JP3076076B2 - 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. Using the position as a signal source, the flow of the line pressure S into and out of the primary pulley 50 is controlled, and the positioning of the movable sheave 51 of the primary pulley 50, and thus the pulley ratio, is controlled.

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 for supplying hydraulic pressure to the load applying unit and the control valve mounting unit, and a hydraulic pressure acting on the load applying unit and the control valve mounting unit by controlling the hydraulic pressure generating unit based on operation information set in advance. And a controller for detecting the operating 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,
They 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 area corresponding to the pressure receiving surface of the movable sheave 61 of the secondary pulley 60 which receives the line pressure S of the first piston 3 having the first pressure receiving surface 3a of the area corresponding to the pressure receiving surface of the movable sheave 51 of 0 which receives the primary pressure. A second piston 4 having a second pressure receiving surface 4a and a third piston 5 described later are connected by a rod 6, and each of the first, second, and third pistons 3, 4, and 5 is connected to a cylinder body 2 The first in the series
Slidably fitted into the cylinder 3b, the second cylinder 4b, and the third cylinder 5b, and one end 6a of the rod 6 protrudes toward the control valve mounting portion 8. Rod 6
The amount of movement of the continuously variable transmission is measured by the movement of an arm 7a of a stroke measuring device 7 provided between the outer periphery of the cylinder block 2 and the rod 6, and transmitted to a control unit 16 described later. The gear ratio and the vehicle speed are calculated.

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.
Throttle wire 8 operated by an actuator (not shown) corresponding to an accelerator pedal for pushing
a is provided.

Further, a hydraulic pressure generator 10 for supplying the pitot pressure Pi and the line pressure S to the balance cylinder 1 and the control valve mounting section 8 is provided. Hydraulic pressure generator 10
A servo motor 11 whose rotation is controlled and started and stopped according to an instruction from the control unit 16 and whose rotation speed is controlled, a pitot pressure generation device 12 that generates a pitot pressure Pi by the servo motor 11, and a servo motor 11 It comprises an oil pump 13 for generating a line S pressure and a rotation sensor 14 for detecting the number of rotations of the servomotor 11 and transmitting the detected number to the control unit.

The pitot pressure Pi generated by the pitot pressure generation device 12 of the hydraulic pressure generation unit 10 is supplied to the control valve mounting unit 8 by a circuit 22Pi, and the detection unit 18
, The pressure is detected and input to the programmable controller 17 of the control unit 16.

The line pressure S generated by the oil pump 13 is guided by the circuit 22S to the second cylinder 4b so as to act on the second pressure receiving surface 4a of the second piston 4 of the balance cylinder 1, and is supplied to the control valve mounting section 8. Is done. Further, the detection unit 18 detects the pressure of the line pressure S, and the programmable controller 17 of the control unit 16
Is input to

The circuit 2 generated by the oil pump 13
The hydraulic pressure supplied to the control valve mounting unit 8 as the line pressure S by the 2S is applied to the control valve mounting unit 8.
Is controlled by the pressure regulator valve 30 and the control valve 40 mounted on the balance cylinder 1 via the circuit 22P as the primary pressure P.
The pressure is supplied to the first cylinder 3b so as to act on the first pressure receiving surface 3a of the piston 3. Further, the primary pressure P is detected by the detection unit 18 and is input to the programmable controller 17 of the control unit 16.

A part of the hydraulic pressure supplied to the control valve mounting section 8 as the line pressure S is supplied from the control valve mounting section 8 as the lubricating oil pressure J to the pitot pressure generating device 12 and the oil pump 13 by the circuit 22J. The pressure is detected by the detection unit 18 and input to the programmable controller 17.

The third cylinder 5b of the balance cylinder 1
In the actual continuously variable transmission, the driving force of the drive belt 70 acting on the primary pulley 50 and the secondary pulley 60 and the frictional force acting on the primary pulley 50 and the secondary pulley 60, and the acting force equivalent to the centrifugal force caused by the rotation of each of the pulleys 50 and 60 itself are described. In order to act on the pressure receiving surface 5a of the third piston 5, the hydraulic pressure generated from the oil pump 19 is set to a predetermined value by the programmable controller 1.
The control pressure is controlled by a proportional solenoid valve 20 which operates based on the information from the controller 7 and is supplied as a control pressure C.
The control pressure C is detected by the detection unit 21 and transmitted to the programmable controller 17.

A controller 16 comprising a programmable controller 17 and a computer 18 controls the servo motor 1 in accordance with preset conditions based on information from the stroke measuring device 7, detectors 18, 21 and rotation speed sensor 14.
1. It has a function of giving an operation instruction to the proportional solenoid valve 20 and the like, and displaying and storing each pressure and the like.

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

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

When the start switch (not shown) of the present 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 controlled in step 3 in accordance with the operation information input to the programmable controller 17 in advance. Clamp in place.

In the following step 4, the shift is set to the "D" range, and in step 5, the throttle wire 8a is fully returned, and in FIG. 4, the throttle cam 90 is shown by a dashed line, and the balance cylinder shown in FIG. From the state where the first piston 3, the second piston 4 and the third piston 5 are located on the left side within 1, the servo motor 11 of the hydraulic pressure generator 10 and therefore the rotation speed of the pitot pressure generator 12 and the oil pump 13, that is, in the actual vehicle the rotational speed of the input shaft is increased by every second R _1, line pressure rotational speed of the servo motor 11 corresponding to the rotational speed of the input shaft is applied to the pressure receiving surface 4a of the second piston 4 at step 6 has reached the N ₁ S detected by the detection unit 18, appropriate pressure in the control unit 16, for example, S ₁ or more in either, also lubricating oil J is a predetermined pressure J
_One or more there or to confirm.

In step 6, the line pressure S supplied from the oil pump 13 is increased by the driving of the servomotor 11, and the line pressure S is changed to the pressure receiving surface 4a of the second piston 4.
To move the rod 6 rightward in the figure. At this time, the primary pressure P and the control pressure C are 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.

Further, when the rotation speed of the servo motor 11 is increased by R ₂ per second in accordance with an instruction from the control unit 16, the primary pressure P is increased while being controlled by the action of the shift control valve 40 and the throttle wire 8a.
Acting on the pressure receiving surface 3a of the first piston 3, the rod 6 starts moving leftward in the figure. This point corresponds to the shift point,
In step 7, the rotation speed at this time is
The shift point is determined by determining whether the difference from the rotation speed of the servo motor 11 detected in step 11 described later is within a predetermined range, and stored in the control unit 15 to be stored.

Next, the rotation speed of the servo motor 11 is set to R ₂ per _second.
Increments, the rotational speed in Step 8 and Step 9 to confirm the pressure S _2, S ₃ of the line pressure S o'clock N ₂ and N _3.

Further, when the rotational speed is 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 obtained by the control unit 16 to confirm whether the difference is within an appropriate range.

Subsequently, the servo motor 11 is decelerated by R ₃ per second, and the vehicle speed, that is, the output shaft speed is calculated by the control unit 16 from the gear ratio measured by the stroke of the stroke measuring device 7. The speed change point is determined in step 11 from the rotation speed of the servo motor 11 when the rotation speed has decreased to the predetermined value, that is, the input rotation speed.
Check the shift point according to whether it is within ₅ .

Similarly, the line pressure S at the time of deceleration and the characteristics of the modulator are confirmed by the operations of steps 12 to 17, and "Ds"
After confirming the characteristics, the servo motor 11 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, a lamp is lit to indicate. I do. 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 section 8, 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 is operated by the controlled hydraulic pressure from the hydraulic pressure generating unit without mounting the control valve on the continuously variable transmission body. Since the test is performed by mounting the control valve alone on the control valve mounting part of the control valve test device, the performance test of the control valve can be easily performed, simplifying the work and greatly improving the work efficiency compared to the past it can.

[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 10 Hydraulic pressure generating part 12 Pitot pressure generator 13 Oil pump 16 Control unit

Claims (6)

(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 driving unit, a control valve mounting unit that functions as a hydraulic control unit and detachably supports a control valve to be tested, and a load applying unit and a control valve. A hydraulic pressure generating section for supplying hydraulic pressure to the mounting section, and a hydraulic pressure generating section based on operation information set in advance. There was controlled, and the load applying portion and a control CVT control valve test apparatus characterized by a control unit for the valve acts on the mounting portion to detect the hydraulic pressure detecting the operating state of the Con roll valve. A first piston having a first pressure receiving surface corresponding to a pressure receiving surface of the 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;
Having a piston, a second cylinder fitted with the second piston, a rod connecting the first and second pistons, and a hydraulic circuit for supplying hydraulic pressure to the first cylinder and the second cylinder. The control valve test device for a continuously variable transmission according to claim 1, wherein the control valve test device is a cylinder. 3. The control valve testing device for a continuously variable transmission according to claim 1, wherein the hydraulic pressure generating unit includes a servomotor whose rotation speed is controlled by the control unit and an oil pump that is rotationally driven by the servomotor. 4. 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. Test equipment generates hydraulic pressure equivalent to line pressure and pitot pressure A control valve mounting unit for supplying a hydraulic pressure corresponding to a line pressure and a peat pressure from the hydraulic pressure generating unit to perform a function of a hydraulic control unit and detachably supporting a control valve to be tested; 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 supplied from the hydraulic pressure generating device and a hydraulic pressure corresponding to the primary pressure supplied from the control valve mounting unit; A control unit for controlling based on set operation information and detecting each hydraulic pressure to detect an operation state of the control valve. 5. A first piston having a first pressure receiving surface corresponding to a pressure receiving surface of a primary pulley, wherein the load applying unit includes:
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. 5. The control valve testing device for a continuously variable transmission according to claim 4, wherein the balance cylinder includes a circuit for guiding the hydraulic pressure and a circuit for guiding the hydraulic pressure corresponding to the line pressure supplied from the hydraulic pressure generating unit to the second cylinder. 6. A hydraulic pressure generator drives and controls an oil pump for supplying a hydraulic pressure corresponding to the line pressure, a pitot pressure generating device for supplying a hydraulic pressure corresponding to the pitot pressure, an oil pump and the pitot pressure generating device. The control valve testing device for a continuously variable transmission according to claim 4 or 5, further comprising a servomotor whose rotation speed is controlled by a section.