• 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:
    Hydraulic assistance device of the mixed hydrodynamic! hydrostatic type incorporating a body (10) in which a first piston (18) is slideably mounted and moveable between a first position allowing the communication of a first chamber (53), joined to a braking circuit, to a reservoir (12), and isolating this chamber (53) from a source of high pressure fluid (86), and a second position isolating the chamber (53) from the reservoir (12) and connecting it with the source (86); a second chamber (30) in the body (10) connected by a passage (90) to the brakes (66), and valve means (92) normally closing the passage (90) and sensitive to the pressure in the chamber (30) so that, when the latter pressure reaches a value which is greaterthan that existing in the first chamber (53), the valve means (92) opens. allowing fluid to flow between the second chamber (30) and the brakes (66).
    公开号:SU1389672A3
    申请号:SU853858828
    申请日:1985-02-27
    公开日:1988-04-15
    发明作者:Кервагоре Жильбер
    申请人:Сосьете Аноним Дба (Фирма)；
    IPC主号:
    专利说明:

    S ff 9 TO 9 11 20 ft f6 Kaz7393S J5
    with
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    This invention relates to the braking control of vehicles
    The purpose of the invention is to increase reliability.
    Figure 1 shows the main brake cylinder, a longitudinal section; Fig. 2 shows a valve assembly communicating wheel brake cylinders with a high pressure source, longitudinal section; in FIG. 3, a clavicle in the stagnated state, a longitudinal section; figure 4 - the same, when braking; fig.Z - the same, when the release; Fig. 6 is the same when braking without a high pressure source.
    Brake master cylinder (figure 1)
    the clearance is installed with the possibility of sliding the control plunger 25. The axial channel 26 drilled in the plunger 25 communicates through the radial channels 27 - 29 with the wheel brake cylinders 30. A saddle 31 is formed in the channel 26 of the plunger 25, the inner diameter of which is equal to the diameter of the plunger 25. The saddle 31 interacts with the drain valve 32 held in the jack 21 of the pusher 8. There is an opening 33 in the jack 21 through which the opening of the ball valve 32 provides communication “- measures 11 with the brake cylinders 30 of the car. The control plunger 25 also includes a pusher 34 which abut when the piston is displaced to the right.
    It has a housing 1, which is installed 20 in the ball inlet valve 35 and
    reservoir 2 for low pressure hydraulic medium. One drilled channel 3 is made in housing 1, one end of which is closed by plug 4. In channel 3, a piston 5 is mounted slidably, which is driven from a brake pedal (not shown). In the piston 5, a stepped blind axial channel 6 is drilled; in the section 7 with a smaller diameter, a caliper 8 is installed slidably. In the pusher 8, axial 9 and radial .10 channels are formed, which together form a channel between the drilled channel 7 and 1 measure 11 crowding out. In the channel 7 a ball valve 12 is installed, pressed by the spring 13 to the seat 14 located on the pusher 8.
    The flow into the surrounding gap 5 of the annular gap 15 of the hydraulic medium is carried out through the opening 16, which is connected through the radial channel I7 in the piston 5 with the channel 7. Between the cavities located on both sides of the ball valve 12, an annular sealing element 18 is installed that slides on and having a low coefficient of friction. The element 18 is held by a washer 19, on which the spring 20 acts, abutting against the right end of the pusher 8, one end of which has increased dimensions and forms the seat 21.
    In the drilled channel 3 of the housing 1, the sleeve 22 is rigidly fixed, which together with the housing forms a working chamber 23. In the sleeve 22 a hole 24 is drilled, in which with a very small
    thirty
    35
    draws it away from the saddle 36. The ball valve is connected to the pan 35 by a spring 37 with a second ball valve 38, which closes the vertex 39 of the channel, which communicates with the 25 source 40 of the high-pressure hydraulic medium.
    The sleeve 22 has a shoulder 41 with a number of grooves 42 that provide hydraulic communication between the chamber 11 and the brake cylinders 30 of the car, but in normal mode it is closed by an annular sponge of the cuff 43, since the working pressure in the chamber 23 is about four times larger pressure in chamber t1.
    In operation, under the action of the spring 13, the piston 5 moves to the right, closes the ball valve 1 and, acting on the pusher 8, closes. Q also has a ball valve 32. When the pusher 8 is moved, the control plunger 25 moves, which, acting on the intermediate pusher 34, opens the ball valve 35. The ball valve 38 is held in open pressure by the hydraulic medium and the open valve 35 passes on the hydraulic medium under pressure to the brake cylinders of the car 30 In addition, the hydraulic medium and pressure through the channel 26 acts on the ball valve 32, balancing the force of the brake pedal. Thus, each given control force is precisely determined for the value of the braking pressure.
    Upon release of the brake pedal, the piston 5 under the action of various preloads again
    45
    50
    55
    0
    five
    pulls it away from the seat 36. The ball valve 35 is connected by a spring 37 to a second ball valve 38 closing the opening 39 of the channel connected to the 5 source 40 of the high-pressure hydraulic medium.
    The sleeve 22 has a shoulder 41 with a number of grooves 42 that provide hydraulic communication between the chamber 11 and the brake cylinders 30 of the car, but in normal mode they are closed with an annular sponge of the cuff 43, since the working pressure in the chamber 23 is about four times greater than the pressure in the chamber t1.
    In operation, under the action of the spring 13, the piston 5 moves to the right, closes the ball valve 12 and, acting on the pusher 8, closes Q also the ball valve 32. As the pusher 8 moves, the control plunger 25 moves, which acts on the intermediate pusher 34, opens the ball valve 35. The ball valve 38 is held in the open position by the pressure of the hydraulic medium, and the open valve 35 passes the flow of the hydraulic medium under pressure to the brake cylinders 30 of the vehicle. In addition, the hydraulic medium under pressure through the channel 26 acts on the ball valve 32, balancing the force of the brake pedal. Thus, for each given control force, a precisely determined amount of braking pressure corresponds.
    Upon release of the brake pedal, the piston 5 under the action of various preloads again 5
    0
    five
    Move to the left. The braking pressure is transmitted through the ball valve 32 to the chamber 11, and the excess hydraulic medium is passed through the ball valve 12 and the channel 17 to the tank 2. If in any position the release is interrupted, the ball valve 32 is closed again and the braking pressure is stabilized at the appropriate level.
    In the event of a failure of the high pressure circuit, for example, if the pump of the battery fails, the ball valve 38 of the device compartment from the high pressure circuit closes. During braking, the seat 21 rests on the sleeve 22. The displacement of the piston 5 causes the pressure in chamber 11 to rise, the pressure of the hydraulic medium acts on the cuff 43, compressing it radially, and the flow of hydraulic medium through the chamber 23 passes to the brake cylinders 30 of the car. This ensures that the car brakes when the high pressure circuit fails.
    It is recommended to choose the axial length of the socket 21 from the condition that in case of failure of the high-pressure circuit to provide an emphasis of the socket 21 to the rear surface of the sleeve 22 before the control plunger 25 begins to contact with it. This allows the ball valve 32 to be released from the preload at the pressure drop in chamber 11 when the braking force is released, providing a quick return of the hydraulic medium from the brake system through channel 26 of the control plunger to reservoir 2 with a concomitant decrease in the system hysteresis.
    The described system provides the ability to change the gain for a given vehicle with a given pedal ratio only by changing the stiffness of the spring 13.
    The described brake device is intended for one brake system, in practice two identical devices are usually used, each of which is associated with a corresponding brake system. In this case, it is recommended to place both devices in a common housing.
    Figure 2 shows a valve device for use in a plant with a battery for a hydraulic medium under pressure.
    0
    Q
    five
    0
    five
    0
    five
    0
    five
    eat and two brake systems. The difference between this variant and the one shown in figure 1 is that the sleeve 22 is slidably mounted in the channel 3. In housing 1, a second opening 44 is made, which, together with channel 29, provides a connection between the chamber 11 and the brake cylinders 30 of the vehicle. The plug 4 contains a tubular support 45, on which a sleeve 46 is slidably mounted. A spring 47 is located around the sleeve 46, is pressed at one end to the annular surface 48 of the plug 4, and the other to the annular surface of the radial outer protrusion 49 of the sleeve 46. The force of the spring 47 pushes the sleeve 22 to the inoperative position, in which the flange 50 is pressed against the corresponding annular surface 51 of the housing 1. A hole 52 formed in the sleeve 46 provides hydraulic-. the casing of the cavity of the sleeve 46 with the surrounding chamber 53. In the event of a high pressure source failure, the chamber 53 does not maintain a pressure level equal to the pressure in the source 40; During braking, the pressure drop in chamber 53 causes the sleeve 22 to move under the action of the spring 54 with the control plunger 25 moving to the right. Moving the sleeve 22 with the cuff 43 installed on it opens a direct connection of the holes 44 of small diameter with the chamber 11. In this situation, the device functions like a normal brake master cylinder.
    In the two options described, the amount perceived by the driver when braking the pedal resistance depends on. the pressure of the hydraulic medium in chamber 11. Under normal conditions, the pressure increases when the piston 5 is displaced slowly, which means that in certain cases there may be an undesirable increase in pedal travel. The device shown in Fig. 3 reduces the pedal travel. This version of the device differs from that shown in Fig. 1 in that the longitudinal channel 9 in the pusher 8 is stepped and has both 55 narrow and 56 wide sections. In a narrow section 55, a rod 57 is slidably mounted, at one end of which a head 58 is made of an enlarged diameter and the other
    end 59 narrowed. In the wide section 56 of the channel 9, a ball valve 60 is placed, pressed by the spring 61 to the valve seat 62. Opening the ball valve 60 causes the stem 57 to displace, with the maximum opening degree of the valve 60 being determined by the gap a between the head 58 of the stem 57 and the inner surface 63 of the socket 21 When the head 58 rests against it, the spring 61 is less stiff than the force generated by the pressure of the hydraulic medium, which attempts to close the ball valve 35, therefore in normal operating conditions the ball valve 60 opens before the ball valve 35.
    At the front end of the piston 5, an annular seal 64 is installed, which is in the non-operating position of the device-2o 32. Although the spring 37 is weak.
    25
    distance B from the compensating orifice 65, providing hydraulic connection of the chamber 11 with the reservoir 2. In the off position, the maximum degree of opening of the ball valve 32 is indicated in, to close the ball valve 32 and push the pusher 34 into contact with the ball valve 35 pusher 8 at distance a + c, i.e. equal., - or less b. Therefore, the ball valve 35 opens when the ball valve 60 is already open, so that in chamber 11 it does not create an overpressure compared to the ambient pressure.
    In FIG. 4, the head 58 of the stem 57 is pressed against the inner surface 63 of the housing, and the ball valves 35 and 60 are open. The nest 21 is separated from the sleeve 22 at a distance of r.
    Fig. 5 shows the position when the braking force is released, i.e. relieve the brake pedal after braking. The spring 20 is released, and the pusher assembly 8, the ball valve 32 and the control plunger 25 are moved to the left, while the ball valve 35 is closed. If the force generated by the spring 20 is less than the force generated by the pressure P in the channel 26 acting on the ball valve 32, then the ball valve 32 opens with a concomitant fall in brake pressure due to passing the hydraulic medium under pressure into chamber 11. Therefore, the rate of decrease in P is proportional to spring stiffness 20. In the off phase
    35
    40
    45
    50
    the force it generates is enough to move the control plunger 25 to the left and keep the ball valve 32 closed. Since the ball valve 32 is affected only by small forces it is in the socket 21 in an almost idle state.
    The ball valves 12 and 60 are then closed and the device functions as a conventional brake master cylinder. The chamber 11 acts as a hydrostatic pressure chamber, in which a pressure is created that is proportional to the force exerted on the piston 5, the stiffness of the spring 20 and the damping effect of the brakes. As in the previous embodiments, the hydraulic pressure is supplied to the brakes through the jaws of the cuff 43. When the braking force is released, the hydraulic medium through the ball valve 32, chamber 11, ball valves 60 and 12 returns to the reservoir.
    The spring 61 has a stiffness sufficient to keep the ball valve 60 closed during emergency braking.
    权利要求:
    Claims (2)
    [1]
    1. The master brake cylinder, comprising a housing with a through-drilled channel, closed on one side with a stopper, a piston connected to the brake pedal with a deaf axial channel in which the pusher is slidably mounted, is spring loaded relative to the piston, which is installed with a possibility of sliding into
    The force of the ball valve 60 remains open and allows the flow of hydraulic fluid from the brakes through the ball valve 12 back to the reservoir. As a result, the pressure in the chamber 11 is practically maintained, as determined by the position of the piston 5.
    In the event of failure of the high pressure circuit, when the brake pedal is activated, the device takes the position shown in Fig.6. The gap r between the seat 21 and the sleeve 22 is reduced to zero, since the force of the spring 20 no longer counteracts the force created by the hydraulic pressure. The spring 61 closes the ball valve 60, which through the intermediate rod 57 closes the ball valve
    five
    ,,
    five
    five
    0
    five
    50
    the force it generates is enough to shift the control plunger 25 to the left and keep the ball valve 32 closed. Since the ball valve 32 is only a small force, it is in the socket 21 in an almost idle state.
    The ball valves 12 and 60 are then closed and the device functions as a conventional brake master cylinder. The chamber 11 acts as a hydrostatic pressure chamber, in which a pressure is created that is proportional to the force exerted on the piston 5, the stiffness of the spring 20 and the damping effect of the brakes. As in the previous embodiments, the hydraulic pressure is supplied to the brakes through the jaws of the cuff 43. When the braking force is released, the hydraulic medium through the ball valve 32, chamber 11, ball valves 60 and 12 returns to the reservoir.
    The spring 61 has a stiffness sufficient to keep the ball valve 60 closed during emergency braking.
    Invention Formula
    1. The master brake cylinder, comprising a housing with a through-drilled channel, closed on one side with a stopper, a piston connected to the brake pedal with a deaf axial channel in which the pusher is slidably mounted, is spring loaded relative to the piston, which is installed with a possibility of sliding into
    the through channel of the housing in which the sleeve is placed, sealed with a cuff and an annular seal, between which the annular flow sleeve bbrazovana annular cavity, connected by radial channels with the axial bore of the sleeve, which houses the plunger with an axial channel, acting on the inlet valve that connects the working chamber connected to wheel brake cylinders, with a pressure chamber connected to a high pressure hydraulic source, moreover, between the piston depressed by the return spring and the plunger is placed an aromatic drain valve separating the plunger axial channel from the chamber
    [2]
    2. The cylinder according to claim 1, characterized with, in that kaHan between peteseni, connected to the tank
    low pressure and communicated with the working part of the collar of the sleeve and
    whose camera, distinguishing and and with the body is formed by an annular gap
    so that, in order to increase the reliable - between them.
    Typically, the sleeve is secured against movement in the through channel of the housing, the working chamber is formed by an annular cavity of the sleeve groove, between the c. wall of the housing and the peripheral part of the collar of the sleeve that separates the annular cavity and the displacement chamber, a channel is formed that allows liquid to flow from the displacement chamber to the annular cavity through the check valve.
    5 W
    :
    formed by a cuff, in the plunger radial channels are made, the axial channel informing it with the cavity of the axial bore of the sleeve, the pressure chamber is formed between the stopper and the end of the sleeve, the piston has a radial channel connecting the axial channel of the piston with the reservoir, and the axial channel in the piston is open to the displacement chamber , and the pusher is installed in contact with a ball drain valve and is made with an axial channel, connected by radial channels with a displacement chamber, a spring-loaded ball valve is installed in the axial channel of the piston, digging axial channel pusher.
    2. The cylinder according to claim 1, characterized with, in that kaHan between ne3. A POP.1 cylinder, characterized in that in the axial channel 25 of the pusher, an additional spring-loaded ball valve and its control rod are in contact with the ball drain valve.
    thirty
    The priority of paragraphs 29.02.84 on PP. 1 and 2; 03.28.84 according to cl.
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    类似技术:
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    US3938333A|1976-02-17|Master cylinder
    US6196641B1|2001-03-06|Fluid pressure boosting device and brake pressure boosting system employing the device
    JP2005162127A|2005-06-23|Vehicular brake device
    US5557935A|1996-09-24|Apply-rate-independent fast-fill master cylinder
    SU1389672A3|1988-04-15|Master brake cylinder
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    EP0059129B1|1985-05-15|Master cylinder with a quick take-up chamber
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    US2964141A|1960-12-13|Hydraulic brake locking device
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    US7093435B2|2006-08-22|Hydraulic controller
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    US4472942A|1984-09-25|Tandem brake master cylinder with anti bottoming system
    US4637208A|1987-01-20|Hydraulic assistance device for braking
    US4413861A|1983-11-08|Fluid pressure control valve unit of the inertia-controlled type
    US4201055A|1980-05-06|Hydraulic master cylinder
    JP2536084Y2|1997-05-21|Hydraulic pressure control device
    JP3944982B2|2007-07-18|Hydraulic brake device for vehicle
    同族专利:
    公开号 | 公开日
    BR8500951A|1985-10-22|
    US4622814A|1986-11-18|
    EP0156677B1|1987-04-22|
    AU565728B2|1987-09-24|
    ES540806A0|1986-04-16|
    JPH0624920B2|1994-04-06|
    AU3919985A|1985-09-05|
    EP0156677A1|1985-10-02|
    ES8606154A1|1986-04-16|
    DE3560128D1|1987-05-27|
    JPS60203564A|1985-10-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    RU2654878C1|2017-02-06|2018-05-23|Открытое акционерное общество "БЕЛАЗ" - управляющая компания холдинга "БЕЛАЗ-ХОЛДИНГ"|Brake cylinder of a vehicle|US3157986A|1962-08-15|1964-11-24|Ralph R Gordon|Positioning system and its control|
    DE2607140A1|1976-02-21|1977-08-25|Bosch Gmbh Robert|HYDRAULIC BRAKE AMPLIFIER FOR A VEHICLE BRAKE SYSTEM|
    BR7900573A|1978-01-31|1979-08-28|Girling Ltd|IMPROVEMENTS IN MECHANICAL DRIVING SERVOMOTORS|
    DE2942979C2|1979-10-24|1992-07-23|Alfred Teves Gmbh, 6000 Frankfurt, De|
    FR2480371B1|1980-04-15|1984-02-17|Ferodo Sa|
    GB2078325B|1980-06-17|1984-02-08|Lucas Industries Ltd|Control valve assemblies for dual hydraulic braking systems|
    GB2099940B|1981-06-09|1985-02-20|Lucas Industries Ltd|Control valve assemblies for two pedaloperated hydraulic braking systems|
    DE3226987C2|1982-07-19|1990-07-05|Alfred Teves Gmbh, 6000 Frankfurt, De|FR2565913B1|1984-06-13|1986-09-19|Dba|BRAKE PRESSURE CONTROL AND MODULATION SYSTEM FOR ANTI-LOCK BRAKE CIRCUIT|
    US4625623A|1984-06-29|1986-12-02|Allied Corporation|Brake booster|
    FR2596129B1|1986-03-19|1988-06-10|Bendix France|ELECTROVALVE|
    FR2596466B1|1986-03-26|1990-03-16|Bendix France|HYDRAULIC ASSISTANCE DEVICE|
    FR2620099B1|1987-03-31|1989-12-01|Bendix France|HYDRAULIC ASSISTANCE DEVICE FOR BRAKING CIRCUIT|
    FR2614591A1|1987-04-28|1988-11-04|Bendix France|HYDRAULIC BRAKE DEVICE FOR VEHICLE|
    JPH0547019Y2|1989-04-11|1993-12-09|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    FR8403105A|FR2560133B1|1984-02-29|1984-02-29|HYDRAULIC ASSISTANCE DEVICE|
    FR8404843A|FR2562015B2|1984-03-28|1984-03-28|HYDRAULIC ASSISTANCE DEVICE|
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