JP6949580B2 - Hydraulic control device - Google Patents

Description

The present invention relates to a hydraulic control device that controls the pressure of hydraulic fluid.

A hydraulic control device including a solenoid valve controls, for example, the hydraulic pressure of the hydraulic oil of a clutch mounted on an automobile. As described in Patent Document 1, the sleeve constituting this hydraulic control device has an input port for supplying hydraulic oil to the inside thereof, an output port for discharging the hydraulic oil from the inside, and an input port. A drain port is formed to drain the hydraulic oil in the output port when the port is closed. That is, the output port communicates with either the input port or the drain port, and at that time, the communication with the remaining one is cut off.

As briefly shown in FIG. 4A, the hydraulic control device 1 has a spool 2 that is displaced under the action of a solenoid valve (not shown). The communication destination of the output port (not shown) is switched by the displacement of the spool 2. Here, FIG. 4A shows a case where the output port and the drain port 3 are in a communicating state.

As shown in FIG. 6 of Patent Document 1, in the hydraulic control device 1 according to the prior art, a part of the land portion 4 provided on the spool 2 overlaps with the drain port 3, and the other parts of the drain port 3 are , The land portion 4 does not overlap (is not blocked by the land portion 4) and is in an open state. FIG. 4A and FIG. 4B, which is visually recognized from the direction of arrow X2 in FIG. 4A, simply show this state.

In this case, the output port is opened, and a hydraulic oil flow path is formed between the output port and the drain port 3 by the annular recess 5 formed in the spool 2. Therefore, the hydraulic oil of the output port is discharged from the drain port 3 through the annular recess 5.

Japanese Unexamined Patent Publication No. 2011-77355

Some tolerance is allowed for the thickness of the land portion 4 and the port diameter of each port including the drain port 3. In FIG. 4B, the case where the thickness of the land portion 4 and the port diameter of the drain port 3 are manufactured at the maximum value within the tolerance is represented by a solid line, and the time when the thickness of the land portion 4 is manufactured at the minimum value is represented by a broken line. By comparing the solid line and the broken line, it is recognized that there is a non-negligible difference in the opening area of the portion of the drain port 3 that is not blocked by the land portion 4.

The supply flow rate or discharge flow rate of the hydraulic oil increases when the opening area of the port is large, and decreases when the opening area of the port is small. As can be understood from this, in the hydraulic control device according to the prior art, for example, the flow rate of hydraulic oil may differ between products having different production lots.

The present invention has been made to solve the above-mentioned problems, and an object of the present invention is to provide a hydraulic control device capable of making the flow rates of hydraulic oil in individual products substantially equal to each other.

In order to achieve the above object , according to one embodiment of the present invention, an input port to which hydraulic oil is supplied, an output port to which the hydraulic oil is discharged, and the input port and the output port are provided. A sleeve formed with a drain port that communicates with the output port when communication is cut off and a drain port that communicates with the output port when communication between the input port and the output port is cut off.
A solenoid valve provided on the sleeve to control the flow rate of the hydraulic oil,
A spool provided with a plurality of lands that are displaced under the action of the solenoid valve and switch the communication destination of the output port to either the input port or the drain port.
With
When the input port and the output port communicate with each other, the plurality of land portions are at least positioned so as not to overlap the input port and the output port, and when the communication between the input port and the output port is cut off. hydraulic control device comprising at least the not overlap the drain port position Ru are provided.

That is, in the present invention, the land portion is fully opened when the port is opened, while it is fully closed when the port is closed. When comparing the individual hydraulic controllers, there is almost no difference in the opening area of the fully opened ports. Therefore, even if there is a difference in the port diameter and the thickness of the land portion within the tolerance range, the flow rate of the hydraulic oil is substantially the same.

After all, with the above configuration, it is possible to avoid a difference in the flow rate of the hydraulic oil between the individual hydraulic control devices, in other words, a variation. That is, for example, even if the products have different production lots, substantially the same flow rate can be obtained. Therefore, the reliability of the hydraulic control device is improved.

In this configuration, when the input port and the output port communicate with each other (both the input port and the output port are fully opened), it is preferable that the land portion does not overlap with the drain port. That is, the input port, the output port, and the drain port may be fully opened. In this case, the drain port is not limited to a position where the land portion is blocked when the input port and the output port communicate with each other. Therefore, the degree of freedom in the position where the drain port is provided is improved. At this time, it goes without saying that the land portion cuts off the communication between the output port and the drain port.

Further, in order to block the communication between the input port and the output port, for example, the input port may be fully closed. At this time, the plurality of land portions may be positioned so as not to overlap the output port and the drain port, that is, a position where the output port and the drain port are fully opened. In this case, the output port is not limited to the position where it is blocked by the land portion. Therefore, the degree of freedom in the position where the output port is provided is improved. At this time, the output port and the drain port communicate with each other by the land portion.

According to the present invention, the land portion provided on the spool is positioned so that the port is fully opened when the port is opened, while it is fully closed when the port is closed. In each hydraulic control device, there is almost no difference in the opening area of the fully opened port. Therefore, even if there is a difference in the port diameter and the thickness of the land portion within the tolerance range, the flow rate of the hydraulic oil is substantially the same.

As a result, for example, it is possible to prevent the flow rate of the hydraulic oil from being different between products having different production lots. That is, the variation in the flow rate of the hydraulic oil is suppressed, and a substantially equivalent flow rate can be obtained. For this reason, the reliability of the hydraulic control device is improved.

It is schematic cross-sectional view of the main part of the hydraulic control device which concerns on embodiment of this invention. It is an enlarged view of the main part of the hydraulic control device when visually recognized from the direction of the arrow X1 of FIG. It is schematic cross-sectional view of the main part when the input port and the output port in the hydraulic control device of FIG. 1 communicate with each other and are in an open state. FIG. 4A is a schematic cross-sectional view of a main part when a part of the land portion provided on the spool is at a position overlapping the drain port, and FIG. 4B is a main part when visually recognized from the direction of arrow X2 in FIG. 4A. It is an enlarged view.

Hereinafter, preferred embodiments of the hydraulic control device according to the present invention will be given, and will be described in detail with reference to the accompanying drawings. In addition, "upper" and "lower" in the following description correspond to upper and lower in each drawing, but this is for convenience only, and the direction when the hydraulic control device is actually used is indicated. It is not specific.

FIG. 1 is a schematic cross-sectional view of a main part of the hydraulic control device 10 according to the present embodiment. The hydraulic control device 10 is a cartridge type mounted on an automobile and attached to a clutch casing 12 constituting a clutch, and is a sleeve 20 housed in a mounting hole 14 formed in the clutch casing 12 and the sleeve 20. It has a solenoid valve 22 provided.

The sleeve 20 has a substantially cylindrical shape, and a valve hole 24 extending along the axial direction of the sleeve 20 is formed inside the sleeve 20. A stopper portion 28 on which the spool 26 is seated is provided in the valve hole 24. Further, on the side peripheral wall of the sleeve 20, the first annular groove 30a to the fourth annular groove 30d are formed along the circumferential direction. A plurality of input ports 32 are provided at the bottom of the first annular groove 30a so as to form a predetermined phase difference between them. On the other hand, a plurality of output ports 34 and a plurality of drain ports 36 are provided at the bottoms of the second annular groove 30b and the third annular groove 30c so as to form a predetermined phase difference between them. .. The input port 32, the output port 34, and the drain port 36 extend along the diameter direction of the sleeve 20 and communicate with the valve hole 24, respectively.

In the present embodiment, the number of input ports 32, output ports 34, and drain ports 36 is four each, and the phase difference between the same adjacent ports is approximately 90 °. In FIG. 1, two pieces having a phase difference of about 180 ° from each other are shown. The input port 32 and the output port 34 are substantially in phase with each other, and the output port 34 and the drain port 36 are substantially in phase with each other. Although not particularly shown, the input port 32, the output port 34, and the drain port 36 communicate with the oil supply passage, the oil discharge passage, and the drain passage formed in the clutch casing 12, respectively.

Here, a first annular filter member 40 and a second annular filter member 42 made of a metal material are arranged at the bottoms of the first annular groove 30a and the second annular groove 30b, respectively. In other words, the input port 32 and the output port 34 are covered with the first annular filter member 40 and the second annular filter member 42, respectively.

An O-ring 56 that seals between the inner wall of the mounting hole 14 and the sleeve 20 is mounted on the remaining fourth annular groove 30d. The outer peripheral wall (outer wall) of the sleeve 20 where the first annular groove 30a to the fourth annular groove 30d are not formed is a sealing surface that abuts on the inner wall of the mounting hole 14. Further, the surface of the sleeve 20 facing the solenoid valve 22 is a mounting surface on which the solenoid valve 22 is mounted, and a fifth annular groove 30e is formed on the mounting surface. An O-ring 58 that seals between the sleeve 20 and the solenoid valve 22 is mounted on the fifth annular groove 30e.

The valve hole 24 accommodates a bottomed cylindrical cap member 60 that closes one end of the valve hole 24, and a long spool 26 having an inner hole 61 extending along the longitudinal direction. .. An annular recess 62, which serves as an oil passage for hydraulic oil, is formed on the outer peripheral wall of the spool 26. Therefore, the spool 26 has a relatively long first land portion 64 (land portion) and a first land portion 62 sandwiching the annular recess 62. It has a shape in which two land portions 66 (another land portion) are formed. The first land portion 64 and the second land portion 66 are in sliding contact with the inner wall of the valve hole 24.

The inner diameter of the inner hole 61 is large in the first land portion 64, while the inner diameter is small in other portions. That is, there is a difference in inner diameter between the inner holes 61, and therefore, a step portion 68 is formed inside the spool 26. Further, a plurality of lateral holes 70 extending in a direction orthogonal to the longitudinal direction are formed above the second land portion 66 of the spool 26. The inner hole 61 communicates with the pilot chamber 72 through the lateral hole 70.

As shown in FIG. 1, when the hydraulic control device 10 is in the closed state, the thickness direction of the first land portion 64 extends over the entire input port 32. Therefore, the input port 32 is fully closed. That is, the first land portion 64 is in a position where the input port 32 is fully closed. Therefore, the hydraulic oil is surely prevented from flowing into the inner hole 61 from the input port 32.

At this time, the entire thickness direction of the second land portion 66 is located above the drain port 36. In other words, the second land portion 66 is a position that does not overlap the drain port 36. That is, the second land portion 66 does not reach the drain port 36. Therefore, as shown in FIG. 2 viewed from the direction of arrow X1 in FIG. 1, the drain port 36 is fully open. At this time, the output port 34 and the drain port 36 communicate with each other via the annular recess 62 (see FIG. 1).

The pilot chamber 72 is a part of the valve hole 24, and is a space defined by a second land portion 66, a sleeve 20, and a fixed core 74 described later. Pilot oil that supplies pilot pressure enters and exits the pilot chamber 72 through a breathing hole 76 formed in the cap member 60.

A return spring 80 is interposed between the cap member 60 and the spool 26. One end of the return spring 80 is seated on the bottom surface of the cap member 60, and the other end is seated on the step portion 68. The return spring 80 directs the spool 26 toward the solenoid valve 22 and urges the spool 26 to repel.

The solenoid valve 22 has a fixed core 74, a bobbin 84 around which an electromagnetic coil 82 is wound, a movable core 86, and a housing 88 accommodating them. The large-diameter end of the fixed core 74 is in contact with the mounting surface of the sleeve 20, and the small-diameter cylindrical portion is inserted into the through hole 90 of the bobbin 84 together with the movable core 86. The tip of the spool 26 is inserted into the hollow inside of the cylindrical portion.

An annular wall 92 that enters the through hole 90 of the bobbin 84 is projected from the ceiling of the housing 88. The bobbin 84 is supported by the annular wall 92. Further, for example, a bush 93 made of resin is fitted in the hollow inside of the annular wall 92. The movable core 86 is displaceably inserted into the hollow interior of the bush 93, and when displaced, it is in sliding contact with the inner wall of the bush 93.

The electromagnetic coil 82 wound around the bobbin 84 is energized from a power source (not shown). A magnetic field is formed around the electromagnetic coil 82 with this energization, and as a result, the movable core 86 is displaced downward in FIG.

The open end of the housing 88 surrounds the large-diameter end of the fixed core 74 and the vicinity of the mounting surface of the sleeve 20, and is crimped inward in the radial direction. As a result, the housing 88 is prevented from coming off from the sleeve 20.

The hydraulic control device 10 configured in this way is attached to the clutch casing 12 via the attachment stay 94.

The hydraulic control device 10 according to the present embodiment is basically configured as described above, and the effects thereof will be described next.

The hydraulic control device 10 operates as follows.

When the electromagnetic coil 82 is not energized and the pilot pressure is not applied to the pilot chamber 72, the spool 26 is elastically urged toward the solenoid valve 22 by the return spring 80 as shown in FIG. Further, the movable core 86 is most retracted by receiving the elastic force of the return spring 80 via the spool 26.

At this time, the first land portion 64 of the spool 26 blocks the entire input port 32. That is, the first land portion 64 is fully closed. In this way, since the first land portion 64 is in the position where the input port 32 is fully closed, hydraulic oil is not introduced from the input port 32 into the valve hole 24. That is, the communication between the input port 32 and the output port 34 is cut off in a non-communication (communication cutoff) state, and the hydraulic control device 10 is in a closed state.

On the other hand, the annular recess 62 extends from the output port 34 to the drain port 36. Therefore, the output port 34 communicates with the drain port 36. At this time, the annular recess 62 is at a position corresponding to the position of the output port 34. Therefore, the output port 34 is fully open.

Here, the entire second land portion 66 is located above the drain port 36. Therefore, the drain port 36 is fully open (see FIG. 2). Therefore, the hydraulic oil in the output port 34 is discharged from the drain port 36 at a predetermined flow rate.

As the electromagnetic coil 82 is energized from this state via the power source, the fixed core 74 is magnetized, and as a result, an electromagnetic force that attracts the movable core 86 is generated. Since this electromagnetic force exceeds the elastic urging force of the return spring 80, the movable core 86 is displaced downward in FIG. 1, that is, toward the fixed core 74 side. At this time, the pilot oil that has passed through the breathing hole 76, the inner hole 61, and the lateral hole 70 is introduced into the pilot chamber 72.

The spool 26, which is pressed by the displaced movable core 86 and receives pilot pressure on the second land portion 66, is integrally displaced with the movable core 86. Along with this, the return spring 80 contracts. As shown in FIG. 3, the spool 26 stops when it is seated on the stopper portion 28. At this time, the entire first land portion 64 is located below the input port 32. In other words, the first land portion 64 is a position that does not overlap (or does not reach) the input port 32. Therefore, the input port 32 is fully opened.

That is, the first land portion 64 is at a position where the input port 32 is fully opened. As a result, hydraulic oil is introduced from the input port 32 into the valve hole 24 at a predetermined flow rate.

On the other hand, the input port 32 and the output port 34 communicate with each other via the annular recess 62. Also at this time, the annular recess 62 is at a position corresponding to the position of the output port 34, and the output port 34 is fully open.

That is, the input port 32 and the output port 34 communicate with each other via the annular recess 62, and the ports 32 and 34 are fully opened. Therefore, the hydraulic oil that has flowed into the valve hole 24 from the input port 32 at a predetermined flow rate reaches the output port 34 through the annular recess 62, and further reaches the oil discharge path from the output port 34 at a predetermined flow rate. leak. The hydraulic oil further flows into the clutch through the oil discharge path to supply a predetermined clutch pressure. After that, the oil returns to the oil supply path via a predetermined path, and is further resupplied from the input port 32 to the valve hole 24 (annular recess 62).

In this way, by fully opening both the input port 32 and the output port 34 when the hydraulic control device 10 is opened, the hydraulic oil can be input and output at a predetermined flow rate. That is, the flow rate of hydraulic oil is stable.

At this time, the entire second land portion 66 of the spool 26 is below the drain port 36. That is, the second land portion 66 is at a position where it does not overlap (approach) the drain port 36. Therefore, the drain port 36 is maintained fully open, and in this state, the communication between the output port 34 and the drain port 36 is cut off, and both ports 34 and 36 are in a non-communication state.

After an appropriate amount of hydraulic oil has been distributed, energization from the power source to the electromagnetic coil 82 is stopped. Along with this, the electromagnetic force acting on the movable core 86 disappears. Therefore, the return spring 80 expands and elastically urges the spool 26 and the movable core 86 integrally. As a result, the spool 26 and the movable core 86 are displaced upward in FIG. 3 and return to the state shown in FIG. That is, the communication between the input port 32 and the output port 34 is cut off, and the flood control device 10 is closed.

At this time, the pilot oil in the pilot chamber 72 is discharged through the lateral hole 70, the inner hole 61, and the breathing hole 76. Further, the hydraulic oil in the vicinity of the output port 34 is discharged to the drain passage at a predetermined flow rate via the drain port 36.

As described above, in the present embodiment, the first land portion 64 is set so that each of the ports 32, 34, and 36 is appropriately fully closed or fully opened when the ports 32, 34, and 36 are in a communicating state or a non-communication state with respect to another port. , The position of the second land portion 66 is set. In FIG. 2, the thickness of the second land portion 66 and the port diameter of the drain port 36 are represented by solid lines when they are manufactured at the maximum values within the tolerance, and are represented by broken lines when they are manufactured at the minimum values. In either case, since the second land portion 66 does not reach the drain port 36, the drain port 36 is fully opened, so that there is almost no difference in the opening area of the drain port 36.

Therefore, in each of the separately manufactured hydraulic control devices 10, the thickness of the first land portion 64 and the second land portion 66 and the port diameters of the ports 32, 34, and 36 are different within the tolerance range. Even when there is, the flow rates of the hydraulic oil flowing in or out from the ports 32, 34, and 36 are substantially the same. That is, for example, it is possible to avoid a variation in the flow rate of the hydraulic oil between the flood control devices 10 having different production lots. Therefore, the reliability of the flood control device 10 is improved.

The present invention is not particularly limited to the above-described embodiment, and various modifications can be made without departing from the gist of the present invention.

For example, an output port that outputs low-pressure hydraulic oil and another output port that outputs high-pressure hydraulic oil may be formed at different positions in the axial direction of the sleeve 20. For example, when forming two output ports 34, an input port may be formed between the low voltage output port and the high voltage output port in the axial direction of the sleeve 20.

Further, in this embodiment, a so-called normally closed valve that is closed when the electromagnetic coil 82 is not energized is illustrated, but a so-called normally open valve that is open when the electromagnetic coil 82 is not energized is used. There may be.

In any case, the first land portion 64 and the second land portion 66 may be positioned so as not to overlap (or reach) the input port, the output port, and the drain port. For example, in the above embodiment, when the communication between the input port and the output port is cut off, the input port is fully closed and the output port is fully opened. On the contrary, the input port is fully opened. And the output port may be fully closed.

Further, in the above embodiment, the hydraulic control device 10 for controlling the hydraulic pressure of the hydraulic oil of the clutch is illustrated, but the present invention includes, for example, a hydraulic control device for controlling the hydraulic pressure of an oil pump or the like. It can also be used as a hydraulic control device.

1, 10 ... Hydraulic control device 2, 26 ... Spool 3, 36 ... Drain port 5, 62 ... Annular recess 14 ... Mounting hole 20 ... Sleeve 22 ... Solenoid valve 24 ... Valve hole 32 ... Input port 34 ... Output port 40 ... No. 1 annular filter member 42 ... 2nd annular filter member 61 ... Inner hole 64 ... 1st land portion 66 ... 2nd land portion 72 ... Pilot chamber 74 ... Fixed core 80 ... Return spring 82 ... Electromagnetic coil 84 ... Bobbin 86 ... Movable core

Claims (1)

Valve hole and an input port you supplying hydraulic fluid toward the valve hole, and an output port for the hydraulic fluid from the valve hole is discharged, the input port and the output port extending along the axial direction a sleeve and a drain port are formed in communication with the output port via the valve bore when the connection cutoff, and communication between the output port and the input port during communication of said output port is blocked with,
A solenoid valve provided on one end side of the sleeve in the axial direction to control the flow rate of the hydraulic oil, and
A first that is provided so as to be in sliding contact with the inner wall of the valve hole, is displaced along the axial direction under the action of the solenoid valve, and switches the communication destination of the output port to either the input port or the drain port. the land portion, the second land portions are provided, and the spool which annular recesses are formed to be sandwiched between at the axial direction and the first land portion and the second land portion,
A return spring, which is arranged in the valve hole and elastically urges the spool toward the solenoid valve,
With
A stopper portion is provided in the valve hole on which the other end side of the spool in the axial direction is seated.
When the input port and the output port communicate with each other at a position where the spool compresses the return spring and is seated on the stopper portion under the action of the electromagnetic valve, the first land portion and the second land portion are said to be the same. the input port I do not overlap the input port and the output port position, together with the output port and the drain port is fully opened toward the valve hole, the output port and the drain by the second land portion Communication with the port is cut off,
When the return spring is extended and the spool is separated from the stopper portion and the communication between the input port and the output port is cut off , the first land portion is closed so that the input port is fully closed. It extends over the entire input port, and disposed in the first land portion and the output port and the drain port I do and the position where the second land portion does not overlap with the drain port is fully open toward the valve hole Rutotomoni, hydraulic control system the drain port and the output port and wherein Rukoto through communication through the annular recess.

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