JPS6285730A - Transmission for four wheel drive - Google Patents

Abstract

PURPOSE:To prevent double stage impact caused from speed change operation of main and sub-transmissions by feeding the line oil pressure directly from a line oil pressure output path in a main hydraulic controller to sub-hydraulic controller for performing the drive control of sub-transmission. CONSTITUTION:A fully hydraulic controller 100 for a three-stage advance single stage back gear type transmission will control supply/discharge of pressure oil to the hydraulic servos C1, C2, B1-B3 in a main transmission by means of a manual valve 105, a 1-2 shift valve 106, a 2-3 shift valve 107, etc. thus to achieve three-stage advance single stage back speed change stages. While a hydraulic control circuit 200 of a sub-transmission or a four wheel drive (4WD) transfer unit will establish any one of 2WD condition, 4WD direct-coupled condition or 4WD decelerating condition by means of a selection valve 201, a modulator valve 210 and an inhibiter 220. Here, the line oil pressure is fed directly from a line oil pressure output path 104 in the fully hydraulic controller 100 to the hydraulic control circuit 200.

Description

[Detailed description of the invention] [Industrial application field] The present invention relates to a four-wheel drive automatic transmission.

[Prior Art] Conventionally, a four-wheel drive automatic transmission includes a main transmission controlled by a main hydraulic control device having a line hydraulic pressure generation source, and the main hydraulic control 2! Sub-hydraulic control fi using the line hydraulic pressure of the I device
The line pressure supply oil passage of the N1 transmission for four-wheel drive supplies line pressure oil via the manual valve or shift valve of the main transmission. 1 (supplied to the transmission.

[Problem to be Solved by the Invention 1] However, in this type of four-wheel drive automatic transmission, the PTA engagement element on the main transmission side is engaged or disengaged by switching the shift lever, and the friction engagement element on the auxiliary transmission side is engaged or disengaged. 2 of engagement or release of
There was a stage shock.

Since the present invention supplies line pressure oil to the auxiliary transmission through a manual valve or a shift valve of the main transmission, it is possible to engage or disengage the friction engagement element on the main transmission side by switching the shift lever and to change the auxiliary transmission. An object of the present invention is to provide a four-wheel drive automatic transmission capable of preventing two-stage shocks due to engagement or disengagement of frictional engagement elements on the machine side.

[Means for Solving the Problems] The four-wheel drive automatic transmission of the present invention includes a main transmission controlled by a main hydraulic control device including a line hydraulic pressure generating source, and a line hydraulic pressure of the main hydraulic control device. In a 4-wheel drive automatic transmission comprising a 4-wheel drive auxiliary transmission whose speed is changed by an auxiliary hydraulic control device using It is configured to be supplied directly from the line hydraulic output oil path.

Effect 1 The present invention will be described in detail.

The present invention provides main hydraulic control 2I! of the line hydraulic pressure output from the line hydraulic pressure generation source of the main hydraulic control device of the main transmission. The above purpose is achieved because the line oil pressure output oil path in the device is directly supplied to the auxiliary hydraulic control device of the 4-wheel drive auxiliary transmission without going through the manual valve or other valves in the main hydraulic control device. achieve.

[Effects of the Invention] With the above configuration, the four-wheel drive automatic transmission of the present invention provides the following effects.

b) Line hydraulic pressure is supplied to the auxiliary hydraulic control device on the auxiliary transmission side without going through the manual valve of the main hydraulic control 11 device on the main transmission side, so that the line hydraulic pressure can be supplied to the main transmission side clutch etc. by switching the shift lever. A two-stage shock of engagement (release) and engagement (release) of the clutch, etc. on the sub-transmission side does not occur.

(Note) Line hydraulic pressure is supplied to the auxiliary hydraulic control device on the auxiliary transmission side without going through the shift valve of the main hydraulic control device on the main transmission side, which allows the clutch, etc. on the main transmission side to be engaged and released.
and the second-stage shock of engagement (disengagement) of the clutch, etc. on the sub-transmission side does not occur.

[Example] A four-wheel drive automatic transmission of the present invention will be described based on an example shown in the drawings.

1 is a main transmission which is a gear type automatic transmission, 10 is a transfer which is a sub-transmission for four-wheel drive connected to the rear part of the main transmission 1 (right side in Figure 2), and 2 is a main transmission 1. It is an output shaft as well as an input shaft of the transfer F10, 3 is the first output shaft of the transfer arranged in series behind the input shaft 2 (right side in FIG. 2), and 110 is a governor fixed to the input shaft 2. valve,
A planetary gear set 4 includes a sun gear 41 spline-fitted to the rear of the input shaft 2, a planetary gear 42 that meshes with the sun gear 41, a ring gear 43 that meshes with the planetary gear 42, and a planetary gear 42. It consists of a carrier 44 that rotatably holds and is connected to the tip of the first output shaft 3 of the transfer.

5 is a multi-plate brake for engaging the ring gear 43 with the transfer gear 94, 50 is 1 to 7 cases 1
This is a hydraulic servo for the brake 5, which is constituted by a cylinder 18A formed within the cylinder 8 and a piston 51 mounted within the cylinder 18A. 7 is a cylinder 71 connected to the carrier 44 and a piston 72 installed in the cylinder 71;
This multi-plate clutch is operated by a hydraulic servo 70, which is arranged on the gear transmission side of the planetary gear set 4, and connects and disconnects the sun gear 41 and the carrier 44.

8 is a multi-disc clutch for connecting and connecting the first output shaft 3 connected to the carrier 44 and the sleeve 9 connected to one sprocket 12 of a link configuration for driving the other output shaft of a transfer to be described later; 1- Ransuf? Sleeve 9 rotatably held within cases 19 and 20
This hydraulic nervo is composed of a cylinder 81 welded to the cylinder 81 and a piston 82 mounted inside the cylinder 81. 1
7 is a second output shaft of the transfer arranged parallel to the first output shaft, 14 is a sprocket 12 fitted with a spline to the sleeve 9, a sprocket 15 fitted with a spline to the second output shaft 17, and these sprockets. This is a link mechanism consisting of a chain 16 stretched between 1 and 1.

A parking gear 73 is provided around the outer circumferential side of the hydraulic cylinder 71 of the friction clutch 7, and the pawl 7 is disposed when the shift lever of the gear type automatic transmission is set to the parking position.
4 meshes with the parking gear 73 to fix the first output shaft 3.

90 is an oil pan of the gear type automatic transmission; 200 is a hydraulic control device for supplying and discharging hydraulic pressure to the clutch 7.8 of the four-wheel drive transfer and the hydraulic servos 70, 80 and 50 of the brake 5; 92 is the hydraulic control device 200 oil pan. Hydraulic servo 7 for clutch 7.8 and brake 5
Pressure oil supplied to 0.80 and 50 is oil pan 9
Case of gear type automatic transmission from 0.

The hydraulic pressure is guided through the hydraulic control device 200 via a vibrator 95 attached to the transfer case 94 and the transfer case 93 .

This transfer is performed by the engine E of the vehicle as shown in Figure 2.
The first output shaft 3 is connected to a propeller shaft C for driving the rear wheels, and the second output shaft 1γ, which is the other output shaft, is connected to the propeller shaft 8 for driving the front wheels. used in conjunction. During normal driving, the line pressure supplied to the hydraulic control device of the gear type automatic transmission is supplied to the hydraulic servo 10 to engage the clutch 7, and the hydraulic servos 50 and 80 are discharged to release the brake 5 and clutch 8. . As a result, the 4-punch gear 41 of the planetary gear set 4 and the carrier 44 are connected,
The power is transmitted from the input @2 to the first output lTl1I3 for rear wheel drive at a reduction ratio of 1, and two-wheel drive driving with the rear wheels is obtained. At this time, the power from the input @2 is transmitted from the carrier 44 to the first output shaft 3 via the clutch 7 without going through the gears 41, 42, 43, so no load is applied to the tooth surfaces of each gear. ,
Gear life increases. When driving in 4-wheel drive while driving in 2-wheel drive, operate the manual shift lever or switch located on the driver's seat etc. When the hydraulic control HM200 is activated to gradually supply line pressure to the hydraulic servo 80 and smoothly engage the clutch 8, the first output shaft 3 and the sleeve 9 are connected,
Power is also transmitted to the front wheels via the link mechanism 14, second output shaft 17, and propeller shaft B, and the power is transmitted from the input shaft 2 to the first output shaft 3 for driving the front wheels and the second output shaft 17 for driving the rear wheels at a reduction ratio of 1. Four-wheel drive driving with transmission is achieved.

When an increase in output torque is required, such as on a steep slope during four-wheel drive driving, the hydraulic pressure to the hydraulic servo is controlled by the inhibitor valve 260, which gradually supplies line pressure to the hydraulic servo 50, and at the same time controls the hydraulic servo 70 at an appropriate timing. The hydraulic pressure is discharged, the brake 5 is gradually engaged, and the clutch 7 is smoothly released. As a result, the sun gear 41 and the carrier 44 are released, and the ring gear 43 is fixed, and the power is decelerated from the input shaft 2 via the sun gear 41, the planetary gear 42, and the carrier 44 to the first output shaft 3.
The torque is transmitted to the second output shaft 17, and a four-wheel drive driving state with large torque is obtained. Table 1 shows the setting range of transfer manual shift 1-, brake 5, clutch 7 and 8.
This shows the engagement and disengagement of the vehicle and the running state of the vehicle.

Table 1 In Table 1, ○ indicates the engagement state of the frictional engagement element, ×
indicates a released state. The reduction ratio λ is the ratio of the number of teeth between the sun gear 41 and the ring gear 43 of the Tt star gear machine, and the value of the reduction ratio is the reduction ratio - (1 + λ) / when λ is 0.5.
This is dedicated for λ=3.0.

Next, a hydraulic control system when the four-wheel drive gear type automatic transmission of the present invention is applied to a gear type automatic transmission with three forward speeds and one reverse speed will be explained with reference to FIG.

Figure [January 00] is an example of a known full hydraulic control system for a gear type automatic transmission with three forward speeds and one reverse speed. The oil is regulated to a predetermined oil pressure (line pressure) by an oil pressure control valve 103 and guided to a line oil pressure output oil passage 104 . The pressure oil led to the line oil pressure output oil path 104 is passed through the manual valve 105 to the 1-2 shift valves 106 J3 and 2-3.
It is guided to the shift valve 107.

A throttle valve 108 generates oil Fi (throttle pressure) in an oil passage 109 according to the throttle level.

110 is a governor valve, which adjusts the hydraulic pressure according to the vehicle speed (governor pressure)
is occurring in the oil passage 111.

1-2 shift valve 106 and 2-3 shift 1 to valve 107 operate oil passage 112.1 in relation to the magnitude of the throttle pressure and governor pressure supplied from oil passage 109 and oil passage 111.
13 and 114, and controls the supply and discharge of pressure oil to the hydraulic servos C1, C2, B1, B2, and B3 of the clutches and brakes.

In this embodiment, at the first forward speed, the hydraulic servo C
Pressure oil is supplied to 1, and at the second forward speed, hydraulic servo CI
, [32], pressure oil is supplied to hydraulic servos CI, C2, and 82 during third forward speed, and pressure oil is supplied to hydraulic servos C2 and B3 during reverse movement.

The hydraulic control circuit 200 of the four-wheel drive transfer device includes:
Speed selection valve 201, modulator valve 210, inhibitor valve 2
Consists of 20.

The speed selection valve 201 controls communication between the line oil r=output oil passage 104 and the oil passages 202 and 203 by operating a shift lever on the driver's seat. During two-wheel drive, the line pressure output oil passage 104 is closed by the spool 204 of the speed selection valve 201. , the line pressure output oil passage 104 communicates with the oil passage 202 when the four-wheel drive is directly connected. During four-wheel drive deceleration, the line pressure output oil passage 104 communicates with the oil passage 202 and the oil passage 203.

The modulator valve 210 has a spool 211 and a spring 2
12, which regulates the pressure oil in the oil passage 203 and connects it to the oil passage 213.
generates modulator pressure.

The inhibitor valve 220 includes a spool 221 and a spring 22.
2. Consisting of oil chambers 223 and 224, the line pressure output oil passage 104 and oil The communication with the passage 225 and the oil passage 226 is switched.

Next, its effect will be explained.

During two-wheel drive...The line pressure output oil passage 104 is not communicated with the oil passage 202 and the oil passage 203. Since no pressure oil is introduced into the oil chamber 223 of the inhibitor valve 220, the spool 221 is moved by the spring 222 to t7 as shown in the figure.
'J, and connects the line pressure output oil passage 104 and the oil passage 225. The line pressure of the line pressure output oil passage 104 is the oil passage 2.
25 to the hydraulic servo 70 of the clutch 7 to engage the clutch 7.

When directly connected to four-wheel drive...The line pressure output oil passage 104 is connected to the oil passage 202. Line pressure output oil passage 104
The line pressure is supplied to the hydraulic servo 70 and engages the clutch 7 in the same manner as in the case of two-wheel drive. Further, the line pressure guided to the oil passage 2O2 is supplied to the hydraulic servo 50 of the clutch 8 to engage the clutch 8.

During 4-wheel drive deceleration...Line pressure output oil passage 104
is connected to oil passage 202 and oil passage 203. The line pressure led to the oil passage 203 is regulated by the modulator valve 210 to generate a modulator pressure in the oil passage 213.

When the governor pressure guided from the oil passage 111 to the oil chamber 224 of the inhibitor valve 220 is above a certain value, the spool 221 is set upward in the figure against the modulator pressure acting on the oil chamber 223 from the oil passage 213, Maintains 4-wheel drive direct connection state. When the vehicle speed decreases and the governor pressure becomes below a certain value A, the spool 22 is
1 moves downward in the drawing, connects the line pressure output oil passage 104 and oil passage 226, and connects the oil passage 225 to the oil drain port 227.

The pressure oil of the hydraulic servo 70 of the clutch 7 is discharged from the oil drain port 227 and the clutch 7 is released, and the line pressure of the line pressure output oil passage 104 is led to the hydraulic servo 50 of the brake 5 through the oil passage 226 to discharge the brake. 5 is engaged, and the four-wheel drive becomes 5A speed state. When the vehicle speed increases in the four-wheel drive deceleration state and the governor pressure exceeds the set value B (B>A), the governor pressure overcomes the modulator pressure and moves the spool 221 upward in the figure, reducing the line pressure output oil. road 104 and oil road 22
6 is disconnected, the oil passage 226 is connected to the oil drain port 228, and the line pressure output oil passage 104 and the oil passage 225 are also connected.

The pressure oil of the hydraulic servo 50 is discharged through the oil passage 226 and the oil drain port 228, and the brake 5 is released.
Line pressure is supplied to the hydraulic servo 70 through 25, the clutch 7 is engaged, and the four-wheel drive is directly connected.

The governor pressure A when changing from the 4-wheel drive direct connection state to the 4-wheel drive deceleration state and the governor pressure B when changing from the 4-wheel drive deceleration state to the 4-wheel drive direct connection state are the land 2 of the spool 221.
Since there is a difference in area between the land 21a and the land 221b, the relationship is (governor pressure B>governor pressure A).

The hydraulic control circuit 200 of the four-wheel drive transfer device includes a solenoid valve 230, 240, a switching valve 250, an inhibitor valve 2601, and a check valve 270, 280.

The solenoid valves 230 and 240 each have a moving core 23.
1.241, solenoid 232.242, spring 2
33.243, opening 234.244, oil drain port 235.2
45, the solenoid 232.242 is energized, and the moving core 231.2 is moved upward in the figure to listen to the opening 234.244, and the pressure oil in the oil passage 237.247 partitioned by the orifice 236.246 is drained. Mouth 23
5. Discharge from 245. When the solenoid 232.242 is de-energized, the moving core 231.241 is moved downward in the drawing by the spring 233.243 to close the opening 234.244 and apply hydraulic pressure (
line pressure).

When you operate the manual shift on the driver's seat and set the H2, H4, or L4 range, the electronic control device (described later) activates the 1.2 solenoid valves 230 and 240 as shown in Table 2.
is ON and OFF controlled, and each frictional engagement element is operated by hydraulic oil selectively sent from the transfer hydraulic control device 200 to each hydraulic servo 50, 70, 80, and the transfer 10 is in each shift state (1). 2 or H4 or L4
). Furthermore, when the first solenoid valve 230 is turned on by the hydraulic circuit configuration as described above, the transfer is set to H2 regardless of whether the second solenoid valve 240 is turned on or off.

The operation of solenoid valves 230 and 240 is as shown in Table 2. ON means energized, and OFF means not energized.

Table 2 The switching valve 250 is composed of a spool 251, a spring 252, and an oil chamber 253, and controls communication between the line hydraulic output oil path 104 and the oil path 292 in accordance with the pressure oil acting on the oil chamber 253.

The inhibitor valve 260 consists of a spool 261.262, a spring 263, and an oil chamber 264.265.266.
The oil chamber 264 and oil passage 290
and controls communication with the oil passage 291.

Next, its operation will be explained.

During two-wheel drive...Solenoid valves 230 and 240 are both de-energized and line pressure is generated in oil passages 237 and 247. The line pressure of the oil passage 237 is controlled by the switching valve 250.
act on the oil chamber 253 to move the spool 251 downward in the figure, thereby blocking the line oil pressure output oil passage 104 and the oil passage 292. The line pressure of the oil passage 247 acts on the oil chamber 264 of the inhibitor valve 260 to move the spools 261 and 262 downward in the figure, connecting the line oil pressure output oil passage 104 and the oil passage 290, and increasing the line pressure of the line oil pressure output oil passage 104. Pressure oil is introduced to the hydraulic servo 70 via the check valve 270 and the clutch 7 is engaged.

When the four-wheel drive is directly connected......The solenoid valve 230 is energized, so the pressure oil in the oil passage 237 is drained from the oil drain port 235, and the spool 251 of the switching valve 250 is connected to the spring 252.
The line hydraulic output oil passage 104 and the oil passage 292 are connected to each other by moving upward in the figure. Pressure oil in the line hydraulic output oil passage 104 is guided to the hydraulic servo 80 through the oil passage 292, and the clutch 8 is engaged. Further, since the solenoid valve 240 is de-energized, the clutch 7 is also engaged in the same manner as in the case of two-wheel drive.

During four-wheel drive deceleration...The solenoid valve 230 is energized, and the clutch 8 is engaged in the same manner as when the four-wheel drive is directly connected. Further, the solenoid valve 240 is also energized, and the pressure oil in the oil passage 247 is discharged from the oil drain port 245. When the governor pressure acting on the oil chamber 265 exceeds a certain value,
The spool 262 is in the lower position shown in the figure, and engages the clutch 7 in the same manner as when four-wheel drive is directly connected. When the vehicle speed decreases and the governor pressure becomes below a certain value A, the spool 262 moves upward in the figure to disconnect the line oil pressure output oil passage 104 from the oil passage 290 and connect the oil passage 290 to the oil drain port 267. The pressure oil in the hydraulic servo 70 is discharged and the clutch 7 is released, and the line hydraulic output oil passage 104 and the oil passage 291 are connected to each other, and pressure oil is supplied to the hydraulic servo 50 via the dinic valve 280 to engage the brake 5. match. When the clutch 1 is released and the brake 5 is engaged, the transfer device enters a deceleration state. From this state, the vehicle speed increases and the governor pressure changes to the set value B (
When B > A), the spool 262 moves downward in the figure, cuts off the communication between the line hydraulic output oil passage 104 and the oil passage 291, connects the oil passage 291 to the oil drain port 268, and closes the hydraulic servo 50.
Pressure oil is discharged to release the brake 5, and at the same time, the line oil pressure output oil passage 104 and the oil passage 290 are connected to each other, and the clutch 7
, and the four-wheel drive is directly connected.

FIG. 5 shows a hydraulic control device according to another embodiment of the present invention, in which a hydraulic control circuit 2 of a four-wheel drive transfer device is shown.
00 is composed of a solenoid valve 300.310, a switching valve 3201, an inhibitor valve 330, and a check valve 340.350.

The solenoid valves 300 and 310 have the same structure as shown in FIG. 4, and their operation is as shown in Table 3.

Table 3 The switching valve 320 includes a spool 321, a spring 332, and an oil chamber 323, and controls communication between the line pressure output oil passage 104 and the oil passage 292 in accordance with the pressure oil acting on the oil chamber 323.

The in/out valve 330 consists of a spool 331, 332, a spring 333, 334, and an oil chamber 335, 336, 337. and hh road 291
Controls communication with.

During two-wheel drive... Both the solenoid valves 300 and 310 are energized, the spool 331 of the switching valve 320 is located at the top in the figure, and the spool 331 of the inhibitor valve 330 is
is positioned at the lower side in the figure by a spring 334. Oil road 1
04 pressure oil is guided to the hydraulic servo 70 through the oil passage 290, and the clutch 7 is engaged.

When directly connected to 4-wheel drive... Since the solenoid valve 300 is de-energized, the spool 321 of the switching valve 320 moves downward in the figure, and the pressure oil in the line pressure output oil passage 104 flows into the oil passage 29.
2 through 1 to the hydraulic servo 80, and the clutch 8 is engaged.

During 4-wheel drive deceleration... Solenoid valve 300.31
Both 0 and 0 are de-energized. The clutch 8 is engaged in the same manner as in four-wheel drive. Spool 3 of inhibitor valve 330
32 is moved upward in the drawing by the hydraulic pressure acting on the oil chamber 335, and the spool 331 is controlled by the governor pressure acting on the oil chamber 336. When the governor pressure is equal to or higher than the set value, the spool 331 is positioned downward in the figure and maintains the directly connected state. When the governor pressure becomes lower than the set value A, the spool 331 is moved upward in the figure by the spring 333, and the line pressure output oil passage 1 is moved upward.
04 and the oil passage 291, engage the brake 5,
Wheel drive deceleration occurs. When the spool 331 moves upward in the drawing, the oil passage 111 also communicates with the oil chamber 337 and presses the spool 331 upward in the drawing. From this state, when the vehicle speed increases and the governor pressure exceeds a value (B>A) that overcomes the force of the spring 333 and the force of the governor pressure acting on the oil chamber 337, the spool 331 moves downward in the figure. 4 again
Wheel drive is directly connected.

[Brief explanation of drawings]

Fig. 1 is a sectional view of a transfer and a known gear type automatic transmission related to the automatic transmission mill for four-wheel drive of the present invention, Fig. 2 is a schematic diagram showing the power transmission system of a vehicle, and Fig. 3 is a forward 3. FIGS. 4 and 5 are circuit diagrams of a hydraulic control device for a four-wheel drive transfer in a four-wheel drive automatic transmission of the present invention when applied to a gear type automatic transmission with one reverse gear. 4
FIG. 2 is a circuit diagram of a four-wheel drive transfer hydraulic control device for a wheel drive automatic transmission.

Claims (1)

[Scope of Claims] 1) A main transmission controlled by a main hydraulic control device including a line hydraulic pressure generation source, and a four-wheel drive whose gears are changed by an auxiliary hydraulic control device that utilizes the line hydraulic pressure of the main hydraulic control device. A four-wheel drive automatic transmission comprising a sub-transmission for four wheels, characterized in that line hydraulic pressure is supplied directly to the sub-hydraulic control device from a line hydraulic output oil path of the main hydraulic control device. Drive automatic transmission.