2ND). Alleviates the shock of shifting gears.

Cam 113 of third control valve 110 interlocking with cam 104
rotates counterclockwise in accordance with the opening degree of the throttle valve to move the spool 111 to the left against the spring force of the spring 112, continuously restricting the communication between the boat 110a and the drain EX, and Alleviates the shift shock when kicking down from TOP to 3RD. Further, the throttle pressure Pt is sent to the boat 400c of the flow rate regulating valve 400 via the oil passage 311 to control the valve 400. That is, when the flow rate adjustment valve 4QO is in the state shown in the figure, the flow rate adjustment valve 4QO flows from the oil passage 307 through only the first inlet boat 400a provided with the throttle 370, and from the outlet boat 400d through the oil passage 307a to the first shift valve 1. When the hydraulic pressure is sent to the boat 120b and the throttle pressure pt increases to overcome the force of the spring 402, the spool 401 moves to the left and passes through both the first and second inlet boats 400a and 400b, thereby opening the exit port. By increasing the amount of pressure oil supplied from the port 400d to the oil passage 307a, both clutches engage when the throttle valve opening is small (the two clutches engage together, and energy is consumed in both latches). In order to prevent the vehicle from slowing down and dropping below its previous speed, the system prevents the next clutch from being engaged until one clutch is completely disengaged. It alleviates the shock of downshifting when driving and stopping.

The discharge oil of the hydraulic pump P is at the inlet bow of the governor valve Vg) 80
a, the governor valve Vg is rotated by its own shaft 82 at a speed proportional to the vehicle speed by a gear 81 meshing with the large-diameter gear DG shown in FIG. A pressure proportional to (hereinafter referred to as governor pressure Pe) is output.

When the first shift valve (1) is in the first position shown, the input oil passage 307a is connected to the output oil passage 316, and another output oil passage 317 is connected to the drain EX via the oil passage 318. The valve body 121 of the first shift valve (1) is shifted to the first position by the spring 122. The first shift valve v1 has a line pressure P introduced from the pressure reducing valve 270 through the oil passage 341, the throttle 361, and the oil passage 340 into the chamber 120A, which its right end face faces.
Due to the hydraulic pressure reduced to a pressure lower than i, it can be moved to the left against the spring force of the spring 122 to take the second position, and when it is in the second position, the output oil passage 316 is drained via the oil passage 315. EX, and another output oil passage 317 is separated from the oil passage 318 and connected to the input oil passage 307a.

When the first shift valve v1 is in either the first or second position, the oil passage 313 is connected to the first speed (LOW) clutch C1, and therefore the manual valve Vm is in the D position.
When in the 3 or D4 position, the first speed clutch C1 is always pressurized and engaged. The spool 121 of the first shift valve v1 is controlled by a first solenoid valve 140, and when the solenoid valve 140 is closed, the pressure introduced into the chamber 120A causes the second position to be set to the second position, and when the solenoid valve 140 is opened, the spring 1
22 to assume the first position.

When the second shift valve 2 is in the first position shown, it blocks the input oil passage 316, connects the output port 130d to the drain EX, connects the input oil passage 317 to the output oil passage 305,
Further, the output oil passage 320 is connected to the drain EX via the oil passage 312. The spool 131 of the second shift valve ■2 is the spring 1
32 to the first position. This shift valve v2
is moved to the left against the spring force of the spring 132 by the governor pressure PG introduced from the boat 130h into the chamber 130A facing the right end surface of the spool 131 through the oil passage 322, the throttle 362, and the oil passage 322a, and is moved to the second position. and when in the second position, disconnect the chemical capo 13Qd from the drain EX and connect it to the input oil passage 316, connect the output oil passage 305 to the drain EX via the oil passage 319, The remaining output oil passage 320 is separated from the oil passage 312 and is connected to the input oil passage 3.
Switch connection to 17.

The spool 131 of the second shift valve V2 is controlled by a second solenoid valve 150, and when the solenoid valve 150 is closed, the second position is set by the governor pressure Pc introduced into the chamber 130A, and when the solenoid valve 150 is opened, the spool 131 is set to the second position by a spring. 132 to assume the first position.

Further, the second shift valve V2 is particularly provided with a click motion mechanism 133 so that its switching operation is performed in an on-off manner. This click motion mechanism 133
is the governor pressure Pc even when the second solenoid valve 150 is closed.
The spool position of the shift valve v2 is limited to either the first or second position in response to a change in the shift valve v2.

Now, as long as the engine E is rotating, the hydraulic oil pressurized by the hydraulic pump P is sent to the governor valve Vg.
g, the pressure is regulated as a signal pressure proportional to the vehicle speed U and guided to the chamber 130A of the second shift valve 2, and the pressure reducing valve 27
The pressure is reduced at 0 and guided to the chamber 120A of the first shift valve (1). Manual valve Vmi<04 (or D3)
position, these two shift valves 140, 15 are used to hold V2 in the first switching position shown.
It is only necessary to energize the respective solenoids 142 and 152 of 0 to open the valves. As a result, the clutches 02 to C4 of the second to fourth speeds are not pressurized, and the first speed clutch C1 is not pressurized.
The first speed reduction ratio is established. Since this first speed generally covers a low speed region, the governor pressure Pc itself is low pressure in this low speed region, and the second solenoid valve 150 is controlled via the throttle 362.
The loss flow rate of the pressure oil discarded from the tank R to the oil tank R is also reduced accordingly, which is economical. This point is when stalled (vehicle speed = 0)
The pressure of the entire system is reduced to the normal pressure level (such as when starting a car).
This is particularly advantageous if the line pressure P1) has to be maintained significantly higher.

Next, the solenoid 152 of the second solenoid valve 150 is energized to maintain the solenoid valve 150 in the open state, and the solenoid 142 of the first solenoid valve 140 is deenergized to keep the solenoid 150 open.
When the valve 0 is closed, hydraulic pressure reduced by the pressure reducing valve 270 is generated in the chamber 120A of the first shift valve V1, and this causes the spool 12 of the shift valve v1 to resist the spring force of the spring 122.
1 moves to the left. Due to this leftward movement of the spool 121, the oil path 3
07a is connected to the oil passage 305 via the oil passage 317, and the oil passage 305 is connected to the bow of the manual valve Vm when in the D4 position.
? Of, to the oil passage 304 via the notch 71a of the spool 71 and the boat 70g, and to the boat 70 when in the D3 position.
f, annular groove 71b of spool 71;

are connected to the oil passage 304 via the boat 70e, and
The speed clutch C2 is engaged under pressure. Therefore, D4 or D
In the 3rd position, the first gear clutch C1 and the second gear clutch C2
are engaged under pressure. However, as shown in FIG. 1, a one-way clutch Co is interposed between the first speed driven gear 18 and the output shaft 16, which transmits torque only in the direction of the driving torque from the engine E. A second speed reduction ratio is established.

Next, with the solenoid 142 of the first solenoid valve 140 deenergized and the solenoid valve 140 closed, the second solenoid valve 150 is opened.
When the solenoid 152 is deenergized and the solenoid valve 150 is closed, the governor pressure Pc at that time is generated in the chamber 130A of the second shift valve v2, and the resistance force by the spring 132 and the click motion mechanism 133 is reduced to the governor pressure. Only when the left power generated by the PG exceeds the left power, the spool 131 moves to the left and assumes the second position. Due to this leftward movement of the spool 131, the oil passage 305 is connected to the drain EX via the oil passage 319, and the engagement of the second speed clutch C2 is released, and at the same time, the oil passage 320 is connected to the oil passage 317, which is a hydraulic pressure source. 3rd gear clutch C3
are engaged under pressure. At this time as well, the first gear clutch C1 is pressurized and engaged, but due to the action of the one-way clutch Co, the third gear clutch
A speed reduction ratio is established.

Next, the solenoid 152 of the second solenoid valve 150 is held in a de-energized state, and the solenoid 14 of the first solenoid valve 140 is held in a de-energized state.
2 is energized again to open the solenoid valve 140, the spool 121 of the first shift valve 1 moves to the right and returns to the illustrated position, connecting the oil passage 317 to the drain EX via the oil passage 318. Then, the third speed clutch C3 is disengaged, and at the same time, the oil passage 316 is connected to the hydraulic pressure source 307a, and pressure oil is supplied to the oil passage 310.

The oil passage 310 is connected to the oil passage 309 via the boats 70m and 70k of the manual valve Vm when in the D4 shift position,
Fourth speed clutch C4 is engaged under pressure. At this time as well, the first speed clutch C1 is pressurized and engaged, but as described above, the reduction ratio of the fourth speed is established by the action of the one-way clutch Co. In this manner, automatic gear shifting from first to fourth gears is performed.

Each reduction ratio of these 1st speed to 4th speed and the 1st speed. The relationship between the second solenoid valves 140 and 150 and the respective solenoids 142 and 152 is shown in Table 1.

■-1-Table On the other hand, hydraulic pump P discharged from regulator valve Vr
A part of the working oil pressure flows into the torque converter T through an oil passage 334 provided with a throttle 368 to increase its internal pressure and is sent to the timing valve 210 and the on-off valve 230. The timing valve 210 has chambers 21OA and 210B introduced with oil pressure to be applied to the second speed clutch C2 and fourth speed clutch C4, respectively, and the spool 211 has a reduction ratio for the second speed or fourth speed established. Sometimes the spring 212
The spring 212 moves to the left against the spring force of the spring 212 to reach the second switching position, and when the first or third speed reduction ratio is established.
The spool 212 is moved to the right by the spring force of
takes the switching position.

When the timing valve 210 is in either of these two switching positions, it connects the input oil passage 325 to the output oil passage 327 and also connects the drain oil passage 32 of the modulator valve 220.
1 to the drain EX, but during the transition to both switching positions, the output oil passage 327 is cut off from the input oil passage 325, and the drain oil passage 321 of the modulator valve 220 is cut off from the drain EX. The oil pressure in the output oil passage 327 of the timing valve 210 is input to the modulator valve 220, modulated, and output to its output oil passage 353. The modulator valve 220 modulates the hydraulic pressure using the governor pressure Pc and the throttle pressure Pt to create the engagement force of the direct coupling clutch Cd, and has oil passages 3 in the chambers 220A and 220B, respectively.
Governor pressure PG, throttle pressure pt via 22, 311
is introduced, and these two pressures and the spring force of the spring 222 move the spool 221 to the left toward the valve opening side, and the feedback pressure of the output oil passage 326 is applied to the oil passage 326a and the throttle 372.
The governor pressure PG is received on the left end surface of the spool 221 via
, the spool 221 is moved to the right toward the valve closing side against the throttle pressure pt and the spring force of the spring 222. As a result, a pressure proportional to the vehicle speed U and the opening degree of the throttle valve appears in the output oil passage 353.

When the pressure output from the modulator valve 220 becomes too high, the spool 221 of the modulator valve 220 moves to the right in the figure against the resultant force of the governor pressure Pc, throttle pressure pt, and spring 222 due to feedback pressure, causing the pressure to increase. is drained to drain EX via the timing valve 210. And when the gear is not changing, the timing valve 21
The drain oil passage 321 of the modulator valve 220 is always connected to the drain EX through the is not drained anywhere.

The reason for doing this is that it is necessary to control the direct coupling clutch CdO engagement force (transmission capacity) only by the third solenoid valve 240, and to prevent the direct coupling clutch CdO engagement force from decreasing excessively during gear shifting. . That is, during a gear shift, the accumulator moves in connection with the gear shift, so that the line pressure PR decreases and the throttle pressure pt also decreases momentarily. For this reason, the spool 221 of the modulator valve 220 moves to the right in the figure, and if the drain oil passage 321 is connected to the drain EX at this time, the engagement force of the direct coupling clutch CdO itself decreases. Therefore, during gear shifting, the drain oil passage 321 of the modulator valve 220 is shut off from the drain EX in conjunction with the timing valve 210 to prevent pressure oil from escaping anywhere, thereby reducing the engagement force of the direct coupling clutch CdO during gear shifting. can be prevented.

The pressure in the output oil passage 353 of the modulator valve 220 is
The oil is led to the cylinder 13 of the direct coupling clutch Cd in the torque converter T via the oil passage 326 from the bow) 230a of the on-off valve 230 via the oil passage 326 via the oil passage 326. Therefore, the engagement force (transmission capacity) of the direct coupling clutch Cd is strengthened according to the vehicle speed U and the opening degree of the throttle valve when the third electromagnetic valve 240 is closed. The on-off valve 230 receives the throttle pressure pt through the oil passage 311 in the chamber 230A, and at the throttle pressure pt, the spool 231 moves to the left in the figure against the spring force of the spring 232 to open the input oil passage 353. It is connected to the output oil passage 326, and when there is no throttle pressure pt, that is, when the throttle valve opening is at the idle position, the spool 231 moves to the right by the spring force of the spring 232 and is held in the position shown in the figure, draining the oil passage 326. It connects to EX and also serves to connect oil passage 325 and oil passage 501. This on-off valve 230 is connected to the direct clutch Cd when the valve opening of the throttle valve is at the idle position.
This is to release the O engagement. At this idle position, the oil passage 325 and the oil passage 501 are connected, so that the amount of oil flowing into the torque converter T from the inlet boat Ta of the torque converter T increases, and the pressure inside the torque converter T increases. Since the piston 13 is pushed to the left in the figure, it is in the idle position (when the accelerator pedal is released)
The disengagement of the direct coupling clutch Cd can be reliably performed.

The third solenoid valve 240 controls opening and closing between the oil passage 326 and the drain EX to control the operating pressure of the direct coupling clutch Cd or the pressure of the piston 13, thereby controlling the clutch CdO.
It functions to control the engagement force, and when the solenoid 242 of this third solenoid valve 240 is energized and opened, the throttle 373
As a result, the oil pressure in the oil passage 326 decreases, and the direct coupling clutch CdO
The engagement force (transmission capacity) is weakened.

The solenoid 242 of this third solenoid valve 240 determines the relative actual speed ratio e between the torque converter T and the output member.
The electronic control unit 33 that measures the speed ratio e is controlled so that the speed ratio e falls within a reference range value, as will be described later. When the solenoid 242 of the third solenoid valve 240 is deenergized and the solenoid valve 240 is closed, the modulator valve 242 is closed.
0 output itself becomes the direct coupling clutch CdO engagement force,
The output acts on the hydraulic cylinder 13 via the on-off valve 230 and the oil passage 326, and the operating pressure increases in proportion to the vehicle speed U, as shown by the solid line 3 in FIG. In FIG. 4, the influence of the throttle pressure Pt is omitted for the sake of simplicity.
This is what happens when 2 is omitted.

On the other hand, when the solenoid 242 of the third solenoid valve 240 is energized and the solenoid valve 240 is open, the hydraulic cylinder 13 is Since it is opened to the drain EX and the pressure decreases, the engagement force of the direct coupling clutch Cd becomes weak or zero, and its operating pressure has the characteristics shown by the broken line (■) in FIG. Therefore, by controlling the duty ratio of the opening time of the third electromagnetic valve 240, the operating pressure of the direct coupling clutch Cd can be created arbitrarily between the solid line I and the broken line ■ in FIG.

In this embodiment, between the solid line ■ and the broken line ■ in FIG.
The duty ratio is controlled in 21 stages from 0 to 20%, of which the representative one shown in Figure 4 is on-duty ratio (hereinafter simply referred to as duty ratio) of 60%.
The solid line (■) indicates the operating pressure when the duty ratio is 30%, and the solid line (■) indicates the operating pressure when the duty ratio is 30%. In Fig. 4, the straight line indicated by the chain line ■ indicates the internal pressure PT of the torque converter T, and the differential pressure between the operating pressure indicated by the solid lines ■ to ■ or the broken line ■ and the internal pressure PT is the direct coupling clutch CdO engagement force. Define strength.

(Operation) FIGS. 5 to 7 are flow charts showing the method of the present invention,
The operation of the method of the present invention will be explained below along with this flowchart.

In FIG. 5, when the ignition switch is first turned on, the CPU of the electronic control unit 33 is initialized (
Step 1): All variables related to transmission capacity control of the direct coupling clutch Cd are set to initial values. Next step 2
Proceed to the vehicle speed detector 31, engine rotation speed detector 34,
Each input data from the gear position detector 35 etc. is read, and in step 3, the time intervals of the vehicle speed pulse signal and the engine rotation speed pulse signal respectively inputted are measured to determine the vehicle speed U,
The engine speed Ne is calculated, and the torque converter T (described later) is operated based on the vehicle speed U and the engine speed Ne.
The speed ratio e between the pump wheel 2 and the turbine wheel 4 (see FIGS. 1 and 2) is calculated (step 4).

This value e is calculated as follows.

When the turbine wheel rotation speed is N2, the speed ratio e of the torque converter T is expressed by the following equation.

- Since it is connected to the cable pulley 30 via a gear train, there is no slippage between them.If the reduction ratio between them is A and the rotation speed of the speedometer cable 30 is N3, then Rotation speed N2 of torque converter output shaft 3
is, N2=A-Nll...(2)
Tona Kuzu. When formula (1) is rearranged using formula (2), the speed ratio e is expressed by the following formula.

In this case, the value of the reduction ratio A may take values A1 to A4 corresponding to each of the detected speeds, that is, the reduction ratios of the first to fourth speeds.

Note that a rotation speed detector may be attached to the input shaft 3 of the auxiliary transmission M in order to determine the output side rotation speed of the torque converter T.

After calculating the speed ratio value e in step 4, the process proceeds to step 5, whereupon a routine for controlling the direct coupling clutch Cd (Cd, C0NTR0L) shown in FIG. 6 is executed.

In FIG. 6, first, in step 1, the engine speed Ne
is larger than a predetermined rotation speed Nes (for example, 3.50 rpm), and if the answer is affirmative (Yes), proceed to step 16 and turn off the third solenoid valve 240, that is, close it and directly connect it. The hydraulic pressure of the clutch Cd is increased to strengthen the engagement force of the direct coupling clutch CdO.

This is because if the engine speed Ne is 3 + 500 rpm or more, there is no risk of problems such as vibration, and the direct coupling clutch C
By increasing the engagement force of d, clutch slippage is suppressed,
It is possible to improve the life span and fuel efficiency of the direct coupling clutch Cd. At this time, the hydraulic pressure supplied to the direct coupling clutch Cd is maintained on the solid line I in FIG. 4.

If the answer to step 1 is negative (NO), it is determined in step 2 whether the gear position of the auxiliary transmission M is the fourth gear, and if the answer is affirmative (Yes), step 6 is performed. If the answer is NO, the process proceeds to step 3, where it is determined whether or not the gear position is the third speed.

If the answer to Step 3 is affirmative (Yes), that is, if the gear position is the third gear, then Step 5 is answered (No).
In each case, proceed to step 4.

As a result of the determination in steps 2 and 3, when the vehicle is in fourth gear, the upper limit vehicle speed U32 is changed to the predetermined vehicle speed U432 in step 6.
(for example, 85 kffi/h), when the vehicle is in third gear, the upper limit vehicle speed U32 is set to the designated vehicle speed U332 (for example, 40 km/h) in step 5, and when the vehicle is in second gear or lower, the upper limit vehicle speed U32 is set to the designated vehicle speed U232 (for example, 30 km/h) in step 4. /h) respectively. In this way, the upper limit vehicle speed U32 is set to the U2321 U3112. and U4
After setting the vehicle speed to one of the vehicle speeds U32, the process proceeds to step 7, where it is determined whether or not the vehicle speed U is greater than the upper limit vehicle speed U32 set in any of the steps 4 to 6, and if the answer is affirmative ( If Yes), problems such as vibration will not occur, so proceed to step 16, and the third solenoid valve 240
Close the valve and strengthen the engagement force of the direct coupling clutch CdO.

If the answer to step 7 is negative (No), that is, if the vehicle speed U is smaller than the upper limit vehicle speed U32, the process proceeds to step 8 where the vehicle speed U is determined to be the lower limit vehicle speed U31 (for example, 6 km/h).
Determine whether the value is greater than or not. The answer is negative (NO),
That is, if the vehicle speed U is lower than the lower limit vehicle speed U31 and is in a low vehicle speed range that requires the torque amplification function of the torque converter T, the process proceeds to step 18 and the third solenoid valve 240 is turned on, that is, opened. As a result, the operating pressure of the direct coupling clutch Cd is lowered, the engagement force of the direct coupling clutch CdO is weakened, and the function of the torque converter T is utilized. At this time, the working oil pressure supplied to the direct coupling clutch Cd changes along the broken line ■ in FIG. If the answer to step 7 and step 8 is affirmative (Yes), that is, if the vehicle speed U is greater than the lower limit vehicle speed U3+, the process advances to step 9, and the gear stage of the auxiliary transmission M is set to the fourth gear.
Determine whether the speed is high or not. If the answer to step 9 is affirmative (Yes), it is determined in step 10 whether the vehicle speed U is greater than a predetermined vehicle speed U36 (for example, 58 km/h), and if the answer is affirmative (Yes), i.e. , when the gear stage is the fourth speed and the vehicle speed U is higher than the predetermined vehicle speed U36, in step 12, the determination values e1 (for example, 92%), C2 (for example, 97%), C3 (for example, 99%) in the predetermined speed ratio range are set. .5%) and cz (for example, 102%). The discrimination value e1 is an upper limit value of a region where the direct coupling clutch CdO engagement force is weak (hereinafter referred to as a weak engagement force region) and a lower limit value of a region approximated to a reference value (hereinafter referred to as a reference value approximation region). The discrimination value e2 is the upper limit value of the reference value approximation region and the lower limit value of the reference value region (target region). The discrimination value e3 is the upper limit value of the reference value region and the lower limit value of the fine adjustment region. The discrimination value e4 is the upper limit value of the fine adjustment region and the lower limit value of the region where the solenoid is turned on and the third electromagnetic valve 240 is opened (hereinafter referred to as the solenoid on region). Step 1
If the answer to 0 is negative (No), that is, the relevant gear is in the 4th gear position.
If the vehicle speed U is smaller than the predetermined vehicle speed U3G, the determination value e+ (for example, 88%) is set in step 13.
C2 (e.g. 94%), e+ (e.g. 97.5%), 6
4 (for example, 99%).

If the answer to step 9 is negative (No), that is, if the gear position is not the fourth gear, the process proceeds to step 11, where it is determined whether the gear position is the third gear. If the answer to step 11 is affirmative (Yes), that is, if the third speed
%), C2 (e.g. 94%), Ill: ] (e.g. 99
7.5% and e<(for example, 99%), respectively.

If the answer to step 11 is negative (No), that is, if the gear position is neither 4th speed nor 3rd speed, the process moves to step 15 and the discrimination values e1 (for example, 88%), C
2 (e.g. 94%), C3 (e.g. 97.5%), +z
(for example, 99%).

After setting the respective discrimination values e1 to e4 in steps 12 to 15, the process proceeds to step 17, where the duty ratio control of the solenoid valve 240 (solenoid valve DUTY C) shown in FIG.
0NTR0L) routine.

Step 1 in FIG. 2. 3. In steps 7 and 7, it is determined in which region of the speed ratio range the current speed ratio e falls. First, considering that the speed ratio e changes from the bottom to the top, if the speed ratio e is in the weak engagement force region, it is difficult to determine whether the speed ratio e is larger than the discrimination value e1 in step 7. The answer is negative (No) and step 8
It is determined whether the timer period T1 has elapsed (T=O).

FIG. 8 shows the duty ratio control state when the speed ratio e passes from the weak engagement force region to the upper reference value approximation region and enters the upper reference value region. As the speed ratio e approaches the reference value region, the rate of increase in the transmission capacity of the direct coupling clutch Cd is controlled to be reduced, that is, the rate of change in the transmission capacity is controlled to be small.

When the speed ratio e is in the weak engagement force region, T1 (for example, 0
．． Every time a period of
By controlling the duty ratio of the zero valve opening time, the engagement force of the direct coupling clutch Cd is gradually strengthened. In FIG. 7, if the answer to step 8 is affirmative (Yes), that is, when the timer period (T1) has elapsed (tl in FIG.
.

t2. and time t3) Each time, in step 9, the timer is set to the value T1, and in step 10, the variable value is set to a value (D-xl) smaller than the previous value by xl, and this is stored. The duty ratio control of the opening time of the third electromagnetic valve 240 (steps 8 to 13) is repeated again over the T1 period at the duty ratio at the stage indicated by the value. Note that step 11 is a limit check, and if the variable value becomes less than 0, problems will occur in program control. Therefore, it is determined whether the variable value is greater than the minimum D11im (for example, O), and the answer is In case of negative (No), that is, when the variable value is smaller than O, the value of the variable value is set to the minimum value Di lim in step 12, and the process moves to step 13. If the answer to step 11 is affirmative (Yes), that is, if the variable value is greater than 0, step 12 is skipped and the process proceeds to step 13.

In step 13, the value of the variable set in step 10 is stored as a variable D32 for later use in control when the speed ratio e enters the reference value range. After this, in step 14, the solenoid 2 of the third solenoid valve 240 is
A counter for controlling the energization time to 42 is set to a value corresponding to the variable value, and then the process returns to step 2 in FIG. 5 and is executed again. Note that the electronic control device 33 operates the third solenoid valve 24 at the same duty ratio, that is, at a constant cycle, until the duty ratio of the third solenoid valve 240 is set to a new value.
Repeat 0 valve opening. Here, the duty ratio of the third solenoid valve 240 is the ratio of the energization time to the solenoid 242 to a predetermined time (for example, 100 m5), and +Do
- When set to 21 steps of D20, the energization time per step is 5 ms.

In this way, when the speed ratio e is in the weak engagement force region, the engagement force of the direct coupling clutch CdO is gradually strengthened toward x1 every period T1.

Next, when the speed ratio e enters the reference value approximation region (time t, 1 in FIG. 8), the answer to step 7 becomes affirmative (Yes), and it is determined in step 15 whether or not the timer period has elapsed. The timer period here is when the speed ratio e is in the weak engagement force region immediately before entering the reference value approximation region, that is, t in FIG.
This is the value T1 set at time 3. If the answer to step 15 is negative (NO), that is, if the timer period T1 has not elapsed, steps 16 to 19 are not executed and step 1 is continued.
3 and 14 are executed, and the third solenoid valve 240 is subsequently controlled to open at the duty ratio set in the weak engagement force region. If the answer to step 15 is affirmative (Yes), that is, when the timer period T1 has elapsed (time t5 in FIG. 8), step 16 sets the timer to a predetermined value larger than the T1 value set in the weak engagement force region. Set T2 (for example, 1 second), and at step 17°, increase the variable value by X2 from the previous value.
Set a value (D-X2) that is decreased by (for example, 1), store this, and then set the duty ratio of the opening time of the third solenoid valve 240 again over the T2 period at the duty ratio at the stage indicated by the D value. control. Then, timer period T2 again
has elapsed and the speed ratio e value is still in the reference value approximation region (at time t6 in FIG. 8), step 15 is performed in the same manner as described above.
Repeat steps 19 and 13. Note that step 18 is a glue mint check similar to step 11, in which it is determined whether the variable value is greater than the minimum value D21im (for example, 0), and if the answer is negative (No), that is, the variable value is When is smaller than 0, the value of the variable is set to the minimum D21im in step 19, and the process moves to step 13.

If the answer to step 18 is affirmative (Yes), that is,
If the variable value is greater than 0, the process moves to step 13 without executing step 19.

When the speed ratio e enters the reference value region at time t7 in FIG. 8, the answer to the determination as to whether the speed ratio e is greater than the discrimination value e2 in step 3 becomes affirmative (Yes), which will be described later in step 20. The flag F1 is set to O, and the process proceeds to step 21, where it is determined whether or not a flag F3, which will also be described later, is set to 1.

If the speed ratio e enters the reference value region from a smaller value, flags F2 and F3 are both set to 0 (steps 5 and 6), and the answer to step 21 is negative (NO).
), and the answer to the question of whether flag F2 is set to 1 in step 24 is also negative (No).
In this case, the process moves to step 26 and it is determined whether or not the timer period has elapsed. The timer period here is the value T2 set when the speed ratio e is in the reference value approximation region, that is, at time t6 in FIG. The answer to step 26 is negative (No
), that is, steps 27 and 28 are not executed until the timer period T2 has elapsed, and steps 41 to 46 described later are executed.
After that, step 14 is executed, and the third solenoid valve 240 is subsequently controlled to open at the duty ratio set in the reference value approximation region.

If the answer to step 25 is affirmative (Yes), that is,
When the timer period T2 has elapsed (time tB in FIG. 8),
In step 27, a unique value when the speed ratio e is in the reference value region, that is, the value T3 (for example, 2 seconds) is set in the timer again in step 27, and in step 28, it is stored as the variable value D32 in step 13 in the previous loop. The value set when the speed ratio e is in the reference value approximation region immediately before entering the reference value region (time t6 in FIG. 8) is set as is. In this way, if the speed ratio e falls within the reference value region,
The third solenoid valve uses the value set just before entering the reference value area (time t6 in Figure 8) without rewriting the value of the variable until the timer period T3 has elapsed (time t9 in Figure 8). The valve opening time of 240 is duty-controlled. Even after time tS, as long as the speed ratio e is within the reference value range, the transmission capacity of the direct coupling clutch Cd is controlled not to be changed.

FIG. 9 shows a duty ratio control state using a method different from that in FIG. 8 in duty ratio control when the speed ratio e enters the reference value region from the weak engagement force region through the reference value approximation region as in FIG. 8. . That is, in the case of FIG. 8, xl and x2
By keeping the same value and making the values of T+, T2, and T3 different, the rate of change over time of the speed ratio e becomes smaller as the speed ratio e approaches the reference value region. In this case, the values of TI, T2, and T3 are all the same, and the values of xl and x2 are different, so that the rate of change over time of the speed ratio e becomes smaller as the speed ratio e approaches the reference value region. be.

Figure 10 shows the duty ratio control state when the speed ratio e exceeds the reference value region, enters the fine adjustment region above the reference value region, and returns to the reference value region again without exceeding the fine adjustment region. shows. In this case, if the speed ratio e enters the reference value region from below, the values of all flags F+, F2, and F3 are zero. Therefore, the speed ratio e increases from the time point 100 in (a) of FIG. 10 and reaches t 1
When the speed ratio e exceeds the reference value region and enters the fine adjustment region directly above it at one point in time, the speed ratio e at step 2 in FIG. 7 becomes the discriminant value e3.
The answer to the determination as to whether it is greater than or not is affirmative (Yes), and the process proceeds to step 29, where the flag F1 is set to 1, and then the process proceeds to step 30. In step 30, the flag F
2 is 0 or not, but since this flag F2 is still set to O, the answer to the determination is affirmative (Yes), and the process moves to step 31 where the flag F2 is set to O.
Set 1 to 2.

Next, in step 32, the variable D32 is set as the variable value D33.
Store the value of . This D32 value is the D value used when the speed ratio e is within the reference value region, that is, the D value used in step 28.
This is the same as the D value set in . Incidentally, FIG. 10 shows changes over time in the values of variables D32 and D33 together with changes in the speed ratio e. In this case, each value of the variables etc. shows only the increase/decrease value with respect to the value set when the speed ratio e value is in the reference value region. Then step 3
Step 3 sets the timer to a predetermined value T4 (for example, 0.4 seconds), and step 34 sets the variable value to be used for control this time.
After setting a value obtained by adding x6 (for example, 6) to 033 used for the previous control, the process returns to step 2 in FIG. 5 via steps 41 to 46 and 14, which will be described later, and is re-executed.

What should be noted here is that when the speed ratio e is in the reference value region just before entering the fine adjustment region, that is, (a
), the timer period T3 set at time 100 is t11.
There is no time-up until the time point 1 is reached, but the speed ratio e reaches the discrimination value e3, that is, the lower limit value of the fine adjustment region 1++
At this point, the timer is immediately reset to the value T4 (step 33), and control is repeated using the value of D set in step 34 until the T4 period has elapsed. When this repetition reaches step 30, the flag F2 was set to 1 in step 31 in the previous loop, so the answer to step 30 is negative (No) and the process moves to step 35, where the timer period T, ! Since I has not timed up yet, the answer to the determination as to whether or not the timer period has elapsed in step 35 is negative (No), and in step 36 the variable value D32 is changed.
X3 to the D33 value set in step 32 above.
(For example, 1) is added and the value is stored. Since the value D32 was set as the variable value 033 in step 32 in the previous loop, if the value set when the speed ratio e is in the reference value region is Do, the value newly stored as the D32 value is this value.

It is equal to the value obtained by adding x3 to

Before the speed ratio e passes the timer period T4, that is,
If it returns to the reference value area again at time t12, the answer in step 3 becomes affirmative (Yes), and the process moves to step 20, where the flag F1 is set to 0. In the next step 21, in this case, the flag F3 is set to 0. Since it is still set to , the process skips over this and moves to step 24. Since flag F2 was set to 1 in step 31, the answer to step 24 is affirmative (Yes), and the process moves to step 25 to set flag F2.
is set to O, skipping step 26 and proceeding to step 27, where the predetermined value T3 is set in the timer. That is, skipping step 26 and proceeding to step 27 means that the timer is reset as soon as the speed ratio e returns to the reference value range.

Next, in step 28, the value D32 stored in step 36 in the previous loop is set as a variable value, and the duty ratio of the opening time of the third solenoid valve 240 is controlled at the duty ratio of the stage indicated by the value of D32.

Then, even at time t13 when the speed ratio e has passed the timer period T3, as long as it is within the reference value range, the T3 value is set in the timer again (step 27), and the D value does not change and remains the same after time tM. Value D32 (step 28
) to control the duty ratio.

In the case of (a) in Fig. 10, the speed ratio e exceeds the reference value region and enters the fine adjustment region for a short period of time (period shorter than the timer period T4).
This is the case when only one person enters. That is, since the speed ratio e has entered the fine adjustment region, as a result of correction with a large value x6 at time 1++, the timer period T4 does not elapse at t12.
The fact that it immediately returned to the reference value region at time point means that the x6 value is too large, and therefore, the return to the reference value region at t
At time i2, in the reference value region just before exceeding the reference value region, that is, by controlling the duty ratio using the value obtained by adding a small correction value x3 to the variable value set at time 100, the speed ratio e is set as the reference value. It is stored in the value area.

In the case of (b) in Fig. 10, the speed ratio e has increased from the time tis, exceeded the reference value region, and entered the fine adjustment region, so correction was applied with a large value x6 at the time t1s. , it does not immediately return to the reference value area but stays in the fine adjustment area for a long time (
This is a case where the timer stays for a time longer than the timer period T4). In this case, immediately before exceeding the reference value area and entering the fine adjustment area, the time period during which the speed ratio e value remains in the fine adjustment area is determined by adding the x6 value to the D value set at time t15. The speed ratio e is maintained in the reference value region by controlling the duty ratio using a value added according to the speed ratio.

Therefore, in the case of (b) in FIG. 10, steps 29 to 34 are executed at the time point t1' as in the case of +a) in FIG. 10 at the time t14.
Steps 29, 30, 35 until reaching point 1
and 36 are executed, respectively. When the timer period T4 reaches time tl-7, the answer to step 35 becomes affirmative (Yes), and the process moves to step 37, where flag F3 is set to 1, and then, In step 38, the value used in the previous loop is stored in D33 as a variable value. Then, in step 39, the timer is set to the T4 value again, and in step 40, the D value is set to
Set the value by adding (for example, 1). and the
At this point, steps 29, 30, 35, and 36 are executed again until the timer period T4 times up, and in step 36, a value obtained by adding the value x3 to the D33 value is stored as the D32 value. At the time l+e, the speed ratio is still e
If is in the fine adjustment region, proceed to step 37.3 as above.
8 respectively. Execution of steps 37 and 38 means that the D33 value is updated to the value obtained by adding x values, and by adding the value x3 to the D value in step 40, the duty value is changed again. The duty ratio control is repeated with this value. Then, at time t19, when the speed ratio e returns to the reference value region, steps 20 and 21
Execute. The answer to step 21 is the answer to step 37.
Since flag F3 is set to 1 in step 22, the result is affirmative (Yes), flag F3 is set to 0 in step 22, and step 2
At step 3, the flag F2 is set to 0, and step 24 is skipped and the process proceeds to step 26, where it is determined whether or not the timer period T4 has timed out. Skipping step 24, ie, not determining flag F2, means that the speed ratio e is changing slowly. If the speed ratio e is changing slowly, the duty value set in the previous loop is used as is. That is, the controller waits until the time period T4 has elapsed, that is, until the time point t°1, and then performs duty control using the duty value set in the previous loop as is. Then, when the time point t°19 is reached, the answer to step 26 becomes affirmative (Yes), and the timer is set to the T3 value in step 27, and step 2
At step 8, the value D32 is set in the variable value. This D32 value is the value set immediately before the fine adjustment area set in step 36 is extracted.

In this way, when the speed ratio e returns to the reference value region, duty ratio control is continued based on the variable value, and as long as the speed ratio e remains within the reference value region, the value is maintained after time t20 and the duty ratio is maintained. Control the ratio.

FIG. 11 shows the control state when the speed ratio e goes from the reference value region to the fine adjustment region, enters the solenoid ON region, and then returns to the reference value region again.

(In addition, FIG. 11 shows a state in which the speed ratio e is in a range larger than the discrimination value e4, that is, in the solenoid ON region.

FIG. 11(a) shows the case where the speed ratio e passes through the fine adjustment region in a short time and enters the region where the solenoid is turned on.
FIG. 11(b) shows the case where the speed ratio e takes a long time to pass through the fine adjustment region and enters the region where the solenoid is turned on. In both cases of (a) and (b) in Fig. 11, the speed ratio e approaches the upper limit value 1.0 (en), so there is a risk of car body vibration, so the duty ratio is the highest, D20.
(The solenoid 242 of the third solenoid valve 240 is turned on to open the solenoid valve 240.) However, when the speed ratio e returns from the solenoid on region to the fine adjustment region, the duty value is In FIG. 11, (a) is set to a larger value than (b).

That is, in (a) of FIG. 11, when the speed ratio e increases from time t2g and enters the fine adjustment region at time t30, first,
The answer to step 2 in Figure 7 is affirmative (Yes), and step 10
Steps 29 to 34 are respectively executed in the same manner as explained in the figure. At this time, the D value and D33 value are 1×6 (for example, 4) and +0, respectively, with respect to the previous value.

And in the next loop steps 29.30.35 and 36
are respectively executed, and in step 36 the D33 value is set to the value Xl
The value obtained by adding (for example, 1) is stored as the D32 value. At this time, flag F3 remains at 0. In this state, if the speed ratio e exceeds the fine adjustment region before the timer period T4 elapses (at time t31), the answer to the determination as to whether or not the speed ratio e in step 1 of FIG. 7 is greater than the discriminant value e4 is The result is affirmative (Yes), and the process moves to step 47 where flag F is set.
2 is set to 1, and in step 48 it is determined whether the flag F3 is set to 1. As mentioned above, flag F
3 remains O and the speed ratio e has left the fine adjustment region and entered the solenoid on region, so the answer to step 48 is negative (No.
), move to step 5o and set the value x5 to the 033 value.
(For example, 6) is added and the value is stored as the D value. Next, in step 51, it is determined (limit check) whether the D value is larger than the DFO value (=20). If the answer is affirmative (Yes), the D value is set to the value DFO in step 52 and the process moves to step 53. If the answer is negative (No), step 52 is skipped and the process moves to step 53. In step 53, the D value (for example, +6) set in step 51 is stored as the D32 value, the timer is set to O in step 54, and the solenoid 2 of the third solenoid valve 240 is set in step 55.
42 is turned on to maintain the solenoid valve 240 in the open state, while at step 56 the electronic control unit 33 stops the valve opening duty ratio control of the third solenoid valve 240, and the fifth solenoid valve 240 is turned on again.
Return to step 2 in the diagram.

Then, when the speed ratio e enters the fine adjustment region again at time t32 in (a) of FIG. 11, the answer to step 2 of FIG. 7 becomes affirmative (Yes), and the flag F1 is set to 1 in step 29. The answer to step 30 is negative because flag F2 was set to 1 in step 47 of the previous loop.
Proceed to step 35.

The answer to step 35 is affirmative (Yes) because the timer was set to O in step 54 of the previous loop.
In step 37, the flag F3 is set to 1, and in the next step 38, the D value (+x5, ie, +6) is stored as the D33 value. Then, in step 39, the timer is set to the predetermined value T.
4, and in step 40 the value of D+x3 (i.e. +6+
1=+7) as a new value, and in step 36 of the next loop, the value of D33+x3 (i.e. +6+1=+7)
is stored as a D32 value.

After that, at time t33, the speed ratio e continues to enter the fine adjustment region, so steps 29, 30° 35.37
-40 respectively. In step 38, the D value (+7) is stored as the D33 value, and in step 40, the value of D+x-1 (+8) is stored as the D value. Then, the answer to step 35 becomes negative (NO) again, and the process moves to step 36.
The value of D33+x3 (+8) is stored as the D32 value.

Next, when the speed ratio e enters the reference value region at the time t°33, it is controlled by the same effect as at the time 19 (Li9-t in FIG. 10), and reaches the time t34, and thereafter the speed ratio e
As long as D is within the reference value range, the duty ratio is controlled without changing the D value.

When the speed ratio e enters the fine adjustment region at time t35 (in case of BL in FIG. 11), steps 29 to 34 in FIG. D32, ie +0 in step 32, D33 in step 34
The value of +x6 (+4) is stored as the D value, and the next (D)Li
-D33+X3 (+1) in Puno Step 36
Store as binary value. Since the speed ratio e is still in the fine adjustment region at the time tI after the T4 period has elapsed, step 29
．． 30. Execute steps 35 and 37 respectively, then proceed to step 38
In step 39, store the D value (+4) as the D33 value.
．． 40 respectively, and in step 40, the value (+5) of I)+x3 is stored as the D value.

Then, at time t37, when the speed ratio e leaves the fine adjustment region and enters the solenoid ON region, the answer to step 1 in FIG. 7 becomes affirmative (Yes), and steps 47 and 48 are executed, respectively.'' In this case, The speed ratio e is from the time t3 to the first T4
Since the fine adjustment region has been entered until the time point t37 in the middle of the next T4 period after the elapse of the period, the state of change in the speed ratio e is gradual, and 1 is set in the flag F3. Therefore, the answer to step 48 is affirmative (Yes), and the process moves to step 49 to obtain the value of D33+x4, that is, +
set 5 as the D value, then execute step 52;
If the answer is affirmative (yes), proceed to step 53;
If negative (NO), step 52 is skipped and the process moves to step 53. In step 53, the D value set in step 49, that is, +5, is stored as the D32 value, and thereafter steps 53 to 56 are executed, respectively, to step 2 in FIG.
Go back and try again.

Then, when the speed ratio e enters the fine adjustment region again at time t3B, steps 29, 30, 35, and 37 are executed, respectively, and the D value (D33+)ll+-15) is
It is stored as 33 values. Next, in step 40, the value D33+Xl:l=+6 is stored in the D value as the D32 value.

Thereafter, when the speed ratio e enters the reference value region at time t39, when the T4 period has not elapsed, at t12 in (a) of FIG.
The control is performed in the same way as at time ti3, and from time t40 to time t44, the duty ratio is controlled without changing the value of D as long as the speed ratio e is within the reference value range.

Note that F1=1 in step 4 in FIG. 7 means that the speed ratio e once enters the fine adjustment region from the reference value region, and the speed ratio e in the next loop passes through the reference value region and changes to the lower coefficient. When entering the weak resultant force region, that is, when the speed ratio e changes rapidly, the flag F1 is set to 1, which means that control should be performed using the D value set in the previous fine adjustment region.

In addition, steps 41 to 46 are limit checks,
If each value of D32 and D33 is larger than the DFO value (for example, 20), each of these values is rewritten to the value DFO.

In addition, although the above embodiment describes the case where a fluid torque converter T is employed as the fluid power transmission device, the present invention is applicable to any automatic transmission for a vehicle that is equipped with other types of fluid couplings, etc. It is.

Further, the predetermined parameter representing the relative slippage amount between the input and output members of the fluid power transmission device may be the difference between the respective rotational speeds of the input and output members.

(Effects of the Invention) As detailed above, according to the direct coupling mechanism control method for a hydraulic power transmission device of an automatic transmission for a vehicle according to the present invention, a predetermined amount of slippage between the output member and the output member of the hydraulic power transmission device is determined. The measured value of the parameter value is compared with a predetermined reference range value set in advance, and based on the comparison result, the transmission capacity of the direct coupling mechanism for a predetermined period to be implemented from now on is determined.

Therefore, even if the transmission capacity of the direct coupling mechanism is set to be strong, it is possible to stably and quickly control the transmission capacity to the reference value (target value) range without causing divergence, and the generation of vehicle body vibration and noise is prevented. This has the effect of reducing fuel consumption, improving power transmission characteristics, and providing an extremely smooth and comfortable driving feeling.

[Brief explanation of the drawing]

Fig. 1 is a schematic diagram of an automatic transmission for a vehicle to which the direct coupling mechanism control method of the present invention is applied, Fig. 2 is a hydraulic control circuit diagram of the automatic transmission for the same vehicle, and Fig. 3 is a diagram of the direct coupling clutch of Fig. 2. Exploded view of the main parts, Figure 4 is a graph showing the relationship between the working oil pressure of the direct coupling clutch and vehicle speed, Figure 5 is the main flowchart showing the control procedure for the working oil pressure (transmission capacity) of the direct coupling clutch, and Fig. 6 is the graph showing the relationship between the working oil pressure of the direct coupling clutch and the vehicle speed. FIG. 7 is a sub-flowchart showing the control procedure carried out in step 5 of FIG. 6. FIG. 8 is a sub-flowchart showing the control procedure carried out in step 17 of FIG. Different,
A graph showing the relationship between speed ratio and duty ratio in control when the speed ratio enters the reference value region from the weak engagement force region through the reference value approximation region. 10 is a graph showing the relationship between the speed ratio and duty ratio in control when the speed ratio goes from the weak engagement force region through the reference value approximation region and enters the reference value region with the same speed ratio. FIG. 11 is a graph showing the relationship between the speed ratio and the duty ratio in control when the fine adjustment region exceeds the reference value region and returns to the reference value region again without exceeding the fine adjustment region. 7 is a graph showing the relationship between the speed ratio and the duty ratio in control when the speed ratio returns from the reference value region to the fine adjustment region to turn on the solenoid and then returns to the reference value region. T...Torque converter (hydraulic power transmission device), 2
... Pump impeller (input member), 4... Turbine impeller (output member), Cd... Direct connection clutch (direct connection mechanism). Applicant: Honda Motor Co., Ltd. / Agent: Patent Attorney Toshi Watanabe Otoma Kanji Nagato 3rd illustration

Claims (1)

[Claims] 1. The predetermined parameter value representing the relative slip amount of the input and output members of a hydraulic power transmission device having an input member and an output member is within a predetermined reference range set in advance. In the method for controlling a direct coupling mechanism of a hydraulic power transmission device for a vehicle automatic transmission, which variably controls the transmission capacity of a direct coupling mechanism that mechanically engages the input and output members, the actual measurement of the predetermined parameter value Compare the value with the predetermined reference range value,
A direct coupling mechanism control method for a hydraulic power transmission device for an automatic transmission for a vehicle, characterized in that the transmission capacity for a predetermined period to be implemented is determined based on the comparison result. 2. Direct coupling mechanism control of a hydraulic power transmission device of an automatic transmission for a vehicle according to claim 1, wherein the predetermined parameter is a ratio of the respective rotational speeds of the input member and the output member. Method. 3. Direct coupling mechanism control of a hydraulic power transmission device for an automatic transmission for a vehicle as set forth in claim 1, wherein the predetermined parameter is a difference between the respective rotational speeds of the input member and the output member. Method. 4. A direct coupling mechanism control method for a fluid power transmission device for an automatic transmission for a vehicle according to claim 1, characterized in that the transmission capacity is kept constant within the predetermined period.