JP2003049933A - Fluid pressure control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a fluid pressure control device capable of achieving both improvement of the reliability of the fluid pressure control and reduction of the manufacturing cost by reducing the number of part items and an assembling man-hour thereof. SOLUTION: A valve body 30 consists of an upper valve body 31, a lower valve body 32 and a separate plate 35. The upper valve body 31 has an inner wall forming a passage 33, and the lower valve body 32 has an inner wall forming a passage 34. A filter function part 37 is mounted on a communicating port 36 just in the upstream of a clutch pressure control valve 10 and an electromagnetic valve 20 of the separate plate 35. Therefore, intrusion of foreign matters into the clutch pressure control valve 10 and the electromagnetic valve 20 is prevented, so that the reliability of the hydraulic pressure control is improved and the hydraulic oil is controlled highly precisely. Further, since there is no need to mount a separate sub-filter on the way of an oil passage, the manufacturing cost of the device is reduced by reducing the number of parts and assembling man-hour of the device.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid pressure control device, and more particularly to a fluid pressure control device suitable for hydraulically controlling a speed change mechanism of an automatic transmission or a continuously variable transmission.

[0002]

2. Description of the Related Art Conventionally, automatic transmissions used for vehicles and the like have a plurality of friction elements for switching gear stages by engaging or disengaging them, and controlling hydraulic pressure applied to each friction element. Shift control is being performed. As a hydraulic control device for an automatic transmission, a hydraulic control device is known in which the hydraulic pressure applied to a plurality of friction elements is directly controlled by a duty solenoid valve or a linear solenoid valve. In such a hydraulic control device, since the hydraulic pressure applied to the friction element is controlled by the solenoid valve, the accumulator is not required and the circuit configuration can be simplified, and the responsiveness when controlling the friction element is improved because no accumulator is provided. To do.

In a hydraulic control device in which the hydraulic pressure applied to a friction element is directly controlled by a solenoid valve, a fixed line pressure may be used as the original pressure of the solenoid valve. By adding these, shift shocks are reduced. The line pressure input as the engagement source pressure of the friction element may be used as a fixed pressure by changing the pressure between the low speed stage and the high speed stage of the forward range.

[0004]

Since the output torque of the engine is small when the throttle opening is small, the friction element can transmit the output torque of the engine even if the hydraulic pressure applied to the friction element is low. However, as described above, even if the pressure is changed between the low speed stage and the high speed stage of the forward range, when the line pressure of the fixed pressure is input to the solenoid valve as the engagement source pressure, the output torque of the fluctuating engine can be reliably maintained. In order to engage the friction element with, the line pressure used as the engagement source pressure must be set to a high pressure.

When the throttle opening is small, in order to control the high pressure line pressure input as the engagement source pressure and add the low pressure hydraulic oil to the friction element, the pressure control range of the solenoid valve from low pressure to high pressure is limited. It is necessary to use only the low pressure range. In order to control the hydraulic pressure applied to the friction element with high precision using only the limited low pressure range, it is necessary to use an expensive solenoid valve with high pressure resolution that controls the hydraulic pressure with high precision within the limited control range. Therefore, there is a problem that the cost increases.

Generally, the line pressure is set to a certain value by discharging the hydraulic oil discharged from the hydraulic pump to the drain side by the line pressure control valve. However, if the hydraulic oil to be added to the friction element is rapidly filled in order to enhance the engagement response of the friction element, the rapid filling of the hydraulic oil cannot be handled due to the response delay of the line pressure control valve, and the line pressure is temporarily reduced. It may decrease. When the line pressure decreases, the hydraulic pressure applied to the friction element also decreases, and gear shift control of the friction element may not be performed properly.

Therefore, the line pressure is adjusted according to the output torque of the engine, and the clutch pressure is controlled by the control valve according to the command pressure of the actuator to control the hydraulic pressure applied to the friction element within a wide hydraulic control range of the actuator. Is possible.

However, in the conventional hydraulic control system for an automatic transmission, in order to improve the reliability of the actuator and the control valve, a main filter is provided upstream of the inlet of the hydraulic oil, and further upstream of the actuator and the control valve. A sub-filter having a larger pore size than the main filter is provided in the oil passage. For this reason, since it is necessary to separately provide a sub-filter in the oil passage, there is a problem that the number of parts increases, the number of assembly steps for attaching the sub-filter increases, and the manufacturing cost increases.

The present invention has been made to solve such a problem, and makes it possible to control the fluid pressure with high accuracy, reduce the number of parts and the number of assembly steps, and reduce the manufacturing cost. An object is to provide a pressure control device. Another object of the present invention is to provide a fluid pressure control device that reliably captures foreign matter in a fluid to enhance reliability. Still another object of the present invention is to provide a fluid pressure control device that improves processing accuracy and reduces processing man-hours.

[0010]

According to the fluid pressure control apparatus of the first aspect of the present invention, the fluid pressure control means for adjusting or switching the fluid pressure applied to the controlled object is housed and has an inner wall forming a fluid passage. A plate member for connecting or blocking the fluid passage is provided between the upper case and the lower case, and the plate member is provided with a filtering means having a function of filtering the fluid flowing through the fluid passage. For this reason, the foreign matter that is suddenly generated in the fluid passage or the foreign matter that remains in the fluid passage at the time of assembly is captured by the filtering means when moved by the flow of the fluid during operation. Therefore, the fluid pressure can be controlled with high accuracy, and it is not necessary to separately provide a sub-filter in the fluid passage, so that the number of parts and the number of assembling steps can be reduced and the manufacturing cost can be reduced.

According to the fluid pressure control device of the second aspect of the present invention, the actuator that receives the hydraulic pressure of the working fluid as the supply pressure operates in response to the switching control signal to output the control pressure. Further, since the filtering means is provided immediately upstream of the actuator, it is possible to prevent foreign matter from entering the actuator and enhance the reliability of fluid pressure control.

According to the fluid pressure control device of the third aspect of the present invention, the control valve whose operation is controlled by the control pressure output from the actuator controls the supply and discharge of the fluid pressure applied to the controlled object. It is possible to prevent foreign matter from entering and improve the reliability of fluid pressure control. According to the fluid pressure control device of the fourth aspect of the present invention, since the magnet is provided on the inner wall of the fluid passage on the upstream side of the filtering means, the magnet is provided after stopping the operation of the iron-based foreign matter captured by the filtering means. It can be recovered by the magnetic force of. Therefore, it is possible to reliably capture the foreign matter in the fluid and improve the reliability.

According to the fluid pressure control device of the fifth aspect of the present invention, since the plurality of through holes are formed in the plate member by laser processing in the plate member, the plurality of through holes having proper hole diameters can be accurately formed. And it can be formed easily. Therefore, the processing accuracy of the filtering means is improved, and the number of processing steps can be reduced.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A plurality of embodiments showing the embodiments of the present invention will be described below with reference to the drawings. (First Embodiment) A first embodiment in which the fluid pressure control device of the present invention is applied to a hydraulic control device for an automatic transmission is shown in FIGS. 1, 2 and 3.

A hydraulic pump 40 shown in FIG. 3 sucks hydraulic oil from an oil pan 41 and uses a reverse clutch (R / R).
C), overdrive clutch (H / C), 2-4 brake (2-4 / B), underdrive clutch (L)
/ C), low reverse brake (LR / B), transfer clutch (TRF), and other hydraulic elements. The line pressure control valve 42 is the solenoid valve 4
Based on the command pressure of No. 4, the working pressure of each friction element is generated together with the secondary valve 43. The decompression control valve 45 reduces the line pressure generated by the line pressure control valve 42. The hydraulic pump 40, the line pressure control valve 42, and the solenoid valve 44 constitute a source pressure generation unit that generates a source pressure of the pressure applied to each friction element.

The clutch pressure control valve 10 and the solenoid valve 20 are
Friction element control means for controlling the hydraulic pressure applied to each friction element other than R / C is configured. Here, the clutch pressure control valve 10 constitutes a control valve, the solenoid valve 20 is a linear solenoid valve, and constitutes an actuator. In the first embodiment, since the clutch pressure is controlled,
The hydraulic module 1 is provided as a fluid pressure control means in which the clutch pressure control valve 10 and the solenoid valve 20 are integrated.
In FIG. 3, the output pressure of the clutch pressure control valve 10 is controlled by applying the command pressure, which is the output pressure of the solenoid valve 20, to the left end of the clutch pressure control valve 10. The clutch pressure control valve 10 includes a spool 11 and a spring 12. The solenoid valve 20 includes an ECU (Electric Contr) not shown.
ol Unit) to drive a valve body (not shown) according to a switching control signal from the solenoid unit (not shown). A main filter 47 is provided on the upstream side of the hydraulic module 1.

As shown in FIGS. 1 and 2, the clutch pressure control valve 10 and the solenoid valve 20 constitute a hydraulic module 1 and are attached to one valve body 30. Although FIG. 1 shows one set of hydraulic modules 1 as the friction element control means for controlling the hydraulic pressure applied to each friction element, the number of hydraulic modules mounted on the valve body 30 is not limited.

Valve body 30 made of aluminum die cast
Is composed of an upper valve body 31 as an upper case, a lower valve body 32 as a lower case, and a separate plate 35 as a plate member. The upper valve body 31 is provided with a passage 3 for circulating hydraulic oil.
The lower valve body 32 has an inner wall forming
Has an inner wall forming a passage 34 for circulating hydraulic oil. A mounting hole 32a is formed inside the lower valve body 32, and the clutch pressure control valve 10 and the solenoid valve 20 are coaxially installed in the mounting hole 32a. That is, the clutch pressure control valve 10 and the solenoid valve 20 are mounted side by side in the mounting hole 32a in the axial direction. Further, the clutch pressure control valve 10 and the solenoid valve 20
May not be coaxial and may be arranged individually.

The separate plate 35 is provided between the upper valve body 31 and the lower valve body 32, and is a member for connecting or disconnecting the communication between the passage 33 and the passage 34. The separate plate 35 is formed with a plurality of communication ports 36 that communicate with the passage 33 and the passage 34, and the clutch pressure control valve 10 or the solenoid valve 20.
To the communication port 36 immediately upstream of the
7 is provided. The filtration function part 37 is for catching a foreign substance suddenly generated in the hydraulic oil or a foreign substance remaining in the passages 33 and 34 during assembly, and is formed on the separate plate 35 by laser processing. It has a plurality of through holes 38. An appropriate value is selected for the number of through holes 38 depending on the type of vehicle. In addition, the hole diameter φ of the through hole 38 is preferably set so as not to deteriorate the responsiveness at an extremely low temperature, and is 0.02 mm to 0.
A value of about 2 mm is adopted. By forming the through holes 38 by laser processing, it becomes possible to accurately and quickly form a large number of small hole diameters. The hole diameter φ of the through hole 38 is formed larger than the hole diameter of the main filter 47 shown in FIG. Here, the arrows shown in FIG. 1 indicate the flow of hydraulic oil, and the uppermost flow passage 3
4 is connected to the communication passage 142 shown in FIG.

The generation of hydraulic pressure for controlling the hydraulic circuit will be described below. Hydraulic oil is sucked from the oil pan 41 by the hydraulic pump 40, and the communication passages 100, 101, 102
It becomes a high pressure and is discharged. The line pressure control valve 42 transfers a part of the hydraulic oil sent from the communication passage 101 to the communication passage 103.
To control the line pressure.

A communication passage 11 branched from the communication passage 100
No. 0 is provided with a pressure reducing control valve 45, and the hydraulic oil output from the pressure reducing control valve 45 is discharged from the communication passage 111 and introduced to the right end of the pressure reducing control valve 45 in FIG. 3 through the throttle 113 of the communication passage 112. The force received by the pressure reducing control valve 45 from the output pressure of the hydraulic oil introduced from the right end and the spring 45a
The pressure of the communication passage 111 does not exceed the line pressure due to the balance with the urging force of
When it is Pa, it is controlled to about 0.5 MPa. This pressure is called the modulation pressure.

The hydraulic fluid whose pressure is controlled to be a modulated pressure by the pressure reducing control valve 45 is guided to the solenoid valve 44 through the throttle 114. The solenoid valve 44 is duty ratio controlled by an output signal from the ECU so as to set an appropriate line pressure according to the operating state of the vehicle such as throttle opening, engine torque and turbine torque. The command pressure of the solenoid valve 44 is transmitted to the left end of the line pressure control valve 42 in FIG. 3 through the communication passage 115. In FIG. 3, the hydraulic oil of the line pressure is introduced into the different diameter portion on the right side of the line pressure control valve 42 through the communication passage 105 branched from the communication passage 102 of the line pressure, and the line pressure is changed by the balance with the command pressure of the solenoid valve 44. Feedback controlled.

The communication passage 142 is a communication passage 1 for modulating pressure.
It branches from 11, is connected to the solenoid valve 20, and is transmitted to the left end of the clutch pressure control valve 10 in FIG. Communication passage 14
The modulated pressure of 2 is transmitted to the solenoid valve 20, and the command pressure linearly controlled according to the instruction of the ECU is transmitted from the solenoid valve 20 to the left end of the clutch pressure control valve 10 in FIG. The force received from the pressure of the communication passage 100, the force received by the clutch pressure control valve 10 from the command pressure of the solenoid valve 20, and the spring 1
By the balance with the urging force of 2, the pressure applied to each friction element is controlled according to the command pressure of the solenoid valve 20.

At this time, the foreign matter suddenly generated in the hydraulic oil or the foreign matter remaining in the passages 33 and 34 of the upper valve body 31 and the lower valve body 32 at the time of assembly rides on the flow of the hydraulic oil to the clutch. It moves to the pressure control valve 10 and the solenoid valve 20 side. If the foreign matter is larger than the hole diameter φ of the through hole 38 of the filtering function portion 37, the foreign matter cannot pass through the through hole 38, and the filtering function portion 37
Captured by. Further, when the foreign matter is smaller than the hole diameter φ of the through hole 38 of the filtration function portion 37, the foreign matter may pass through the through hole 38, but it becomes difficult to pass when the foreign matter has a whisker shape.

Next, a sub-filter is arranged in the passage 34 immediately upstream of the clutch pressure control valve 10 and the solenoid valve 20 in place of the filtering function portion 37 of the first embodiment shown in FIGS. 1 and 2. A comparative example will be described with reference to FIGS. 6 and 7. The same reference numerals are given to substantially the same components as those in the first embodiment.

As shown in FIGS. 6 and 7, the separate plate 235 has a plurality of communication ports 236 which communicate with the passage 33 formed in the upper valve body 31 and the passage 34 formed in the lower valve body 32. And a sub-filter 237 is provided in the passage 34 immediately upstream of the clutch pressure control valve 10 or the solenoid valve 20. The arrows shown in FIG. 6 indicate the flow of hydraulic oil.

In the comparative example having the above structure, the sub-filter 237 is arranged in the passage 34 formed in the lower valve body 32. As described above, since it is necessary to separately provide the sub-filter 237 having a larger hole diameter than the main filter in the oil passage, the number of parts is increased and the number of assembly steps for attaching the sub-filter 237 is increased.
There is a problem that the manufacturing cost increases.

On the other hand, in the first embodiment, the clutch pressure control valve 10 of the separate plate 35 or the solenoid valve 2 is used.
Since the filtering function portion 37 is provided at the communication port 36 immediately upstream of 0, foreign matter can be prevented from entering the clutch pressure control valve 10 and the solenoid valve 20, and the reliability of hydraulic control can be improved. It becomes possible to control the hydraulic oil with high precision. Further, since it is not necessary to separately provide a sub filter in the oil passage, the number of parts and the number of assembling steps can be reduced, and the manufacturing cost can be reduced.

Further, in the filtering function part 37, since the plurality of through holes 38 are formed in the separate plate 35 by the laser processing, the plurality of through holes 38 having an appropriate hole diameter can be accurately and easily formed. . Therefore, the processing accuracy of the filtration function unit 37 is improved, and the number of processing steps can be reduced.

(Second Embodiment) A second embodiment is shown in FIG.
The same components as those in the first embodiment shown in FIG. 1 are designated by the same reference numerals. As shown in FIG. 4, the separate plate 13
5 includes a passage 33 formed in the upper valve body 31.
And a plurality of communication ports 136 communicating with the passage 34 formed in the lower valve body 32, and the inside of the valve body 130 composed of the upper valve body 31, the lower valve body 32 and the separate plate 135 is formed. Separate plate 135 immediately after the introduction of hydraulic oil
A filtering function part 137 as a filtering means is provided at a communication port 136 at a position crossing the line. The filtration function portion 137 is for capturing foreign matter that is suddenly generated in the hydraulic oil, or foreign matter that remains in the passages 33 and 34 during assembly, and is formed on the separate plate 135 by laser processing. It has a plurality of through holes 138. A proper value is selected for the number of the through holes 138 depending on the type of vehicle, and it is desirable that the diameter of the through holes 138 is set to a level that does not deteriorate the responsiveness at a cryogenic temperature.
A value of about m to 0.2 mm is adopted. Through hole 13
By forming 8 by laser processing, it becomes possible to form a large number of small hole diameters accurately and quickly. The through hole 138 has a hole diameter larger than that of the main filter. Here, the arrow described in FIG. 4 has shown the flow of the hydraulic fluid. Also in the second embodiment having the above configuration, the same effect as in the first embodiment can be obtained.

(Third Embodiment) FIG. 5 shows a third embodiment.
The same components as those in the first embodiment shown in FIG. 1 are designated by the same reference numerals. As shown in FIG. 5, in the third embodiment,
The top and bottom of the first embodiment shown in FIG. 1 are installed upside down, and the filtering function part 3 of the upstream passage 33 of the filtering function part 37 is further installed.
The magnet 50 is provided on the inner wall facing the ground 7 in the ground direction.

In the third embodiment having the above construction, the same effect as that of the first embodiment can be obtained. Further, in the third embodiment, the upstream side passage 33 of the filtration function part 37.
Since the magnet 50 is provided on the inner wall of the filtration unit 3,
The iron-based foreign matter captured by 7 falls under its own weight after the operation is stopped, and the foreign matter dropped by the magnetic force of the magnet 50 can be collected. Therefore, it is possible to reliably capture the foreign matter in the hydraulic oil and improve the reliability.

Next, a modification of the third embodiment is shown in FIG.
The top and bottom are the reverse of the third embodiment shown in FIG. In the modification shown in FIG. 8, since the magnet 50 is provided on the inner wall of the upstream passage 34 of the filtration function part 137, the filtration function part 13 is provided.
The iron-based foreign matter captured by 7 falls under its own weight after the operation is stopped, and the foreign matter dropped by the magnetic force of the magnet 50 can be collected. Therefore, it is possible to reliably capture the foreign matter in the hydraulic oil and improve the reliability.

In the embodiments of the present invention described above,
Although the linear solenoid valve is applied to the actuator, it goes without saying that a duty solenoid valve whose duty ratio is controlled can be applied to the present invention. Further, the actuator of the present invention can be applied to a solenoid valve for controlling the line pressure. In that case, the line pressure control valve 42 of the first embodiment shown in FIG. 3 corresponds to the control valve, and the solenoid valve 44 corresponds to the actuator. Furthermore, the fluid pressure module may have a switching valve that switches the fluid pressure applied to the controlled object.

Further, in the above-described embodiments, the fluid pressure control device of the present invention is applied to the hydraulic control device for the automatic transmission, but the present invention can also be applied to the hydraulic control device for the continuously variable transmission. However, it can be applied to a hydraulic control device for other machines such as machine tools.

[Brief description of drawings]

FIG. 1 is a sectional view showing a first embodiment in which a fluid pressure control device of the present invention is applied to a hydraulic control device for an automatic transmission.

FIG. 2 is a plan view showing a separate plate of the first embodiment.

FIG. 3 is a hydraulic circuit diagram showing a first embodiment in which the fluid pressure control device of the present invention is applied to a hydraulic control device for an automatic transmission.

FIG. 4 is a sectional view showing a second embodiment in which the fluid pressure control device of the present invention is applied to a hydraulic control device for an automatic transmission.

FIG. 5 is a sectional view showing a third embodiment in which the fluid pressure control device of the invention is applied to a hydraulic control device for an automatic transmission.

FIG. 6 is a cross-sectional view showing a hydraulic control device for an automatic transmission according to a comparative example.

FIG. 7 is a plan view showing a separate plate of a comparative example.

FIG. 8 is a sectional view showing a modified example of the third embodiment in which the fluid pressure control device of the present invention is applied to a hydraulic control device for an automatic transmission.

[Explanation of symbols]

1 Hydraulic module (fluid pressure control means) 10 Clutch pressure control valve (control valve) 20 Solenoid valve (actuator) 30, 130 valve body 31 Upper valve body (upper case) 32 Lower valve body (lower case) 33, 34 passage 35,135 Separate plate (plate member) 37, 137 Filtration function part (filtration means) 38,138 Through hole (through hole) 50 magnets

   ─────────────────────────────────────────────────── ─── Continued front page    F-term (reference) 3H082 AA12 CC02 DB12 DB35 EE13                 3H089 BB23 BB27 DA02 DC03 GG02                       HH17 JJ13                 3J063 AA01 AB01 AB22 AC03 BA11                       CC13 CC16 XE04 XE05                 3J552 MA01 NA06 PA67 QA41B                       QA42B SA51

Claims (5)

[Claims] 1. A fluid pressure control means for adjusting or switching a fluid pressure applied to an object to be controlled, an upper case and a lower case having an inner wall for accommodating the fluid pressure control means and forming a fluid passage, and the upper case. A plate member provided between the lower case and for communicating or blocking the passage; and a filtering unit provided in the plate member and having a function of filtering a fluid flowing through the passage. And a fluid pressure control device. 2. The fluid pressure control means includes an actuator that receives the hydraulic pressure of a working fluid as a supply pressure and outputs a control pressure by operating in response to a switching control signal, and the filtration means includes: The fluid pressure control device according to claim 1, wherein the fluid pressure control device is provided immediately upstream of the actuator. 3. The fluid pressure control means includes a control valve that controls the supply and discharge of the fluid pressure applied to the controlled object by being operation-controlled by the control pressure output from the actuator. 2. The fluid pressure control device according to 2. 4. A magnet provided on an inner wall of the passage upstream of the filtering means.
2. The fluid pressure control device according to 2 or 3. 5. The fluid pressure control device according to claim 1, wherein the filtering means has a plurality of through holes formed in the plate member by laser processing.