JPS6136558A - Hydraulic control device of speed change gear - Google Patents

Abstract

PURPOSE:To prevent unstabilization of discharged oil pressure by providing a deflating device in an operation oil return path extending from a hydraulic power transmission device to an oil sump of an operation oil circulating path in a hydraulic control device of a speed change gear. CONSTITUTION:A hydraulic power transmission device (torque converter) 50 includes a pump 55, a turbine 56 and a stator 57, and a hydraulic control device has an oil pump 101, a pressure regulating valve 10, a direct coupled clutch control valve 40 and so on. An oil path 6B which is an operation oil return path from a torque converter 50 is provided with a deflating device 3, whereby when air is discharged from the torque converter 50 to the oil path 6B, air is automatically discharged. Thus, a sudden expansion of air can be prevented to prevent an excessive increase of pressure in a transmission gear and a leakage of oil.

Description

[Detailed Description of the Invention] [Field of Industrial Application] The present invention applies to fluid transmission devices such as torque converters and fluid couplings, and transmissions such as 3!2 ring gear type, constant mesh type, and continuously variable transmission. The present invention relates to a hydraulic control device for a combination transmission.

[Prior Art] This type of hydraulic control device regulates the pressure of hydraulic oil sucked up by an oil pump from an oil pan (oil reservoir) according to vehicle running conditions such as vehicle speed, throttle opening, and selected position of the select lever. It mainly generates line pressure for driving the fluid actuator (hydraulic servo), secondary line pressure that is the operating pressure of fluid transmission fi and If, ll1Wi oil pressure, etc. Further, the hydraulic oil supplied to the fluid transmission device is returned to the oil pan either as is or after being cooled by being circulated through an oil cooler.

[Problems to be Solved by the Invention] However, in automatic transmissions for vehicles, the foaming performance of the hydraulic fluid is significantly reduced at extremely low temperatures such as those found in cold regions.
Hydraulic oil is discharged from the lubricant supply hole of the transmission and agitated by a rotating member to generate foamy hydraulic oil containing many small bubbles, and this foamy hydraulic oil is sent into the fluid transmission device. In a fluid transmission device, air and mail are separated by centrifugal force due to the difference in specific gravity, and due to buoyancy, an air pocket is generated at a slightly higher position from the center, and this air is Released intermittently.

This intermittently released air is compressed in the hydraulic circuit and rapidly engraves when it returns to the oil pan (oil sump). As a result, the pressure within the transmission increases, oil leaks through the breather, and if the oil pump sucks in the released air, the oil pressure becomes unstable.

SUMMARY OF THE INVENTION An object of the present invention is to provide a hydraulic control system for a transmission that can prevent oil leakage and destabilization of the oil pump discharge hydraulic pressure.

[Means for Solving the Problems] The hydraulic control device for a transmission of the present invention is configured to circulate the pressure oil generated by the hydraulic source to the oil reservoir via the fluid transmission device. Transmission i! Operation from the oil sump to the oil sump
jThe configuration includes a venting device installed on the return route.

[Operation of the invention, =-=] The hydraulic control device of the present invention for a 3-m1-meter hydraulic system supplies hydraulic oil I! from the fluid transmission device to the oil pan. Since the air bleed device is attached to the lyA path, a sudden flow of air can be prevented, and as a result, excessive pressure rise in the transmission and oil leakage can be prevented. Also, since air is prevented from being sucked into the oil pump, oil pressures such as discharge oil pressure and line pressure are stabilized.

〔Example] Next, the present invention will be explained based on an embodiment shown in the drawings.

50 is a fluid transmission device (torque converter in this embodiment)
, a pump 55, a turbine 56 and a stator 51
The pump 55 is connected to an mtPA crankshaft 58 via a front cover 51, and is connected to an output shaft 59 of a turbine 56, and is connected to an inner surface (first surface) 52 of the front cover 51 and the output shaft 59. A direct coupling clutch 54 consisting of a clutch disc 53 connected to a shaft 59 is provided.

Hydraulic control consists of an oil source consisting of an oil strainer 100 and an oil pump 101 arranged in an oil reservoir, a pressure regulating valve (regulator valve) 10, a throttle valve 20, and a second
A pressure regulating section consisting of a pressure regulating valve 30, a cutback valve 104, a cooler bypass valve 105, a pressure relief valve 106, a direct clutch control valve 40, and a third air extraction device of the present invention, a normal manual valve, and a 1-2 shift valve. , 2-3 shift valve, 3-4 shift valve, clutch, brake σ Each hydraulic servo is opened by the output of the computer, and each shift valve is opened by tI.
It consists of a shift (speed change) control section including a solenoid valve controlled by II.

Hydraulic oil pumped up from an oil reservoir by an oil pump 101 via an oil strainer is adjusted to a predetermined oil pressure (line pressure) by a pressure regulating valve 10 and then supplied to an oil path 1 .

The pressure regulating valve 10 has a spool 12 provided with a spring 11 at the lower side in the figure, and a third plunger that abuts the spool 12 and is arranged in series at the lower side in the figure. Spool 12
is the third lower end land of the third plunger from the bottom in the figure.
Throttle pressure of oil passage 9 applied to 1 and spring 11
When moving backward, line pressure is applied from the oil passage 5 to the upper land 32 of the plunger 11, and from the other side, the upper land 121 of the spool 12 is applied to the upper land 32 of the spool 12.
It receives the feedback pressure of the line pressure applied to the line pressure, adjusts the communication surface between the oil passage 1, the oil passage 6, and the drain boat 14, and outputs line pressure to the oil passage 1 according to the running conditions. , supplies yarn surplus pressure oil to the oil passage 6.

In the throttle valve 20, a throttle plunger 201 strokes in accordance with the amount of depression of the accelerator pedal, and the plunger 201 and a spring 204 are connected to a bent spool 202.
Move the spool 202 via the spring 203 between the
The line pressure supplied from the oil passage 1 is regulated to a throttle pressure according to the throttle opening and output to the oil passage 9.

The second pressure Jv) valve 30 has a spool 32 on which a spring 31 is mounted downward in the drawing. The spool 32 receives the hydraulic pressure of the oil passage 6 from above on the illustrated upper end land 321, and receives the spring load f! of the spring 31 from the other side. Then, the throttle pressure of the oil passage 9 is shifted to the small-diameter lower end land 322 shown in the figure by the number plate, and the degree of communication between the oil passage 6, the lubricating oil supply oil passage 7, and the drain boat 34 is adjusted to W4, and the oil passage 6 Secondary line pressure (torque converter pressure) according to throttle pressure
At the same time, lubricating oil is supplied to the oil passage 1.

The lock-up relay valve 40 has a spool 42 (lower part shown) and a large diameter plunger 43 (upper part shown) connected in series.
A spring is attached to the upper end of the plunger 43 in the drawing. From above, the spool 42 is connected to the large diameter plunger 43 via r2 to the oil passage 1, and the solenoid pressure Ps of the oil passage 1B in which the solenoid valve S° is provided and the spring load of the spring 41 It is displaced by receiving the line pressure of the oil passage 8 supplied from the shift section 11911 from below. When the solenoid pressure Ps is at a high level, the spool 42 is set to the negative position shown in the figure, and connects the oil passage 6, which is the hydraulic pressure source, with the direct coupling clutch release side oil passage 6A, and also connects the circulation oil passage 6C to the oil cooler with the direct coupling clutch. It will connect with the Yagawa Oil Road 6B. As a result, the clutch release side 50A of the clutch disc 53 has a higher oil pressure than the clutch engagement side 508, the clutch disc 53 separates from the inner surface 52 of the front cover, and the direct coupling clutch 54 is released. In this state, the hydraulic oil is oil sump → oil pump 101 → oil path 1 → oil path 6 → oil path 6A.
→In-out boat 5a of torque converter 50→In-out boat 5b of torque converter 50→Oil passage 6B→
Circulation is performed from oil path 6C → oil cooler → oil sump, and air accumulated in torque converter 50 is intermittently discharged via oil path 6B, which is the hydraulic oil return path, lock-up relay valve 40, and oil path 6C. . Further, when the solenoid pressure Ps of the oil passage 1B is at a low level, the spool 42 is set upward in the figure, and the oil passage 6 communicates with the oil passage 6B, and the oil! l 6
A contacts drain boat 44. As a result, the oil pressure on the clutch engagement side 50B of the clutch disc 53 becomes louder than the oil pressure on the clutch release side 50A, the clutch disc 53 is pressed against the inner surface 52 of the front cover, and the direct coupling clutch 54 is engaged.

The eleventh solenoid valve S that controls the lock-up relay valve 40 controls the oil pressure in the illustrated upper end oil chamber 43 of the lock-up relay valve 40 that communicates with the oil path 1B that communicates with the oil path 1 via the orifice r2. This solenoid valve S generates high-level solenoid pressure in the oil chamber 43 when not energized, and presses the spool 42 downward in the drawing together with the stepped spring 41, and when energized the spool 42 is positioned at the bottom in the drawing. The pressure in the oil chamber 43 is evacuated and reversed to a low level solenoid pressure, and the spool 42 is positioned upward in the figure.

The air vent @3 of the present invention is attached to the oil passage 6B, which is the hydraulic oil return path from the torque converter 50, and
When air is exhausted from the fluid transmission device 250, the air is selectively exhausted into the automatic transmission case. In addition,
The air removal device may be disposed in the oil passage 6C.

Bukke viLlli! 3, as shown in FIG. 2, has a hollow pore I-shaped main body 3A in which a large inner diameter valve seat chamber 302 with a valve port 301 is provided at the rear end of the rO1 compared to the front end, and a A cylindrical spring retainer 3B fixed coaxially by caulking, a spherical valve 3C arranged in a valve seat chamber 302 in the main body 3A, and a spherical valve 3c that presses the spherical valve 3C against the valve port. and a spring 3D interposed between the retainer 3B and the retainer 3B. In this air venting device 3, when the pressure in the oil passage 6B exceeds a set value, the valve port 301 opens.
Air is selectively discharged by the restrictor RO. In this case, some hydraulic oil is discharged, but by appropriately selecting one diameter of rO, the amount of hydraulic oil discharge can be made sufficiently smaller than the air discharge n1. Note that a plurality of venting devices 3 may be provided, and the restrictor rO may be a large number of minute holes.
Furthermore, six somewhat larger rows provided in one row would also be 9.

FIG. 3 shows another embodiment.

In this embodiment, the spool 42 of the lock-up relay valve 40
A center hole 45 is provided in the upper part of the spool 42, and a rO is provided in the wall between the lower end land 4a and the intermediate land 4b to communicate the oil passage 6B and the oil passage 6C. Furthermore, a large inner diameter valve seat chamber 47 is provided in the upper end land 4C shown in the figure, and when the spool 42 is set in the upper position shown in the figure, it is connected to the drain boat 4B, and when it is set to the lower blade shown in the figure, it is closed. A drain hole 4θ is formed, and a center hole 4 in yJ is formed.
Attach the spring retainer plug 4A to the upper end opening of 5! A spherical valve 4C is disposed in the valve seat chamber 47, and a spring 4D is interposed between the valve 4C and the retainer plug 4A to press the valve 4C against the valve port 4E. By providing it within the spool 42 as in this embodiment, there is no need to provide a mounting space for the air venting device 3 shown in the previous embodiment, and the number of man-hours for mounting can also be reduced. In addition, since air is allowed to bleed only when the direct clutch is released, it is possible to prevent oil from constantly leaking and to improve air bleed mr*.

Although a restriction alone may be used as the air venting device, using a combination of a restriction and a relief valve has the advantage of reducing oil leakage in steady state and releasing only air, and preventing oil leakage in stationary state.

FIG. 4 shows yet another embodiment.

In this example! In the lock-up relay valve 4° shown in FIG. 3, the spool 42 and the plunger 43 are integrated into one spool 408, and a drain hole 46 is formed to connect the center hole 45 and the drain boat 48. The lock-up relay valve 4° of this embodiment also has the same effect as that shown in FIG.

[Brief explanation of drawings]

Fig. 1 is a schematic diagram of the hydraulic pressure 1i1J ill @ Iff of an automatic transmission for a vehicle using the transmission hydraulic control device of the present invention, Fig. 2 is a sectional view of an embodiment of the air extraction device, and Fig. 3 is a A sectional view of another embodiment of the air venting device, W44 is a sectional view of still another embodiment of the venting device W.

Claims (1)

[Scope of Claims] 1) An air vent device in the hydraulic oil return path from the fluid transmission device to the oil reservoir in the hydraulic oil circulation path for circulating the pressure oil generated by the hydraulic power source to the oil reservoir via the fluid transmission device. Hydraulic control device for the transmission equipped with. 2) The hydraulic oil return path is provided with an oil cooler and a relief valve that prevents overpressure fluid from flowing into the oil cooler, and the air venting device is provided between the fluid transmission device and the relief valve. A hydraulic control device for a transmission according to claim 1, further comprising a hydraulic control device for a transmission. 3) The hydraulic oil circulation path is provided with an oil passage switching valve that switches communication between the hydraulic oil outgoing path from the hydraulic power source to the fluid transmission device or the hydraulic oil return path and the fluid transmission device, and the air purge device is 2. The hydraulic control device for a transmission according to claim 1, wherein the hydraulic pressure control device is configured to communicate with the hydraulic oil return path in response to control of a valve body. 4) The fluid transmission device is provided with a direct coupling clutch,
The speed change according to claim 3, wherein the oil passage switching valve is a spool valve that engages and disengages the direct coupling clutch, and the air venting device is provided in a spool of the spool valve. Machine hydraulic control device. 5) The transmission control device according to claim 4, wherein the air vent device is communicated with the circulation path only when the direct clutch is released. 6) The hydraulic control device for a transmission according to claim 1, wherein the air venting device is an opening with a throttle. 7) The hydraulic control device for a transmission according to claim 1, wherein the air venting device comprises an opening with a throttle and a relief valve provided in the opening.