• 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:
    1514102 Dual circuit braking systems WABCO WESTINGHOUSE GmbH 25 Oct 1976 [3 Nov 1975] 44179/76 Heading F2F A brake control (e.g. an hydraulic master cylinder, Fig. 4, or a pneumatic relay valve, Fig. 3) has a first piston controlling the braking pressure to one brake circuit, and a second piston controlling the braking pressure to a second circuit, the second piston having two separate areas subject respectively to the output from the first piston and the pressure actually existing in the brakes of the first circuit. This allows the (second) circuit pressure for front brakes 18 (Fig. 1) to depend in part on the pressure downstream of a load responsive valve 11 in the (first) rear brake circuit leading to brakes 13. The hydraulic master cylinder (Fig. 4) has a first piston 62a and a second piston 62 subject to pressure from the first piston and to pressure at port 108b from the rear brake circuit downstream of the load responsive valve. The pneumatic relay valve (Fig. 3) has a first piston 41 controlling the flow from a high pressure supply at 32 through a valve 35 to the rear brake circuit port 8a. Circuit pressure then acts under the piston 41 in opposition to the control force on top of the piston. The second piston 43 has an area 46 subject to pressure under the piston 41, and an area 47 subject to rear brake pressure introduced at 86. The piston 43 controls a valve 54 controlling flow between inlet and outlet ports 6, 16. The valve 54 is operated mechanically through rod 57 if the first circuit fails.
    公开号:SU738502A3
    申请号:SU762416155
    申请日:1976-11-01
    公开日:1980-05-30
    发明作者:Райнеке Эрих
    申请人:Вабко Вестингхауз Гмбх (Фирма)；
    IPC主号:
    专利说明:

    (54) DOUBLE-CIRCUIT BRAKE SYSTEM
    one
    This invention relates to the automotive industry and can be used in brake systems to regulate the braking forces on the front and rear axles depending on the vehicle load.
    It is known that automatic load sensing regulators are used so that the pressure in the brake cylinders corresponds to the state of loading the car. The spring deflection or air spring pressure determines, by means of the brake force regulator, the magnitude of the adjustable brake pressure. On trucks, the braking pressure is regulated, especially on the rear axle, since different loading conditions affect the effectiveness and stability of braking.
    A load-dependent control device in the rear axle brake line is known. The pressure in the system is created by a double master cylinder. The control device does not regulate in the front brake circuit, but only when the circuit leaves this circuit, the pressure created by the master cylinder is regulated so that in the brake car
    the hinge of the rear axle ensures that the pressure 1 is necessary for effective braking.
    The various loading conditions not only affect the redistribution of the braking forces of the rear axle, but to a greater or lesser extent also the redistribution of the brakes Hijix of the forces of the front axle.
    Thus, it is necessary to regulate the braking forces (braking torques) acting on the brakes of the front axle, in a certain ratio to the braking forces (braking torques) acting on the brakes of the rear axle.
    With simultaneous regulation, the specific braking forces are equal, there is an advantage in operation, since the wear of the friction linings occurs evenly with each braking on each Ko, ie.
    For the simultaneous adjustment of the brake pressure in the front axle, technical solutions are known in which a special valve is provided which is subjected to pressure from the rear axle. These valves require large additional
    manufacturing costs. In addition, when the brake line is reached from the rear axle in the brake line of the non-rare one, there is a very low brake rate. This braking pressure is not enough to deplete the required braking effect of the front brakes when exiting from one line.
    In order to solve this problem, the well-known valve was equipped with a costly and easily outdated control mechanism, which, when the pressure in the rear axle brake line disappears, switches the front axle brake valve of the front axle, ensuring its complete flow.
    The closest solution to the invention is a dual-circuit brake system of a car, containing a two-section pressure control device in the brake cylinders of the wheels of the front and rear axles, the first section of which with the following piston is connected to the rear axle line, in which the pressure regulator is installed, load sensitive car, and the second section with a controllable piston is connected to the front axle line, while the controllable piston is installed with the possibility of interaction with the drive element with piston units present during a failure of the rear axle 2 backbone.
    In a known device for simultaneous adjustment of the brake pressure of the front axle, a control valve is installed which has a constant gear ratio and is subjected to a controlled pressure in the rear axle brake line so that the gear ratio changes with the adjustable pressure in the rear axle brake line. At the same time, this control valve is provided with an additional control device - a switching valve, which, depending on the pressure in the rear axle brake line, is subjected to a controlled pressure from the rear axle brake line or uncontrolled pressure from the front axle in such a way that when the brakes leave the system The rear wheels brakes the front wheels continue to act.
    The purpose of the invention is the optimal distribution of brake pressure in the wheel cylinders.
    This goal is achieved by the fact that in the second section a separating ring is rigidly fixed, with the indicated ring, housing and peripheral surface of the controlled piston limited to the control chamber connected to the rear axle line behind the pressure regulator.
    In addition, in order to change the ratio of the working surfaces of the controlled pistons, an intermediate ring is installed in the second section between the separating ring and on the 1st em of the piston.
    FIG. 1 shows a diagram of a brake system with a pneumatic two-piece brake crane; in fig. 2 is a diagram of a brake installation with a hydraulic m. Double master lopMOSHbi.vi cylinder; in fig. 3 - principle scheme of a pneumatic two-section brake cylinder with elements; in fig. 4 is a schematic diagram of a hydraulic dual main brake cylinder with components.
    The tanks 1 and 2 of compressed air by pipelines 3 and 4 are connected to the inlets 5 and 6 of the two-section torm cranes 7 of the automobile’s dual-circuit braking system. The first section 1 of the brake valve 7 and its output 8 are connected via pipe 9 to the inlet 10 of the automatic pressure-sensitive pressure regulator 11, the control output 12 of which is connected to pneumatic wheel brakes
     the cylinders 13 of the rear axle through the line 14. The output 12 of the controller 1 is also connected via pipeline 15 to the connection a, provided for on the crane 7. The second section II of the crane 7 and its
    5 output 16 through line 17 is connected to pneumatically. Wheel brake cylinders 18 of the front axle.
    The braking system (Fig. 2) contains a pneumatically actuated pneumatic hydraulic device which, by means of a pneumatic tandem cylinder or pneumatic tandem amplifier, actuates a hydraulic double master cylinder (since the invention relates only to the hydraulic part of the installation, then the description pneumatic part is not presented).
    The first section I of the dual master brake cylinder 19 and its output 20 are connected via a pipe 21 to an input 22 of an automatic load-dependent hydraulic regulator 23 of a braking force or pressure, the control output 24 is connected to a rear axle hydraulic wheel brake cylinders 25 26. The output 24 of the regulator 23, in addition, is connected by a pipeline 27 to a connection c. Located on the double brake master cylinder 19.
    The second section 11 of cylinder 19 and its outlet 28 are connected via a line
    0 29 with hydraulic wheel brake cylinders 30 of the front axle.
    FIG. Figure 3 depicts a tandem tormoz crane, in which the actuator lever, using a stepped piston and a controlled relay relay, actuates two inlet and exhaust valves located in each section. It consists of a mechanical brake valve (1 section) and
    controlled by the brake pressure of the i-th section of the relay valve (2-section), which, when leaving the main line of the rear axle, can be mechanically driven by a thrust coupling.
    The inner space of the valve body 31 is divided into upper (1-brake section) and lower (II - brake section) parts of which each have valve elements for controlling the passage of pressure means between their respective inlet and outlet ports. The upper part of the housing 31 is divided into an inlet chamber 32 and two chambers 33, and 33g. brake air, and the chamber 32 is separated from the valve chamber 331, which, when the brake is not working, is closed by a combined inlet and outlet for the valve element 35. This valve element enters the retaining ring 36 at the upper end of the valve sleeve 37, which is movably located in the ring-shaped sealing gasket 38. The lower part of the spring 39 is supported on the lintel of this sealing ring, the upper end of which co-operates with the ring 36 of the sleeve 37 to press the element 35 down to the hermetic application valve seat 34.
    Through an elastic element 40 with a brake pedal is connected by kinematic locking the following step porzhn 41, which is located in the chamber 33 j of brake air with the possibility of movement, llpv; the free pedal, the piston 41 is held in the upper position by means of a spring 42 placed between the bottom of the chamber 33 I and the bottom surface of the piston 41. When moving downward, the piston 41 tightly enters element 35 and opens the connection between chamber 33 connected to the inlet 5. and camera 32, so that the working medium can flow through exit 8 (Fig. 1) to the braking force controller 11 and then to the rear axle cylinder 13.
    A control relay consisting of pistons 43 and 44 is located in the lower part of the housing 31. The piston 43 and housing 31 are limited in distribution chamber 46 and control chamber 47 separated from the second brake air chamber 48 separated by an intermediate ring 45. Both pistons 43 and 44 are arranged to move one below the other, with the piston 44 being pressed by the spring 49, which interacts with the annular surface of the piston 44, when upward, so that to the chambers 46 and 47 through the holes 50 and 5 The working medium is supplied from the chambers 33, and 33 and the brake air, the working surface 52 and the peripheral surface 53 are loaded, and the pistons 43 and 44 move as one unit.
    If the lower end of the piston 44 enters into interaction with the lower combination.
    5P. By the way 1. By the valve element 54, the inlet 55 opens; the outlet 55g is closed to connect the line 17 to the pipe 4 via inlet 6 and outlet 16. When it is created in the sea of 48, it is active H; J MObejjHHn :. U,) (}: | Nei 43 and 44 and moves them together with the Neve X as long as the opening 55 :: the exhaust outlet 55 2. does not close. Thus, this valve works / is the same as the valve 1 sec.
    A piston is provided for the valve of the 1st section. .pr1 vodprm 1st in action mechanical. while for normal operation of the valve of the i-th section, a pneumatically controlled relay relay piston is provided, which is controlled by the brake pressure of the 1st section. To control the relay piston, its control chamber is connected through the opening to the brake pressure chamber of the 1st section. When the brake pressure in the 1st section disappears after mechanical activation, at which the pedal is fully depressed, the brake pressure regulation becomes a function of the GT section and at the same time an auxiliary braking action is achieved.
    The pressure in the brake cylinders of the front axle is adjusted as follows. As a result of the separation of the working surface of the control piston, which is affected by the braking pressure, on the surface 52 p 53 there is a division of the control KaNjepbi through the ring 45 into two chambers 46 and 47. The surface 53 is acted upon by the control torus. the cerebral pressure from the outlet 12 of the regulator 11, and consequently the pressure of the brake cylinder of the rear axle; -;, while the surface 52 is subjected to the action of an unregulated brake pressure.
    The change in the magnitude of the control of the braking force of the front axle to the control of the braking force of the rear ax is influenced by the change in the magnitude of both surfaces 52 and 53 g of the Arshn 43. It is 45, the annular surface of which is also affected by the unregulated braking pressure of the 1st braking section, along with surface 52 total surface. The ratio of working surfaces can be changed by a rigidly fixed split ring 56. Therefore, any desired ratio of control of the braking force ms / cd by two axes can be achieved by mounting the ring 45 i of the ring 56 with the appropriate dimensions. The crane 7 is designed in such a way that the 45h 56 rings can be interlocked. This means that only after replacing these two parts, the ratio of working surfaces changes, this means that the sizes of the piston 43 (44) for all brake cranes with different designs remain the same, which allows It makes them in large batches and provides an easy replacement.
    According to the proposed solution, the front axle is subjected to pressure, the value of which can lie between the adjustable pressure of the front axle and the unregulated pressure of the rear axle. In the first case, the surface 52 is zero, and in the latter case, the surface 53 is zero.
    If the rear axle line is out of order and together with the total load of the corresponding working surfaces of the front axle brake line, then with full braking, the full braking pressure from the front axle brake line is maintained by mechanical actuation. This is also the case when, when mechanical control is deactivated, depending on the load of the braking force regulator, the regulator comes to zero position, despite the full load of the vehicle and under normal conditions of braking the loaded car, the necessary braking action e is achieved.
    Brake valve dual-circuit brake system works as follows.
    By activating the brake pedal, the piston 41 moves downward, thereby closing the outlet and opening the inlet. As a result, compressed air coming from tank I through pipeline 3 and inlet 5 flows from chamber 32 to chamber 33 i through outlet 8 and pipeline 9 to braking force controller 11 and further, adjusting the axle load, through line 14 to rear cylinder 13 axis.
    Pressure arises in chamber 33, under pressure 41, and simultaneously a force acts on surface 52 of pressure shaft 43 (44) through opening 50 in chamber 46. Under the action of pressure on both surfaces 52 and 53, the relay layer consisting of the portions 43 and 44 moves downward against the force of the spring 49, while the hole 55 g is closed and the hole 55 j is open. Compressed air flows from the inlet 6 through the outlet 16 into the cylinders 18 of the front axle, which are filled in accordance with the controlled pressure in the chambers 46 and 47.
    The pressure arising in the chamber 331 acts on the lower part of the pressure 41, which as a result moves against the force of the element 40 up until the forces balance on both sides of the pressure 41. In this position, the inlet and outlet are closed (the initial position of the seat 34).
    Under the action of increasing pressure in chamber 48, which, together with spring 49
    acts on the bottom of the surfaces 43 and 44, they move upward until they reach the position of the overlap, i.e., close the holes 55 and 55g.
    When leaving the main line connected to section II, the rear axle main line continues to operate according to the same principle; in the event of an exit from the trunk associated with section 1, the control of the relay is terminated. Section II valves are mechanically actuated as follows: with the brakes shown, the piston 42 is lowered. As soon as it comes into contact with the insert 57, which is rigidly connected to the piston 44, the piston 44 moves downwards during the next stroke, the opening 55 closes and the opening 55 i opens. Highway 17, despite exit from section I, continues to operate.
    The principle of operation of the above described brake valve of a two-line brake installation operating on a compressed air is also suitable for a dual-circuit or double master cylinder in a hydraulic two-trunk brake system.
    Consider the work of a two-circuit or
    J double master brake cylinder 19 (FIG. 4), housing 58 of which has ports 59 and 60 for connecting fluid tanks. If actuated on an inaccurate 61 with a cuff 62 in the direction of the working sleeve 63; (63 J, first
    0, the compensating orifice 64 is sealed with the seal sleeve 62, and the pressure chamber 65 of the 1st section is closed. The brake fluid is under pressure, as the brake fluid is applied to pressure evenly in all directions, then in the pressure chamber 66 of the I-th section by means of constrictions 63) (63g) and after the compensation opening 67 is closed by the internal cuff 68, the same ratios are transmitted pressure. At the same time
    0 brake fluid is compressed in chamber 65, feeds via working valve 69 and outlet 20 to pipe 21, and brake fluid is compressed in chamber 66, flows through operating valve 70 and outlet 28 to brake line 29.
     Porsche 63: (63 j), consisting of two parts, is made with an annular surface 71, which limits the control chamber connected via a connection in with the output 24 of the regulator 23, which regulates the braking pressure.
    The 63 pressure (63 g) acts as an unregulated pressure through the working surface 72, and an adjustable pressure through the surface 71. The change in the ratio of the regulation of the braking force of the front axle to the regulation of the braking force of the rear axle also occurs by changing the values of both surfaces 71 and 72 and replacing porshn bzg and rings 73.
    In the master cylinder, when one of the two lines fails, the working condition of the other brake line is also maintained, thereby achieving the necessary auxiliary braking action. If, for example, a leakage place is formed in the brake line connected to the 1st section, pressure may not be generated when the brake pedal is pressed in the pressure chamber 65, as the brake fluid flows out. In this case, the surface 74 presses against the surface 72 and mechanically transmits the pressure force through the working piston 63 into the pressure chamber 66. Thus, the second brake line continues to work.
     If a leak is created in the second brake line, no brake pressure arises in the pressure chamber 66. The piston 631 moves forward without resistance until the surface 75 collides with the surface 76 so that the first brake line continues to operate.
    权利要求:
    Claims (2)
    [1]
    1. A dual-circuit brake system of a car, containing a two-section pressure control device in the brake cylinders of the front and rear axle wheels, the first section of which with the next piston is connected to the rear axle line, in which the vehicle pressure regulator is installed, and the second section the controllable vehicle is connected to the front axle line, while the controllable piston is installed with the possibility of interaction with the drive element of the following drive when leaving the main line, days of the axis, characterized in that,
    0 in order to optimally distribute the brake pressure in the wheel cylinders, in the second section the separator is firmly fixed, and the indicated ring, corus and peripheral surface of the controlled piston is limited to the control gauge connected to the rear axle of the rear axle for the pressure regulator .
    [2]
    2. The system according to claim 1, characterized in that, in order to change the ratio of the working surfaces of the controlled surface, an intermediate ring is installed in the second section between the separating ring and the controlled piston.
    Information sources,
    taken into account in the examination
    1. Patent of US school No. 3904253, cl. 303/22, 1976.
    2. For the application of the Federal Republic of Germany No. 2248923, cl. B 60 T 8/22 1974 (prototype).
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    类似技术:
    公开号 | 公开日 | 专利标题
    SU738502A3|1980-05-30|Two-circuit car braking system
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    US4040673A|1977-08-09|Fluid pressure operable brake apparatus with load-compensating means for vehicles with tandem rear axles
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    US3279867A|1966-10-18|Control valve
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    US3945689A|1976-03-23|Combined load-sensing proportion and relay valve
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    同族专利:
    公开号 | 公开日
    DE2548973B1|1976-12-09|
    FR2329487A1|1977-05-27|
    YU266376A|1983-04-27|
    YU37286B|1984-08-31|
    JPS5257471A|1977-05-11|
    SE412349B|1980-03-03|
    CS209432B2|1981-12-31|
    ATA802676A|1979-03-15|
    SE7611804L|1977-05-04|
    ES452924A1|1977-11-16|
    GB1514102A|1978-06-14|
    BE847949A|1977-03-01|
    FR2329487B1|1983-07-08|
    NL185401B|1989-11-01|
    JPS5939345B2|1984-09-22|
    US4116492A|1978-09-26|
    CH602380A5|1978-07-31|
    PL109174B1|1980-05-31|
    NL185401C|1990-04-02|
    HU176042B|1980-11-28|
    NL7612142A|1977-05-05|
    AT353120B|1979-10-25|
    IT1062209B|1983-09-20|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US3183042A|1963-02-04|1965-05-11|Wagner Electric Corp|Ratio selector valve|
    DE1555112C3|1966-07-01|1974-10-10|Daimler-Benz Ag, 7000 Stuttgart|Compressed air braking system for commercial vehicles|
    DE1935537A1|1969-07-12|1971-02-11|Westinghouse Bremsen U Appbau|Brake valve for three-circuit air brake systems|
    BE755816A|1969-09-17|1971-02-15|Bendix Westinghouse Automotive|VALVE FOR DOUBLE BRAKE CIRCUIT|
    DE2156784A1|1971-11-16|1973-05-24|Daimler Benz Ag|SWITCHING DEVICE|
    IT994358B|1972-10-05|1975-10-20|Daimler Benz Ag|LOAD-DEPENDENT DOUBLE CIRCUIT BRAKE FOR VEHICLES IN PARTICULAR OMNIBUS OR SIMILAR LOAD VEHICLES|
    FR2248182B1|1973-10-18|1976-06-18|Dba|
    DE2361257C2|1973-12-08|1983-10-13|Robert Bosch Gmbh, 7000 Stuttgart|Pressure ratio valve|
    US3934942A|1974-07-22|1976-01-27|The Berg Manufacturing Company|Dual circuit brake valve|
    DE2452952C2|1974-11-08|1989-10-26|Alfred Teves Gmbh, 6000 Frankfurt, De|
    DE2458515C2|1974-12-11|1986-04-17|Alfred Teves Gmbh, 6000 Frankfurt|Brake force regulator for a dual-circuit brake system|
    US3966263A|1975-08-25|1976-06-29|The Weatherhead Company|Blend back proportioning valve for brake system|DE2825559C2|1978-06-10|1985-07-04|Robert Bosch Gmbh, 7000 Stuttgart|Dual circuit brake valve|
    DE2907426C2|1979-02-26|1988-03-03|Wabco Westinghouse Fahrzeugbremsen Gmbh, 3000 Hannover, De|
    DE2914232C2|1979-04-09|1987-11-12|Wabco Westinghouse Fahrzeugbremsen Gmbh, 3000 Hannover, De|
    US4360239A|1980-01-21|1982-11-23|Mcdonnell Douglas Corporation|Manual/auto brake valve|
    FR2482917B1|1980-05-22|1984-12-14|Citroen Sa|
    FR2486892B1|1980-07-21|1984-03-16|Kamskoe Ob Proizv|
    GB2121496B|1982-05-28|1985-06-26|Lucas Ind Plc|Improvements in dual brake valves|
    DE3439086A1|1984-10-25|1986-05-15|Wabco Westinghouse Fahrzeugbremsen GmbH, 3000 Hannover|RELAY VALVE DEVICE|
    US4679865A|1985-04-13|1987-07-14|Wabco Westinghouse Fahrzeugbremsen Gmbh|Relay valve device|
    DE19546056A1|1995-12-09|1997-06-12|Teves Gmbh Alfred|Hydraulic brake system with high pressure source and pedal operated metering valve|
    IN2013CH05978A|2013-12-20|2015-06-26|Wabco India Ltd|
    US9932025B2|2013-12-20|2018-04-03|Wabco India Limited|Pneumatic control valve|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE19752548973|DE2548973C2|1975-11-03|Dual-circuit brake system with load-dependent control for motor vehicles|
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