JPH01306356A - Anti-lock device - Google Patents

Abstract

PURPOSE:To eliminate an end plug as well as to contrive an reduction in cost by constituting one open end of an inner cylinder to be No.2 outlet, housing the open end of No.2 outlet in a cylinder hole, and concurrently bringing an exhaust value into contact with the open end section of No.2 outlet. CONSTITUTION:An exhaust passage 24 is provided in such a way as to be branched from a main flow passage 22 which communicates a master cylinder 21 with a wheel brake 23, and a normally closed exhaust valve 26 is provided for the passage 24, which is opened by electromagnetic force with power supply energized so as to let the exhaust passage 24 be communicated. In addition, a branching point is provided with a sleeve 32 composed of three ports, that is, an inlet 34, No.1 outlet 35 and No.2 outlet 36, and a flow-rate switch-over valve 25 equipped with a spool 41 which enables the communication among the respective ports to be switched over. In this case, one open end of the sleeve 32 is so constituted to be No.2 outlet 36 so that an open end on No.2 outlet side is housed in a cylinder hole. Concurrently, an exhaust port 26 is brought in contact with the open end on No.2 outlet side of the sleeve 32 so that the cylinder hole is closed. This constitution thereby allows an end plug which is currently used, to be eliminated, thereby making it possible to contrive an reduction in cost.

Description

[Detailed description of the invention]

The present invention relates to an anti-rotation locking device, and more specifically, in an automobile brake system, a signal from a wheel speed detector is guided to an electronic information processing device to detect the locked state of the wheels. When excessive slip occurs due to excessive braking or its signs are detected, a solenoid valve is activated to reduce the amount of inflow hydraulic fluid in the brake system, thereby maintaining brake pressure regardless of whether the brake is depressed. This relates to a system that suppresses and controls braking force by reducing pressure. BACKGROUND ART Conventionally, various proposals have been made regarding this type of anti-lock device.
In the method disclosed in the publication, a normally open inlet valve is interposed in the main flow path that communicates the pressurization source (master cylinder) activated by the operation of the brake pedal and the wheel cylinder of the brake device. A normally closed discharge valve is installed in each discharge flow path that communicates with the brake fluid storage tank.
Both the inlet valve and the discharge valve are electrically operated based on commands from the electronic information processing device. In this device, when the anti-lock is not activated, power is not supplied to either the inlet valve or the discharge valve, and the hydraulic fluid flows into the wheel cylinder according to the amount of depression of the brake pedal, while when the anti-lock is not activated, the brake fluid is When reducing the pressure, power is supplied to the inlet valve and discharge valve, the inlet valve is closed, the discharge valve is opened, the working fluid from the wheel cylinder side is returned to the storage tank, and the pump pumps it up to the master cylinder side. ing. And when pressurizing the brake fluid again,
When power is not supplied, the inlet valve is opened, the discharge valve is closed, and when the brake fluid pressure is maintained at a constant pressure, power is supplied to only the inlet valve to close it, and since the discharge valve is in the closed position, the brake fluid is The pressure is kept constant. In this way, this device can control in three modes: pressure reduction, pressure increase, and constant pressure maintenance, but it requires two valves that are operated by power supply, an inlet valve and a discharge valve, and the number of parts is low. There are drawbacks such as increased cost and installation effort. An anti-lock device which eliminates the above-mentioned drawbacks and has a simplified structure with only one solenoid valve is disclosed in Japanese Patent Application No. 11244/1986.
It is proposed in No. 0. This device has the configuration shown in FIG. 3, and instead of providing the electromagnetically operated introduction valve in the main channel 3 that communicates the pressure source 1 and the wheel cylinder 2, it is operated by the return spring 1 and hydraulic pressure. A non-electromagnetically actuated 3-point, 2-position switching flow rate control valve 5 is provided, and a normally closed 2-point, 2-position switching electromagnetic discharge valve 7 is provided in the discharge passage 6.
has been established. In this device, the above-mentioned non-electromagnetic,! By combining the amount control valve 5 and the electromagnetic discharge valve 7, the anti-lock device is operated with two-mode control of only pressure reduction and pressure increase. As shown in the figure, the structure of the flow control valve 5 is that it is inserted into the cylinder block 10 and the spool 12 is inserted into the cylinder block 10.
is urged by a return spring 4 and fitted so as to be slidable in the axial direction, while an inlet 13 through which hydraulic fluid from the master cylinder flows into the sleeve II, and a first outlet 14 through which hydraulic fluid flows out to the wheel cylinder. , a second outlet 15 for discharging the hydraulic fluid to the hydraulic fluid storage tank via the discharge valve 7 is provided in a direction perpendicular to the axial direction. The electromagnetically operated discharge valve 7 has a liquid passage 61 in the center that communicates with the second outlet 15, a stator 63 having an electromagnetic coil 62 on its exterior, and a frame surrounding the electromagnetic coil 62 to form a magnetic path. 64, a non-magnetic guide ring 65 whose one end on the inner diameter side is press-fitted into the stator 63 in a liquid-tight manner, and the other end on the outer diameter side is press-fitted into the frame 64 in a liquid-tight manner; the guide ring 65 is urged in a direction away from the stator 63 by a spring 66; , a liquid that is slidably housed on the inner periphery of the thin wall of the guide ring 65, is attracted to the stator 63 when power is supplied to the electromagnetic coil 62, and forms a discharge path in the center of the armature 67 that is movable against the biasing force of the spring 66. A fixed valve seat 68 having a passage and press-fitted into the frame 64, and a movable valve body 69 integrally press-fitted into the armature 67 and capable of blocking communication with the discharge passage 6 by abutting against the fixed valve seat 68. The movable valve body 69 is located on the second outlet 15 side of the discharge liquid path 6 with the fixed valve seat 68 as a boundary. Problems to be Solved by the Invention In the flow control valve of Japanese Patent Application No. 61-112440 mentioned above, it is necessary to close the open end of the sleeve 11 formed in the cylinder block IO with an end plug 16, as shown in the figure.
Even if the electromagnetic discharge valve 7 is arranged in a direction perpendicular to the axial direction of the flow control valve 5, or even if it is arranged in series with the flow control valve 5, the second outlet needs to be arranged perpendicular to the spool 12. Therefore, the end plug 16 is required in either case. Therefore, there are disadvantages in that the cost increases due to the increase in the number of parts and the required space increases. Also, sleeve l! In the return spring chamber I7 of
Since the structure is such that a small flow rate of liquid is generated only during flow rate control when the electromagnetic discharge valve 7 is powered on, there is a problem in that air cannot be easily vented from the return spring chamber 17. Therefore, if air (bubbles) remains in the return spring chamber 17, the bubbles collapse when the pressure of the population 12 increases, causing the spool 12 to move to the anti-lock operating position, making sudden pressurization impossible and , the responsiveness of the operation of the spool 12 deteriorates due to the q(E) of air bubbles,
In other words, there was a drawback that the brake piping system did not respond well to the pressure of the brake piping system.Furthermore, it is necessary to bleed air from the brake piping system during the vehicle assembly process, but generally speaking, a vacuum pump is used rather than a master cylinder or a vacuum pump. The common practice is to dispose of the brake piping system and then pump the brake fluid (commonly called vacuum filling).On the other hand, each welfare element of the brake system is usually filled with brake fluid to prevent leakage. After carrying out performance tests, it is moved to the vehicle assembly process. Therefore, in order to complete the evacuation of the brake piping system within a certain working time during vacuum filling, it is necessary to reduce the amount of residual brake fluid in each component of the brake system. It is necessary to maintain a constant value. (If there is a large amount of residual gas, the degree of vacuum attainment will decrease due to defoaming.) 1. However, as mentioned above, the movable valve body 69 of the discharge valve 7
is present at the second outlet rather than the fixed valve seat 68, so that not only the return spring chamber 17 but also the valve chamber 70 where the liquid passage 61, armature 67, and movable valve body 69 are present during normal braking (during non-andirosoku control) After the performance test is completed, it is necessary to drain the brake fluid from these parts, but this is not easy because the valve chamber 70 is a dead end in the closed state shown in the figure. (It is desirable that the brake fluid in the pump circuit between the discharge valve 72 of the pump 71 and the fixed valve seat 68 remains.) In addition, since the brake fluid normally acts on the guide ring 65, the stator 63
It is necessary to ensure liquid tightness between the housing and the frame 64, and although rolling or welding may be used to ensure liquid tightness, this results in increased space and cost. In order to solve the above-mentioned problems, the present invention provides an anti-lock device having the following configuration. That is, a) a discharge passage provided so as to branch from the main passage communicating the pressurization source and the wheel brake; and 1)) a discharge passage provided in this discharge passage, which is opened by electromagnetic force when supplied with electricity, and the discharge passage is placed in a communicating state. C) a normally closed discharge valve that can be used as A hollow cylindrical sleeve having a port; - A spool that is slidably fitted into this sleeve and has a liquid path including an orifice, and can switch the communication state of each port; - This spool is connected to one When the anti-lock is not activated, the spool is in the non-activated position and the inlet and the first outlet are connected through a large flow path, and when the anti-lock is depressurized, the discharge valve is opened. By discharging the hydraulic fluid from the second outlet to the discharge passage, the spool moves against the biasing force of the return spring due to the biasing force caused by the differential pressure generated at both ends of the spool, and the first and second outlets
When the outlet is closed in communication and the hydraulic fluid of the wheel brake is discharged to the discharge path, and the discharge valve is de-energized when the anti-lock is pressurized, the flow of the hydraulic fluid from the second outlet toward the discharge valve is stopped (12), and the flow of the hydraulic fluid from the second outlet to the discharge valve is stopped. If the liquid pressure at
a flow rate switching valve configured such that when the fluid pressure difference at the outlet becomes equal to or less than this pressure difference, the spool returns to the non-operating position by the biasing force of a return spring and communicates with the large flow path; and d)
2. An anti-lock device having a casing having a cylinder hole with one end open for accommodating an AE amount switching valve; The second outlet side opening end is housed in the cylinder hole, and the discharge valve is inserted into the second outlet (n) of the sleeve.
11 Close the cylinder hole by contacting the open hole end u
The present invention provides an anti-lock device characterized in that the anti-lock device is configured to be closed. Further, in the anti-lock device according to the present invention, a fixed valve seat is provided in the discharge passage and has a liquid passage that constitutes a discharge flow passage as a discharge valve; A movable valve body that can open and close a passage; - An armature that is accompanied by this movable valve body and can be moved by electromagnetic force; - An electromagnetic coil is mounted on the exterior and one end faces the armature and attracts the armature by electromagnetic force when power is supplied. a stator, and a spring that biases the armature in a direction away from the stator and causes the movable valve body to abut against the fixed valve seat when not supplied with power to close the liquid passage, and is opened by electromagnetic force when supplied with power. In an anti-lock device equipped with a normally closed discharge valve that can communicate with the discharge passage, the movable valve body and the armature are connected to the discharge passage on the side opposite to the side communicating with the second outlet with the fixed valve seat as the boundary. The biasing force of the spring acts on the movable valve body against the force of the hydraulic pressure of the second outlet that acts on the seal effective diameter of the movable valve body and the fixed valve seat when the discharge valve is not powered. The present invention provides an anti-lock device characterized in that it is configured as follows. Furthermore, in the anti-lock device according to the present invention, one end of the return spring is locked to the spool, and the other end is locked to the discharge valve, and a filter is provided in the discharge path communicating with the discharge valve, The other end of the return spring is secured to one end of the filter. In this device, the open end of the cylinder hole that houses the flow rate control switching valve is closed with a discharge valve made of a solenoid valve, which eliminates the need for an end plug that was previously required. In addition, since the open end of the sleeve serves as the second outlet, the return spring chamber inside the sleeve can be made into a depressurizing flow path through which a large flow rate passes, making it easy and reliable to bleed air from the return spring chamber. It can be done. In addition, since the movable valve body of the discharge valve is configured to exist in the discharge passage on the opposite side of the second outlet with the fixed valve seat as a boundary, the valve chamber containing the armature, movable valve body, and guide ring is normally affected by brake fluid pressure. Therefore, not only is there no need to drain the brake fluid from the valve chamber for vacuum filling, but there is also no need to ensure fluid tightness between the guide ring and stator under high hydraulic pressure between the frame. It has a unique effect, and other effects will become clear from the description of the embodiments. EXAMPLES Hereinafter, the present invention will be explained in detail with reference to examples shown in the drawings. The brake stem equipped with the anti-lock device according to the present invention is almost the same as the conventional example shown in FIG. It communicates with a wheel brake 23 including a wheel cylinder via a passage 22, and a discharge passage 24 branches from the main passage 22, and a non-electromagnetically actuated flow rate control switching valve 25 and an electromagnetically actuated discharge passage are connected at the branch position. The valve 26 is installed in series and combined in one cylinder block 27. The above discharge flow path 2/1 is the hydraulic fluid storage tank 2
The plunger pump 29 communicates with the master cylinder 2I via a reflux passage 30, and the hydraulic fluid discharged into the discharge passage 24 is communicated with the plunger pump 29 via the plunger pump 29. It is pumped to the master cylinder 21 side. To explain in detail the structure of the flow rate control switching valve 25 and the discharge valve 26 provided at the branch point between the main flow path 22 and the discharge flow path 23, a cylinder hole 3I is provided in one cylinder block 27.
A flow control switching valve 25 is provided in the cylinder hole 31.
At the same time, the sleeve 32 of the cylinder hole 3 is fitted and fixed.
A discharge valve 26 made of a solenoid valve is installed so as to close the opening side of the discharge valve 1. The sleeve 32 is open at both ends, and one end thereof is fixed to the bottom surface of the cylinder hole 31, while the other end is connected and fixed to the frame 33 of the discharge valve 26. A hydraulic fluid port 34 is formed between the outer peripheral surface of the sleeve 32 and the inner peripheral surface of the hole 31, which communicates with the main flow path 22 on the master cylinder 21 side, and a first hydraulic fluid outlet that communicates with the brake device 23 side. 35, and the opening axis portion on the side connected to the frame 33 serves as a second outlet 36 for the hydraulic fluid that linearly communicates with the discharge valve 26 side. Further, the sleeve 32 is provided with a first introduction passage 37 and a second introduction passage 38 which communicate with the above-mentioned population 34 and which penetrate in the radial direction, and an outlet passage 3 which communicates with the first outlet 35 and penetrates in the radial direction.
9, and a groove 40 is formed by cutting out the inner surface at a position close to the second outlet 36. A spool 41 is fitted into the sleeve 32 so as to be slidable in the axial direction. An orifice 43 is formed at the tip on the side of the second output hole 36. Further, on the bottom side of the spool 41, a second liquid passage 44 in the radial direction that selectively communicates with the first introduction passage 37 according to the movement of the spool 41 is provided orthogonally to the first liquid passage 42. The second liquid passageway 44 has a metal edge at its outer open end. moreover,
On the outer peripheral surface of the spool 4I, a third fluid passage 45 which is long in the axial direction is formed which constantly communicates with the outlet passage 39 and selectively communicates with the second introduction passage 38. The tip of the spool 41 where the orifice 43 is formed is formed as a spring receiver 46, and the second outlet 3 of the sleeve 32
A return spring 49 is fixed to the inner surface of the liquid passage 47 of the frame 33 which communicates with the liquid passageway 47 of the frame 33, and is compressed between it and the spring receiver 48. A filter 50 is attached to the spring receiver 48, and the sleeve 32, spool 41 and frame 3
Dust is collected from the working fluid flowing out into the fluid passage 47 through the return spring chamber 51 surrounded by 3. A discharge valve 26 installed to close the open end side of the hole 31
As shown in the figure, the liquid passage 47 communicating with the second outlet 36 on the same axis is formed at the inner end of the axial core of the frame 33, and a fixed valve seat 54 is provided in the liquid passage 47. The fixed valve seat 54 is opened and closed by a movable valve body 56, which will be described later. In this way, the second outlet 36 formed at the axial opening end of the sleeve 32 of the flow rate control switching valve 25 is arranged in series in the same direction as the discharge valve 26, so that the working fluid flows directly from the second outlet 36 to the discharge valve 26. I try to be guided in a straight line. The frame 33 of the discharge valve 26 has a large-diameter valve chamber 52 in its axial center, which communicates with the liquid passage 47 that communicates with the second outlet 36.
, and a discharge liquid passage 53 that communicates the valve chamber 52 and the discharge passage 24 is formed. While the fixed valve seat 54 is attached to the liquid passage 47, an armature 55 is fitted in the hollow portion 52 so as to be slidable in the axial direction, and the fixed valve seat 54 is fixed to the movable valve body 56 fixed to the armature 55. I try to open and close it. A stator 58 is installed in the frame 33 at a position facing the armature 55, and a coil 59 is installed at its outer periphery, and when power is supplied, the coil 59 is energized to move the armature 55 and movable valve body 56 in the direction of the arrow. The valve seat 54 is operated to open the valve seat 54. Further, a spring 60 is compressed between the armature 55 and the stator 58, and when power is not supplied, the spring 60 is biased to close the valve seat 54 with the movable valve body 56. Further, on the outer periphery of the armature 55, a thin outer periphery is placed on the inner diameter side of the frame 33, and a thick inner periphery 63 is placed on the stator 5.
Guide rings 6 and 1 are press-fitted and fixed to the outer diameter portions of the distal ends of the guide rings 6 and 8, respectively, and guide the armature 55 in a sliding manner. In addition, in the figure, 6I is an O-ring to prevent liquid leakage at each part. Since the hydraulic fluid storage tank 28 connected to the discharge flow path 24 and the plunger pump 29 for circulating the hydraulic fluid to the master cylinder 21 have a known configuration, a description thereof will be omitted. Next, the braking action provided with the anti-lock device having the above structure will be explained. When anti-lock is not applied during normal operation, the large flow path is formed as shown in FIG. closes the valve seat 54. That is, the second outlet 36 of the flow control switching valve 25 is in a closed state. In the non-antilock state, the spool 4I is biased by the return spring 49 and is at the upper end position in the figure, and the second introduction passage 38 of the sleeve 32, which is constantly in communication with the hydraulic fluid port 34, is connected to the third passage on the outer periphery of the spool 41. It communicates with the liquid path 45. The third fluid passage 45 is the outlet passage 3 of the sleeve 32.
It communicates with the first outlet 35 via 9. Therefore, the inlet 34 of the flow control switching valve 25 communicates only with the first outlet 35, and the mask cylinder 21 and the wheel brake 23 communicate with each other. At this time, a large flow path is formed between the inlet 35 and the first outlet 36 of the flow rate control switching valve 25, as described above, through which a large flow of the working fluid does not pass through the orifice or the like. Therefore, it is possible to control the brake by supplying hydraulic fluid to the brake 23 from the main channel 22 in accordance with the amount of depression of the brake hydraulic pressure lever 20. In the non-anti-lock state, the inlet 35 is connected to the first introduction path 37,
It passes through the second liquid passage 44, the first liquid passage 42, and the return spring chamber 49 to the second outlet 36.
Since the valve seat 54 on the side of the discharge valve 26 communicating with the outlet 36 is closed, the hydraulic fluid is not discharged from the second outlet 36, and therefore, normal brake fluid pressure does not act on the valve chamber 52. On the other hand, when a wheel speed detector or the like (not shown) detects the occurrence of excessive slip or its sign and establishes an anti-lock state, the coil 59 of the electromagnetic discharge valve 26 is supplied with power and energized. Therefore, the armature 55 descends in the figure,
Interlockingly, the movable valve body 56 descends against the spring 60 to open the valve seat 54 and open the second outlet 36 of the flow rate control switching valve 25.
Allows for outflow from. Therefore, the hydraulic fluid that has flowed into the return spring chamber 51 from the inlet 34, the first introduction path 37, the second liquid passage 44, and the first liquid passage 42 via the orifice 43 flows out from the second outlet 36, and flows out from the discharge valve. 26 valve seats 54
After passing through the valve chamber 52 and the discharge passage 53, it is discharged to the discharge passage 24. During the above operation, as shown in FIG. 2(n), the orifice 4
The differential pressure generated before and after 3 acts on both ends of the spool 1'l, and the spool 41 moves (downwards in the figure) against the biasing force of the return spring 49. Therefore, the second introduction path 38 and the third fluid passage 4 communicating with the hydraulic fluid port 34
5 is cut off, and the large flow path that communicates the population 34 with the first outlet 35 is also closed. When the spool 41 reaches the position shown in FIG. 2 (II[) by the above operation, both the first introduction path 37 and the second introduction path 38 communicating with the hydraulic fluid port 34 are blocked by the spool 41, and the first outlet 35 and the second outlet 36. On the other hand, at the position, the first exit 35
communicates with the second outlet 36 via the lead-out path 39, the third liquid passage 45, the groove 40, and the return spring chamber 51. Therefore, a reduced pressure flow path is formed in which the hydraulic fluid in the vehicle brake 23 passes from the first outlet 35 to the second outlet 36, passes through the discharge valve 26 that is opened by power supply, and is discharged to the discharge flow path 24. Ru. That is, the hydraulic fluid on the wheel brake side is discharged, the brake pressure is reduced, and the wheels are anti-locked. Further, when the communication between the first introduction path 37 and the second liquid passage 44 is cut off, the first introduction passage 37, the second liquid passage 44, and the first liquid passage 42
The flow rate passing through the orifice 13 becomes zero,
The differential pressure before and after the orifice 43 begins to decrease. Then, the spool 11 is again moved upward in the drawing by the biasing force of the return spring 49. Then, the first introduction path 37
and the second liquid passage 44 are brought into communication, the flow rate passing through the orifice 43 is ensured again, a pressure difference is generated in the front and rear, and the biasing force of the return spring 49 is overcome again to lower the liquid to the illustrated position. In other words, the first introduction path 3 is in the position shown in the figure.
A metal ringing action is performed between the inner diameter side edge of 7 and the outer circumferential edge of the second liquid passage 44, and the return spring 49
A pressure difference equal to the value obtained by dividing the biasing force by the effective seal diameter between the outer diameter of the spool 41 and the inner diameter of the sleeve 32 is generated before and after the orifice and the orifice 43, and the flow rate passing through the orifice 43 based on this differential pressure is The liquid flows from the population 34 through the first introduction path 37, the second liquid passage 44, the first liquid passage 42, the orifice 43, and the spring chamber 51, and the amount of liquid from the wheel brake via the first outlet is also transferred to the second outlet 36. It is discharged to the discharge channel 24 through. When the discharge valve 26 is de-energized during anti-lock pressure increase, the movable valve element 56 is urged by the spring 60 and moves to close the valve seats 5 and 1, thereby closing the discharge valve 26. Therefore, discharge of the hydraulic fluid from the second outlet 36 of the flow rate control switching valve 25 is stopped. However, in this state, the pressure of the spring chamber 51 connected to the first outlet 35 is lower than the pressure of the population 34, so the population 34, the first introduction path 37, the second liquid passage 4/1, the first liquid passage 42 The hydraulic fluid flows into the wheel brake 23 via the orifice 43, the spring chamber 51, the discharge groove 40, the outlet path 39, and the first outlet 35. Therefore,
The spool 3I is shown in FIG. 2 (IV) as shown in FIG. 2 (IV).
It is located at the same position as in the reduced state of IIt) and performs a metering action, leading the same small flow rate to the wheel brake 23 via a small flow path of the type described above. When the pressure difference between the population 34 and the first outlet 35 becomes lower than the E Re differential pressure, the spool 41 rises in the figure due to the biasing force of the return spring 49, and as shown in FIG. 2 (H), the third outlet of the spool 41 The liquid path 15 returns to the non-operating position where it communicates with the second introduction path 38, and the Moekiinu flow path is communicated with it. If air exists in the spring chamber 5I, the return spring chamber 51 will be in the first position during anti-lock (when the discharge valve is opened by power supply)
Since the working fluid is included in the depressurizing channel through which the working fluid flows from the outlet 35 to the second outlet 36, and the decompressing channel has a large flow rate without an orifice, the air in the return splinter chamber 51 can be completely vented. , and be able to do it easily. In addition, since the structure is such that normally Breagie hydraulic pressure does not act on the R-chamber 52, the liquid sealing structure of the guide ring 64 can be easily completed, and furthermore, the discharge from the second outlet 36 to the fixed valve seat 5. The volume of the flow path is small, making it easy to drain brake fluid. Effects of the InventionAs is clear from the explanation in Section 1-1, the present invention provides a) a discharge passage provided to branch from a main passage communicating a pressurization source and a wheel brake, and b) a discharge passage provided in the discharge passage. Is the ji/j valve set in place and connected to the discharge passage using electromagnetic force by power supply?
(c) a normally closed discharge valve; and c) an inlet communicating with the pressurizing source, a first outlet communicating with the front S wheel brake, and a second outlet communicating with the discharge valve. A hollow cylindrical sleeve having three outlet ports; - A spool that is slidably fitted into the sleeve and has a liquid path including an orifice, and can switch the communication state of each of the ports; - The spool is provided with a return spring that biases the spool in one direction, and when the anti-lock is not activated, the spool is in the inactive position and connects the population and the first outlet through a large flow path, and when the anti-lock is depressurized, the spool is discharged. By opening the valve and discharging the hydraulic fluid from the second outlet to the discharge path, the spool moves against the biasing force of the return spring due to the biasing force due to the differential pressure generated at both ends of the spool, and the spool moves between the first outlet and When the second outlet is connected to allow the hydraulic fluid of the wheel brake to be discharged to the discharge path, and the discharge valve is de-energized when the anti-lock is pressurized, the flow of the hydraulic fluid from the second outlet toward the discharge valve is stopped; When the hydraulic pressure of the artificial fluid is higher than the hydraulic pressure of the first outlet, it passes through the orifice from the inlet to the first outlet, forming a small channel through which a small flow rate flows, and the difference in the hydraulic pressure between the inlet and the first outlet increases. When the pressure difference falls below this differential pressure, the spool returns to the non-operating position by the biasing force of a return spring and communicates with the large flow path; d) a hole at one end for housing the flow rate switching valve; In an anti-lock device that connects a cylinder hole with a housing, one open end of the sleeve is configured to be the second outlet, and the second outlet side open end is connected to the open end of the cylinder hole. The flow rate switching valve is housed in the cylinder hole so as to be located on the hole side, and the discharge valve is brought into contact with the open end of the sleeve on the second outlet side, thereby closing the cylinder hole. , in the discharge valve, the movable valve body and the armature are arranged so as to be present in the discharge passage on the side opposite to the side communicating with the second outlet with the fixed valve seat as a boundary, and when the discharge valve is not supplied with electricity, The structure is such that the biasing force of the spring described in n7D acts on the movable valve element against the force of the hydraulic pressure of the second outlet acting on the seal effective diameter of the fixed valve seat, so it has the following effects. . That is, (1) The open end of the sleeve of the flow rate control switching valve is configured as the second outlet, and the open end of the sleeve is closed with a discharge valve made of a solenoid valve, which is not necessary in the past. It is possible to eliminate the need for end plugs. (2) Since the return spring chamber in the sleeve of the flow rate control switching valve is a depressurizing flow path through which a large flow rate passes, air can be easily and reliably removed from the return spring chamber.

[Brief explanation of the drawing]

FIG. 1 is a partially cross-sectional overall configuration diagram showing an embodiment of the present invention;
FIG. 2 is a sectional view sequentially showing the operation of the embodiment shown in FIG. 1, and FIG. 3 is a partially sectional overall configuration diagram showing a conventional example. 20...Plake petal, 21...Master cylinder, 22...Main flow path, 23...Wheel brake, 24...
- Discharge channel, 25... Channel control switching valve, 26... Discharge valve, 27... Housing, 31... Hole, 3
2... Sleeve, 34... Inlet, 35... First outlet, 36... Second outlet, 41... Spool, 42.
44.45...Liquid passage, 43...Orifice, 49...Return spring, 51...Return spring chamber, 54...Fixed valve seat, 55...Armature, 56...
・Movable valve body, 58...stator, 59...coil,
60...Spring. Patent applicant Sumitomo Electric Industries, Ltd. Representative Patent attorney Aoyama Hajime and two others Figure 2 (I
) Figure 2 (n) Figure 2 (m) Figure 2 (TV) Procedural Amendment) 11'I full 1. i: 3 (1-1'11 heads No. 135010 Shiji? Name of the invention 7□'/ch[2-link device 1''I: 3, Relationship with the person making the amendment Patent applicant il:+il'i , 'jζ Masterpiece (213), 4-5-33 Kitahama, Chuo-ku, Inusaka-shi, Osaka Prefecture Sumitomo Electric Industries, Ltd. Address: 2-1-61 Mi, Chuo-ku, Osaka-shi, Osaka 540 Address 6 Subject of amendment +41 , 'j All Zen Civilization Specification Book 1, Title of Invention Anti-lock Device U 2, Claim 18a) A discharge passage provided so as to branch from a main passage communicating a pressurization source and a wheel brake; b) C) a normally closed discharge valve that is provided in the discharge passage and can be opened and communicated with the discharge passage by electromagnetic force when supplied with electricity; and C) provided at the branch point, - an inlet that communicates with the pressurization source, and the wheel brake. A hollow cylindrical hole having three ports, a first outlet communicating with the discharge valve, and a second outlet communicating with the discharge valve; - A sputum fluid passage slidably fitted within the curse flame and including an orifice. a spool that can switch the communication state of each port, and a return spring that biases this spool in one direction, and when the anti-lock is not activated, the spool is in the inactive position and the inlet is closed. and the first outlet are connected through a large flow path, and when the anti-lock pressure is reduced, the discharge valve is opened and the hydraulic fluid is discharged from the second outlet to the discharge passage, thereby reducing the biasing force due to the differential pressure generated at both ends of the spool. , the spool moves against the biasing force of the return spring, connects the first outlet and the second outlet, discharges the wheel brake hydraulic fluid to the discharge path, and de-energizes the discharge valve when the anti-lock is pressurized. , the flow of hydraulic fluid from the second outlet to the discharge valve is stopped, and if the hydraulic pressure at the inlet is higher than the hydraulic pressure at the first outlet, it flows from the pump through the orifice to the first outlet and the small A small flow path is formed through which the flow rate flows, and when the liquid pressure difference between the inlet and the first outlet becomes equal to or less than this pressure difference, the spool returns to the non-operating position by the biasing force of the return spring and communicates with the large flow path. d) a housing having a cylinder hole with one end open for accommodating the flow rate switching valve; The flow rate switching valve is housed in the cylinder hole such that the second outlet-side open end is located on the open-hole side of the cylinder hole, and the discharge valve is located at the second outlet-side open end of the cylinder hole. An anti-lock device characterized in that the anti-lock device is configured to abut against the cylinder hole, thereby closing the cylinder hole. 2.8) a discharge passage provided so as to branch from the main passage that communicates the pressurization source and the wheel brake; and b) a fixed valve provided in the discharge passage and having a liquid passage constituting the discharge passage. - A movable valve element that can open and close this liquid passage by moving against and away from the fixed valve seat, - An armature that can be moved by electromagnetic force accompanying this movable valve element, - An exterior electromagnetic coil - A stator that has one end facing the armature and attracts the armature by electromagnetic force when power is supplied; - The armature is urged in a direction away from the stator, and the movable valve body is brought into contact with the fixed valve seat when not energized to achieve the above-mentioned effect. C) a normally closed discharge valve having a spring that closes the liquid path, and which can be opened by electromagnetic force when supplied with electricity to bring the discharge path into communication; C) provided at the branch point; a hollow cylindrical pot 11 having three ports, a first outlet communicating with the wheel brake l, and a second outlet communicating with the discharge valve; an orifice slidably fitted into the inner cylinder; - a spool that has a liquid passage including a fluid path and can switch the communication state of each port; - a return spring that biases this spool in the position direction, and when the anti-lock is not activated, the spool is in the inoperative position When the anti-lock pressure is reduced, the discharge valve is opened and the hydraulic fluid is discharged from the second outlet to the discharge passage, which creates a pressure difference between the two ends of the spool. The spool moves against the biasing force of the return spring due to the biasing force,
The first outlet and the second outlet are made to communicate with each other so that the hydraulic fluid for the wheel brakes is discharged to the discharge path, and when the discharge valve is de-energized when the air lock is pressurized, the hydraulic fluid flows toward the first and second discharge valves. If the flow of fluid stops and the fluid pressure at the inlet is higher than the fluid pressure at the first outlet, the fluid flows from the population through the orifice to the first outlet.
A small flow path is formed in which a small flow of water flows toward the outlet, and when the difference in liquid pressure between the first outlet and the first outlet becomes lower than this pressure difference, the spool returns to the non-operating position due to the biasing force of the return spring, allowing the large flow path to flow. In an anti-lock device having a flow rate switching valve configured to communicate with the above-described movable valve body and armature, the movable valve body and the armature are located in a discharge passage on a side opposite to the side communicating with the second outlet with the fixed valve seat as a boundary. When the discharge valve is not energized, the biasing force of the spring in the discharge valve is movable against the force of the hydraulic pressure of the second outlet that acts on the seal effective diameter of the movable valve body and the fixed valve seat. An anti-lock device characterized in that it is configured to act on a valve body. 3. Detailed Description of the Invention Industrial Application Field The present invention relates to an anti-lock device, and more specifically, in an automobile brake system, a signal from a wheel speed detector is guided to an electronic information processing device to detect the locked state of the wheels. When excessive slip occurs or signs thereof are detected due to sudden braking, a solenoid valve is activated to reduce the amount of hydraulic fluid flowing into the brake system, thereby reducing brake pressure regardless of whether the brake is depressed. The present invention also relates to a device that suppresses and controls braking force by regulating pressure. 2. Description of the Related Art In the past, various proposals have been made regarding this type of anti-lock device. For example, Japanese Patent Publication No. 49-28307
In the method disclosed in the publication, a normally open inlet valve is interposed in the main flow path that communicates the pressurization source (master cylinder) activated by the operation of the brake pedal and the wheel cylinder of the brake device, while the wheel cylinder and the brake are connected to each other. A normally closed discharge valve is installed in each discharge channel that communicates with the hydraulic fluid storage tank.
Both the introduction valve and the discharge valve are electrically operated based on commands from the T-child information processing device. In this device, when the anti-lock is not activated, power is not supplied to either the inlet valve or the discharge valve, and the hydraulic fluid flows into the wheel cylinder according to the depression distance of the brake pedal, while when the anti-lock is not activated, that is, the brake fluid is When the pressure is to be reduced, power is supplied to the introduction valve and the discharge valve, so that the introduction valve closes and the discharge valve opens, thereby discharging the working fluid from the wheel cylinder side into the storage tank. And, when pressurizing the brake fluid again, open the inlet valve and close the discharge valve as when de-energized. When maintaining the brake fluid pressure at a constant pressure, power is supplied to only the inlet valve to close it, and the discharge valve is in the closed position, thereby keeping the brake fluid pressure constant. In this way, this device can control in three modes: pressure reduction, pressure increase, and constant pressure maintenance, but it requires two valves that are operated by power supply, an inlet valve and a discharge valve, and the number of parts is low. The disadvantage is that it increases the installation time and the cost. A patent application filed in 1983 was developed as an anti-lock device that solved the drawbacks of the two and simplified the configuration by requiring only one solenoid valve.
No. 1-112440 has been proposed, but the device has a configuration inappropriate for practical use. When the above device is put into practical use, it will have a configuration as shown in FIG.
Instead of providing the electromagnetically actuated inlet valve, a de-energized actuated three-bottom, two-position switching flow control valve 5 actuated by the return spring 4 and hydraulic pressure is provided, and a normally closed valve is provided in the discharge passage 6. Therefore, a two-bottom, two-position switching electromagnetic discharge valve 7 is provided. In this device, the non-excited flow rate control valve 5 and the electromagnetic discharge valve 7 are combined to perform undylot control using two modes of pressure reduction and pressurization only. As shown in the figure, the structure of the flow control valve 5 is such that a spool I2 is fitted into an inner cylinder II inserted into a cylinder block 10 so as to be slidable in the axial direction by biasing a spool I2 with a return spring 1. A first outlet 13 through which the hydraulic fluid from the master cylinder flows into the cylinder II, a first outlet 14 through which the hydraulic fluid flows out to the wheel cylinder, and a second outlet OX5 through which the hydraulic fluid flows out to the hydraulic fluid storage tank through the discharge valve 7. The structure is such that they are respectively provided in a direction perpendicular to the axial direction. The electromagnetically actuated discharge valve 7 has a liquid passage 6I in the center that communicates with the second outlet 15, and includes a stator 63 that is equipped with an electromagnetic coil 62, and a frame 64 that surrounds the electromagnetic coil 62 and forms a magnetic path. , a non-magnetic guide ring 65 whose one end on the inner diameter side is press-fitted into the stator 63 in a liquid-tight manner and the other end on the outer diameter side is press-fitted into the frame 64 in a liquid-tight manner, and is urged in a direction away from the stator 63 by a spring 66; A passage that forms a discharge passage is housed in the thin-walled inner circumference of the guide ring 65 so as to be freely slidable, is attracted to the stator 63 when power is supplied to the electromagnetic coil 62, and is movable against the biasing force of the spring 66. A fixed valve seat 68 which has a liquid passage and is press-fitted into the frame 64, and a movable valve body 69 which is integrally press-fitted into the armature 67 and can block communication with the discharge passage 6 by abutting against the fixed valve seat 68. The movable valve body 69 is located on the second outlet I5 side of the discharge liquid path 6 with the fixed valve seat 68 as a boundary. Problems to be Solved by the Invention In the flow control valve shown in FIG. Even if the discharge valve 7 is arranged in a direction perpendicular to the axial direction of the flow control valve 5, or even if it is arranged in series with the flow control valve 5, the second outlet needs to be arranged perpendicular to the spool 12. Therefore, the end plug 16 is required in any case. Therefore, there are disadvantages in that the cost increases due to the increase in the number of parts and the required space increases. Furthermore, the return spring chamber 17 of the inner cylinder 11 has a structure in which a small liquid flow is generated only when the electromagnetic discharge valve 7 is powered and the flow rate is controlled.
There is a problem in that it is not easy to bleed air inside the 7. Therefore, if air (bubbles) remain in the return spring chamber 17, the bubbles will collapse when the pressure at the inlet 12 increases, causing the spool 12 to move to the anti-lock device (device), making sudden pressurization impossible. At the same time, due to the presence of air bubbles, the responsiveness of the operation of the spool I2 deteriorates, so to speak, the effectiveness of the brake in response to the amount of depression of the brake piping system becomes poor, which is a drawback. Although it is necessary to bleed air, the common method is to drain the brake piping system from the master cylinder's reserve tank to a vacuum pump, and then pump the brake fluid (generally called vacuum filling). On the other hand, each component of the brake system is usually filled with brake fluid, leaked, and tested for performance before being moved to the vehicle assembly process, and therefore the brake piping system must be evacuated within a certain working time during vacuum filling. In order to complete the process, it is necessary to maintain the amount of residual brake fluid in each component of the brake system at a constant value. The movable valve body 69 of the discharge valve 7 as shown in FIG.
is present at the second outlet from the fixed valve seat 68, so the return splinter chamber 17 is connected to the valve chamber 70 where the LaLaron liquid passage 6I, the armaduro 7, and the movable valve body 69 are present during normal braking (non-braking). The structure is such that the hydraulic pressure (during anti-lock control) is applied, and it is necessary to drain the brake fluid from these parts after the performance test is completed, but this is easy because the valve chamber 70 is a dead end in the closed state shown in the figure. Not. (It is desirable that the brake fluid in the pump circuit between the discharge valve 72 of the pump 71 and the fixed valve seat 68 remains.) Also, since the brake pressure normally acts on the guide ring 65, there is a gap between the stator 63 and the frame 64. It is also necessary to ensure liquid tightness between the parts, and although this is sometimes achieved by rolling or other methods, this results in increased space and cost. Means for Solving the Problems In order to solve the above problems, the present invention provides an anti-lock device having the following configuration. That is, a) a discharge passage provided so as to branch from the main passage that communicates the pressurization source and the wheel brake, and b) a discharge passage provided in this discharge passage, which can be opened by electromagnetic force when supplied with electricity to bring the discharge passage into a communicating state. a normally closed discharge valve; and C) three ports provided at the branch point: an inlet communicating with the pressurization source, a first outlet communicating with the wheel brake, and a second outlet communicating with the discharge valve. a hollow cylindrical inner cylinder having: - a spool that is slidably fitted into the inner cylinder and has a liquid passage including an orifice, and allows switching of the communication state of each port; and a return spring that biases the spool in one direction, and when the anti-lock is not activated, the spool is in the non-activated position and communicates the population and the first outlet through a large flow path, and when the anti-lock is depressurized, the discharge valve By opening the valve and discharging the hydraulic fluid from the second outlet to the discharge path, the spool moves against the biasing force of the return spring due to the biasing force due to the differential pressure generated at both ends of the spool, and the spool moves between the indicated outlet and the second outlet. When the two outlets are made to communicate with each other to discharge the hydraulic fluid of the wheel brakes to the discharge path, and the discharge valve is de-energized when the anti-lock is pressurized, the flow of the hydraulic fluid from the second outlet to the discharge valve is stopped, and the hydraulic fluid from the second outlet is stopped. If the fluid pressure at the inlet is higher than the fluid pressure at the first outlet, the inlet communicates with the orifice and heads toward the first outlet, forming a small flow path through which a small flow of water flows, and the difference in fluid pressure between the population and the first outlet increases. d) a flow rate switching valve configured such that the spool returns to the non-operating position due to the biasing force of a return spring and communicates with the large flow path when the pressure difference falls below; In an anti-lock device having a casing having a cylinder hole, one open end of the inner cylinder is configured to serve as the second outlet, and the second outlet side open end is accommodated in the cylinder hole. The present invention provides an anti-lock device characterized in that the discharge valve is brought into contact with the second outlet-side open end of the inner cylinder, thereby closing the cylinder hole. Further, in the anti-lock device according to the present invention, the discharge valve provided in the discharge passage includes a fixed valve seat having a liquid passage constituting a discharge flow passage; A movable valve body that can open and close a passage; - An armature that is accompanied by this movable valve body and can be moved by electromagnetic force; - An electromagnetic coil is mounted on the exterior and one end faces the armature and attracts the armature by electromagnetic force when power is supplied. A stator; - A spring that biases the armature in a direction away from the stator and causes the movable valve body to contact the fixed valve seat when not energized to close the liquid passage, and is opened by electromagnetic force when supplied with electricity. In an anti-lock device equipped with a normally closed discharge valve that can communicate with a valve discharge passage, the movable valve body and the armature are present in the discharge passage on the opposite side of the side communicating with the second outlet with the fixed valve seat as a boundary. The discharge valve is arranged so as to resist the force exerted by the hydraulic pressure of the second outlet on the seal effective diameter of the movable valve body and the fixed valve seat when the discharge valve is not energized.
The present invention provides an anti-lock device characterized in that the urging force of a spring in the discharge valve is configured to act on a movable valve body. Furthermore, in the anti-lock device according to the present invention, one end of the return spring is locked to the spool, and the other end is locked to the discharge valve, and a filter is provided in the discharge path communicating with the discharge valve, The other end of the return spring is secured to one end of the filter. Function As mentioned above, in this device, the open end of the cylinder hole that houses the flow rate control switching valve is closed with a discharge valve made of a solenoid valve, so the end plug that was conventionally required can be eliminated. Moreover, since the open end of the inner cylinder serves as the second outlet, the return spring chamber in the inner cylinder can be made into a depressurizing flow path through which a large flow rate passes, and the air in the return spring chamber can be easily and reliably vented. It can be done. In addition, since the movable valve body of the discharge valve is configured to exist in the discharge passage on the opposite side of the second outlet with the fixed valve seat as a boundary, the valve chamber containing the armature, movable valve body, and guide ring is normally affected by brake fluid pressure. Therefore, not only is there no need to drain the brake fluid from the valve chamber for vacuum filling, but there is also no need to ensure fluid tightness between the guide ring and stator under high fluid pressure between the frames. It has a unique effect, and the other effects are clear from the explanation of the embodiment. Hereinafter, the present invention will be explained in detail with reference to embodiments shown in the drawings. A brake system equipped with an anti-lock device according to the present invention is almost the same as the conventional example shown in FIG. 22, it communicates with a wheel brake 23 including a wheel cylinder, and a discharge flow path 24 branches from the main flow path 22, and a non-excited flow control switching valve 25 and an electromagnetically operated discharge valve are installed at the branch position. 26 are installed in series and combined in one cylinder block 27. The discharge flow path 24 is a working fluid storage +qf
28 communicates with a known plantar pump 29, and the plantar pump 29 communicates with the master cylinder 2! via a return flow path 30. The hydraulic fluid discharged to the discharge passage 24 is pumped up to the master cylinder 21 side by a plant pump 29. In this embodiment, a so-called reflux type structure as shown in - is exemplified in the configuration after the discharge flow path 24, but the hydraulic fluid storage tank 2
8 is shared with the storage tank of the master cylinder, and the pressure fluid pumped up by the pump is introduced into the hydraulic booster via the pressure accumulator, and is discharged from the circuit between the master turn ring and the wheel brakes through the discharge flow path. The liquid may be replenished by introducing liquid whose pressure has been regulated by a hydraulic pressure booster into the same circuit. Alternatively, a so-called full power type pressurization source without a master turn ring may be used. In short, the present invention can be used in combination with any pressure source structure and any structure after the discharge flow path. To explain in detail the structure of the flow rate control switching valve 25 and the discharge valve 26 provided at the branch point between the main flow path 22 and the discharge flow path 24, a cylinder hole 31 is bored in one cylinder block 27, and the cylinder block 27 is provided with a cylinder hole 31. A sleeve 32 of a flow rate control switching valve 25 is fitted and fixed in the hole 31, and a discharge valve 26 made of a solenoid valve is installed so as to close the open side of the cylinder hole 31. Although this sleeve 32 is provided to more advantageously realize the inner cylinder described above, it is also possible to provide the inner cylinder directly on the cylinder block 27. The sleeve 32 is open at both ends, and one end thereof is fixed to the bottom surface of the cylinder hole 31, while the other end is connected and fixed to the frame 33 of the discharge valve 26. Between the outer circumferential surface of the sleeve 32 and the inner circumferential surface of the hole 31, a hydraulic fluid port 34 communicating with the main flow passage 22 on the master cylinder 2 side is formed, and a first hydraulic fluid port communicating with the brake device 23 side is formed. forming an outlet 35 and the frame 3
The opening axis portion on the side connected to the valve 3 serves as a second outlet 36 for the hydraulic fluid that communicates linearly with the discharge valve 26 side. The sleeve 32 also has a first tube extending through the sleeve 32 in the radial direction and communicating with the tube 34.
An introduction passage 37 and a second introduction passage 38 are bored, and a radially penetrating outlet passage 39 communicating with the first outlet 35 is bored, and a cutout is made from the inner surface at a position close to the second outlet 36. A groove portion 40 is formed. A spool 4I is fitted into the sleeve 32 so as to be slidable in the axial direction. An orifice 43 is formed at the tip on the side of the second output hole 36. Further, on the bottom side of the spool 41, a second liquid passageway 44 in the radial direction is provided which selectively communicates with the first introduction passageway 37 according to the movement of the spool 4I.
It is drilled perpendicular to 2. Further, on the outer circumferential surface of the spool 41, a third fluid passage 45 which is elongated in the axial direction is formed, which constantly communicates with the outlet passage 39 and selectively communicates with the second introduction passage 38. The tip of the spool 41 where the orifice 43 is formed is formed as a spring receiver 46, and the second outlet 3 of the sleeve 32
A return spring 49 is compressed between a spring receiver 48 fixed to the inner surface of the liquid passage 47 of the frame 33 and communicated with the liquid flow path 47 of the frame 33. A filter 50 is attached to the spring receiver 48, and the sleeve 32, spool 41 and frame 33 are attached.
The liquid passageway 4 passes through the return spring chamber 51 surrounded by
Dust is collected from the hydraulic fluid that flows out to 7. A discharge valve 26 installed to close the open end side of the hole 31
The bipedal frame 33 has a second outlet 36 as shown in the figure.
The liquid passageway 47 that communicates with the liquid passageway 47 on the same axis is formed at the inner end of the axis thereof, a fixed valve seat 54 is fixed to the liquid passageway 47, and the fixed valve seat 54 is connected to a movable valve to be described later. It opens and closes with a body 56. In this way, the sleeve 32 of the flow control switching valve 25
A second outlet 36 formed at the axially open end of the drain valve 26 is arranged in series in the same direction as the discharge valve 26, so that the working fluid is directly led straight to the discharge valve 26 from the second outlet 36. The frame 33 of the discharge valve 26 has a second +4++
A large-diameter valve chamber 52 is formed in the shaft core portion in communication with a liquid passage 47 that communicates with the liquid passage 6 , and a discharge liquid passage 53 is formed that communicates the valve chamber 52 with the discharge passage 24 . ing. The above liquid passage 4
While the fixed valve seat 54 is attached to the hollow part 52, an armature 55 is fitted in the hollow part 52 so as to be slidable in the axial direction, and a movable valve body 56 fixed to the armature 55 opens and closes the fixed valve seat 54. I have to. Inside the frame 33,
A stator 58 is located opposite the armature 55.
and a coil 59 is installed on its outer periphery, and when power is supplied, the coil 59 is energized to operate the armature 55 and the movable valve body 56 in the direction of the arrow, thereby opening the valve seat 54. Further, a spring 60 is installed between the armature 55 and the stator 58, and when it is not energized, the spring 60 is biased and the movable valve body 56 is moved against the valve seat 58.
is closed. Further, a guide ring 64 is provided on the outer periphery of the armature 55 and has a thin outer periphery part pressed into the inner diameter side of the frame 33 and a thick inner periphery part 63 press-fitted into the outer diameter part of the tip of the stator 58. I'm guiding you. The movable valve body 56 and the armature 55 can be made integrally, or they can be made separately to provide a minute alignment function between the ridges. In the figure, reference numeral 61 is an O-ring, which is used to seal each part to prevent liquid leakage. A hydraulic fluid storage tank 28 connected to the discharge passage 24 and a plunger pump 2 that circulates the hydraulic fluid to the master turn cylinder 21
9 has a well-known configuration, so its explanation will be omitted. Next, the braking action provided with the anti-lock device having the above structure will be explained. When the anti-lock is not activated during normal operation, the large flow path is in the deaf state shown in FIG. 56 closes the valve seat 54. That is, the second outlet 36 of the flow control switching valve 25 is in a closed state. When the spool 41 is in the non-angular state (7), the spool 41 is biased by the return spring 49 and is at the upper end position in the figure.
The second portion of the sleeve 32 is in constant communication with the hydraulic fluid port 34.
The introduction path 38 communicates with a third liquid passage 45 on the outer periphery of the spool 41 . The third liquid passage 45 communicates with the first outlet 35 via the outlet passage 39 of the sleeve 32 . Therefore, the population 34 of the flow rate control switching valve 25 is ! It communicates only with the outlet 35, and the master cylinder 21 and the wheel brake 23 communicate with each other. At this time, a large flow path is formed between the port 34 of the flow rate control switching valve 25 and the first outlet 35, as described above, through which a large flow of hydraulic fluid passes without passing through an orifice or the like. Therefore, the hydraulic fluid can be supplied from the main passage 22 to the brake 23 in accordance with the amount of depression of the brake pedal 20 to restore control of the brake. At the time of non-anti-lock, the population 34 is connected to the first introduction path 37,
It passes through the second liquid passage 44, the first liquid passage 42, and the return spring chamber 51 to the second outlet 36.
Since the valve seat 54 on the side of the discharge valve 26 communicating with the outlet 36 is closed, the hydraulic fluid is not discharged from the second outlet 36, and therefore, normal brake fluid pressure does not act on the valve chamber 52. On the other hand, when a wheel speed detector or the like (not shown) detects the occurrence of excessive slip or its sign and establishes an anti-lock state, the coil 59 of the electromagnetic discharge valve 26 is supplied with power and energized. Therefore, the armature 55 descends in the figure,
Interlockingly, the movable valve body 56 descends against the spring 60 to open the valve seat 54 and open the second outlet 36 of the flow rate control switching valve 25.
Allows for outflow from. Therefore, the hydraulic fluid that has flowed into the return spring chamber 51 from the inlet 34, the first introduction path 37, the second liquid passage 44, and the first liquid passage 42 via the orifice 43 flows out from the second outlet 36, and flows out from the discharge valve. 26 valve seats 54
It is discharged to the discharge passage 24 via the valve chamber 52 and the discharge passage 53. During the above operation, as shown in FIG. 2 (II), the differential pressure generated in the upper part of the orifice 43 acts on both ends of the spool 4 (see FIG. middle, descending).Therefore, the hydraulic fluid population 3
The communication between the second introduction path 38 and the third liquid passage 45, which are in communication with each other, is cut off, and the large flow path that communicates the inlet 34 and the first outlet 35 is closed. When the spool 41 reaches the position shown in FIG. 2 ('fl) due to the above operation, both the first introduction passage 37 and the second introduction passage 38 communicating with the hydraulic fluid port 34 are blocked by the spool 41, and the first outlet 35 and the second output [-13G. When the dough is in this position, the first outlet 35 communicates with the second outlet 36 via the outlet path 39, the third liquid passage 45, the groove 40, and the return spring chamber 51. Therefore, the hydraulic fluid in the vehicle brake 23 flows through the first outlet 35.
The discharge valve 2 passes through the second outlet 36 and is opened by power supply.
6 to form a reduced pressure channel that is discharged to the discharge channel 24. In other words, the hydraulic fluid on the wheel brake side is drained,
Reduce brake pressure and anti-lock the wheels. Moreover, when the communication between the first introduction path 37 and the second liquid passage 44 is cut off, the first introduction passage 37, the second liquid passage 44, and the first liquid passage 1
The flow passing through 2 and the orifice 43 becomes zero,
The differential pressure before and after the orifice 43 begins to decrease. Then, the spool 41 is again moved upward in the drawing by the biasing force of the return spring 49. Then, the first introduction path 37
The flow m passing through the first liquid passage 42 is ensured, and a pressure difference is generated in the executive, which again overcomes the biasing force of the return spring 49 and descends to the illustrated position. That is, at the illustrated position, a metal ringing action is performed between the inner diameter side edge of the first introduction passage 37 and the outer circumference edge of the second liquid passage passage 4.1, and the return spring 49
A differential pressure equal to the biasing force divided by the seal 1-T radius between the outer diameter of the spool 41 and the inner diameter of the sleeve 32 is generated at the center of the orifice 43, and the passage through the orifice 43 based on this differential pressure The entire flow is from the inlet 34 to the first introduction path 37 and the second
The amount of liquid from the wheel brake passes through the liquid passage 44, the first liquid passage 42, the orifice 43, and the spring chamber 51, and the first outlet and is discharged to the discharge passage 24 through the second outlet 36. When the discharge valve 26 is de-energized during anti-lock pressure increase, the movable valve body 56 is urged by the spring 60 and moves, closing the valve seat 54 and closing the discharge valve 2G. The discharge of the working fluid from the second +1 L+ 36 of the control switching valve 25 is stopped. However, in this state, the pressure in the spring chamber 5I connected to the first outlet 35 is 6 lower than the pressure at the inlet 34, so the inlet 34, The hydraulic fluid that has flowed in through the first introduction path 37, the second liquid passage 44, the first liquid passage 42, the orifice 43, and the spring chamber 51 is transferred to the discharge section 40, the discharge passage 39, and the first liquid passage 42.
Via the outlet 35 it is led to the wheel brake 23. Therefore, the spool 41 is connected to the second
It is located at the same position as the depressurized deaf in Figure C111), performs a metering action, and guides the same small flow rate to the wheel brake 23 through the above-mentioned small flow path. , when the pressure difference falls below the above-mentioned pressure, the spool 41 rises in the figure due to the biasing force of the return spring 49, and as shown in FIG. 2 (1).
As shown in FIG. 3, the spool 41 returns to the non-operating position where it communicates with either the third liquid passage 45 or the second introduction passage 38, and the large flow passage is brought into communication. In the present invention, with the above configuration, when air exists in the return splinter chamber 51 of the flow rate control switching valve 25, the return spring Room 51 or the 51st! It is included in the depressurizing flow path through which the working fluid flows from the output 35 to the second tit 1-]3G, and since the depressurizing flow path has a large flow rate without an orifice, the air in the return spring chamber 51 Be able to remove it completely and easily. In addition, since the valve chamber 52 is structured so that normal brake fluid pressure does not act on it, the fluid sealing structure of the guide ring 64 can be easily completed, and the discharge flow path from the second outlet 36 to the fixed valve seat 54 can be easily constructed. The small volume makes it easy to drain the brake fluid. As is clear from the explanation in ``Effects of the Invention'', the present invention provides a) a submerged exhaust passage that branches off from the main passage that communicates the pressurization source and the 1T wheel soligi, and b) this exhaust passage. installed on the road,
C) a normally closed discharge valve that can be opened by electromagnetic force when supplied with electricity to communicate the discharge path; and C) a first outlet that is provided at the branch point and that communicates with the pressurization source and the wheel brake. 1. A hollow cylindrical inner cylinder that connects three ports of the second outlet communicating with the discharge valve; - A liquid passageway that is slidably fitted into the cylinder and includes an orifice, and that is connected to each of the ports. and a return spring that biases this spool in one direction, and when the anti-lock is not activated, the spool is in the inactive position and a large flow of water flows through the population and the first outlet. When the anti-lock pressure is reduced, the discharge valve is opened and the hydraulic fluid is discharged from the second outlet to the discharge passage, and the biasing force of the return spring is applied by the biasing force due to the differential pressure generated at both ends of the spool. The spool moves against the resistance, connects the first outlet and the second outlet, and discharges the working fluid of the wheel brake to the discharge path. , the flow of hydraulic fluid from the second outlet to the discharge valve stops, and if the hydraulic pressure at the person [1] is higher than the hydraulic pressure at the first outlet, the flow from the person [1 to the first outlet through the orifice. Opposite, a small channel is formed through which the small stream-1 flows,
d) a flow rate switching valve configured to allow the spool to return to the non-operating position by the biasing force of a return spring and communicate with the large flow path when the fluid pressure difference between the fluid pressure and the first outlet becomes equal to or less than this pressure difference; In an anti-knock device for housing a flow M switching valve and having an open hole at one end, the anti-knock device is configured such that one open end of the inner cylinder becomes the second outlet. 2
The flow rate switching valve is accommodated in the cylinder hole such that the outlet side open end is located on the open side of the cylinder hole, and the discharge valve is brought into contact with the second outlet side open end of the inner cylinder, and the The cylinder hole is closed, and the movable valve body and armature of the discharge valve are arranged in a discharge passage on a side opposite to the side communicating with the second outlet with the fixed valve seat as a boundary. (When the discharge valve is not energized, the biasing force of the spring acts on the movable valve body against the force of the hydraulic pressure of the second outlet that acts on the movable valve body and the fixed valve seat radius. Since the structure is configured as shown in FIG. Since the discharge valve is closed by a solenoid valve, the conventionally required end plug can be omitted.In addition, the large flow passes through the return spring chamber in the inner cylinder of the flow control switching valve. Since it is a reduced pressure flow path, the air in the return spring chamber can be easily and reliably removed.

[Brief explanation of the drawing]

FIG. 1 is a partially cross-sectional overall configuration diagram showing an embodiment of the present invention;
Figures 2 (1), (II), (ll), and (IV) are 4' cross-sectional views showing the operation of the embodiment shown in Figure 1, and Figure 3 is a partial cross-section showing the conventional example, which is caused by +1 as a whole. . 20... Plaque belt, 21... Master turn ring, 22... Main flow path, 23... Wheel brake, 24...
- Discharge channel, 25... Channel control switching valve, 26... Discharge valve, 27... Housing, 31... Hole, 3
2... Inner cylinder, 34... Population, 35... First exit,
36...Second exit, 41...Spool, 42.44
．． 45...Liquid passage, 43...Orifice, 49...Return spring, 51...Return spring chamber, 54...Fixed valve seat, 55...Armature, 56...
・Movable valve body, 58...stator, 59...coil, 60...spring. Patent applicant Sumitomo Electric Industries, Ltd.

Claims (1)

[Scope of Claims] 1. a) A discharge passage provided so as to branch off from the main passage communicating the pressurization source and the wheel brake; b) A discharge passage provided in this discharge passage and opened by electromagnetic force when supplied with electricity. a normally closed discharge valve capable of bringing the discharge passage into communication; c) provided at the branch point; - an inlet communicating with the pressurization source; a first outlet communicating with the wheel brake; a hollow cylindrical sleeve having three ports with two outlets; a spool that is slidably fitted into the sleeve, has a liquid path including an orifice, and can switch the communication state of each port; - It has a return spring that biases this spool in one direction, and when the anti-lock is not activated, the spool is in the non-activated position and the inlet and the first outlet are connected through a large flow path, and when the anti-lock is depressurized, By opening the discharge valve and discharging the hydraulic fluid from the second outlet to the discharge path, the spool moves against the biasing force of the return spring due to the biasing force due to the differential pressure generated at both ends of the spool, and the hydraulic fluid is discharged from the first outlet. When the hydraulic fluid of the wheel brake is discharged to the discharge passage by communicating the hydraulic fluid with the second outlet and the discharge valve is de-energized when the anti-lock is pressurized, the flow of the hydraulic fluid from the second outlet toward the discharge valve is stopped. , when the hydraulic pressure at the inlet is higher than the hydraulic pressure at the first outlet, a small flow path is formed from the inlet through the orifice to the first outlet, through which a small flow rate flows;
d) a flow rate switching valve configured such that when the liquid pressure difference between the inlet and the first outlet becomes equal to or less than this pressure difference, the spool returns to the non-operating position by the biasing force of a return spring and communicates with the large flow path; An anti-lock device having a housing having a cylinder hole with one end open for housing a flow rate switching valve, wherein one open end of the sleeve is configured as the second outlet, and the second outlet side opening The flow rate switching valve is housed in the cylinder hole so that its end is located on the open side of the cylinder hole, and the discharge valve is brought into contact with the second outlet side open end of the sleeve, thereby closing the cylinder hole. An anti-lock device characterized by: 2. a) a discharge passage provided to branch from the main passage communicating the pressurization source and the wheel brake; and b) a fixed valve provided in the discharge passage and having a liquid passage constituting the discharge passage. - A movable valve element that can open and close this liquid passage by moving against and away from the fixed valve seat, - An armature that can be moved by electromagnetic force accompanying this movable valve element, - An exterior electromagnetic coil - A stator that has one end facing the armature and attracts the armature by electromagnetic force when power is supplied; - The armature is urged in a direction away from the stator, and the movable valve body is brought into contact with the fixed valve seat when power is not supplied, thereby achieving the above-mentioned process. a normally closed discharge valve that has a spring that closes the liquid path and can be opened by electromagnetic force when supplied with electricity to bring the discharge path into communication; c) provided at the branch point; a hollow cylindrical sleeve having three ports: an inlet, a first outlet communicating with the wheel brake, and a second outlet communicating with the discharge valve; and a liquid containing an orifice slidably fitted within the sleeve. a spool having a passageway and capable of switching the communication state of each port, and a return spring that biases this spool in the position direction, and when the anti-lock is not activated, the spool is in the inactive position and the inlet is closed. and the first outlet are connected through a large flow path, and when the pressure of the anti-lock is reduced, the discharge valve is opened and the hydraulic fluid is discharged from the second outlet to the discharge path. The spool moves against the biasing force of the spring, and the first
The outlet and the second outlet are made to communicate with each other so that the hydraulic fluid of the wheel brake is discharged to the discharge path, and when the discharge valve is de-energized when the anti-lock is pressurized, the flow of the hydraulic fluid toward the second outlet discharge valve is stopped. When the hydraulic pressure at the inlet is higher than the hydraulic pressure at the first outlet, a small flow path is formed through which a small flow passes from the inlet to the first outlet through the orifice, and the difference in hydraulic pressure between the inlet and the first outlet is equal to this difference. and a flow rate switching valve configured such that when the pressure falls below the pressure, the spool returns to a non-operating position by the biasing force of a return spring and communicates with the large flow path, wherein the movable valve body and the armature is arranged in the discharge passage on the side opposite to the side communicating with the second outlet with the fixed valve seat as a boundary, and acts on the seal effective diameter of the movable valve body and the fixed valve seat when power is not supplied to the discharge valve. An anti-lock device characterized in that the biasing force of the spring acts on the movable valve body against the force exerted by the hydraulic pressure at the outlet.