JP3076077B2 - Control valve test equipment for continuously variable transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a control valve testing apparatus for a continuously variable transmission for testing a control valve for controlling a shift of a continuously variable transmission.

[0002]

2. Description of the Related Art CVT (Continuous) for automobiles
sly Variable Transmission
A belt type continuously variable transmission referred to as n) is disclosed in, for example,
As disclosed in Japanese Patent No. 65755, an output shaft is arranged in parallel with an input shaft connected to an engine via a clutch, and a primary pulley is provided on the input shaft, and a secondary pulley is provided on the output shaft.

The primary pulley is equipped with a primary cylinder, which is a hydraulic cylinder, and the secondary pulley is equipped with a secondary cylinder, and a drive belt is wound around the primary pulley to constitute a belt drive unit. Here, the area of the pressure receiving surface of the movable sheave that constitutes the primary cylinder is set to be large by the area of the pressure receiving surface of the movable sheave that constitutes the secondary cylinder, and the primary pressure changes the ratio of the winding diameter of the drive belt to each pulley and starts. The speed is continuously and continuously changed from the maximum speed to the maximum speed. The output shaft is configured to transmit driving wheels via a reduction gear, a differential gear, and the like.

The hydraulic control unit of such a continuously variable transmission includes an oil pump directly driven by an engine, a control valve for controlling a line pressure and a shift supplied by the oil pump, an input shaft rotation speed, an accelerator opening, and a shift. It consists of an input signal for detecting the ratio.

Next, the hydraulic control unit will be described with reference to FIG.

The control valve is composed of a pressure regulator valve 30 and a shift control valve 40. The pressure regulator valve 30 is a valve for supplying an optimum hydraulic pressure to the secondary pulley 60 when power is transmitted through the drive belt 70. The line pressure S discharged from the oil pump 80 directly rotated by the engine acts on the circuits 81 and 82 and the spring 3
The pressure is balanced with 1.

This pressure is supplied by a feed bar 55 for detecting the position of the movable sheave 51 of the primary pulley 50.
Spring 3 of direct pressure regulator valve 30
Change the set length of 1. Therefore, when the gear ratio is large (low state), the spring 31 is compressed, so that the line pressure S is high. On the contrary, when the gear ratio is small (overdrive state), the spring 31 is returned, so that the line pressure S is reduced. . Further, the pitot pressure Pi proportional to the rotation speed of the primary pulley 50 is applied to the circuit 83 on the opposite side of the spring 31 so that the line pressure S increases when the engine rotation speed increases and the discharge amount of the oil pump 80 increases. Is holding down.

The shift control valve 40 has a "D"
(Driving) and "Ds" (sporty driving) range are valves that control a continuous shift from a low state to an overdrive state in a range, a depression amount of an accelerator pedal (not shown), an engine speed, a shift. The position and the signal source are used as signal sources to control the inflow and outflow of the line pressure S to and from the primary pulley 50, and to control the positioning of the movable sheep 51 of the primary pulley 50, and thus the pulley ratio.

In the low state, the shift control valve 40 is pushed to the left in the drawing by the spring 43, and when the engine speed increases, the pitot pressure P of the circuit 84 increases.
i rises, the spool 41 moves to the right, and the circuit 85
The line pressure S flows out to the circuit 86 as the primary pressure P and is guided to the primary pulley 50. This point is a shift start point from the pulley ratio low state, and the engine speed N _{a in} FIG. 5 showing a shift characteristic diagram depending on the depression amount of the accelerator pedal.
To N _b throat of the engine speed to start the shifting from (required engine speed) is determined.

If the accelerator pedal is depressed during traveling in the overdrive state, the force for pushing the spool 41 to the left by the shift cam 90 interlocked with the accelerator pedal increases, and the required rotation speed increases. The change from point B to point C in the shift characteristic diagram shown in FIG. 5 increases the acceleration of the vehicle (kickdown).

Conversely, if the accelerator pedal is released while the vehicle is running fully open, the required rotational speed decreases, so the shift characteristic diagram of FIG. 5 changes from point D to point E (upshift).

Further, a modulator plunger 42 is provided in the shift control valve 40 to guide the line pressure S to the chamber a. When the line pressure S decreases as the pulley ratio changes from the low state to the overdrive state, the modulator plunger 42 becomes Spring 4 against spool 41
By the urging force of No. 4, it moves rightward in the figure, and the force received from the spring 45 is increased. This means that the required engine speed is increased while shifting from the low state to the overdrive state. As a result, a shift characteristic in the upper right direction is obtained in which the engine speed increases with respect to the pulley ratio change from low to overdrive.

A spool 4 is provided for the springs 43 and 45.
The compensation plunger 46 provided on the side opposite to 1 is provided with a pin 47 into which a pitot pressure Pi is guided to the chamber b and pushed by a shift cam 90 interlocked with an accelerator pedal.
Are connected via a spring 48. The role of the plunger 46 is to prevent the spool 41 from moving leftward when the accelerator pedal is suddenly depressed, and to prevent the hydraulic pressure of the primary pulley 50 from draining abruptly. If the primary cylinder 52 is low and not filled with oil, a time lag occurs at the start of shifting, so that the lubricating oil pressure J is always guided to the primary cylinder 52.

Reference numeral 91 denotes an engine brake valve which functions to keep the engine speed relatively high when engine braking is required on a slope or the like and when traveling on a mountainous road having many curved roads.

That is, in the "D" range, since the circuit 87 is closed by the switching plunger 92, the lubricating pressure J is guided to the circuit 88 of the engine brake valve 91 to overcome the urging force of the spring 93, and 94 is pushed to the right.

On the other hand, when the select lever 75 is shifted to the "Ds" range, the switching plunger 92 moves upward, the lubricating pressure J of the circuit 87 is drained, and the spool 94 of the engine brake valve 91 is provided with a spring 93. Pushed to the left by the force, the engine brake arm 9
5 also moves to the left at the same time. Therefore, regardless of the movement of the shift cam 90 of the shift control valve 40, the spool 41 is pushed to the left by the engine brake arm 95.

Accordingly, a shift characteristic corresponding to at least the amount of depression of the accelerator by the engine brake valve 91 is obtained.

In order to test the control valve for controlling the hydraulic pressure configured as described above, it is not possible to inspect all the performances of the control valve alone, and the control valve is installed in the continuously variable transmission. Is inspected by the driver's cab as an overall performance test.

The prior art is disclosed in JP-A-63-17 / 1988.
Japanese Patent Application Laid-Open No. 2004-2004-2004 discloses an on-line automatic diagnosis apparatus for a hydraulic control device that automatically diagnoses whether or not a hydraulic control device of a rolling mill is normal.

[0020]

The performance of the control valve can also be tested by incorporating the control valve into the continuously variable transmission and conducting a comprehensive performance test of the continuously variable transmission as described above. However, if a defect of the continuously variable transmission is found in the cab and the cause is due to the control valve, remove the oil pan etc. from the continuously variable transmission, remove the control valve, adjust and replace the control valve. And put it on the continuously variable transmission again,
The test work becomes complicated, such as mounting an oil pan or the like and performing a test again at the driver's cab.

Accordingly, an object of the present invention is to perform a performance test of a control valve by a test of the control valve alone.
It is an object of the present invention to provide a control valve test device for a continuously variable transmission which can simplify the operation.

[0022]

A control valve testing apparatus for a continuously variable transmission according to the present invention which achieves the above objects is provided on an input shaft and an output shaft arranged in parallel, and on an input shaft and an output shaft, respectively. A primary pulley and a secondary pulley whose groove width is variably controlled in the axial direction by hydraulic pressure, a belt drive unit including a drive belt wound between these pulleys, a hydraulic supply unit, and hydraulic pressure from the hydraulic supply unit. In a test apparatus for testing the control valve used in a continuously variable transmission having a hydraulic control unit that supplies a primary pulley and a secondary pulley of the belt drive unit by controlling the control valve by a control valve, the load corresponds to the load of the belt drive unit. A load applying section that generates a load to be applied and a hydraulic control section, and detachably supports the control valve to be tested And a control valve mounting portion that,
A hydraulic pressure generating unit that supplies hydraulic pressure to the load applying unit and the control valve mounting unit, and a hydraulic pressure generating unit that controls the hydraulic pressure generating unit based on preset operation information, and detects a hydraulic pressure acting on the load applying unit and the control valve mounting unit. And a control unit for detecting an operation state of the control valve.

[0023]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a control valve testing apparatus for a continuously variable transmission according to the present invention will be described below with reference to the drawings.

FIG. 1 is a schematic diagram for explaining the present test apparatus. For convenience of explanation, the hydraulic pressure corresponding to the line pressure, the hydraulic pressure corresponding to the primary pressure, the hydraulic pressure corresponding to the pitot pressure and the lubricating hydraulic pressure in the continuously variable transmission are shown. Line pressure,
These are called primary pressure, pitot pressure and lubrication oil pressure.

In the figure, reference numeral 1 denotes a balance cylinder that generates a load corresponding to the load of a belt drive unit in a continuously variable transmission.
The first piston 3 having the first pressure-receiving surface 3a having an area corresponding to the pressure-receiving surface of the movable sheave 51 of 0 receiving the primary pressure P corresponds to the pressure-receiving surface of the movable sheave 61 of the secondary pulley 60 which receives the line pressure S. Area of second pressure receiving surface 4a
And a third piston 5 described later are connected by a rod 6, and the first, second, and third pistons 3, 4, and 5 are connected to each other in a cylinder body 2. The rod 6 is slidably fitted into the first cylinder 3b, the second cylinder 4b, and the third cylinder 5b, and one end 6a of the rod 6 projects toward the control valve mounting portion 8.

The amount of movement of the rod 6 depends on the cylinder block 2
The arm 7a of the stroke measuring device 7 installed between the outer periphery of the rod 6 and the rod 6 is measured and transmitted to a control unit 17, which will be described later, and the speed ratio and the vehicle speed of the continuously variable transmission are calculated from the movement amount. It has become.

The control valve mounting section 8 performs the same function as the hydraulic control section of the continuously variable transmission, and controls the pressure regulator valve 3 which is a control valve to be tested.
0 and the shift control valve 40 are formed so as to be detachably supported, and the rod 9 is provided so as to be able to protrude and retract to change the set length of the spring 31 of the pressure regulator valve 30, and the pin 47 of the shift control valve 40.
There is provided a throttle wire 10 operated by an actuator (not shown) for pushing the throttle wire.

Further, an oil pump 11 as a hydraulic pressure generator
Is provided, and the hydraulic pressure discharged from the oil pump 11 is
The pressure is controlled by the first proportional solenoid valve 12 according to an instruction from the control device 17, and the flow rate is controlled by the second proportional solenoid valve 13 controlled by the control device 17. The pressure is supplied to the second cylinder 4b and the control valve mounting unit 8 via the circuit 21S, and the pressure is detected by the detection unit 20 and input to the programmable controller 18 of the control unit 17. The hydraulic pressure discharged from the oil pump 11 is
The pressure is controlled by the third proportional solenoid valve 14 in accordance with an instruction from the control unit 17 and is set as the pitot pressure Pi in the circuit 21Pi.
The pressure is supplied to the control valve mounting unit 8 via the control unit 20, and the pressure is detected by the detection unit 20 and input to the programmable controller 18 of the control unit 17.

The hydraulic pressure generated by the oil pump 11 and controlled by the first and second proportional control valves 12 and 13 and supplied to the control valve mounting section 8 as the line pressure S via the circuit 21S is applied to the control valve mounting section. 8
The circuit 2 is controlled by the pressure regulator valve 30 and the shift control valve 40 mounted on the
1P, the first piston 3 of the first piston 3 of the balance cylinder 1
The pressure is supplied to the first cylinder 3 b so as to act on the pressure receiving surface 3 a, and the pressure is detected by the detection unit 20 and input to the programmable controller 18 of the control unit 17.

A part of the hydraulic pressure supplied to the control valve mounting section 8 as the line pressure S is guided from the control valve mounting section 8 as lubricating oil pressure J to the detecting section 20 by the circuit 21J, and the pressure is detected. It is input to the programmable controller 18 of the control unit 17.

The third cylinder 5b of the balance cylinder 1
In the third piston, the driving force corresponding to the centrifugal force, the frictional force, and the centrifugal force caused by the rotation of each pulley itself by the drive belt of the actual continuously variable transmission acting on the primary pulley 50 and the secondary pulley 51 is used. In order to act on the third pressure receiving surface 5a of FIG. 5, the hydraulic pressure generated from the oil pump 11 is controlled by a fourth proportional solenoid valve 15 which operates based on information from a preset programmable controller 18 and becomes a control pressure C. Supply. The control pressure C is detected by the detection unit 16 and transmitted to the programmable controller 18.

A control unit 17 comprising a programmable controller 18 and a computer 19, based on information from the stroke measuring unit 7 and the detection units 16 and 20, according to preset conditions, each of the proportional solenoid valves 12, 13, 14, 15
Etc., and has a function of displaying and storing each pressure and the like.

Next, the operation of the thus constructed control valve testing apparatus for a continuously variable transmission will be described with reference to the flowcharts shown in FIGS.

At step 1, the pressure regulator valve 30 and the shift control valve 40, which are the control valves to be tested, which are preliminarily incorporated into one body, are attached to the control valve mounting portion 8.

When the start switch (not shown) of the apparatus is turned on in the next step 2, the control valves such as the pressure regulator valve 30 and the shift control valve 40 are set in step 3 in accordance with the information previously input to the programmable controller 18. Clamp in position.

In the subsequent step 4, the shift is set to the "D" range, and in step 5, the throttle wire 10 is fully returned and the throttle cam 90 is shown by a dashed line in FIG. The oil pump 11 is operated from the state where the first, second, and third pistons 3, 4, and 5 in the first position are on the left side, and the first
And second proportional solenoid valves 12 and 13 rpm of the vehicle of the oil pump is controlled by an instruction from the control unit 17 so that the same hydraulic and flow rate and the line S for ejecting increments every second R _1. Also controlled by the third proportional solenoid valve 14 to control unit 17 so as to be similar to the rate of increase when the pitot pressure Pi at the same time increased by the engine speed per second R ₁ of vehicle.

The first, second and third proportional solenoid valves 1
2,13,14 In Step 6 the rotational speed of the input shaft to be determined reaches the line pressure S and Pitot pressure Pi corresponding to the line pressure S and Pitot pressure Pi when the N ₁ by the engine rotational speed by controlling the the line pressure S acting on the pressure receiving surface 4a of the second piston 4 detector detects at 20, a suitable pressure in the control unit 17, or is, for example S ₁ or more, lubricating oil J
There is checked predetermined pressure J ₁ or more.

In step 6, the oil pump 1
1 and the first and second proportional control valves 12, 13
Is increased, the line pressure S acts on the pressure receiving surface 4a of the second piston 4, and moves the rod 6 rightward in the figure. At this time, the primary pressure P and the control pressure C are each 0, and the continuously variable transmission in which the stroke of the stroke measuring device 7 indicating the shift state is also 0 is in a low state.

[0039] Further instructions proportions in line pressure increases by every second R ₂ the input shaft by S from the control unit 17, pitot pressure P
i, when the first, second, third and fourth proportional control valves 12, 13, 14, 15 are controlled so as to obtain the control pressure C,
Shift control valve 40 and throttle wire 1
By the action of 0, the primary pressure P is increased while being controlled, acts on the pressure receiving surface 3a of the first piston 3, and the rod 6 starts moving leftward in the figure. This point corresponds to the shift point. In step 7, the line pressure S at this time is detected by the detection unit 20, and the control unit 17 calculates and stores the input shaft rotation speed corresponding to this time. A shift point is confirmed by determining whether the difference from the determined input shaft speed is within a predetermined range.

Next at a rate that increases first, a second input shaft which is determined the third and fourth proportional solenoid valve 12, 13, 14, 15 by the engine speed of a motor vehicle equipped each per R ₂ lines increased pressure S, pitot pressure Pi, the control pressure C, the input shaft rotational speed at step 8 and step 9 to confirm the pressure S _2, S ₃ of the line pressure S when corresponding to N ₂ and N _3.

Further, when the input shaft rotation speed corresponds to N ₄ , the primary pressure P and the line pressure S are detected, and the difference between the primary pressure P and the line pressure S is determined by the control unit 17 to determine whether the difference is within an appropriate range. Confirm.

[0042] Then first at a rate where the input shaft rotational speed decelerated by every second R _3, second third and fourth control valves 12, 13,
The control unit 17 calculates the vehicle speed, that is, the input rotation speed when the output shaft rotation speed sharply decreases, from the speed ratio measured by the stroke of the stroke measuring device 7 by controlling each of the input and output units 14 and 15, and calculates the rotation speed of the input shaft. seek shift point in step 11 than the number, shift point verify proper example is the input shaft speed depending on whether a predetermined rotational speed N _5.

Similarly, the operation of steps 12 to 17 confirms the line pressure S during deceleration and the modulator characteristics.
The "Ds" characteristic is confirmed, the oil pump is stopped in step 18, and it is determined in step 19 whether each operation of the control valve is appropriate. For example, when it is determined that all the check items have been properly operated, Displayed by lamp lighting. In step 20, each test result is printed out, in step 21, unclamped, and in step 22, the control valve is removed from the control valve mounting portion, and the control valve test is completed.

[0044]

According to the control valve for a continuously variable transmission according to the present invention described above, the control valve of the control valve testing apparatus in which the control valve is hydraulically controlled without mounting the control valve on the continuously variable transmission body. Since the test can be performed by mounting it alone on the mounting part, the performance test of the control valve can be easily performed.
Work can be simplified, and significant improvement in work efficiency can be expected.

[Brief description of the drawings]

FIG. 1 is a schematic diagram illustrating an embodiment of a control valve testing device for a continuously variable transmission according to the present invention.

FIG. 2 is a part of a flowchart showing the operation of the control valve testing device for a continuously variable transmission.

FIG. 3 is a flowchart showing the operation of the control valve testing device for a continuously variable transmission following FIG. 2;

FIG. 4 is an explanatory diagram of a hydraulic control unit of the continuously variable transmission.

FIG. 5 is a shift characteristic diagram of the continuously variable transmission.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Balance cylinder (load application part) 3 1st piston 3a 1st pressure receiving surface 3b 1st cylinder 4 2nd piston 4a 2nd pressure receiving surface 4b 2nd cylinder 8 Control valve mounting part 11 Oil pump (oil pressure) Generator 12 proportional solenoid valve 13 proportional solenoid valve 14 proportional solenoid valve 15 proportional solenoid valve 17 control unit

Claims (3)

(57) [Claims] An input shaft and an output shaft disposed in parallel with each other;
A primary pulley and a secondary pulley provided on the input shaft and the output shaft, respectively, and the groove width is variably controlled in the axial direction by hydraulic pressure; a belt drive unit including a drive belt wound between these pulleys; And a hydraulic pressure control unit for controlling the hydraulic pressure from a hydraulic pressure supply unit with a control valve and supplying the hydraulic pressure to a primary pulley and a secondary pulley of a belt drive unit. A load applying unit that generates a load corresponding to the load of the belt drive unit, a control valve mounting unit that functions as a hydraulic control unit and detachably supports a control valve to be tested, a hydraulic pressure generating unit, It is arranged between the generating unit and the load applying unit and the control valve mounting unit, and from the hydraulic pressure generating unit to the load applying unit and A proportional solenoid valve for controlling the hydraulic pressure supplied to the control valve mounting portion, and controlling the proportional solenoid valve based on preset operation information, and detecting the hydraulic pressure acting on the load applying portion and the control valve mounting portion. A control unit for detecting an operation state of a control valve. 2. An input shaft and an output shaft arranged in parallel,
A belt drive unit that is provided on each of the input shaft and the output shaft and has a primary pulley and a secondary pulley whose groove width is variably controlled in the axial direction by hydraulic pressure, and a belt driving unit that has a drive belt wound between these pulleys; A supply unit, a pressure regulator valve that controls the line pressure from the hydraulic pressure supply unit according to the pitot pressure generated according to the rotation speed of the primary pulley, and supplies the line pressure to the secondary pulley, based on a depression amount of an accelerator pedal and an engine speed. Testing the control valve used in a continuously variable transmission having a hydraulic control unit having a control valve consisting of a shift control valve for controlling a line pressure from a hydraulic supply unit to a primary pulley and supplying the primary pressure as a primary pressure. In the test equipment, the hydraulic pressure generation part is proportional to the hydraulic pressure from the hydraulic pressure generation part. Hydraulic pressure equivalent to the line pressure and pitot pressure controlled by the magnetic valve is supplied to perform the function of a hydraulic control unit, and a control valve mounting unit to which the control valve is detachable and a proportional solenoid valve A load applying unit that generates a load corresponding to the load of the belt driving unit by a hydraulic pressure corresponding to the line pressure controlled by the hydraulic pressure corresponding to the primary pressure supplied from the control valve mounting unit, and a proportional solenoid valve are preset. A control unit for controlling the control valve based on the operating information and detecting each hydraulic pressure to detect an operation state of the control valve. 3. A first piston having a first pressure receiving surface corresponding to a pressure receiving surface of a primary pulley;
A second cylinder having a first cylinder in which the first piston is fitted, and a second pressure receiving surface corresponding to a pressure receiving surface of the secondary pulley;
, A second cylinder in which the second piston is fitted, a rod connecting the first and second pistons, and a hydraulic pressure corresponding to the primary pressure supplied to the first cylinder from the control valve mounting portion. 3. The control valve for a continuously variable transmission according to claim 2, wherein the control valve is a balance cylinder having a circuit that guides the hydraulic pressure from the hydraulic pressure generation unit to the second cylinder and a circuit that guides the hydraulic pressure corresponding to the line pressure controlled by the proportional control valve. Testing equipment.