• 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:
    1519063 Power steering T R W Inc 31 Oct 1975 [6 Nov 1974] 45511/75 Heading B7H In a vehicle steering system comprising a steering control valve 14 manually operable to. direct fluid from a variable source 44 to a steering motor 20 via a metering device 18, a hydraulic system is provided which is responsive to the fluid pressure demand for steering by the metering mechanism to vary the fluid pressure output of the source to the metering device to effect steering. As shown in Fig. 1, actuation of control valve 14 causes fluid from conduit 72 to be ported to operating chamber 68 of motor 20 via metering device 18. Fluid discharged from chamber 78 is directed to a variable size size orifice 82 and to a flow compensator valve 30. The size or orifice 82 varies directly with the rate of rotation of the steering wheel 64. Thus the pressure signal through conduit 32 varies as a function of the size of orifice 82 and hence the compensator valve 30 varies the output of a variable swash plate pump via a motor chamber 100 according to the demand for steering fluid made by torque applied to steering wheel 64. The variable orifice 82 is preferably formed between the valve spool (152) Fig. 2A (not shown) and the valve housing and forms the subject of Specification 1,519,062. In a modification of the steering system the variable orifice (270) Fig. 5 (not shown) is provided on the pump side of metering device (18b). Alternatively, conduit means may conduct a relatively large fluid flow from the pump to the metering device (18a) Fig. 3 (not shown) and by means of constriction (200) conduct a relatively small flow to variable orifice (202).
    公开号:SU1077563A3
    申请号:SU752188499
    申请日:1975-11-06
    公开日:1984-02-29
    发明作者:Ли Рау Джим
    申请人:Трв Инк (Фирма)；
    IPC主号:
    专利说明:

    The image relates to transport engineering, in particular, to steering systems with an amplifier. A car steering system is known, having a hydraulic steering mechanism, which is hydraulically connected to a variable-capacity hydraulic pump. With a hype robakom: and with an excursion hydraulic cylinder Y | . The lack of a system is the lack of a tracking mechanism that provides a consistent action between the angle of rotation of the steering wheel and the angle of the gate of the steered wheels. Also known is a car steering system containing a variable displacement hydraulic pump mechanically connected to the car engine, an actuating hydraulic cylinder that is mechanically connected to the steering wheels of the car, a hydraulic steering mechanism whose moving hydraulic distributor is kinematically connected to the steering wheel and the metering device and is hydraulically connected by means of a pressure hydroline to the hydraulic pump, control hydroline, and cottage hydraulic pump discharge line - with ..gi.drobakom. and executive hydraulic lines - with an executive turn hydraulic cylinder 2. . A disadvantage of the known steering device is that it is not possible to change the supply of the hydraulic pump depending on the angle of rotation of the steering wheel. The purpose of the invention is to increase maneuverability by providing the possibility of changing the hydraulic pump feed depending on the steering wheel angle. This goal is achieved by the fact that the vehicle’s steering system, which contains a variable-capacity hydraulic pump, is mechanically connected to the car engine, the steering hydraulic cylinder mechanically connected to the driven wheels of the car, the hydraulic steering mechanism, movable, whose hydraulic control valve is kinematically connected to the steering wheel and the metering device, and is hydraulically connected by means of pressure hydraulic lines to the said hydraulic pump, the control hydraulic lines - to hydraulic pump feed control unit; - with hydraulic tank and executive hydraulic lines - with hydraulic actuator of rotation, equipped with an adjustable choke with a variable cross section, depending on the movement of the moving element, installed in the hydraulic line of the hydraulic distributor between the hydraulic line and the metering device, with the hydraulic line connected to the hydraulic line with the hydraulic line and the metering device, with the hydraulic line connected to the hydraulic line with the hydraulic line and the metering device, the hydraulic line connected to the hydraulic line is connected to the hydraulic line and the metering device, with the hydraulic line connected to the hydraulic line connected to the hydraulic line and the metering device, with the hydraulic line connected to the hydraulic line connected to the hydraulic line and the metering device; mentioned adjustable throttle with dosing device. Fig. 1 is a schematic representation of a vehicle steering system; Fig, 2 - hydraulic steering mechanism, a general view; Fig, 3 - the same scheme. The vehicle’s steering system includes a variable displacement hydraulic pump 1, which is hydraulically connected via hydraulic line 2 to a hydraulic steering mechanism 3. Hydraulic pump 1 is driven by engine 4-, When the steering system is in operation (FIG. 1), the working fluid from hydraulic pump 1 supplied through the metering device .o 5 to the executive hydraulic cylinder 6 of rotation through the hydraulic steering mechanism 3; Controllable wheels 7 and 8 are connected to the hydraulic cylinder. To the VC system The node 9 controls the performance of the hydraulic pump. The control unit 9 may have different forms. In the proposed embodiment, the control unit 9 includes a flow compensation valve 10. Which is driven to work with a reciprocating disk to change the performance of the hydraulic pump 1 steering, in order to reduce the load on the engine 4 and increase the service life of the hydraulic pump 1 steering control valve 10 flow affects the operation of the motor 11 by moving the inclined reciprocating disk 12 of the hydraulic steering pump 1 to the position corresponding to the minimum performance when the hydraulic steering mechanism 3 is turned on A closed or closed position, blocking the flow of fluid to or from the steering cylinder 6, is still supportive. a lower reserve pressure corresponding to the spring 13 of the flow compensation valve. The steering hydraulic pump 1 is a well-known type of axial piston hydraulic pump and includes a rotatable drum 14 having a plurality of cylinders in which the pistons 15 are slidable, the drum is connected to the input shaft 16, which is continuously rotated by the engine 4 proportional to changes in engine operating speed. When the steering hydraulic pump 1 is in the minimum performance position, the surface 17 of the swash plate 12 engages the stopper surface 18, so that the stationary working surface 19 which engages with the pistons 15 is perpendicular to the central axis of the input shaft 16 and the drum 14 When the swash plate 12 is in the minimum capacity position, the rotation of the drum. 14 input shaft 16 is not enough to force the pistons. 15 to reciprocate inside the cylinders, and the steering hydraulic pump 1 is not capable of supplying working fluid under pressure above the reduced level,
    During the movement of the piston 20 of the motor with an inclined disk to the left (FIG. 1), a relatively strong bias spring 21 rotates the inclined disk 12 from the position of the minimum capacity to the working position. This rotation causes the working surface, 19 of the inclined disk 12 to be at an acute angle The central axis of the drum 14 and the input shaft 16, therefore, rotating the drum 14 by continuously rotating the input 16 causes the piston 15 to reciprocate and release the working fluid from the hydron Sos 1 steering through a conduit; 22, The further the inclined disk 12 moves from the minimum capacity position, the further each of the pistons moves through the working stroke during each revolution of the drum 14 and the greater the flow of the working fluid of the steering hydraulic pump 1,
    When the steering wheel 23 rotates, the hydraulic steering mechanism -3 is turned on, the working fluid passes from the steering hydraulic pump 1 to the metering device 5 and from the latter to the working chamber 24 of the steering hydraulic cylinder with a speed varying directly depending on the speed of rotation of the steering wheel 23 ,
    The metering device 5 and the hydraulic steering gear 6 are interconnected. The metering device 5 preferably includes a rotor 25, which rotates relative to the stationary stator 26 at a speed varying as a function of the speed of rotation of the steering wheel 23. As this movement flows, a fluid is metered into the hydraulic cylinder 6. The steering wheel 23 is connected to the rotor through
    a hydraulic steering mechanism 3, consisting of a spool 27, which is axially driven by an input shaft 28f connected to the steering wheel 23 when the latter is rotated,
    The spool 27 is connected to the rotor 25 by means of a splined shaft 29. At the neutral position, the rotor 25 is locked against possible rotation. The spool 27 moves to a position depending on the forces applied to it from the steering shaft 28. The interaction of the spool 27 and the metering device 5 are known. When pre-rotating, steering wheel rotation of the first wheel 23
    5 additional movement of the rotor 25 causes axial movement of the steering mechanism 27 in the direction and neutral,
    When the hydraulic mechanism of the left mechanism 3 is turned on for the operating mode c (FIG. 1), the working fluid from the steering hydraulic pump is directed through the pipeline 30 through the load sensing hole 31
    5 of variable section to the metering device, which supplies the working fluid to the pipeline connected to the working chamber 24 by the hydraulic line 32 of the hydraulic cylinder 6, the size of the hole 31, made in the block (FIG. 3). and the flow rate of the working fluid to the metering device 5 varies in direct dependence on the speed of rotation of the steering wheel 23 and / or the steering load change. The metering flow of working fluid from the metering device 5 causes the piston 33 of the hydraulic cylinder 6 to move to the left ( fig. 4), as the piston moves. 33 left wheel 7
    0 and 8 rotate. And the working fluid is discharged from the chamber 34 of the hydraulic cylinder through conduit 35 to the steering mechanism 3, This working fluid passes through potassium: eyebrow
    5 anti-cavitation hole 36, which is connected to exhaust pipe 37, return feed pipe 38 is hydraulically connected to valve pressure chamber 39, pressure of working fluid through pipe 38 varies as a function of the speed of rotation of the steering wheel 23 and the demand for fluid by the dosing device 5 from variable load. Therefore, valve spool 40 moves to the left.
    (FIG. 1) under the action of the bias spring 13 and the pressure of the fluid in the chamber 39 with a force that varies in direct dependence on the change in the scientific research institute of working fluid flow. The pressure of the working fluid in the opposite chamber 41 of the valve 10 flow varies in direct dependence on changes in the discharge pressure of the hydraulic pump 1, due to the action of bias
    springs 13 the discharge pressure of the working fluid of the hydraulic pump 1 is always greater than the pressure of the working fluid in the chamber 39 by an amount corresponding to the spring 13 gain. In one of the proposed variants of the invention, the size of the spring 13 is chosen to maintain between the discharge pressure of the working fluid from the hydraulic pump 1 and pressure in chamber 39 reserve and load-balancing differential of 1.4 MPa
    When the spool-spool 40 moves to the left (FIG. 1), an outlet 42 from the drain pipe 43 is connected to a channel 44 leading to the pipe 45 and through a high pressure safety valve 46 to the pipe 47 leading to the flow valve 10. The annular groove 48 in the flow valve 10 connects the pipe 47 directly to the pipe 49 even if valve bridges 50 block the flow of working fluid from the pressure chamber 44 to the pipe 49, Since the pipe 49 is directly connected by a motor with an inclined disk, the slide 40 with the jumper 50 in the direction to the left (Fig. 1) reports the camera 51 of the motor with a drain. Of course, this allows the spring 21 to move the swashplate 12 and increase the performance of the hydraulic pump 1 steering,
    With increasing performance of the hydraulic pump 1 increases the pressure in the chamber 41 of the valve 10 flow. Excessively high pressure in the chamber 41 moves the valve 40 to the right (FIG. 1). When the hydraulic cylinder 6 has a certain predetermined operating speed corresponding to the speed at which the steering wheel 23 rotates, the metering device 5 starts and the reserve pressure is restored, the cylindrical valve lintel 50 again locks up the flow of working fluid between conduit 43 and conduit 45 to hydraulically lock the inclined-disk motor 11. I
    It is assumed that during rotation of the steering wheel at a constant speed, the operating speed of engine 4 may either increase or decrease. Since steering hydraulic pump 1 is a forced-type hydraulic pump, changing its drive speed changes the flow rate of the working fluid from the hydraulic pump through the hydraulic steering gear 3 to the steering cylinder 6. This is expressed in the pressure change in chamber 41. The detected pressure change causes the spool 40 to shift
    under the influence of either the pressure of the working fluid in the chamber 41, or the pressure in the chamber 39, moving the inclined disk 12 in the direction of changing the performance of the hydraulic pump 1 of the steering control so as to maintain the operating speed of the hydraulic cylinder constant for a given value, even if the frequency engine rotation 4.
     When the steering wheel 23 is rotated, the steering mechanism 3 is actuated. The initial rotation of the steering wheel, 23, opens the hole 31 to the value corresponding to the required speed of rotation of the steering wheel. In this case, the working fluid enters through the opening 31 both in the metering device 5 and in the pipeline 38,
    0 The hydraulic pump 1 begins to operate before the hydraulic steering mechanism 3 is opened, by applying pressure to the chamber 41 of the valve 10. The pressure in the chamber 41 is equal to the spring force 13 and.%
    5 to the pressure in chamber 39, which is retracted to the reservoir through the opening 52. If the forces acting on the spool 40 tend to move it right, then the excess force of the spring 13 and
    The Q pressure tends to move the spool to the left, while the chamber 41 communicates with the chamber 51 by reducing the performance of the hydraulic pump 1. Accordingly, before opening
    with steering gear 3 spool 40
    is in a balanced position. Research institutes, when the output pressure on one line of spool 40 is equal to the spring force, At this time, the inclined disk 12 of the hydraulic pump is in the position of the minimum capacity, maintaining the minimum reserve pressure.
    As soon as the steering mechanism 3 and hole 31 are opened,
    5, the opening 52 closes. Thus, the pressure of the working fluid is communicated through the conduit 38 to the chamber 39. This causes the movement of the spool 40 to the left and leads to a corresponding slight increase in the performance of the hydraulic pump 1 due to the fact that the camera 51 of the motor with an inclined disk communicates with the release. As the output of the hydraulic pump 1 increases, the pressure in the chamber 41 increases. Similarly, the pressure in the pipeline 38 increases, as does the pressure acting on the metering device 5.
    As soon as a pressure is established that is sufficient for steady-state
    the operating mode of the metering device 5, the valve spool 40 moves against the action of the spring 13.
    Of course, the greater the speed of the steering wheel 5a, the more
    the working fluid flowing through the metering device 5, and the more the size of the aperture 31 increases to maintain the spring pressure at an increased steering speed. As the size of the orifice 31 increases, the pressure drop in this orifice decreases and increases, the pressure in the pipeline 38. This increase in pressure is transmitted to the chamber 39 and, in order to meet this demand, the performance of the hydraulic pump 1 increases. If the capacity of the hydraulic pump 1 exceeds the requested dosage device then the pressure in the chamber 41 increases and the slide 40 moves to the right, the pressure in the chamber 51 is diverted. As a result, the performance of the hydraulic pump 1 decreases. Accordingly, the system operates to provide pressurized fluid flow as requested. In addition, the aperture 31 functions so as to maintain the pressure differential between chamber 41 and 39, equal to the resulting pressure of the spring 18. One of the proposed variants of the steering mechanism 3 is shown in FIG. 3. in the steering mechanism, various pipelines are connected, which are locked when the mechanism finds; SY in neutral or inactive mode, with the exception of pipe 38 connected to the outlet through hole 52, When shifted; to the left spool 53 (FIG. 3) for switching on the hydraulic cylinder 6, the working fluid from the supply line 30 is conducted through the valve channel 54 to the metering device 5, the metered flow of the working liquid is directed from the metering device 5 through the channel 55 to the motor power supply line 30. The pressure of the working fluid transmitted from the hydraulic cylinder b through the pipe 35 is discharged through the opening 36 to the discharge pipe 37. With the return flow pipe 38 through
    0 channel 56 is connected to the corresponding passage; The working fluid from the supply pipe 30 passes through an orifice 31 of variable size before it goes to the metering device 5 and to channel 56, leading to the return pipe 38,
    When the valve 54 is displaced to the right (Fig. 3), the working fluid under pressure is directed from pipeline 30 through channel 57 to the metering device 5, and from the latter through valve passage 14 to the pipeline 35, the working liquid, enters 5 Sch to the metering device 5,
    passes through the hole 31 of variable size. The valve channel 57 downstream of the opening 31 is connected through the valve passage 58 to the return flow pipe 38. The working fluid from the hydraulic cylinder 6 and the pipe 32 is directed through the metering opening 31 to the discharge pipe 37,
    The invention allows
    5 Turn the steering wheel to provide the flow of the working fluid to the steering from the hydraulic pump in accordance with the speed of rotation of the steering wheel.
    Q VU8, 1
    3
    35
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    57)
    ,, .., - p- -
     J L i-b ± r4.I
    37
    zg
    l1
    53
    vy
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    five
    Sh
    Yes
    FIG. 3
    权利要求:
    Claims (1)
    [1]
    VEHICLE STEERING SYSTEM containing a variable displacement hydraulic pump; mechanically connected with the car’s engine, an executive turning hydraulic cylinder, mechanically connected to the steered wheels of the car, a hydraulic steering gear., the movable element of the hydraulic distributor of which is kinematically connected to the steering wheel and the metering device and is hydraulically connected via a pressure hydraulic line to the said hydraulic pump, a control hydraulic line - with a control unit for supplying a hydraulic pump, a drain hydraulic line - with a hydraulic tank and about executive hydraulic lines - with an executive hydraulic turning indicator, characterized in that, in order to improve maneuverability by providing the possibility of changing the flow of the hydraulic pump depending on the angle of rotation of the steering wheel, it is equipped with an adjustable throttle with a variable cross-section, depending on the movement of the movable element, installed in the hydraulic distributor between the pressure hydraulic and the metering the device, and the aforementioned control line is hydraulically connected to the line connecting the adjustable throttle to the metering their device.
    SU t , 11) 77563
    类似技术:
    公开号 | 公开日 | 专利标题
    SU1077563A3|1984-02-29|Steering system of automobile vehicle
    US3996742A|1976-12-14|Fluid flow control apparatus
    US4420934A|1983-12-20|Automotive vehicle hydraulic system
    US3795107A|1974-03-05|Hydrostatic transmission and control system
    US4383412A|1983-05-17|Multiple pump load sensing system
    US4958493A|1990-09-25|Open-center steering control unit with flow amplification
    US3964262A|1976-06-22|Hydrostatic transmission control system
    US3886742A|1975-06-03|Single pump hydrostatic transmission control and supply system
    CA1072817A|1980-03-04|Pilot operated pressure compensated pump control
    US3333415A|1967-08-01|Hydraulic transmission and speed and direction control valve therefor
    US4034564A|1977-07-12|Piston pump assembly having load responsive controls
    US3375756A|1968-04-02|Multiple- or variable-speed motors notably hydraulic motors with monitoring system and its applications
    US3152445A|1964-10-13|Hydrostatic transmission
    US5620026A|1997-04-15|Fluid controller and improved backflow prevention therefor
    US5167291A|1992-12-01|Hydrostatic drive system for vehicles
    US3855792A|1974-12-24|Hydrostatic transmission drive system
    USRE34746E|1994-10-04|Open-center steering control unit with flow amplification
    US3241318A|1966-03-22|Fluid controls
    US5184691A|1993-02-09|Auxiliary power steering system
    US3708978A|1973-01-09|Regulating apparatus for axial piston machines or the like
    US3995973A|1976-12-07|Variable displacement hydraulic system
    US6769451B2|2004-08-03|Power beyond steering unit with bypass
    US3872669A|1975-03-25|Hydrostatic transmission control system
    US4334832A|1982-06-15|Constant output fluid pump
    US3485047A|1969-12-23|Hydraulic motor having speed and directional control system
    同族专利:
    公开号 | 公开日
    SE406889B|1979-03-05|
    CA1045940A|1979-01-09|
    JPS5819505B2|1983-04-18|
    LU73750A1|1976-06-11|
    FR2290339B1|1980-10-31|
    GB1519063A|1978-07-26|
    DK493475A|1976-05-07|
    ES442374A1|1977-09-01|
    IT1045500B|1980-05-10|
    US4079805A|1978-03-21|
    SE7512393L|1976-05-07|
    BE835256A|1976-03-01|
    AU501822B2|1979-06-28|
    DK142763B|1981-01-19|
    FR2290339A1|1976-06-04|
    DE2549871A1|1976-05-13|
    IE43787B1|1981-06-03|
    NL7512894A|1976-05-10|
    JPS5169837A|1976-06-16|
    PL106053B1|1979-11-30|
    IE43787L|1976-05-06|
    AU8636775A|1977-05-12|
    DE2549871C2|1989-05-11|
    BR7507261A|1976-08-03|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    RU2457971C2|2007-06-18|2012-08-10|ФОРД ГЛОБЭЛ ТЕКНОЛОДЖИЗ, ЭлЭлСи|Slide valve for steering with hydraulic booster|US2892311A|1958-01-08|1959-06-30|Deere & Co|Hydraulic apparatus|
    US2892312A|1958-01-27|1959-06-30|Deere & Co|Demand compensated hydraulic system|
    US3438200A|1967-03-31|1969-04-15|Int Harvester Co|Power steering with directional admittance and poppets|
    US3452543A|1967-11-06|1969-07-01|Trw Inc|Hydrostatic device|
    US3750405A|1971-08-16|1973-08-07|Int Harvester Co|Closed center hydraulic system|
    DE2208842C2|1972-02-25|1983-09-01|Robert Bosch Gmbh, 7000 Stuttgart|Drive of a steering device and several accessories for vehicles by a hydrostatic transmission|
    US3834278A|1972-12-15|1974-09-10|Trw Inc|Power steering system with auxiliary power capability|
    US3915253A|1974-02-15|1975-10-28|Hyster Co|Load sensing steering system|
    US4016949A|1975-11-24|1977-04-12|Allis-Chalmers Corporation|Hydrostatic load sensitive regenerative steering system|US3996742A|1976-03-04|1976-12-14|Trw Inc.|Fluid flow control apparatus|
    US4011721A|1976-04-14|1977-03-15|Eaton Corporation|Fluid control system utilizing pressure drop valve|
    IT1077304B|1976-06-23|1985-05-04|Eaton Corp|REGULATOR FOR DEVICES OPERATED BY THE PRESSURE OF A FLUID|
    JPS6217334Y2|1977-07-18|1987-05-02|
    DK466980A|1979-11-07|1981-05-08|Danfoss As|HYDROSTATIC CONTROL DEVICE|
    US4534577A|1979-11-14|1985-08-13|Howard D U|Remotely adjustable steering compensator|
    US4410193A|1979-11-14|1983-10-18|Howard D U|Remotely adjustable compensator for centering steering systems|
    DE3018792C2|1980-05-16|1983-03-31|Danfoss A/S, 6430 Nordborg|Hydrostatic control device, in particular steering device|
    DE3107915C2|1981-03-02|1985-12-05|Danfoss A/S, Nordborg|Hydraulic control device, in particular steering device|
    US4665695A|1981-03-13|1987-05-19|Trw Inc.|Hydrostatic load sense steering system|
    US4410059A|1981-04-08|1983-10-18|Nissan Motor Company, Limited|Fluid-operated control apparatus for power-assisted steering system of automotive vehicle|
    US4452041A|1981-10-23|1984-06-05|Trw Inc.|Hydrostatic steering system with delayed input torque column|
    US4454716A|1982-02-03|1984-06-19|Trw Inc.|Load sense hydrostatic vehicle steering system|
    US4481770A|1982-03-22|1984-11-13|Caterpillar Tractor Co.|Fluid system with flow compensated torque control|
    US4510751A|1982-04-22|1985-04-16|The Cessna Aircraft Company|Outlet metering load-sensing circuit|
    US4507920A|1982-05-19|1985-04-02|Trw Inc.|Steering control apparatus|
    US4576003A|1982-10-29|1986-03-18|Trw Inc.|Hybrid load-sense vehicle hydrostatic steering system|
    DE3376104D1|1982-10-29|1988-05-05|Trw Inc|Hybrid load sense vehicle hydrostatic steering system|
    US4522565A|1983-04-22|1985-06-11|Ford Motor Company|Steering gear control valve for variable displacement pump|
    WO1994004828A1|1992-08-25|1994-03-03|Hitachi Construction Machinery Co., Ltd.|Hydraulic drive unit of hydraulic working machine|
    US6598696B2|2001-12-21|2003-07-29|Visteon Global Technologies, Inc.|Device and method for purging trapped air from a vehicle steering gear housing|
    US20070137923A1|2005-12-19|2007-06-21|Dennis Kenneth J|Method and apparatus for enhancing vehicle performance|
    WO2007090231A1|2006-02-06|2007-08-16|Truck Whisperer Limited|Method and apparatus for enhancing automobile power steering performance|
    AU2007100088A4|2006-02-06|2007-03-08|Truck Whisperer Limited|Method and apparatus for enhancing car performance|
    EP2123540A1|2008-05-21|2009-11-25|Delphi Technologies, Inc.|Hydraulic power steering|
    CN106314532A|2015-06-23|2017-01-11|镇江液压股份有限公司|Composite metering type hydraulic steering unit|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    US52123674A| true| 1974-11-06|1974-11-06|
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