JPS5827151Y2 - Hydraulic control device in hydraulically operated automatic transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates primarily to a hydraulic control device for a hydraulically operated automatic transmission for automobiles.

Originally, this type of device was composed of a switching valve, an accumulator, and a servo piston, and it is preferable to make it easy to manufacture and to make the device relatively compact as a whole.

The purpose of the present invention is to obtain a device that satisfies the above requirements.
The mission mechanism 7 includes a hydraulically operated clutch 3, a gear type clutch 5 switched by a shifter 4, and a plurality of stages of a drive gear train 6 selected by both clutches 3 and 5; In a hydraulically operated automatic transmission equipped with an oil pump 8 interlocked with A main block 9 and a sub-block 10 are sequentially stacked and attached to the inner surface of the partition wall 1, and the main block 9 is formed so that a plurality of stages of the driving gear train 6 are disposed therebetween.
A switching valve 12 for selectively applying pressure oil from the oil pump 8 to the hydraulically operated clutch 3 and the servo piston 11 that operates the shifter 4 of the gear type clutch 5 is housed therein, and the sub-block 10 an accumulator 13 for the hydraulically operated clutch 3 and the servo piston 1;
1, and the switching valve 12 is accommodated in the main flock 9 in an axial direction parallel to the partition wall 1, and the accumulator 13 and the servo piston 11 are arranged in the sliding direction perpendicular to the partition wall 1. The blocks 9 and 10 are housed in a sub-block 10, and form oil passages therebetween, and restrict the movement of the piston 13a of the accumulator 13 and the servo piston 11, so that each piston 13
Separate plate 2 forming the working hydraulic chambers a and 11;
The two shafts 14 and 15 are superimposed on each other through the shafts 14 and 15, and are laterally offset from the shafts 14 and 15.

To explain this in detail, the mission mechanism 7 has an input shaft 14 and an output shaft 15 supported by the partition wall 1 and extending parallel to each other. The oil pump 8 is driven by one of the shafts 14 and 15 and has an outer case 8a fixed to the partition wall 1, and the switching valve 12 is parallel to the partition wall 1. The accumulator 13 and the servo piston 11 are accommodated in the sub-block 10 in the sliding direction perpendicular to the partition wall 1, and both blocks 9, 10V'i and The servo piston 11 is laterally offset from both shafts 14 and 15, and has a shift fork 11a extending in the opposite direction to the main block 9 and a shift fork 11b at its tip.
The pressure receiving surface 13b of the pressure oil of the accumulator piston 13aU in 3 is arranged on the main block 9 side.

More specifically, as shown in FIG. 1, a transmission case 2 (as clearly shown in FIG. The input shaft 14 is connected to the output shaft 18 of the engine via the torque converter 20 in the torque converter case 16, and the output shaft 15 is connected to the output shaft 18 in the differential case 17. It is connected to the wheel side via the differential gear 19.

The drive gear train 6 consists of three forward stages and one reverse stage, and the hydraulically operated clutches 3 are arranged at three positions, two on the left and right on the input shaft 14 and one on the output shaft 15. ■Speed, 2nd speed and 3rd speed
In addition, a gear type clutch 5 is provided on the output shaft 15 so that the reverse gear can be selected by rightward movement of the shifter 4.

Furthermore, three switching valves 12 are arranged, as shown in FIG. 3, a central manual valve 12a, a 1-2 shift hull 7" 12b below it, and a 2-3 shift pulse 7" 1 above it.
2 c, and furthermore, the accumulator 1
As clearly shown in FIG. 4, servo pistons 3 are provided at the upper and lower front, and the servo piston 11 is arranged behind them.

Throttle pressure response valve 21Fi shown in FIG. 5 generates throttle pressure for switching shift valves 12b and 12c, and is arranged in series between the pressure receiving surfaces of pump 8 and shift pulps 12b and 12c. t 2 l
Consists of 3 valves: b, 21 and c.

These 31-piece valves 21a, 21b, and 21c are accommodated in the subblock 10 in three stages in the sliding direction of the accumulator 13, and since the wall thickness of the subblock 10 can be shared, the projected area can be reduced. Multiple valves can be placed.

Furthermore, two details of the accumulator 13 are as shown clearly in FIG.

According to the above configuration, main block 9 and sub block 1
0 forms an oil path between the two, and is stacked in two stages via a separate plate 22 that restricts the movement of the accumulator piston 13a and the servo piston 11 and forms an operating hydraulic chamber for each piston 13a, 11. Therefore, it is advantageous that the projected area can be made small in the overlapping direction.Furthermore, since the accumulator 13, which is relatively high in height, and the servo piston 11, which requires a stroke, are arranged close to each other, it is possible to reduce the burden on other parts. In addition, since the switching valve 12 has a relatively small diameter, the main block 9 can be made relatively thin.Furthermore, since the switching valve 12 and the accumulator 13 are close to each other, the switching valve 12 has a relatively small diameter. The hydraulic pressure immediately after the valve 12 can be controlled by the accumulator 13, so that the pressure rise characteristic can be accurately obtained. Furthermore, the servo piston 11 is also close to the switching valve 12, so that the delay in operation can be eliminated, thus reducing the delay in operation as a whole. It is possible to obtain a relatively compact device with less shock at the time of shifting, and it can be easily configured in a front engine, front drive type automobile.

To explain further, in order to increase the capacity of the accumulator 13, it is necessary to increase the diameter and lengthen the stroke, and in order to obtain sufficient operating force, the diameter of the servo piston 11 must also be increased and the arrangement of the gears must be adapted. Therefore, when the two parts are separated from each other, the arrangement of other parts is restricted and the overall thickness becomes thicker. It is preferable that the two be provided close to each other so as to have a common thick portion.

However, in this case, when the accumulator 13 is orthogonal to the servo piston 11, the projected area as a whole increases and the height of the cylinder portion of the servo piston 11 is not effectively utilized. It is a good idea to have one.

Furthermore, since the oil path from the manual pulp or shift valve as the switching valve 12 to the hydraulically operated clutch 3 is generally a curved path with high flow resistance, if the accumulator 18 is placed away from the valve 12, a large amount of pressure oil will be absorbed. flows into the passage and is easily affected by the resistance, thus the switching valve 12
The pressure receiving surface 13b1 facing the accumulator 13 should be a short passage.

Furthermore, the gear type clutch 5 is generally switched after the power system is once disconnected, and then the power system is re-established. Therefore, in order to shorten the shift operation time, it is necessary to speed up the movement of the shifter 4. This request can be met by placing the servo piston 11 close to the switching valve 12.

Thus, it is preferable that the accumulator 13 is provided directly above the discharge port of the shift valve as the switching valve 12, and the servo piston 11 is provided directly above the port of the manual pulp as the switching valve 12, so that they communicate over the shortest distance.

Furthermore, it is also conceivable to attach the main block 9 and the sub-block 10 side by side to the inner surface of the partition wall 1;
This not only increases the projected area but also makes the internal passages long and complicated, which is undesirable.

In this way, according to the present invention, the main block 9 that accommodates the switching valve 12 and the sub-block 10 that accommodates the accumulator 13 and the servo piston 11 are made separately, so manufacturing can be facilitated.
A switching valve 12 is housed in the axial direction parallel to the partition wall, and an accumulator 13 and a servo piston 11 are housed in the sub-block 10 in a sliding direction perpendicular to the partition wall 1. Both blocks 9 and 10 (I'i The piston 13a of the accumulator 13 and the servo piston 11 are prevented from moving by forming an oil passage between them.
3a and 11 through the separate plates 22 that form the hydraulic pressure chambers 3a and 11, the oil passages are short and the passage resistance is reduced, making it easy to match the characteristics of the rise or fall of the oil pressure, and Since no special stopper is required for the pistons 13a, 11, each piston 13a, 11 can be moved right next to the main block 9, and can be mounted without increasing the height of the sub-block 10. 10 is the input shaft 14 of the mission mechanism 7
Since it is laterally offset from the output shaft 15, a relatively thin main block 9 housing the relatively small diameter switching valve 12 and a relatively thick main block 9 housing the relatively large diameter accumulator 13 and the servo piston 11 are formed. This has the advantage that the sub-block 10 can be contained within a relatively small projected area.

[Brief explanation of the drawing]

Fig. 1 is a cutaway plan view of an example of a transmission equipped with the device of the present invention, Fig. 2 is a side view thereof, Fig. 3 is a rear view thereof, Fig. 4 is a side view of only the main parts thereof, and Fig. 5 Figures and Figure 6 are the ■-V
FIG. 3 is a cross-sectional view taken along line and VI-VI. 1... Bulkhead, 2... Mission case, 3... Hydraulic operated clutch, 4... Shifter, 5... Gear type clutch, 6...
Drive gear train, 7...□Rough 3F mechanism, 8...
... Oil pump, 9 ... Main flock, 10
...Sub block, 11 ... Servo piston, 12 ... Switching valve, 13 ... Accumulator.

Claims (1)

[Claims for Utility Model Registration] A hydraulically operated clutch 3, a gear type clutch 5 operated by a shifter 4, and a drive gear selected by both clutches 3, 5 are disposed within a transmission case 2 having a partition wall 1 on its end face. In a hydraulically operated automatic transmission comprising a transmission mechanism 7 that is connected to a plurality of stages in a row 6, and an oil pump 8 interlocked with the transmission mechanism 7, the transmission mechanism 7 is supported by the partition wall 1 and parallel to each other. It has an extending input shaft 14 and an output shaft 15, and is formed so that a plurality of stages of the drive gear train 6 are disposed between the shafts 14 and 15, and on the inner surface of the partition wall 1, a main block 9 and a sub A servo piston 11 that operates the hydraulically operated clutch 3 and the shifter 4 of the gear type clutch 5 is installed by sequentially stacking the blocks 10 and the main block 9 and supplying pressure oil from the oil pump 8 to the hydraulically operated clutch 3 and the shifter 4 of the gear type clutch 5.
The sub-block 10 accommodates a switching valve 12 that selectively acts on the hydraulically operated clutch 3 and the servo piston 11. The accumulator 13 and the servo piston 11 are accommodated in the sub-block 10 in a sliding direction perpendicular to the partition wall 1, and both blocks 9 and 10 are accommodated in the main block 9 in parallel axial directions. , forming an oil passage between the two, and controlling the movement of the piston 13a of the accumulator 13 and the servo piston 11 via a separate plate 22 that forms an operating hydraulic chamber for each piston 13a. A hydraulic control device for a hydraulically operated automatic transmission, which is installed laterally offset from the two shafts 14°15.