• 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:
    A control valve is provided which is designed to be set in place on a hydraulic circuit of a two-drum type hydraulic-actuated winch for controlling the actuation of the hook and the boom of a crane, and to be employed for actuating a hoisting-up clutch, a hoisting-down clutch, and a brake.
    公开号:SU1195923A3
    申请号:SU752177552
    申请日:1975-10-10
    公开日:1985-11-30
    发明作者:Нисида Казумори；Тоемура Акихиро；Хасимото Масами
    申请人:Кабусики Кайся Комацу Сейсакусе (Фирма)；
    IPC主号:
    专利说明:

    The invention relates to a hydraulically driven space drive and can be used, for example, to control the mechanisms of a two-drum winch lift clutch, lowering clutch and brake. The purpose of the invention is to expand the functionality. FIG. 1 is a schematic diagram of a hydraulically driven two-drum winch; in fig. 2 is a schematic diagram of the hydraulic drive of the winch in FIG. 3 is a table explaining the mode of operation of the clutch engagement; in fig. 4 - hydraulic control valve of the winch hydraulic actuator; in fig. 5 is a section A-L in FIG. 4j in FIG. 6 - time cut BB in FIG. four; in fig. 7 - the same, with a small displacement of the spool; in fig. 8 - the same, with an intermediate displacement of the spool; in fig. 9 - the same, when the slide is close to full ;, in FIG. 10, is a graph of the relationship between the spool stroke, flow rate and pressure. Distributing valve 1 (see fig. 6) contains a spool 2 installed in cavity 3. body 4 with the ability to interact with bores 5 and 6 made on the surface of the cavity 3, the first of which is connected to the pressure hydraulic line 7, and the second with a working cylinder 8, a piston 9 installed in the hammer 2 with the formation of a command chamber 10 communicated with the second bore 6, a rod 11 mounted in the cavity 3 of the housing 4, with the possibility of reciprocating movement and engagement with the lever 12 located outside the body 4 of the valve 1, ne 13, the second 14 and the third sleeve 15, sequentially installed with the possibility of sliding on the rod 11, the first 16, installed between the first 13 and second sleeve 14, the second spring 17 installed between the second 14 and the third 15 sleeve, the end plug 18, installed in the cavity 3 of the housing 4 on the side of spool 2, the third spring 19 installed between the stopper 18 and the spool 2 to interlock the connection with the first 5 and second 6 bores when the spool 2 is in neutral position 32 The initial force of the first spring 16 is equal to the initial force The second spring 17 is larger than the initial force of the third spring 19, and the stiffness of the second spring 17 is greater than the rigidity of the first spring 16, which is greater than the rigidity of the third spring 19. I The two-drum winch, which contains hydraulic control valve 1, contains a rotary actuator 20 The left shaft 21 is mounted with a low speed clutch 22, and the left shaft 23 is a high speed clutch 24. The gears 25 and 26 of the sleeves 22 and 24 are engaged with the gears 27 and 28 of the input shafts 29 and 30 of the clutches that control, respectively, to Rook and boom lifting mechanism (not shown). The shafts 29 and 30 are united by a common shaft 31, on the shafts 29 and 30 there are respectively a hook lifting clutch 32 and a boom lifting clutch 33, at the output of which there are driven transmissions with brake shafts 34 and 35. Except; Moreover, the shafts 29 and 30 are connected to the shafts 36 and 37 of the clutches, on the shafts 36 and 37 are mounted the coupling 38 lowering the hook and the coupling 39 lowering the boom, and the outputs of the couplings 38 and 39 are also connected to the brake shafts 34 and 35, on the shafts 36 and 37 are mounted respectively 40 and 41 brake hooks and arrows. The shafts 34 and 35 are kinematically connected with the drums 42 and 43 of the hook and boom, on which the cables 44 are wound. The brakes 40 and 41 are activated by the force of the springs, and are switched off by the fluid pressure at the time, the clutch 32 and 33 of the lift and the coupling 38 and 39 lowering, as well as the clutches 22 and 24 are turned on by the pressure of the fluid, and are turned off by the force of the springs. The winch hydraulic actuator (see Fig. 2) contains a pump 45, a split valve .46 for separating the flow between the power hydroline 47. And the lubricating hydroline 48. The hydrolines 47 and 48 further branch out into the hydrolines 49, 50 and 51, 52, respectively. The hydroline 49 is connected to the inlet of a multi-way valve 53 for controlling a low speed clutch 22 and a high 3
    a speed clutch 24, and a safety valve 54, the outlet of which is connected to the lubricating hydroline 48 via the overflow hydroline 55 having a cooler 56.
    Power hydrolines 50 V, point 57 are divided into power hydrolines 58 of the hook and power hydrolines 59 of the boom, with power hydrolines 58 having control valves 60, 1 and 61 connected in parallel to control the sleeves 38 and 32 of lowering and lifting the hook and brake 40 control lever hook 12.
    Power hydrolysis 59 has distribution valves 62-64 connected in parallel to control the sleeves 39 and 33 of lowering and lifting the boom and the boom brake 41 from the control lever 65.
    Lubricating hydroline 48 has a safety valve 66 to prevent the pressure in this hydraulic line from increasing and maintain it at a constant level, while the lubricant of hydroline 51 is brought into the space between the friction clutch discs 22 and 24, and the lubricating hydraulic lip 52 fits in the space between the friction clutch disc 32 , 33, 38 and 39 and brakes 40 and 41, as well as to the gears 67. Above the sleeves 22, 24, 32, 33, 38 and 39 and the brakes 40 and 41 is located a tank 68 for feeding with liquid. all hydraulic lines through auxiliary hydraulic lines 69 and 70, which prevents air from entering the hydraulic system.
    Distribution valves 60, 61, 1, 62, 64 and 63 are installed parallel to each other (see Fig. 4 and 5), and their pressure lines 71 and 72, 7 are connected by a channel. 73 and further with power hydroline 58 through opening 74 with throttle 75, and pressure hydraulic lines 76-78 - with channel 79 and further with power hydraulic line 59 through opening 80 with throttle 8
    Each of the distribution valves 60, 61, 1, 62, 64 and 63 (see Fig. 6) in the housing 4 has drain holes 82 and 83.
    The spool 2 has a groove 84 for interacting with the bores 5 and 6 of the housing 1 and the hole 85 for
    95923 4
    the camera 10 communicates with the bore 6, the sleeve 15 is held on the rod 11 by a retaining ring 86, and the sleeve 13 abuts against the shoulder 87 of this rod and into the body 4. Between the first sleeve 13 and the second sleeve 14 there is a gap S-, and between the second sleeve 14 and the third sleeve 15 - the gap Sj. The initial position. SRI spool 2 divides the bore 5 and 6.
    The winch and the control valve included in the design of its hydraulic drive work as follows.
     When the multi-way valve 53 is set to position 1 (high speed) and the control valves 1 and 61 are set to operating position, high-speed clutch 24 and hook lifting clutch 32 are turned on, and hook brake 40 is turned off. As a result, the hook drum 42 rotates, winds the cable 44 and the hook
    rises.
    Other combinations of valve positions 53 and dispensing valves define different control modes for the hook and boom. These combinations are illustrated in FIG. 3
    The operation of the distribution valve 1, having an identical structure with valves 60-64.
    When the lever 12 is in the neutral position (Fig. 6), the spool 2 closes the pressure line 7, the section of the bores 5 and 6 of the body.
    When the lever 12 is displaced to the left (see Fig. 7), the spring 19 is compressed first, and the spool 2 moves to the left until it connects the bore 5 with the bore 6. The working fluid from the hydraulic line 7 flows into the working hydroline 8
     and at the same time in the command chamber 10 and acts on the spool 2 to the right. The point in communication of bores 5 and 6 corresponds to point A in FIG. 10 and pressure P in the hydroline
    0 8. From this moment on, the pressure of the fluid coming out of the working hydraulic 8 is proportional to the change in the position of the lever 12, and the working force on this lever is equal to
    5 the sum of the force of the spring 19 and the force of the pressure on the 9
    When the lever 12 is shifted further from the position shown in FIG. 7, displacing the rod 11, the pressure in the working hydroline 8 grows and the force from the pressure on the piston 9 rises, extending to the right on the spool 2, the force on the lever 12 rises, and the springs 16 and 17 are compressed until the sleeve 13 resists sleeve 14, as shown in FIG. 8 (point 8 in FIG. 10). At this moment, the fluid pressure in the hydroline 8 corresponds to the point Pj, and the force on the lever corresponds to the point Pr in FIG. 10. Thus, the increase in the pressure of the fluid in the working hydraulic rail 8 from point A to point B {fig. 10) is determined by the relationship between the forces of the springs 16 and 17, which are equal in this area, on the one hand, and on the other hand, the sum of the efforts on the spool directed to the right, i.e. force on the piston 9 and the detachment 19. In this case, the force on the lever 12 increases smoothly and slowly and, accordingly, the pressure in the working hydroline 8 also increases smoothly and slowly, upon further movement of the lever 12 from the position shown in FIG. 8, a second spring 17 is compressed, having a higher stiffness. Consequently, the control force on the lever 12 increases sharply and the pressure of the fluid coming out of the working hydraulic line 8 also increases sharply. When the rod 11 is shifted "u l
    (Rig. 1 fits to the position shown in Fig. 9, the sleeves 13-15 abut each other, forming a kind of a single body (point C in Fig. 10). At the same time, the spool 2 moves the rod 11 to a position in which The bores 5 and 6 are connected seamlessly to each other.The pressure in the hydraulic line 8 increases sharply (point P in Fig. 10) to the response pressure of the safety valve built into the hydraulic system, and the operating force on the lever 12 also sharply increases (the РЗ point in FIG. 10) .. Since the pressure Pj at point 6 is chosen equal to the switching pressure of all the couplings, the opera The torus senses that all clutches are turned on due to the fact that the working force on lever 12 increases. Therefore, the time required to fill a part of the stroke volume of each clutch can be significantly reduced. Because the pressure corresponding to point 8 is small, the clutches will slip the small force applied to them and the brake remains on. The feeling of the varying force on the levers 12 and 65 allows the operator to determine the moments of switching on and off of the clutches and brakes, controlled by the hook and boom of the lift transport mechanism. Dp
    About - Disable x Enabled
    (rig. 3
    g
    Stf oz fgtj (gt
    65
    S3
    SI
    .so
    195923. H 53A-A 01 / S / 77 7 766 I / I / I
    (pus. 5 58 7C / 75 72 73 ill / I S-5 7 W - 5 S3 13 102 8 6 55 y 77
    . (put.S 7J 7ff e 7 73 5. Ill / 17 3 Г6 ft t f383 Yu
    12 13
    权利要求:
    Claims (1)
    [1]
    DISTRIBUTING VALVE containing a spool installed in the body cavity with the possibility of interacting with bores made on the surface of the cavity, the first of which is connected to the pressure hydraulic line, and the second to the working hydraulic line, the piston installed in the spool with the formation of the command chamber communicated with the second bore, the rod installed * in the body cavity with the possibility of reciprocating movement and interaction with the lever located outside the valve body, the first, second and third bushings, after thoroughly installed with the possibility of sliding on the rod, the first spring installed between the first and second bushings, the second spring installed between the second and third bushings, the end plug installed in the housing cavity from the spool side, the third spring installed between the plug and the spool to interrupt communication between the first and second bores when the spool is in the neutral position, cast in that, in order to expand the functionality, the initial force of the first spring is equal to then initial force of the second spring, and more than a third of the initial force of the spring and the second spring stiffness greater than the first spring rate, which is greater than the third spring constant.
    类似技术:
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    US3729171A|1973-04-24|Reversible towing winch and method for operating same
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    US5083646A|1992-01-28|Hydraulic device for operating a clutch in an industrial vehicle
    US3417845A|1968-12-24|Actuating system for multi-ratio transmission
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    US4574931A|1986-03-11|Minimum purge volume hydraulic clutch actuator
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    GB697088A|1953-09-16|Improvements in or relating to hydraulic power transmissions for conveying continuous rotary motion
    US3336820A|1967-08-22|Power transmission
    同族专利:
    公开号 | 公开日
    JPS5143229A|1976-04-13|
    JPS5824805B2|1983-05-24|
    US3990352A|1976-11-09|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US3106135A|1961-07-13|1963-10-08|New York Air Brake Co|Hydraulic system|
    US3473566A|1968-04-19|1969-10-21|Clark Equipment Co|Control valve|
    DE1939293A1|1969-08-01|1971-02-11|Kracht Pumpen Motoren|Pressure regulator|
    JPS4864021U|1971-11-22|1973-08-14|
    JPS5335282B2|1972-03-27|1978-09-26|
    US3895703A|1973-10-26|1975-07-22|Caterpillar Tractor Co|Combined steering clutch and brake control for crawler tractors|DE2716495C2|1977-04-14|1979-03-01|Wabco Westinghouse Gmbh, 3000 Hannover|Pressure control valve|
    JPS6218322Y2|1978-03-25|1987-05-12|
    US4417833A|1979-12-04|1983-11-29|Iscar Ltd.|Rotary slot cutting tools|
    US4369677A|1980-07-03|1983-01-25|Ford Motor Company|Transmission throttle pressure regulator assembly|
    US4367763A|1981-03-09|1983-01-11|Glen Brand|Four-way directional valve|
    DE3219150C3|1982-05-21|1991-06-13|Karl Zinner|PUNCHING TOOL WITH SELF-CLAMPING INSERT|
    US4498847A|1982-06-29|1985-02-12|Kabushiki Kaisha Komatsu Seisakusho|Control system for variable displacement hydraulic pumps|
    US4576200A|1985-03-26|1986-03-18|Applied Power Inc.|Hydraulic pressure reducing control valve|
    US4865176A|1988-02-26|1989-09-12|Caterpillar Inc.|Modulating inching valve with automatic pressure control|
    FR2636695B1|1988-08-25|1993-04-30|Renault Vehicules Ind|PNEUMATIC CLUTCH CONTROL DEVICE|
    EP0939712A1|1996-11-22|1999-09-08|Svendborg Brakes A/S|A hydraulic braking system|
    US6443424B1|2000-05-19|2002-09-03|Atlas Polar Company Limited|Clutch arm centering device|
    WO2005064187A1|2003-12-09|2005-07-14|Gkn Driveline International Gmbh|Hydraulic system for two multiplate clutches|
    US7631591B2|2006-11-21|2009-12-15|Clark Equipment Company|Two stage spool centering mechanism|
    CN102278331A|2011-06-22|2011-12-14|徐州徐工随车起重机有限公司|Multi-way directional valve for lorry-mounted crane and control method thereof|
    CN102797722B|2012-08-29|2014-10-15|电子科技大学|Hydraulic reversing valve with axially moving and rotating functions|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    JP49116130A|JPS5824805B2|1974-10-11|1974-10-11|
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