• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    An antilock mechanism for use in a hydraulic brake system including a hydraulic pressure source (21), a wheel brake (23), and a drain channel (24), includes a flow control valve (25) and a drain valve (26) provided in the drain channel (24). The flow control valve (25) has an inlet port (34) connected with the hydraulic pressure source (21), a first outlet port (35) connected with the wheel brake (23), and a second outlet port (36) connected with the drain channel (24). A spool (41) is slidably inserted in the housing (27, 32). The spool comprises first axial conduit (42A) and a second axial conduit (42B) separated by a wall (57) having a fixed orifice (43) formed therein, and is biased by a return spring (49). The drain valve (26) is located adjacent the open end of the housing (27, 32) such that the second outlet port (36) of the flow control valve (25) and a valve member (56) of the drain valve (26) are connected straight.
    公开号:SU1655298A3
    申请号:SU4614218
    申请日:1989-05-30
    公开日:1991-06-07
    发明作者:Хасида Коити；Кохно Терухиса；Таката Кодзи
    申请人:Сумитомо Электрик Индастриз Лтд (Фирма)；
    IPC主号:
    专利说明:

    2.5, separated by a partition 26 having a constant cross section throttle 27 formed therein, and spring-loaded by means of a return spring 32. The drain valve 7 is located near the open end of the housing so that the second outlet 18 of the regulator 6 and the valve element 37 of the valve 7 are connected with each other directly. 3 hp f-ly, 5 ill.
    This invention relates to automotive brake systems.
    The purpose of the invention is to increase the reliability of the device.
    FIG. 1 shows schematically t anti-lock device; in fig. 2 - flow controller in the absence of anti-blocking phase; in fig. 3 to the same in the intermediate phase; FIG. A is the same in phase 2 pressure relief; in fig. 5 is the same in the pressure boosting phase.
    The master brake cylinder 1, which is a pressure source, actuated by depressing 2 brake pedal 2, is connected to a wheel brake 3 containing a wheel brake cylinder through a main line 4. A drain line 5 is retracted from the main line 4. - J are installed in series flow regulator 6 and drain valve 7 with electromagnetic control, which are mounted in one cylindrical block 8. The drain line 5 is connected to the plunger pump 9 via the reservoir U for brake fluid. The plunger pump 9 is connected to the master brake cylinder 1 via the circulation line 11, so that the plunger pump 9 can pump the brake fluid drained into the drain line 5 to the brake master cylinder 1. In the described embodiments, the structure behind the drain line 5 is described as having as mentioned, the circulatory system, but another system can be used. For example, the brake fluid reservoir 10 may be combined with the master cylinder 1. In this case, the pumped fluid is directed into the main brake cylinder line through a hydraulic booster to compensate for the drained brake fluid
    In addition, the brake fluid can be supplied by the so-called irreversible booster system,
    not having a master brake cylinder. Thus, the proposed anti-lock device can be used in combination with any known system for supplying brake fluid under pressure and any known drain device behind the drain line 5.
    A hole 12 is formed in the cylindrical block 8. A sleeve 13 is fixed in the hole 12 of the cylinder, having a bore 14, and a drain valve 7, which is an electromagnetic valve, is installed so that it closes the open end of the hole 12 of the cylindrical block. Block 8 together with. gil- Slot 13 forms a housing for a flow controller 6.
    Sleeve 13 is used to facilitate machining of the bore.
    14 and, therefore, in order not to use the sleeves 13, the opening can be performed directly in the cylindrical block 8. Both ends of the sleeves 13 are open. One end rests against the bottom of the cylinder bore 12, and the other end is in contact with the housing.
    15sleeve valve 7 and attached to it. An inlet 16 for brake fluid is formed between the outer periphery of the sleeve 13 and the inner periphery of the hole 12 of the cylinder, leading to the brake master cylinder 1 of the main line 4.
    In addition, a first outlet port 17 is formed for the brake fluid, leading to the wheel brake 3. In the axial center passage on the side leading to the housing 15, a second outlet port 18 is formed to guide the brake fluid in a straight line to the drain valve 7. At the intake The aperture 16 is provided with a filter 19 for trapping dust and impurities contained in the brake fluid coming from the master brake cylinder.
    In addition, the sleeve 13 has an inlet port 21),. passing in the radial direction to the inlet. 16, the first exhaust port 21 and the second exhaust port 22, which radially extend to the first exhaust port 17.
    The sleeve 13 is tightly inserted with the possibility of free sliding in the axial direction of the spool 23. In the latter, the first 24 and second 25 axial channels are made, which are separated by a partition 26 having an axle 2 / made in it in the axial direction. In addition, in the spool 23, there are made, starting from the side closest to the bottom, the holes in the cylindrical block, the first 28 and second 29 radial channels extending in the radial direction to the first axial channel 24, and the third radial channel 30 passing in the radial direction to the second axial channel 25. The first radial channel 28 opens and closes the first inlet channel 20 in accordance with the movement of the spool 23, and the edges of these channels form the metering edge of the throttles of variable cross section. The second 29 and third 3U radial channels are formed in front and behind the throttles 27, i.e. the throttle is located between them, and the first 21 and second 22 exhaust channels open and close, respectively, in accordance with the movement of the spool 23.
    The end of the spool 23 is shaped so as to form the holder 31 of the spring 32 compressible between the holder 31 and the holder 33 fixed on the end surface of the housing 15 facing the second outlet 18 of the sleeve 13. A filter 34 is fixed in the holder 33 to trap impurities from the brake fluid flowing into the drain valve 7 from the formed by the sleeve 13, the spool 23 and the body 15 of the cavity 35 for the return spring.
    A fixed brake fluid leakage is attached to the housing 15.
    In the normal (normal) working condition, i.e. state of regulation without anti-blocking action, a path with a lower hydraulic resistance, passing from the source of hydraulic pressure to the wheel brake, operates. In this state, the energy to the electromagnetically controlled valve seat 36, which is opened and closed by means of the movable valve member 37. Thus, the second outlet 18, formed in the axial direction at the open end of the sleeve 13 of the flow regulator 6, is located in the same direction in series with the drain valve 7 so that the tor55
    0
    five
    0
    Molecular fluid flows from the second outlet 18 in a straight line to the drain valve 7.
    In the housing 15 of the drain valve 7, a large-diameter valve chamber 38 passing along the central axis of the housing is arranged in one line and connected to the second outlet 18 through the valve seat 36. The exhaust channel 39 leading from the valve chamber 38 is also provided in the housing 15 drain line 5. In the valve chamber 38, the bore 40 is installed with the possibility of free sliding in the axial direction. The fixed valve seat 36 is opened and closed by means of a movable valve element 37 fixed in the core 40, i.e. The fixed valve seat 36 and the movable valve element 37, which form the sealing part of the drain valve 7, are located respectively on the side of the second outlet port 18 and on the side of the valve chamber 38 of the drain valve 7. In the case 15, a stator 40 is mounted opposite the core 40, which is wound on winding 42. When electric current is applied, winding 42 is energized, which causes movement of the core 40 and the movable valve element 37 in the direction of the arrow and, consequently, the opening of the fixed valve seat 36. At the same time, 5 are conductive with between the armature 40 and the stator 41 of the spring 43 which, when no electric current supply closes stationary valve Saddle 36 through the movable valve element RL
    The movable valve element 37 and. Measles 40 can be performed as a single unit or separate. In the latter case, it is possible to additionally use a central adjustment mechanism between the valve element 37 and the bark 40. The O-ring 44 is installed for J
    five
    0
    0
    five
    55
    no drain valve / do not serve. Consequently, the winding 42 is not excited, so that the movable valve element 37 closes the fixed valve seat 36, while the second outlet 18 of the flow regulator 6 is also closed. During the regulation state without anti-lock action, the return spring 32, pressing the spool 23, shifts it towards the upper end (Lig. 2). Thus, the inlet 16 for brake fluid and the first inlet
    and a pressure in the lower part of the spool 23 facing the second axial channel 25 of the cavity 35 and the second outlet 18. The force depending on this pressure differential causes the spool 23, overcoming the force of the return spring 32, to move downwards. As a result, the passage between the second radial channel 29 of the spool 23 and the first outlet channel 21 of the sleeve 13 is closed and the path with a lower hydraulic resistance is provided by the channel of the channel 20. The sleeve 13 communicates with per-15 covered (Fig. 3). The same way,
    the radial channel 28 of the spool 23, and the second radial channel 29 communicates with the first outlet channel 21 of the sleeve 13. Consequently, the inlet 16 of the flow regulator is connected to the first outlet 17 through a path with a lower hydraulic resistance formed by the inlet channel 20, the first radial channel 28, the first axial channel 24, the second radial channel 29 and the first exhaust channel 21. At the same time brake fluid flows from the main brake cylinder 1 to the wheel brake 3, and its quantity depends on Stand on the brake pedal 2, thus providing brake control.
    25
    thirty
    since the passage between the third radial channel 30 of spool 23 and the second outlet channel 2 /. the sleeves 13 are also closed, and the supply of brake fluid to the second discharge opening 1 / and its discharge through this opening is stopped, which ensures that the pressure of the fluid in the wheel brake 3 is kept constant.
    This shutdown (stopping) condition helps move the spool 23 downward, but it is also possible to provide a very small passage between the second axial channel 25 or cavity 35 and the outlet 17, before the pressure relief path is fully created.
    On f ig ig. 4 shows the state (mode) of pressure relief with anti-blocking action, when the pressure in the forest brake 3 is relieved through the pressure relief path formed, starting from the wheel brake 3, with the main line 4, the first exhaust hole G /, the second outlet a channel 22, a third radial channel 30, a second axial channel 25, a cavity 35, a second exhaust hole 18, a fixed valve seat 36 with a movable valve element 3 /, a valve chamber 38, an exhaust channel 39 and a drain line 5 to reduce wheel braking regardless Mo from acting on the brake pedal. The pressure relief mode with the anti-blocking action of FIG. Figure 3 shows an intermediate state in which a path with a lower hydraulic resistance has just been blocked. When a wheel speed sensor (not shown) or other means detects signs of excessive slip, an electric current is applied to energize the winding 42 of the drain valve 7. At the same time, the measles 40 begin to descend, as shown in FIG. 2, with the result that the spring 43 is lowered, overcoming the action of the spring 43, the movable valve element 37 opens the fixed valve seat 36, which allows
    On f ig ig. 4 shows the state (mode) of pressure relief with anti-blocking action, when the pressure in the forest brake 3 is relieved through the pressure relief path formed, starting from the wheel brake 3, with the main line 4, the first exhaust hole G /, the second outlet channel 22, a third radial channel 30, a second axial channel 25, a cavity 35, a second exhaust hole 18, a fixed valve seat 36 with a movable valve element 3 /, a valve chamber 38, an exhaust channel 39 and a drain line 5, to reduce wheel braking regardless about by the action of the brake pedal. The pressure relief mode, with the anti-blocking action of the brake fluid, is drained from ... .., .., the second outflow opening 18 of the control - is provided during braking
    L TORA 6 flow in valve Kame-with anti-blocking effect. 38. Consequently, there is a failure. When the brake fluid continues to pressurize between the first 24 and the second (from the intermediate state, we pore 25 axial channels, i.e. between
    as shown in FIG. 3) flow out of the drain of the valve 7, the spool 23 continues to fall and, when it reaches the position shown in Fig. 4, the third radial channel 30 of the spool 23
    the pressure in the upper part of the spool 23 communicating with the inlet opening 16, the inlet channel 20, the first radial channel 28 and the first axial channel 24, and the pressure in the lower part of the spool 23 facing the second axial channel 25 of the cavity 35 and the second outlet 18. The force, depending on this pressure differential, causes the spool 23, overcoming the force of the return spring 32, to move downwards. As a result, the passage between the second radial channel 29 of the spool 23 and the first outlet channel 21 of the sleeve 13 is closed and the path with lower hydraulic resistance is turned
    five
    0
    since the passage between the third radial channel 30 of spool 23 and the second outlet channel 2 /. the sleeves 13 are also closed, and the supply of brake fluid to the second discharge opening 1 / and its discharge through this opening is stopped, which ensures that the pressure of the fluid in the wheel brake 3 is kept constant.
    This shutdown (stopping) condition helps move the spool 23 downward, but it is also possible to provide a very small passage between the second axial channel 25 or cavity 35 and the outlet 17, before the pressure relief path is fully created.
    On f ig ig. 4 shows the state (mode) of pressure relief with anti-blocking action, when the pressure in the park brake 3 is discharged through the pressure relief path formed, starting from the wheel brake 3, with the main line 4, the first exhaust outlet G /, the second outlet channel 22, a third radial channel 30, a second axial channel 25, a cavity 35, a second exhaust hole 18, a fixed valve seat 36 with a movable valve element 3 /, a valve chamber 38, an exhaust channel 39 and a drain line 5, to reduce wheel braking regardless Mo from acting on the brake pedal. Pressure relief mode with anti-blocking action
    five
    .. .., .., 0vii provide during braking
    em (from the intermediate state,
    as shown in FIG. 3) flow out of the drain valve 7, the spool 23 continues to fall and, when it reaches the position shown in Fig. 4, the third radial channel 30 of the spool 23
    communicates with the second outlet channel 22 of the sleeve 13 and a pressure relief path is formed, in which the first outlet port 17 communicates with the second outlet port 18 through the second radial outlet channel 22, the third radial channel 30, the second axial channel 15 and the cavity 35. Thus, the brake the fluid from the wheel brake 3 passes through the second outlet 18, flows into the drain line 5 through the drain valve 7, which is open, the brake pressure drops and anti-lock regulation occurs.
    Upon further lowering of the spool 23, the first radial channel 28 reaches a position in which it does not communicate with the inlet channel .10, and the flow of brake fluid from the inlet port 16 is stopped. In this state, if the cross sectional area of the spool 23 is denoted by the letter A, the force F of the return spring 32 and the brake pressure (in particular, the equivalent pressure in the second axial channel 25 in this state) by the letter P, then the pressure in the first axial channel 24, communicating with the second-axial channel 25 through the throttle 27 located between them, can be expressed as an equilibrium pressure, which is maintained at the level of P + F / A. In the following, the F / A value will be represented as DR. With continued supply of electrical energy to the drain valve, this balance is maintained, although the braking pressure decreases.
    When the anti-lock regulation is relocated, as shown in FIG. 5, to an increase in pressure and stop the flow of electric current to the drain valve 7, the movable valve element 37 under the action of the spring 43 moves and closes the fixed valve seat 36, thereby closing the drain valve 7.
    AT THIS DRAINS BRAKE FLUID FROM
    the second outlet port 18 of the flow controller 6 is stopped. In this state, during the period in which the differential between the pressures of the source of hydraulic pressure and the pressure in the wheel brake exceeds a predetermined pressure P, a differential DR of pressure is created, determined by the force of the return spring 32 acting
    about 5
    0 5 0 h 0
    five
    Q
    five
    on the spool 23, and the cross-sectional area of the spool 23, in front. and behind constant cross section throttles 27, made in spool 23. The cut-off edges of the first radial channel 28 and inlet channel 20 form a variable cross section choke, which only allows a flow equivalent to the flow determined by the constant cross section throttles 27 and the specified differential pressure penalties, and hydrogenerations are formed successively through both throttles with a high hydraulic resistance between the source of hydraulic pressure and the wheel brake, i.e. from the source of hydraulic pressure through the main line, 4, inlet 16, inlet channel 20, variable cross section throttle, first radial channel 28, first axial channel 24, constant cross section throttle 27, second axial channel 25, third radial channel 3D, second outlet channel 22, the first outlet 17, the main line 4 to the wheel brake 3.
    Thus, when the pressure differential between ducts 24 and 25 is greater than the DR, the spool 23 moves downward, with the result that the passage between the inlet duct 20 and the first radial duct 23 is narrowed. And when this pressure drop is less than the DR, the spool 23 moves up and the passage widens. Consequently, the passage forms a variable cross section throttle through which only as much brake fluid flows as is required to maintain said constant pressure drop.
    In addition, if the pressure drop is maintained at an AR level, the flow through a constant-flow choke 27 will be constant. Therefore, the passage of the throttles of variable cross section is automatically adjusted to maintain the same constant flow rate as through the throttle of the constant cross section.
    Thus, a small constant flow of brake fluid passing through the throttle 2 / is supplied to the wheel brake 3, which ensures a gradual increase in the brake pressure. At this time (when a path is formed with a large hydraulic resistance) in the gap between the spool 23 and
    A sleeve 13 connecting the inlet 16 to the first outlet 17 does not form any leakage path that is exposed to the differential between the pressure in the inlet 16 and the pressure in the first outlet 17 and is parallel to the throttle of constant cross section. The only leakage path subjected to the total pressure drop is consistent with the throttle 27 and, therefore, the leakage through this path is controlled by throttles of variable cross section, as long as it is less flow through the throttle of the constant cross section, and therefore no problems arise. Another leakage is minimal because there is only a differential differential pressure from the other gaps between the spool 23 and the bore 14. When the pressure differential between the inlet port 16 and the first outlet port 17 gradually decreases (due to the supply of brake fluid through the path with a large hydraulic resistance) and the value D.P., the spool 23 returns to the position shown in FIG. 2, under the action of the return spring 32, and again, as a result of this, the described path with a lower hydraulic resistance will be created.
    When air bubbles enter the cavity 35 of the flow controller 6 in the proposed anti-lock device, such bubbles can be easily removed regardless of the orientation of the device. When the anti-lock device is positioned so that the second outlet port 18 is at the bottom (Fig. 1), the valve 23, when pressure is applied to the inlet port 16, moves to the gradual pressure increase position (Fig. 5), compressing the air if it is in the cavity 35 At this time, since the third radial channel 30 of the spool 23 is in a position near the top of the cavity 35 and as a result of the movement of the spool 23 it communicates with the second outlet channel 22 of the sleeve 13, the flow of fluid passing through the path with large hydraulic resistance In addition, the air bubbles out of the cavity 35 through the third radial channel 30, the second outlet channel 22 and the first outlet 17 are pushed out. After removing the air from the cavity 35, the unwanted movement of the spool 23 is stopped, resulting in the spool 23 returning to the position shown in FIG. 3, under the action of the return spring 32, the fluid flow passing through the path with less hydraulic resistance quickly removes the air in the first axial channel 24. In this way, the residual air remaining in the flow regulator return cavity 1 can be easily removed without opening the drain valve 7.
    If the device (FIG. 1) is inverted so that the second outlet 18 is at the top, the spring return cavity opens when the drain valve 7 and the pressure relief path open. Therefore, since the vent is a wide channel that does not pass through the throttle, the air in the cavity for the return spring can be quickly removed to the drain line when the drain valve 7 is operated.
    In addition, the smaller the volume of the cavity for the return spring, the more efficient the removal of air. Since the movable valve element 3 /, the bore 40 and the spring 43 of the drain valve 7 are located outside the cavity 35 for the return spring, i.e. on the side of the discharge line 5, the cavity for accommodating the return spring is made with the minimum capacity required.
    Thus, in the proposed anti-lock device, the removal of air can be carried out easily and quickly, even if the second outlet port 18 is located above or below.
    In addition, since the drain valve, which is a solenoid valve, closes the open end of the bore 14, a plug, which is usually required to close the aperture, is not needed.
    权利要求:
    Claims (4)
    [1]
    1. An anti-lock device comprising a pressure modulator, in the casing of which a flow regulator and a drain valve are mounted, and the flow regulator includes
    the ax mounted axially sliding in the bore of the casing which is open at least on one side, and the return spring pressing the slide, in the spool the first and second axial channels separated by a partition in which a constant throttle is made are made in the body an inlet that is connected by a pressure line to a source of hydraulic pressure, a first outlet that is connected to the cylinder brake cylinder and communicates depending on the position of the ash a flow control valve with an inlet orifice along a path with a lower hydraulic resistance or along a path with a greater hydraulic resistance sequentially through a constant flow throttle and a variable flow throttle formed between the housing and the slide valve, the second outlet opening forming the first outlet and the inlet channel with the drain valve open, the pressure relief path communicated with the drain line, and the drain valve includes a fixed seat with an opening m, communicating a second outlet with an outlet channel, a movable valve element pressed against the seat by a spring, and the measles of a solenoid connected to the valve element, the action of which is directed against the action of the spring, characterized in that, in order to increase the reliability by air bubbles from the cavity of the return spring, the second outlet is formed by the final open section of the bore of the body between the valve and the drain valve,
    five
    20
    "., 25 ™ 40
    The said bore is bore, with the solenoid measles, valve element and the saddle with the orifice aligned with the bore of the body.
    [2]
    2. A device according to claim 1, 1, which is in that the valve element is located in relation to the saddle on the side of the exhaust channel.
    [3]
    3. The device according to paragraphs. 1 and 2, about t - the fact that the first axial channel forms a large part of the tract with a lower hydraulic resistance, and the second axial channel forms part of the pressure relief tract.
    [4]
    4. Device on PP. 1-3, about t - in that the flow controller is equipped with an installed
    In the case with a sleeve in which the regulator spool is installed, three channels are made in the wall of the sleeve, the first of which is connected to the inlet, and the second and third are connected to the first exhaust channel, the first and second radial channels extending from the first axial channel, and the third radial channel deviating from the second axial channel, with a path with less hydraulic resistance formed by the first channel in the sleeve, the first radial channel, the first axial channel, the second radial channel in the spool and the second a channel in the sleeve, and a path with a large hydraulic resistance is formed by the first channel in the sleeve, a variable bushing throttle between the edges of the first channel in the sleeve and the first radial channel in the spool, the first radial channel, the first axial channel, a constant throttle, and the second axial channel , the third radial channel in the spool and the third channel in the sleeve.
    h
    with
    O-v
    sch
    W LH
    cho
    gz 4
    21
    29
    Fig5
    类似技术:
    公开号 | 公开日 | 专利标题
    SU1655298A3|1991-06-07|Antiblocking device
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    RU1788935C|1993-01-15|Modulator and system of auxiliary steering gear with modulator
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    US5887955A|1999-03-30|Brake fluid pressure control apparatus
    EP0453900B1|1994-06-29|Braking circuit provided with antilocking apparatus
    JP3191172B2|2001-07-23|Brake pressure control device
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    同族专利:
    公开号 | 公开日
    AU610722B2|1991-05-23|
    KR900017855A|1990-12-20|
    AU3474689A|1989-12-07|
    DE68908476T2|1994-01-05|
    US4915459A|1990-04-10|
    EP0344544A1|1989-12-06|
    CA1316970C|1993-04-27|
    KR920002083B1|1992-03-10|
    EP0344544B1|1993-08-18|
    DE68908476D1|1993-09-23|
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    法律状态:
    2005-01-10| REG| Reference to a code of a succession state|Ref country code: RU Ref legal event code: MM4A Effective date: 20030531 |
    优先权:
    申请号 | 申请日 | 专利标题
    JP13504188A|JPH0565387B2|1988-05-31|1988-05-31|
    JP13504088A|JPH0565386B2|1988-05-31|1988-05-31|
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