JPS5936525Y2 - hydraulic control valve - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic control valve, and more particularly to a hydraulic control valve that is most suitable for use in a hydraulic brake system of an automobile.

In automobile brake systems, when removing the air from the brake fluid in the brake system, the brake pedal is depressed repeatedly to forcefully send the brake fluid to the wheels, but at this time, the brake fluid is restricted from flowing back into the mask cylinder. To this end, backflow limiting valves such as residual pressure valves and throttle valves have conventionally been provided in brake systems.

In addition, in order to prevent the rear wheels from lifting up and locking due to the inertia of the car body when the brakes are applied suddenly, the rate of increase in the hydraulic pressure in the rear wheel cylinders is adjusted to a predetermined so-called turning point pressure. In the above, a pressure reducing valve is used to reduce the pressure.

However, conventionally, the backflow restriction valve was installed at the outlet of the mask cylinder, and the pressure reducing valve was installed in the brake fluid piping.
This resulted in disadvantages such as an increase in the number of parts, making the car heavier and more expensive.

The purpose of the present invention is to eliminate the above-mentioned drawbacks of the conventional technology. , a valve body that is biased toward the outlet side connected to the brake application device by the biasing force of the first elastic member, and the outlet side that exceeds a predetermined position of the valve body due to the biasing force of the first elastic member. a locking means that can be engaged with the valve body to prevent the valve from moving toward the outlet side; a second elastic member tensioned with a predetermined preload; a piston having a through hole that is energized, and the difference between the energizing force due to the hydraulic pressure that the piston receives on the outlet side and the energizing force due to the hydraulic pressure that the screw I/N receives on the inlet side. If it becomes larger than the biasing force of the second elastic member,
The piston moves to the inlet side and closes the through hole of the screws with the valve body, thereby increasing the pressure on the outlet side compared to the pressure on the artificial side when a predetermined pressure is exceeded. In the hydraulic control valve, the communication between the inlet side and the outlet side is cut off or restricted by engagement of the valve body and the locking means, and This is achieved by a hydraulic control valve characterized in that a valve is provided on either one of the stop means and a valve that allows liquid to move from the inlet side to the outlet side and prohibits the reverse movement.

With the above configuration, the number of parts can be reduced, the weight of the entire vehicle body can be reduced accordingly, and manufacturing costs can also be reduced.

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

As shown in FIGS. 1 and 2, the hydraulic pressure control valve according to the embodiment of the present invention is housed in valve mounting bodies 8 and 8' that are integrally formed in the two-system mask cylinder 2. .

As is well known, an oil reservoir 1 is placed on the mask cylinder 2.
14 is fixed, and when the brake pedal P is operated, the hydraulic pressure generated in the two hydraulic pressure generating chambers in the cylinder hole 10 of the mask cylinder 2 is directed to the horizontal outlet 4°4' and the downward outlet 6, respectively. , 6' to the wheel cylinders of both front wheels and both rear wheels.

Since both hydraulic pressure control valves provided in the valve mounting bodies 8 and 8' have completely the same structure, only the hydraulic pressure control valve and throttle valve provided in the front valve mounting body 8 will be described in the following.
This will be explained with reference to FIGS.

A cylinder hole 18 for housing a valve box is formed in the valve mounting body 8 and extends in the vertical direction in the figure and opens on the outlet 6 side, and a hydraulic pressure control valve 16 according to the present invention, which will be explained in detail below, is housed in this cylinder hole 18. The valve box 24 is fitted.

The head of the valve body 24 has a conical shape, and this portion is in close contact with a conical recess formed at the top of the outlet screw 22 which is screwed into the open end of the cylinder hole 18.

By tightening the outlet screw 22, the side edge of the conical head of the valve body 24 is pressed against a step formed in a part of the cylinder hole 18.

In this way, the liquid communication chamber 20 is formed at the bottom of the cylinder hole 18.
The valve body 24 is fixed to the cylinder hole 18 so as to form a cylinder hole 18 .

The outlet screw 22 is provided with a through hole as the outlet 6, and the liquid communication chamber 20 communicates with one of the hydraulic pressure generating chambers 12 in the cylinder hole 10 of the master cylinder 2 via the side hole 14.

Next, the hydraulic pressure control valve 16 accommodated in the above-mentioned valve box 24 will be explained.

A stepped cylinder hole 120 is formed in the valve box 24, and the hydraulic pressure control valve 16 of this embodiment is accommodated in the cylinder hole 120.

The hydraulic control valve 16 mainly includes a valve body 28 which is biased downward by a spring 38 as a first elastic member, and which restricts the downward movement of the valve body 28 and is fixed to the valve body 24. It is biased downward by the locking casing 26 as a locking means and the spring 62 as a second elastic member, and is slidable in the vertical direction in the small diameter portion 30 of the stepped cylinder hole 120 of the valve body 24. It is separated from the stepped piston 32.

The locking casing 26 has a cylindrical shape, and a flange portion 34 formed at its upper end, together with a disk 36 having a central opening 42, connects to an annular groove 24a formed at the upper end of the valve body 24. By being tightly fitted, the locking casing 2
6 is fixed to the valve body 24.

A locking chamber 40 is formed by the locking casing 26 and the disk 36, and communicates with the liquid communication chamber 20 described above through a central opening 42 of the disk 36.

The valve body 28 has a valve stem 48 extending vertically, a flange portion 44 integrally formed in the center thereof, and a circumferential surface of the flange portion 44 and a circumferential surface of a portion of the lower portion of the valve stem 48. The lower portion of the valve stem 48 passes through a hole 56 provided in the center of the bottom portion 54 of the locking casing 26 .

A plurality of holes 46 are formed in the flange portion 44 of the valve body 28, and the valve body 28 is urged downward by a spring 38 stretched between the flange portion 44 and the above-mentioned disk 36. The downward movement of the valve body 28 due to this bias is restricted by the shoulder portion 52 of the valve rubber 50 being seated on the bottom portion 54 of the locking casing 26 .

At the cylinder hole 18 of the valve body 24, the locking casing 2
6, a stepped piston 32 is disposed such that its large diameter portion can slide relative to the small diameter portion of the cylinder hole 18.

A seal ring holder ring member 70 is fixed to the stepped portion 68 of the cylinder hole 18, and a spring holder ring 60 is fixed to the top of the stepped piston 32.

A sealing knee ring 72 is fitted between the ring member 70 and the spring bearing 60, and the small diameter portion of the stepped piston 32 is configured to be able to slide through the through hole of the ring member 70 and knee ring 72. has been done.

Further, in the spring receiver, a spring 62 is stretched between the ring 60 and the flange portion 34 of the locking casing 26, thereby urging the piston 32 downward.

A through hole 64 is bored in the stepped piston 32 and faces the valve stem 48 of the valve body 28 described above.

A plurality of grooves 66 are formed in the large diameter end of the piston 32 in the radial direction.
are formed, and an outlet chamber 82 communicates with these grooves 66.
is formed between the large-diameter end of the piston 32 and the bottom 80 of the small-diameter portion 30 of the stepped cylinder hole 18 of the valve body 24 .

A through hole 84 is provided in the head of the valve body 24, through which the above-mentioned outlet chamber 82 communicates with the outlet 6.

The large diameter side of the piston 32 is sealed against the small diameter cylinder hole 30 by an O-ring 110.
A ring-shaped air chamber 74 formed by the small diameter side of the valve case 2 and the small diameter cylinder hole 30 passes through a horizontal hole 76 formed in a part of the circumferential wall of the valve box 24, and connects the circumferential side of the valve box 24 and the cylinder hole 18. This gap 78 also includes a small gap (not visible in the figure) between the valve body 24 and the lower part of the cylinder hole 18, and a gap 78 between the head of the valve body 24 and the cylinder hole 18. It communicates with the atmosphere through the gap between the hole 18 and the threaded portion of the outlet screw 22.

The valve body 24 is sealed at its upper portion from the cylinder hole 18 by an O-ring 112.

A residual pressure chamber 58 is formed between the locking casing 26 configured as described above and the piston 32, and this is caused by the valve stem 48 of the valve body 28 engaging with the through hole 64 of the piston 32. When not in use (state shown), it communicates with the outlet 6 through the through hole 64.

As described above, the hydraulic pressure control valve 16 is housed in the cylinder hole 18 of the valve mounting body 8, but the valve mounting body 8 is further formed with a stepped cylinder hole 90 extending laterally. A throttle valve 88 is disposed within the bore 90 .

The hole 90 communicates with the above-mentioned liquid communication chamber 20 laterally (through L86), and a valve chamber 92 for the throttle valve 88 is formed inside the small diameter side of the hole 90.

The throttle valve 88 is made of an elastically deformable material such as rubber and includes a spring 98 that urges a parot-shaped valve body 96 to the left in the figure, and a valve seat member 100.

The valve body 96 is in the illustrated state due to the biasing force of the spring 98.
The slope portion contacts the end portion of the valve seat member 100.

A cylindrical gap 94 is formed between the circumferential side of the valve body 96 and the cylinder hole 90, and the valve seat member 1 of the valve body 96
A plurality of small notches 104 are provided at the corners that contact 00.

The valve seat member 100 has a large-diameter hole 106 that serves as an outlet chamber for the valve body 96, and a guide hole 108 that communicates with the hole 106.

The outlet chamber 106 communicates with the outlet 4 through a guide hole 108, and with the valve chamber 92 through a plurality of notches 104 and gaps 94.

An opening 102 is formed at the left end of the valve body 96 and can be opened and closed by the difference in hydraulic pressure between the left and right sides.

The outlet 4 for one of the front wheels is formed as a through hole of an outlet screw 130, and the top of this outlet screw 130 has a conical shape similar to the outlet screw 22 having the outlet 6 for one of the rear wheels described above. A recess is formed.

Therefore, by screwing the outlet screw 130 into the open end of the stepped cylinder hole 90, this recess is formed in the valve seat member 10.
The corner portion of the valve seat member 100 is pressed against the stepped portion of the cylinder hole 90.

In this way, by tightening the outlet screw 130, the valve seat member 1
00 will be fixed to the valve mounting body 8.

The operation of this embodiment configured as described above will be explained below.

When the brake is not applied, that is, when the brake pedal P is not depressed, the hydraulic pressure control valve 16 and the throttle valve 88 are in the state shown in FIG.

That is, the fluid pressure in the fluid communication chamber 20, the locking chamber 40, the valve chamber 92 of the throttle valve 88, and the outlet chamber 106 on the front wheel side, which communicate with the fluid pressure generation chamber 12 where the fluid pressure is zero, is zero; The hydraulic pressure in the residual pressure chamber 58 of the pressure control valve 16 and the outlet chamber 82 on the rear wheel side is maintained at a predetermined residual pressure, as will be described later.

Further, the valve element 28 is brought into contact with the bottom part 54 of the locking casing 26 at its valve rubber 50 due to the biasing force of the spring 38, and the residual pressure in the residual pressure chamber 58 causes the valve rubber 50 to be pressed against the valve stem 4.
8 as shown in the figure.

On the other hand, due to the biasing force of the spring 62, the stepped piston 32
Its lower end is in contact with the bottom 80 of the cylinder hole 30, and the valve stem 48 of the valve body 28 and the piston 32 are spaced apart from each other.

Also, the piston 32 is subjected to residual hydraulic pressure due to the difference between its large-diameter side cross-sectional area and small-diameter side cross-sectional area, but since the force of the spring 62 resisting this is greater, it does not move upward. The state shown is maintained.

When the brakes are applied, hydraulic pressure is generated in the hydraulic pressure generation chamber 12, the liquid communication chamber 20, the locking chamber 40, and the valve chamber 92 of the throttle valve 88, and as shown in FIG. It pushes open the opening 102 of the body 96 and flows through the gap 94 and notch 104 along the outer circumference of the valve body 96, into the outlet chamber 106, through the hole 108 and through the outlet 4 to the wheel cylinder of the front wheel.

When the hydraulic pressure in the locking chamber 40 rises and exceeds a predetermined residual pressure in the residual pressure chamber 58, the brake fluid in the locking chamber 40 flows through the hole in the flange portion 44 of the valve body 28, as shown in FIG. 46 and spread the valve rubber 50, passing between the valve rubber 50 and the valve stem 48, the residual pressure chamber 58, the holes 64 of the screws 1 to 32, the outlet chamber 82, the holes 84, and the outlet 6. and flows to the rear wheel cylinder.

The hydraulic pressure applied to the piston 32 increases as the depression force on the brake pedal P increases, but when the predetermined hydraulic pressure is not reached, the biasing force of the spring 62 is still greater.
The piston 32 maintains the state shown by the solid line in FIGS. 2 and 3.

That is, in such a state, the hydraulic pressure to the front wheel cylinder and the hydraulic pressure to the rear wheel cylinder increase at the same rate.

When the hydraulic pressure further increases and the hydraulic pressure on the screw I-n 32 exceeds the force applied by the spring 62, the screw I-n 32 compresses the spring 62, as shown by the dashed line in FIG. and move upwards.
The lower end of the valve stem 48 of the valve body 28 is connected to the through hole 6 of the screw I-ne 32.
4 and closes the through hole 64.

The hydraulic pressure at this time is called the breaking point pressure. The through hole 64 is connected to the valve body 2.
When the hydraulic pressure in the residual pressure chamber 58 further increases with the valve stem 48 of No. 8 closed, the sum of the hydraulic pressure received from the residual pressure chamber side of the screw I/N 32, that is, the small diameter side, and the biasing force of the b62 increases. Since the fluid pressure received from the outlet chamber 82 side of the piston 32, that is, the large diameter side, is exceeded, the piston 32 moves downward, and the through hole 64
is separated from the valve stem 48 of the valve body 28 and opened.

Then, the hydraulic pressure in the outlet chamber 82 rises again together with the hydraulic pressure in the residual pressure chamber 58, and the upward hydraulic pressure against the piston 32 is increased by the spring 6.
Beyond the second biasing force, the piston 32 moves upward again and its through hole 64 is closed by the valve stem 48 of the valve body 28.

As described above, the residual pressure in the residual pressure chamber 58 is increased by increasing the pressing force on the brake pedal P, and the vertical movement of the piston 32, that is, the opening and closing of the through hole 64 is repeated, so that the so-called "throttle opening" is caused. As a result, when the hydraulic pressure exceeds the corner pressure, the rate of increase in the hydraulic pressure in the outlet chamber 82 relative to the hydraulic pressure in the residual pressure chamber 58 decreases.

In other words, the hydraulic pressure control valve 16 functions as a pressure reducing valve.

On the other hand, the rate of increase of the hydraulic pressure in the outlet chamber 106 of the throttle valve 88 relative to the hydraulic pressure in the valve chamber 92 does not change even if the pressure exceeds the corner pressure.

That is, the hydraulic pressure in the outlet chamber 106 is the same as the hydraulic pressure in the valve chamber 92, and increases as the hydraulic pressure in the hydraulic pressure generating chamber 12 increases.

When the brake is released, the hydraulic pressure generation chamber 12 and the liquid communication chamber 20
And the hydraulic pressure in the locking chamber 40 and the valve chamber 92 of the throttle valve 88 decreases.

Therefore, the valve rubber 50 of the valve body 28 of the hydraulic pressure control valve 16 is again in close contact with the valve stem 48, while the hole 1 of the valve body 96 of the throttle valve 88
02 is closed, the brake fluid in the outlet chamber 106 flows through the notch 104 and the gap 94, and the hydraulic pressure in the outlet chamber 106 is closed.
It gradually decreases due to the aperture effect of 04.

As described above, when the brake is released, the valve rubber 50 of the valve body 28 first comes into close contact with the valve stem 48, blocking the flow of brake fluid from the residual pressure chamber 58 to the locking chamber 40. When the hydraulic pressure in the locking chamber 40 communicating with the generating chamber 12 decreases, the force due to the difference in hydraulic pressure on both sides of the valve element 28 exceeds the biasing force of the spring 38, and the valve element 28 moves as shown by the solid line in FIG. move upwards.

As a result, the valve rubber 50 of the valve body 28 is attached to the locking casing 2.
6, the brake fluid flows from the residual pressure chamber 58 to the valve body 28 and the locking casing 26 as shown by the arrow in FIG.
and into the locking casing 26.

At this time, the difference in fluid pressure acting on both sides of the piston 32 causes the spring 6
2, it rises as shown by the dashed line in FIG. 4, and its through hole 64 engages with the valve stem 48 of the valve body 28 and is closed.

On the other hand, in the crest valve 88 as well, when the force due to the difference in hydraulic pressure on both sides of the valve body 96 exceeds the biasing force of the spring 98, the valve body 96
moves to the right and leaves the valve seat member 100.

As a result, the brake fluid passes from the outlet chamber 106 through the gap 94 between the valve body 96 and the valve seat member 100 and between the outer peripheral surface of the valve body 96 and the cylinder hole 90, as shown by the arrow in FIG. The fluid flows into the pressure generating chamber 12 and exits into the outlet chamber 106.
The hydraulic pressure of decreases.

When the hydraulic pressure in the hydraulic pressure generating chamber 12 further decreases, the hydraulic pressure control valve 16
The hydraulic pressure received from the through hole 64 side of the valve body 28 and the locking chamber 4
When the difference between the hydraulic pressure received from the zero side exceeds the biasing force of the spring 38, the valve body 28 moves further upward as shown by the dashed line in FIG. Leave.

This allows the brake fluid to flow from the outlet chamber 82 to the piston 32.
through hole 64 , residual pressure chamber 58 , and valve rubber 50 of valve body 28
and the bottom 54 of the locking casing 26 into the locking chamber 40 .

This reduces the hydraulic pressure in the outlet chamber 82.

Incidentally, when the hydraulic pressure becomes equal to or less than the breaking point pressure, the piston 32 moves downward and assumes the position shown by the solid line in FIG. 4.

When the fluid pressure in the fluid pressure generating chamber 12 further decreases to near zero,
The difference in hydraulic pressure on both sides of the valve body 28 of the hydraulic pressure control valve 16 becomes smaller than the biasing force of the spring 38, the valve body 28 moves downward, and the valve rubber 50 of the valve body 28 locks again. Casing 26
seated on the bottom 54 of.

This stops the flow of brake fluid, and the hydraulic pressures in the residual pressure chamber 58 and the outlet chamber 82 are maintained at a predetermined residual pressure.

On the other hand, the difference in hydraulic pressure on both sides of the valve body 96 of the throttle valve 88 also becomes smaller than the biasing force of the spring 98, so that the valve body 96
8, it is moved to the left in the figure and is seated on the valve seat member 100 again.

Thereafter, the brake fluid flows from the outlet chamber 106 into the hydraulic pressure generating chamber 12 through the notch 104 and the gap 94 in the valve body 96 which has a throttling effect.

That is, the hydraulic pressure in the outlet chamber 106 gradually decreases to zero due to the throttling effect of the notch 104.

The backflow limiting effect of this embodiment will be explained below.

When removing air from brake fluid that has entered the brake system due to repair, inspection, failure, etc., the brake fluid is forced into the brake system from the mask cylinder 2 by repeatedly depressing the brake pedal P.

During this repeated depression, when the brake pedal P is released, the brake fluid in the brake system tends to flow back toward the hydraulic pressure generation chamber 12 of the mask cylinder 2, but this embodiment prevents this. Or be restricted.

That is, as long as the force due to the difference in hydraulic pressure on both sides of the valve body 28 of the hydraulic pressure control valve 16 is smaller than the urging force of the valve body 28, the valve rubber 50 of the valve body 28 will be pressed against the bottom part 54 of the locking casing 26. Since the driver is seated, the brake fluid in the brake system for the rear wheels does not flow back to the hydraulic pressure generation chamber 12 side.

That is, when the brake pedal P is depressed, the brake fluid is forced from the hydraulic pressure generating chamber 12 to the outlet 6 by pushing the valve rubber 50 of the valve body 28 apart as described above. At this time, the valve rubber 50 of the valve body 28 is seated on the bottom 54 of the locking casing 26,
Since the valve rubber 50 is in close contact with the valve stem 48, brake fluid cannot flow from the residual pressure chamber 58 side to the locking chamber 40 side.

Furthermore, as long as the force due to the difference in hydraulic pressure on both sides of the valve body 96 of the throttle valve 88 is smaller than the biasing force of the spring 98, the valve body 96 is seated on the valve seat member 100. Due to the throttling effect of the notch 104 provided in the valve body 96, the brake fluid flows into the outlet chamber 10.
The liquid gradually flows backward from the liquid pressure generating chamber 6 to the liquid pressure generating chamber 12 side.

Therefore, the brake fluid pumped through the opening 102 of the valve body 96 does not return to the hydraulic pressure generation chamber 12, or the brake fluid is transferred from the hydraulic pressure generation chamber 12 side to the outlet chamber 106 side by the next depression before returning. be pumped to.

As described above, according to this embodiment, air can be removed reliably, but the hydraulic pressure control valve 16 according to this embodiment has various other effects as described below.

(1) Since the conventionally required residual pressure action (also for the purpose of improving brake response) and pressure reducing action can be performed, there is no need for an independent residual pressure valve and pressure reducing valve as in the past.

Therefore, the number of valves can be reduced as a whole, and the installation work to the vehicle body can be simplified.

(2) Since the valve body 28 also serves as the valve body of the conventional residual pressure valve and pressure reducing valve, the number of parts is small, the weight is also small, and the cost is also reduced.

(3) Since the throttle valve 88 and the throttle valve 88 are housed in the valve mounting body 8 integrated into the mask cylinder 2, when the mask cylinder 2 is mounted on the vehicle body, these valves are also mounted on the vehicle body at the same time. Installing the valve is easy.

(4) Since all the components are housed within the valve box 24, handling and assembly are easy.

Another embodiment of the present invention will be described below with reference to FIG.

This embodiment differs from the above-mentioned embodiment only in the structure of the locking casing 26 and the valve body 28, so only this part is illustrated in FIG. 5, and the other parts are completely the same as in FIG. It was done.

The locking casing 226 as the locking means of this embodiment also has the same shape as the above-mentioned embodiment, but has two holes 246 bored in its circumferential wall, and an annular ring so as to cover these holes 246. Valve rubber 250 is stretched over the circumferential side.

The valve body 228 consists of a cylindrical valve body 252 and a valve stem 248, and is pushed downward by a spring 238 as a first elastic member stretched between the valve body 252 and the disk 36. It is energized.

An arcuate projection is formed on the bottom surface of the valve body 252, and a plurality of notches 229 are provided in this projection.

Therefore, due to the downward urging force of the spring 238 described above, the valve body 229 is brought into contact with the bottom portion 254 of the locking casing 226 at the arcuate protrusion on the bottom surface thereof.

Therefore, the locking chamber 240 is formed by a plurality of notches 22 of the valve body 228.
The notch 229 communicates with the throttle chamber 258 through the valve body 9 of the throttle valve 88 in the aforementioned embodiment.
Like the notch 104 in No. 6, it has a constricting effect.

That is, communication between the locking chamber 240 on the inlet side and the throttle chamber 258 on the outlet chamber side is restricted.

The throttle chamber 258 is formed between the locking casing 226 and the piston 32 in the same way as the residual pressure chamber 58 in the previous embodiment, but it is named this way because it does not function as the residual pressure chamber 58. .

When the hydraulic pressure in the locking chamber 240 is higher than the hydraulic pressure in the throttle chamber 258, the brake fluid in the locking chamber 240 pushes the valve rubber 250 open, passes through the hole 246, and passes through the notch 229 of the valve body 228. It flows into the throttle chamber 258.

In the opposite case, while the force due to the difference in hydraulic pressure on both sides of the valve body 228 exceeds the biasing force of the spring 238, the valve body 252 of the valve body 228 and the locking casing 226 are moved upward. It flows into the locking chamber 240 through the bottom part 254 of the valve body 228, and gradually engages only through the notch 229 of the valve body 228 while the force due to the above-mentioned hydraulic pressure difference does not exceed the biasing force of the spring 238. It flows into the stop chamber 240.

When the brake fluid is pumped by repeatedly depressing the brake pedal to remove air from the brake fluid, when the brake pedal is released during the repetition, the brake fluid in the brake system is pumped on both sides of the valve body 228. As long as the force due to the hydraulic pressure difference is less than the biasing force of the spring 238, the valve body 2
Since it gradually flows backward through only the notch 229 of 28,
As in the first embodiment, the air in the brake fluid does not enter the hydraulic pressure generating chamber and is surely released.

In other respects, the hydraulic pressure control valve of this embodiment operates in the same manner as the hydraulic pressure control valve 16 of the first embodiment and produces similar effects.

Moreover, the valve rubber 250, which serves as a valve that allows liquid to move from the inlet side to the outlet side and prohibits the reverse, has a simpler shape than the valve rubber 50 of the first embodiment.

Although the embodiments of the present invention have been described above, the present invention is not limited to these and various modifications can be made based on the technical idea of the present invention.

For example, a notch corresponding to the notch 229 may be provided in the shoulder portion 52 of the valve body 28 of the first embodiment, similarly to the valve body 228 of the second embodiment.

In this case, the residual pressure effect as described above disappears in the residual pressure chamber 58, and the notch has a throttling effect on the brake fluid, so the residual pressure chamber 58 becomes a throttling chamber.

Further, the notch 229 of the valve body 228 of the second embodiment does not need to be cut.

In this case, the throttling chamber 258 acts as a residual pressure chamber, so it becomes a residual pressure chamber.

In the hydraulic control valve 16 of any of the above embodiments, the valve body 2
When the notch is cut at 8 or 228, the valve body performs a throttling action and a pressure reducing action, and when the notch is not cut, a residual pressure action and a pressure reducing action are performed.

As explained above, according to the present invention, the valve body performs a residual pressure action or a throttling action, that is, a backflow restriction action in addition to the originally necessary pressure reducing action, so the present invention reduces the number of parts in the brake system. In addition, the present invention has various effects such as greatly simplifying the assembly of the hydraulic control valve and reducing manufacturing costs.

[Brief explanation of the drawing]

The drawing shows a hydraulic control valve according to an embodiment of the present invention.
Fig. 1 is a side view of a valve mounting body housing a solid-liquid control valve shown together with a mask cylinder to which this embodiment or other embodiments are applied, and Fig. 2 shows a liquid pressure control valve of this embodiment. 3 and 4 are cross-sectional views for explaining the action of the hydraulic pressure control valve, and FIG. 5 is a cross-sectional view of the hydraulic pressure control valve according to another embodiment of the present invention. FIG. 3 is a cross-sectional view of important parts. In the figure, 16... hydraulic pressure control valve, 26...
...Lock casing, 28 ... Valve body, 3
2...Stepped piston, 38...Spring,
62...Spring, 64...Through hole, 22
6... Locking casing, 228... Valve body, 238... Spring.

Claims (1)

[Scope of utility model registration request] a first elastic member disposed on the inlet side connected to the brake fluid pressure generation source; a valve body biased toward the outlet side connected to the brake application device by the biasing force of the first elastic member;
A locking means that can engage with the valve body to prevent the valve body from moving beyond a predetermined position toward the outlet side due to the biasing force of the first elastic member, and is tensioned with a predetermined preload. a second elastic member; and a piston having a through hole that is biased toward the outlet side by the biasing force of the second elastic member, and the piston is biased toward the outlet side by the biasing force due to hydraulic pressure that the piston receives at the outlet side and the piston is biased toward the outlet side by the biasing force of the second elastic member. When the difference between the biasing force due to the hydraulic pressure received on the population side becomes larger than the biasing force of the second elastic member, the piston moves to the inlet side and the through hole of the piston is connected to the valve. In the hydraulic control valve, which is closed by a body and thereby reduces the pressure on the outlet side compared to the pressure on the inlet side when a predetermined pressure is exceeded, the engagement between the valve body and the locking means is provided. communication between the inlet side and the outlet side is cut off or restricted depending on the situation, and either the valve body or the locking means is configured to allow liquid movement from the inlet side to the outlet side. A hydraulic control valve characterized by being provided with a valve that prohibits reverse operation.