JPH1130320A - Hydraulic control device for automatic transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To restrain excess variation for the discharge flow rate of a hydraulic pump to smoothly control a shift constantly. SOLUTION: This device is equipped with: a hydraulic pump driven by an engine, a flow control valve 2 equipped with a spool 5 equipped with an orifice 50 to control a flow rate from the hydraulic pump based on the pressure difference between the fore and rear of the orifice 50, and a hydraulic control means for driving the shift mechanism of an automatic transmission in accordance with pressure oil from the flow control valve 2; and the flow control valve 2 demarcates a damping chamber 8, for restraining the excess displacement of the spool 5, between the outer periphery of the spool 5 and the inner periphery of the hole part 6A of a valve body 6.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement in a hydraulic control device for an automatic transmission, and more particularly to a flow control valve.

[0002]

2. Description of the Related Art A hydraulic control device for an automatic transmission mounted on a vehicle has conventionally used a hydraulic pump driven by an engine, and the discharge pressure of the hydraulic pump is controlled by a flow control valve constituted by a spool valve. After being adjusted to have a predetermined flow characteristic, it is supplied to each hydraulic circuit of the automatic transmission, and the flow control valve is controlled by an orifice formed in the spool.
When the engine speed rises above a predetermined value, the flow to the hydraulic circuit is prevented from becoming excessive, and a predetermined flow characteristic is obtained.

[0003]

However, in the above-mentioned conventional hydraulic control apparatus, when the flow rate is adjusted only by the differential pressure across the orifice provided in the flow control valve, the discharge flow rate of the hydraulic pump greatly changes. In some cases, the discharge flow rate of the flow control valve may not change smoothly. In particular, in a V-belt type automatic transmission (continuously variable transmission), since the pulley squeezes and presses the V-belt due to the line pressure from the hydraulic control device, an excessive change in the flow rate occurs and the hydraulic pressure is reduced. When the hydraulic pressure decreases, the contact frictional force between the V-belt and the pulley also changes, causing slippage and the like, which may hinder smooth shifting control. Had to be set to

The present invention has been made in view of the above problems, and an object of the present invention is to suppress excessive fluctuations in the discharge flow rate of a hydraulic pump and constantly perform speed change control.

[0005]

According to a first aspect of the present invention, a hydraulic pump driven by an engine and a spool having an orifice are slidably disposed in a hole formed in a valve body. A flow control valve that controls the flow rate from the pressure control valve based on the differential pressure across the orifice, and hydraulic control means that drives a transmission mechanism of the automatic transmission in accordance with pressure oil from the flow control valve. In the hydraulic control device, the flow control valve defines a damping chamber that suppresses displacement of the spool between an outer periphery of the spool and an inner periphery of the valve body.

According to a second aspect of the present invention, in the first aspect, the automatic transmission is constituted by a continuously variable transmission, and the continuously variable transmission is at least shifted by a hydraulic pressure from hydraulic control means. Control the ratio.

According to a third aspect of the present invention, in the first aspect, the flow control valve has a thin portion of a spool formed to have a smaller outer diameter toward an inflow port communicating with a hydraulic pump; The valve body has a small-diameter portion that forms a predetermined gap with the outer periphery, and the damping chamber communicates with the inflow port through the gap.

[0008]

According to the first aspect of the present invention, a damping chamber for suppressing an excessive displacement of a spool is provided in a flow control valve to absorb a sudden change in a supply flow rate of a hydraulic pump. Can stabilize the supply of hydraulic pressure to the automatic transmission, improve the stability of the shift control of the automatic transmission, and provide a damping chamber between the outer periphery of the spool and the inner periphery of the valve body. Therefore, it is not necessary to change the outer diameters of the spool and the valve body, and it is possible to suppress an increase in the size of the apparatus and an increase in manufacturing cost.

According to a second aspect of the present invention, when a continuously variable transmission for controlling at least a gear ratio based on a hydraulic pressure from hydraulic control means is employed as an automatic transmission, the discharge pressure of a hydraulic pump is temporarily reduced. Even if the pressure suddenly changes, the excessive displacement of the spool is suppressed by the action of the damping chamber, and the flow rate changes gradually.Therefore, when the discharge pressure of the hydraulic pump returns, the discharge flow rate In the continuously variable transmission in which the change is prevented and the speed ratio is controlled at least by the hydraulic pressure supplied from the hydraulic pressure control means, the change in the speed ratio can be suppressed, and the stability of the speed change control can be further improved.

According to a third aspect of the present invention, in the flow control valve, a thin portion is formed on a spool directed to an inflow port side communicating with the hydraulic pump, and a predetermined gap is provided between the outer periphery of the thin portion and the valve body side. By forming a small-diameter portion that forms the damping chamber and the inflow port side through this gap,
Suppressing excessive displacement of the spool by sucking and discharging pressure oil to the damping chamber, easily setting the pressure receiving area difference between both ends of the spool, forming a thin portion at one end of the spool, and forming the thin portion Since only the small diameter portion to be inserted is formed on the valve body side, the damping chamber and the flow path to the damping chamber can be defined without changing the outer diameter of the spool and the valve body, etc. Increase can be suppressed.

[0011]

Embodiments of the present invention will be described below with reference to the accompanying drawings.

FIGS. 1 and 2 show an embodiment in which the present invention is applied to a hydraulic control device of a V-belt type continuously variable transmission.
A continuously variable transmission 17 as an automatic transmission includes a primary pulley 16 connected to an engine (not shown) as a pair of variable pulleys, and a secondary pulley 26 connected to a drive shaft. They are connected by a belt 24.

The primary pulley 16 of the continuously variable transmission 17
A fixed conical plate 18 that rotates integrally, forms a V-shaped pulley groove that is disposed opposite to the fixed conical plate 18, and has a shaft formed by hydraulic pressure that acts on the primary pulley cylinder chamber 20 from the shift control valve 10. It comprises a movable conical plate 22 that can be displaced in the direction.

On the other hand, the secondary pulley 26 is connected to the axle side, and has a fixed conical plate 30 that rotates coaxially and integrally with the secondary pulley 26.
And a movable conical plate 34 displaceable in the axial direction in accordance with a line pressure acting on the secondary pulley cylinder chamber 32, while being arranged to face the V-shaped pulley groove.

The movable conical plate 22 of the primary pulley 16 and the movable conical plate 34 of the secondary pulley 26 are displaced in the axial direction to change the contact radius with the V-belt 24 so that the primary pulley 1 and the secondary pulley 26 The pulley ratio can be changed steplessly.

For example, if the width of the V-shaped pulley groove of the primary pulley 16 is reduced, the V
Since the contact radius with the belt 24 becomes large, a large pulley ratio (the gear ratio is on the Low side) can be obtained. If the movable conical plates 22 and 34 are displaced in the opposite direction, the pulley ratio becomes smaller (the gear ratio becomes Hi).

Such shift control for changing the width of the V-shaped pulley groove of the primary pulley 16 and the secondary pulley 26 is performed by hydraulic control of the primary pulley cylinder chamber 20, and the control valve 3 (hydraulic control means). Control valve 10 for regulating the line pressure supplied from the
This is performed by controlling the step motor 12 described above.

The step motor 12 drives the transmission control valve 10 in response to a command from a controller (not shown) via the transmission link 11, and adjusts the hydraulic pressure supplied to the cylinder chamber 20 of the primary pulley 16 by actually controlling the hydraulic pressure. Control is performed so that the pulley ratio matches the target pulley ratio.

The feedback means mainly composed of the transmission control valve 10 and the transmission link 11 includes a step motor 12
For example, it is connected to one end of a transmission link 11 having a predetermined lever ratio via a rack and pinion mechanism (not shown). A spool of the transmission control valve 10 is connected to the middle of the transmission link 11, and a feedback member (not shown) responsive to an axial displacement of the movable conical plate 22 is connected to the other end of the transmission link 11. It is.

The shift control valve 10 regulates the line pressure from the line pressure circuit 4 in accordance with the drive amount (rotational position) of the step motor 12 to adjust the line pressure from the cylinder chamber 2
The shift control is performed by supplying the value to 0. On the other hand, the cylinder chamber 32 of the secondary pulley 26 is in communication with the line pressure circuit 4, and a predetermined contact frictional force is always secured by holding and pressing the V-belt 24 according to the line pressure.

Here, the hydraulic control device for supplying the line pressure to the line pressure circuit 4 includes a hydraulic pump 1 driven by an engine (not shown), a flow control valve 2 for controlling the flow rate of the hydraulic pump 1 to predetermined characteristics, and The control valve 3 is configured to regulate the pressure oil from the flow control valve 2 to set the line pressure according to the operation state, and the control valve 3 includes, for example, a pressure regulator valve.

On the other hand, as shown in FIG. 2, the flow control valve 2 is constituted mainly by a cylindrical spool 5 which is slidable in the axial direction in a hole 6A formed inside the valve body 6. .

First, the valve body 6 communicates with the right end of the hole 6A in the drawing to be connected to the discharge port of the hydraulic pump, and the control valve 3 communicates with the left end of the hole 6A in the drawing. And a hole 6 at a predetermined position between the inflow port 2A and the discharge port 2C.
A drain port 2B connected to the tank in communication with A is formed.

An orifice 50 having a predetermined inner diameter is formed through the cylindrical spool 5 that slides in the hole 6A on the discharge port 2C side. The end face of the spool 5 having the orifice 50 and the valve body are formed. A spring 7 for urging the spool 5 rightward in the drawing is interposed between the inner circumference of the spring 6 and the inner circumference of the spool 6.

In the middle of the spool 5 in the axial direction, a drain hole 5 that allows communication between the inner periphery of the spool 5 and the drain port 2B is provided.
3 are formed at predetermined positions.

From the right side to the right end of the drawing with respect to the drain hole 53, a thin portion 5a whose outer diameter is reduced via a step 52 is provided.
Is extended to the inflow port 2A side, and a damping orifice 51 is formed at a predetermined position near the step portion 52 on the outer periphery of the thin portion 6A and communicates with the outer periphery of the thin portion 5a and the inner periphery of the spool 5. .

On the other hand, in the hole 6A on the inflow port 2A side,
The inside diameter is smaller than the hole 6A via the step 60, and
A small diameter portion 61 that forms a predetermined gap between the thin portion 5a of the spool 5 and the thin portion 5a and the step 52 of the spool 5 and the hole 6A and the step 60 of the valve body 6 are damped. A chamber 8 is defined. The damping chamber 8 allows the suction and discharge of the pressure oil through a flow path 9 formed by a gap between the outer periphery of the thin portion 5 a and the inner periphery of the small diameter portion 61, and a damping orifice 51. The inner circumference of the spool 5 and the suction and discharge of pressure oil are enabled.

Further, the flow path 9 is formed with a gap larger than the gap between the hole 6A and the outer periphery of the spool 5, for example, formed with a gap of several hundred microns, and applies the hydraulic pressure from the inflow port 2A to the step 52. Then, a pressure receiving area on the right side of the spool 5 is formed, and a difference from the pressure receiving area on the left end of the spool 5 is set to a predetermined value. The pressure receiving area of the spool 5 is
The left side in the figure is set larger than the right side, that is, the pressure receiving area downstream of the orifice 50 is set larger than the pressure receiving area upstream of the orifice 50.

The operation is described below, with the above configuration.

When the hydraulic pump 1 constantly supplies the pressure oil, the pressure oil flowing from the inflow port 2A flows from the discharge port 2C through the orifice 50 to the control valve 3C.
At this time, the spool 5 moves to a position where the pressure receiving area difference of the orifice 50 formed on the spool 5, that is, the pressure receiving area difference between the right and left sides of the spool 5 and the urging force of the spring 7 are balanced, for example, In the state of FIG. 2, a part supplied from the inflow port 2A is discharged to the tank through the drain hole 53 and the drain port 2B, and the remaining flow is supplied to the control valve 3.

On the other hand, when the flow rate to the inflow port 2A suddenly decreases due to a sudden decrease in the engine speed or the like, the spool 5 urged by the spring 7 starts displacing to the right in the figure while reducing the damping chamber 8.

At this time, the pressure oil in the damping chamber 8 is discharged from the flow path 9 and the damping orifice 51 to the inflow port 2A side and the inner circumference of the spool 5, and is discharged from the flow path 9 and the damping orifice 51. Due to the resistance, excessive displacement of the spool 5 to the right side is suppressed, and when the discharge pressure of the hydraulic pump 1 temporarily decreases temporarily and then returns instantaneously, the action of the damping chamber 8 is used. ,
Excessive displacement of the spool 5 is suppressed, and the drain hole 53
The amount of communication between the port and drain port 2B slowly changes (reduces)
Therefore, when the discharge pressure of the hydraulic pump 1 is restored, the flow rate to the discharge port 2C is prevented from greatly increasing, and the flow rate fluctuation can be smoothed. V-belt type continuously variable transmission 17 whose ratio is controlled
Thus, the change in the gear ratio can be suppressed, and the stability of the gear change control can be improved.

On the other hand, in the prior art, since the spool is displaced in response to a temporary decrease in the discharge pressure of the hydraulic pump 1, the drain is shut off, and when the hydraulic pressure returns at the next moment, the flow control valve In particular, in the V-belt type continuously variable transmission 17 in which the contact frictional force and the speed ratio are controlled by the line pressure, the speed ratio fluctuates, and the discharge pressure of the hydraulic pump 1 sharply increases. , The shifting operation becomes unstable.

Conversely, when the engine speed is rapidly increased at the time of starting, for example, the flow rate to the inflow port 2A is also rapidly increased, so that the spool 5 is displaced to the left in the drawing against the spring 7 and the damping chamber 8 is enlarged. The displacement starts rightward in the drawing.

At this time, the damping chamber 8 sucks the pressure oil from the flow path 9 and the damping orifice 51, and due to the resistance of the pressure oil passing through the flow path 9 and the damping orifice 51, excessive displacement of the spool 5 to the left side occurs. Is suppressed.

Therefore, in the case where the discharge pressure of the hydraulic pump 1 temporarily increases suddenly and then returns instantaneously, the excessive displacement of the spool 5 is suppressed by the action of the damping chamber 8. Since the amount of communication between the drain hole 53 and the drain port 2B gradually changes (expands), when the discharge pressure of the hydraulic pump 1 returns, it is possible to prevent the flow rate to the discharge port 2C from greatly decreasing. In the same manner as described above, the V-belt type continuously variable transmission 17 in which the flow rate fluctuation can be smoothed, and the contact friction force and the speed ratio are controlled by the line pressure can suppress the speed ratio fluctuation, thereby improving the stability of the speed change control. Can be improved.

On the other hand, in the prior art, since the spool is displaced in response to a temporary sudden increase in the discharge pressure of the hydraulic pump 1, the amount of communication of the drain increases, and the hydraulic pressure returns at the next moment. As a result, the flow rate from the flow control valve suddenly decreases, and in the V-belt type continuously variable transmission 17, fluctuations in the gear ratio and insufficient contact friction force occur, and the operation of the transmission becomes unstable. It is.

Thus, the flow control valve 2 is connected to the damping chamber 8.
Is provided to absorb fluctuations in the supply flow rate of the hydraulic pump 1, so that the continuously variable transmission 1
7, the stability of the speed change control of a continuously variable transmission in which the speed ratio and the contact friction force (= transmission torque capacity) change depending on the line pressure. You can do it.

The damping chamber 8 is defined by a thin portion 5a, a hole 6A and steps 52, 60 provided on the inflow port 2A side of the spool 5, and the outer circumference of the thin portion 5a and the small diameter of the valve body 6 are formed. Since the pressure oil enters and exits through the flow path 9 having a predetermined gap between the portions 61 and the damping orifice 51 formed through the thin portion 5a, the outer diameters of the spool 5 and the valve body 6 are changed. The flow path 9 and the pressure receiving area difference between the two ends of the spool 5 can be easily set, and can be configured with the same size as the conventional example.
Therefore, it is possible to easily replace the device, and it is possible to suppress an increase in the size of the device and an increase in manufacturing cost.

In the above embodiment, the case where the V-belt type continuously variable transmission is adopted as the automatic transmission has been described.
The same operation and effect can be obtained by employing an automatic transmission of a planetary gear type or a toroidal type.

[Brief description of the drawings]

FIG. 1 is a block diagram of a continuously variable transmission showing an embodiment of the present invention.

FIG. 2 is a sectional view of the flow control valve.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Hydraulic pump 2 Flow control valve 2A Inflow port 2B Drain port 2C Discharge port 3 Control valve 4 Line pressure circuit 5 Spool 5a Thin part 6 Valve body 7 Spring 8 Damping chamber 9 Flow path 10 Transmission control valve 11 Transmission link 12 Step motor 16 Primary pulley 17 Continuously variable transmission 18 Fixed conical plate 20 Primary pulley cylinder chamber 22 Movable conical plate 24 V belt 26 Secondary pulley 30 Fixed conical plate 32 Secondary pulley cylinder chamber 34 Movable conical plate 50 Orifice 51 Damping orifice 52 Step 53 Drain hole 60 Step 61 Small diameter part

Claims (3)

[Claims] 1. A hydraulic pump driven by an engine and a spool provided with an orifice are slidably disposed in a hole formed in a valve body, and a flow rate from the hydraulic pump is changed to a differential pressure across the orifice. And a hydraulic control unit that drives a transmission mechanism of the automatic transmission in accordance with the pressure oil from the flow control valve. A hydraulic control device for an automatic transmission, wherein a damping chamber for suppressing displacement of the spool is defined between the outer periphery of the spool and the inner periphery of the valve body. 2. The automatic transmission according to claim 1, wherein the automatic transmission comprises a continuously variable transmission, and the continuously variable transmission controls at least a gear ratio based on a hydraulic pressure from a hydraulic control unit. A hydraulic control device for an automatic transmission according to claim 1. 3. A flow control valve, comprising: a thin portion of a spool formed to have a smaller outer diameter toward an inflow port connected to a hydraulic pump; and a small diameter portion of a valve body forming a predetermined gap with the outer periphery of the thin portion. The hydraulic control device for an automatic transmission according to claim 1, further comprising: a damping chamber communicating with the inflow port through the gap.