WO2018196393A1 - 一种用于带式输送机重载启动的液粘调速装置 - Google Patents

一种用于带式输送机重载启动的液粘调速装置 Download PDF

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Publication number
WO2018196393A1
WO2018196393A1 PCT/CN2017/115553 CN2017115553W WO2018196393A1 WO 2018196393 A1 WO2018196393 A1 WO 2018196393A1 CN 2017115553 W CN2017115553 W CN 2017115553W WO 2018196393 A1 WO2018196393 A1 WO 2018196393A1
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WIPO (PCT)
Prior art keywords
output shaft
oil
hole
valve core
cylinder
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PCT/CN2017/115553
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English (en)
French (fr)
Inventor
孟庆睿
江帆
田祖织
赵呈昊
张新
Original Assignee
中国矿业大学
徐州秩润矿山设备科技有限公司
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Application filed by 中国矿业大学, 徐州秩润矿山设备科技有限公司 filed Critical 中国矿业大学
Priority to US16/095,242 priority Critical patent/US10935084B2/en
Priority to CA3020430A priority patent/CA3020430C/en
Priority to AU2017408803A priority patent/AU2017408803B2/en
Publication of WO2018196393A1 publication Critical patent/WO2018196393A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types
    • F16D25/123—Details not specific to one of the before-mentioned types in view of cooling and lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/28—Automatic clutches actuated by fluid pressure
    • F16D43/284—Automatic clutches actuated by fluid pressure controlled by angular speed
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
    • B65G23/00—Driving gear for endless conveyors; Belt- or chain-tensioning arrangements
    • B65G23/24—Gearing between driving motor and belt- or chain-engaging elements
    • B65G23/26—Applications of clutches or brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/30—Systems of a plurality of automatic clutches

Definitions

  • the invention relates to the technical field of belt conveyor starting process control, in particular to a liquid viscosity speed regulating device for heavy-duty starting of a belt conveyor.
  • the liquid viscosity speed regulating clutch is used for the start process control of the belt conveyor. It can control the belt conveyor to complete the starting process according to the given speed curve, reduce the dynamic stress of the belt conveyor during the starting process, and prolong the service life. At the same time, the speed can be realized during the running process to save energy and reduce consumption.
  • the starting torque of the liquid viscosity speed regulating clutch is selected according to the rated load of the belt conveyor. However, since the belt conveyor is often started under overload conditions, the selected liquid viscosity speed regulating clutch often cannot meet the requirements; if directly selected
  • the high-torque liquid-adhesive speed-adjusting clutch has difficulty in starting the speed by adjusting the torque of the speed-regulating clutch during normal operation.
  • the object of the present invention is to overcome the deficiencies in the prior art, to provide a large starting torque under full load or even overload conditions to achieve a reliable smooth start, and to provide a suitably small torque during smooth operation, which is convenient.
  • Speed control at the same time has a compact structure, stable operation, low cost, easy maintenance of liquid viscosity speed control device.
  • Liquid viscosity speed regulating device for heavy-duty starting of belt conveyor, comprising input shaft, inner friction plate group, outer friction plate group, inner piston, outer piston, oil inlet valve core, oil return valve core, output shaft ;
  • the input shaft end plate is fixedly coupled with the annular protrusion in the middle of the input shaft through the bolt VIII, and is fixedly coupled with the input shaft spline cylinder through the bolt VI; the internal spline of the input shaft spline cylinder and the outer friction plate in the inner friction plate group
  • the spline is formed by the spline, and the external spline of the input shaft spline cylinder and the inner friction plate of the outer friction plate group are dynamically coupled by the spline; the inner friction plate of the inner friction plate group is larger than the left end of the output shaft through the spline and the output shaft
  • the outer spline of the diameter cylinder forms a dynamic coupling, and the outer friction plate in the outer friction plate group is dynamically coupled with the inner spline of the output shaft spline cylinder through the spline; the outer baffle passes through the bolt I and the output shaft spline cylinder
  • the left end surface is fixedly coupled; the output shaft end plate
  • the output shaft control plate has a radial oil hole on the inner cylindrical surface, and a radial hole I is opened in the outer cylindrical surface of the output shaft control plate in parallel with the radial oil hole, and the oil inlet valve is installed in the radial hole I a transverse oil hole is formed in each of the inner and outer annular grooves of the output shaft control plate, so that the radial oil hole communicates with the two annular grooves through the radial hole I; the inlet valve is installed at the top of the inlet valve core
  • the core spring, the spring pressure plate I is fixedly coupled with the output shaft control plate by the bolt III, and presses the inlet valve core spring to the top of the inlet valve core; the diameter of the top of the inlet valve core is smaller than the diameter of the radial hole I, so that the radial oil hole With the output shaft outside the control board
  • the annular groove communicates; the bottom of the inlet valve core seals the radial oil hole to the transverse oil hole of the annular groove in the
  • a radial hole II having the same size as the radial hole I is formed on the output shaft control plate and the radial hole I is symmetric with respect to the output shaft axis, and a return valve core is installed in the radial hole II;
  • the oil return valve core The top end is equipped with a return valve spool spring, and the spring pressure plate II is fixedly coupled with the output shaft control plate through the bolt IV, and the oil return valve core spring is pressed against the top end of the oil return valve core; the inner shaft oil return hole is opened on the output shaft control plate.
  • the oil return valve core has two upper and lower annular grooves
  • the lower annular groove of the oil return valve core causes the inner annular groove of the output shaft control plate to communicate with the outer side of the output shaft control plate through the inner oil cylinder oil return hole B;
  • the annular groove on the oil return valve core is slightly lower than the outer oil cylinder return oil hole C,
  • the cylinder at the upper end of the annular groove on the oil return valve spool prevents the outer annular groove of the output shaft control plate from communicating with the outer side of the output shaft control plate through the outer cylinder oil return hole C.
  • the output shaft is supported by a bearing III and a bearing IV, and the bearing III and the bearing IV are installed in the right bearing housing;
  • the output shaft is provided with a pressure oil inlet hole A, which is in communication with the radial oil hole of the output shaft control board;
  • the input shaft is provided with an inner friction plate group lubricating oil inlet hole D and an outer friction plate group lubricating oil inlet hole E.
  • the liquid viscosity adjusting device further includes a housing installed between the left bearing housing and the right bearing housing, and the inner friction plate group and the outer friction plate group are mounted in the housing.
  • the input shaft is supported by a bearing I and a bearing II, the bearing I is mounted in the left bearing housing, and the bearing II is mounted in the inner hole of the output shaft end disc.
  • the liquid viscosity speed regulating device of the invention is provided with an inner friction plate combined with an outer friction plate group.
  • the outer friction plate group works, and can provide a large torque to complete the starting process against static friction; the torque required for normal operation If the outer friction plate is open, the inner friction plate group starts to work, and the inner friction plate group provides less torque, which is sensitive to torque adjustment and convenient for speed regulation of the device;
  • the liquid viscosity speed regulating device of the invention has compact structure, reliable performance, low cost and wide practicality.
  • Figure 1 is a schematic view of the structure of the present invention
  • the liquid viscosity adjusting device of the present invention mainly comprises an input shaft 1, an inner friction plate group 7, an outer friction plate group 12, and an inner portion.
  • the piston 21, the outer piston 15, the oil inlet valve core 20, the oil return valve core 27, the output shaft 25, and the like are composed. among them:
  • the input shaft 1 is supported by a bearing I3 and a bearing II5, the bearing I3 is mounted in the left bearing housing 2, and the bearing II5 is mounted in the inner bore of the output shaft end disc 34; the input shaft end disc 6 is passed through a bolt VIII35 and a circle in the middle of the input shaft 1
  • the ring protrusions are fixedly coupled and fixedly coupled to the input shaft spline cylinder 8 by bolts VI32.
  • the inner spline of the input shaft spline cylinder 8 and the outer friction plate of the inner friction plate group 7 are dynamically coupled by a spline, and the outer spline of the input shaft spline cylinder 8 and the inner friction plate of the outer friction plate group 12 pass.
  • the spline forms a dynamic coupling;
  • the inner friction plate in the inner friction plate group 7 is movably coupled to the outer spline of the large diameter cylinder at the left end of the output shaft 25 by a spline, and the outer friction plate in the outer friction plate group 12 is splined and
  • the inner spline of the output shaft spline cylinder 11 forms a dynamic coupling;
  • the outer baffle 9 is fixedly coupled to the left end surface of the output shaft spline cylinder 11 by the bolt I10;
  • the output shaft end disc 34 passes the bolt VII33 and the cylinder at the left end of the output shaft 25.
  • the fixed coupling; the output shaft spline cylinder 11 and the output shaft control panel 19 are fixedly coupled by bolts II14.
  • the left end surface of the output shaft control board 19 has an annular groove near the outer cylindrical surface and the inner hole area, and the outer piston 15 and the inner piston 21 are respectively installed in the two annular grooves;
  • the right end face of the output shaft spline cylinder 11 has a circle
  • the hole, the outer piston spring 13 is installed in the circular hole, the right end surface of the outer piston spring 13 acts on the end surface of the outer piston 15;
  • the left end of the output shaft 25 has a round hole at the right end surface of the large diameter cylinder near the outer cylindrical surface, and the inner piston spring 22 is installed In the circular hole, the right end surface of the inner piston spring 22 acts on the end surface of the inner piston 21;
  • the output shaft control plate 19 is fixedly coupled to the large diameter cylinder at the left end of the output shaft 25 by a bolt V31.
  • the output shaft control plate 19 has a radial oil hole 36 formed in the inner cylindrical surface, and a radial hole I37 is opened in the outer cylindrical surface of the output shaft control plate 19 in parallel with the radial oil hole, and two of the output shaft control plate 19 are A transverse oil hole 38 is defined in each of the annular grooves, so that the radial oil hole 36 communicates with the annular groove through the radial hole I37, and the inlet valve core 20 is installed in the opened radial hole I37, and the oil inlet valve core
  • the top end of the 20 is equipped with an inlet valve core spring 18, and the spring pressure plate I17 is fixedly coupled with the output shaft control plate 19 through the bolt III16, and the inlet valve core spring 18 is pressed against the top end of the inlet valve core 20;
  • Small, the radial oil hole 36 communicates with the annular groove near the outer cylindrical surface of the output shaft control plate 19; the bottom end of the inlet valve core 20 seals the radial oil hole 36 to the annular groove near
  • a radial hole II39 of the same size is opened at an axisymmetric position parallel to the radial oil hole and close to the radial oil hole radial hole, and the oil return valve core 27 is installed in the radial hole II39, back
  • the top end of the oil valve core 27 is provided with a return valve core spring 28, and the spring pressure plate II30 is fixedly coupled with the output shaft control plate 19 through the bolt IV29, and the oil return valve core spring 28 is pressed against the top end of the oil return valve core 27, and is controlled by the output shaft.
  • the two annular grooves of the plate 19 traverse the radial hole to open the inner cylinder return hole B and the outer cylinder return hole C; the return valve core 27 has two annular grooves near the top end and the lower end, and the oil return valve core
  • the lower end annular groove allows the inner annular groove of the output shaft control plate 19 to communicate with the outer side of the output shaft control plate 19 through the inner cylinder return hole B, and the annular groove at the top end of the return valve core 27 is slightly lower than the outer cylinder return hole C
  • the cylinder at the upper end of the annular groove at the top end of the oil return valve core 27 prevents the outer annular groove of the output shaft control plate 19 from communicating with the outside of the output shaft control plate 19 through the outer cylinder oil return hole C.
  • the output shaft 25 is supported by a bearing III23 and a bearing IV24, and the bearing III23 and the bearing IV24 are mounted in the right bearing housing 26; the output shaft 25 is provided with a pressurized oil inlet hole A, which communicates with a radial oil hole of the output shaft control plate 19;
  • the shaft 1 is provided with an inner friction plate group lubricating oil inlet hole D and an outer friction plate group lubricating oil inlet hole E.
  • the housing 4 is mounted between the left bearing housing 2 and the right bearing housing 26, and the inner friction plate group 7, the outer friction plate group 12, and the like are all mounted in the housing 4.
  • the input shaft 1 starts to rotate under the action of the external motor, the pressure oil inlet hole A is connected to the pressure oil, the inner friction plate group lubricating oil inlet hole D and the outer friction plate group lubricating oil inlet hole E are all introduced.
  • the output shaft 25 is provided to start outputting the starting torque, and the magnitude of the starting torque is controlled by adjusting the pressure of the pressure oil entering the pressure oil inlet hole A; at this time, the oil return valve core 27 acts on the oil return spool spring 28 Next, cut off the oil return passage of the outer cylinder.
  • the output shaft speed is increased to the rated speed.
  • the inlet valve core 20 is compressed and the oil valve core spring 18 is moved outward to cut off the oil inlet passage of the outer cylinder, and the oil inlet passage of the inner cylinder is opened.
  • the pressure oil enters the inner cylinder, pushes the inner piston 21 against the inner friction plate group 7, and the inner friction plate group 7 starts to engage to provide the torque required for the output shaft 25.
  • the return oil valve core 27 is compressed back to the oil valve under the centrifugal force.
  • the core spring 28 moves outward, opens the oil return passage of the outer cylinder, and cuts off the oil return passage of the inner cylinder. That is, the torque is supplied by the inner friction plate group 7 during normal operation.
  • the outer friction plate group 12 has a large diameter, the large torque required for starting can be provided to overcome the static friction to complete the starting process; and the inner friction plate group 7 has a small diameter, which can provide the torque required for normal operation, and is convenient. Speed adjustment during operation.
  • the liquid viscosity adjusting device of the present invention can automatically switch the engagement state of the outer friction plate group 12 and the inner friction plate group 7 according to the operating speed of the output shaft 25, and provide the required torque, which can satisfy the heavy load starting condition such as full load overload.
  • the demand is compact, reliable, low cost, and has a wide range of practicalities.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
  • General Details Of Gearings (AREA)

Abstract

一种用于带式输送机重载起动的液粘调速装置。输入轴（1）与输出轴（25）通过花键筒（8）、内摩擦片组（7）、外摩擦片组（12）相联接，内、外摩擦片组（7、12）分别由内油缸和外油缸控制，而内油缸和外油缸的进油与回油由进油阀芯（20）和回油阀芯（27）自动控制。起动时，压力油进入外油缸，推动外摩擦片组（12）接合，提供输出轴（25）所需要的扭矩；起动完成后，输出轴（25）转速升高，在离心力作用下，进油阀芯（20）和回油阀芯（27）外移，压力油进入内油缸，推动内摩擦片组（7）接合，提供输出轴（25）所需的扭矩，同时外油缸回油。即起动时由外摩擦片组（12）提供起动所需的大扭矩，正常运行时由内摩擦片组（7）提供较小的扭矩。实现了起动和正常运行所需的不同扭矩的自动切换，且结构紧凑、性能可靠、造价低，具有广泛的实用性。

Description

一种用于带式输送机重载启动的液粘调速装置 技术领域
本发明涉及带式输送机起动过程控制技术领域，具体涉及一种用于带式输送机重载起动的液粘调速装置。
背景技术
液粘调速离合器用于带式输送机起动过程控制，能够控制带式输送机按给定的速度曲线完成起动过程，减小带式输送机在起动过程中所承受的动应力，延长使用寿命；同时在运行过程中可实现调速，实现节能降耗。通常液粘调速离合器的起动扭矩按带式输送机的额定载荷选取，但由于带式输送机经常在超载的工况下起动，因此选取的液粘调速离合器经常不能满足要求；如果直接选取大扭矩的液粘调速离合器，虽然起动过程没有问题，但在正常运行时通过调节调速离合器的扭矩来实现调速比较困难。
发明内容
本发明的目的是克服已有技术中的不足之处，提供一种能在满载甚至超载工况下提供大的起动扭矩实现可靠的平稳起动，又能在平稳运行时提供适当小的扭矩，方便调速控制，同时具有结构紧凑、运转平稳、造价低、维护方便的液粘调速装置。
为实现上述目的本发明采用如下技术方案：
一种用于带式输送机重载起动的液粘调速装置，包括输入轴、内摩擦片组、外摩擦片组、内活塞、外活塞、进油阀芯、回油阀芯、输出轴；
输入轴端盘通过螺栓VIII与输入轴中部的圆环凸起固定联接，通过螺栓VI与输入轴花键筒固定联接；输入轴花键筒的内花键与内摩擦片组中的外摩擦片通过花键形成动联接，输入轴花键筒的外花键与外摩擦片组中的内摩擦片通过花键形成动联接；内摩擦片组中的内摩擦片通过花键与输出轴左端大直径圆筒的外花键形成动联接，外摩擦片组中的外摩擦片通过花键与输出轴花键筒的内花键形成动联接；外挡板通过螺栓I与输出轴花键筒的左端面固定联接；输出轴端盘通过螺栓VII与输出轴左端的圆筒固定联接；输出轴花键筒与输出轴控制板通过螺栓II固定联接；输出轴控制板左端面靠近外圆柱面和靠近内孔区域分别开有外环形槽和内环形槽，外活塞和内活塞分别安装在外环形槽和内环形槽内；输出轴花键筒右侧端面开有圆孔，外活塞弹簧装在圆孔内，外活塞弹簧右端面作用在外活塞端面；输出轴左端大直径圆筒右侧端面靠近外圆柱面处开有圆孔，内活塞弹簧安装在圆孔内，内活塞弹簧右端面作用在内活塞端面；输出轴控制板通过螺栓V与输出轴左端的大直径圆筒固定联接；
输出轴控制板在内圆柱表面开有一径向油孔，在输出轴控制板外圆柱面与该径向油孔平行位置开有一径向孔I，所述径向孔I内安装有进油阀芯；在输出轴控制板的内外两个环形槽处各开有一横向油孔，使径向油孔横穿过径向孔I与两个环形槽相通；进油阀芯顶端安装有进油阀芯弹簧，弹簧压板I通过螺栓III与输出轴控制板固定联接，把进油阀芯弹簧压在进油阀芯顶端；进油阀芯顶部直径小于径向孔I的直径，使径向油孔与输出轴控制板外 环形槽相通；进油阀芯底部封住径向油孔通往输出轴控制板内环形槽的横向油孔；
输出轴控制板上与径向孔I关于输出轴轴对称的位置开有与径向孔I同样大小的径向孔II，径向孔II内安装有回油阀芯；所述回油阀芯的顶端安装有回油阀芯弹簧，弹簧压板II通过螺栓IV与输出轴控制板固定联接，把回油阀芯弹簧压在回油阀芯顶端；输出轴控制板上开有内油缸回油孔B和外油缸回油孔C，所述内油缸回油孔B和外油缸回油孔C分别横穿内外两个环形槽和径向孔II；回油阀芯上开有上下两个环形槽，回油阀芯的下环形槽使输出轴控制板的内环形槽通过内油缸回油孔B与输出轴控制板外侧相通；回油阀芯上环形槽略低于外油缸回油孔C，回油阀芯上环形槽上端的圆柱使输出轴控制板的外环形槽不能通过外油缸回油孔C与输出轴控制板外侧相通。
进一步的：所述输出轴由轴承III和轴承IV支撑，轴承III和轴承IV安装在右轴承座内；输出轴开有压力油进油孔A，与输出轴控制板的径向油孔相通；输入轴开有内摩擦片组润滑油进油孔D和外摩擦片组润滑油进油孔E。
进一步的：所述液粘调速装置还包括壳体，所述壳体安装在左轴承座和右轴承座之间，内摩擦片组、外摩擦片组等均安装在壳体内。
进一步的：所述输入轴通过轴承I和轴承II支撑，轴承I安装在左轴承座内，轴承II安装在输出轴端盘的内孔中。
本发明的有益效果为：
1、本发明的液粘调速装置设有内摩擦片组合外摩擦片组，设备起动时，外摩擦片组工作，可以提供大扭矩使设备克服静摩擦力完成起动过程；正常运行时需要的扭矩较小，则外摩擦片组分开，内摩擦片组开始工作，且内摩擦片组的提供的扭矩较小，对扭矩调节反映灵敏，方便于设备的调速；
2、进油阀芯和回油阀芯随转速的升高在离心力作用下外移，使外油缸内的压力油外泄同时使压力油进入内油缸，实现外摩擦片组和内摩擦片组工作的自动切换；
3、本发明的液粘调速装置结构紧凑、性能可靠、造价低，具有广泛的实用性。
附图说明
图1为本发明的结构简图；
图中标号：1-输入轴，2-左轴承座，3-轴承I，4-壳体，5-轴承II，6-输入轴端盘，7-内摩擦片组，8-输入轴花键筒，9-外挡板，10-螺栓I，11-输出轴花键筒，12-外摩擦片组，13-外活塞弹簧，14-螺栓II，15-外活塞，16-螺栓III，17-弹簧压板I，18-进油阀芯弹簧，19-输出轴控制板，20-进油阀芯，21-内活塞，22-内活塞弹簧，23-轴承III，24-轴承IV，25-输出轴，26-右轴承座，27-回油阀芯，28-回油阀芯弹簧，29-螺栓IV，30-弹簧压板II，31-螺栓V，32-螺栓VI，33-螺栓VII，34-输出轴端盘，35-螺栓VIII，36-径向油孔，37-径向孔I，38-横向油孔，39-径向孔II，A-压力油进油孔，B-内油缸回油孔，C-外油缸回油孔，D-内摩擦片组润滑油进油孔，E-外摩擦片组润滑油进油孔
具体实施方式
下面结合附图对本发明进一步说明。
图1所示，本发明的液粘调速装置主要由输入轴1、内摩擦片组7、外摩擦片组12、内 活塞21、外活塞15、进油阀芯20、回油阀芯27、输出轴25等组成。其中：
输入轴1通过轴承I3和轴承II5支撑，轴承I3安装在左轴承座2内，轴承II5安装在输出轴端盘34的内孔中；输入轴端盘6通过螺栓VIII35与输入轴1中部的圆环凸起固定联接，通过螺栓VI32与输入轴花键筒8固定联接。
输入轴花键筒8的内花键与内摩擦片组7中的外摩擦片通过花键形成动联接，输入轴花键筒8的外花键与外摩擦片组12中的内摩擦片通过花键形成动联接；内摩擦片组7中的内摩擦片通过花键与输出轴25左端大直径圆筒的外花键形成动联接，外摩擦片组12中的外摩擦片通过花键与输出轴花键筒11的内花键形成动联接；外挡板9通过螺栓I10与输出轴花键筒11的左端面固定联接；输出轴端盘34通过螺栓VII33与输出轴25左端的圆筒固定联接；输出轴花键筒11与输出轴控制板19通过螺栓II14固定联接。
输出轴控制板19左端面靠近外圆柱面和靠近内孔区域均开有环形槽，外活塞15和内活塞21分别安装在两个环形槽内；输出轴花键筒11右侧端面开有圆孔，外活塞弹簧13装在圆孔内，外活塞弹簧13右端面作用在外活塞15端面；输出轴25左端大直径圆筒右侧端面靠近外圆柱面处开有圆孔，内活塞弹簧22安装在圆孔内，内活塞弹簧22右端面作用在内活塞21端面；输出轴控制板19通过螺栓V31与输出轴25左端的大直径圆筒固定联接。
输出轴控制板19在内圆柱表面开有一径向油孔36，在输出轴控制板19外圆柱面与该径向油孔平行位置开有一径向孔I37，在输出轴控制板19的两个环形槽处各开有一横向油孔38，使径向油孔36横穿过径向孔I37与环形槽分别相通，进油阀芯20安装在所开的径向孔I37内，进油阀芯20顶端安装有进油阀芯弹簧18，弹簧压板I17通过螺栓III16与输出轴控制板19固定联接，把进油阀芯弹簧18压在进油阀芯20顶端；进油阀芯20顶端直径较小，使径向油孔36与靠近输出轴控制板19外圆柱面的环形槽相通；进油阀芯20底端封住径向油孔36通往靠近输出轴控制板19内孔的环形槽的横向油孔38。
输出轴控制板19上在与径向油孔平行且靠近径向油孔径向孔的轴对称位置开有同样大小的径向孔II39，回油阀芯27安装在该径向孔II39内，回油阀芯27的顶端安装有回油阀芯弹簧28，弹簧压板II30通过螺栓IV29与输出轴控制板19固定联接，把回油阀芯弹簧28压在回油阀芯27顶端，通过输出轴控制板19的两个环形槽横穿该径向孔开有内油缸回油孔B和外油缸回油孔C；回油阀芯27靠近顶端和低端开有两个环形槽，回油阀芯27低端的环形槽使输出轴控制板19的内环形槽通过内油缸回油孔B与输出轴控制板19外侧相通，回油阀芯27顶端的环形槽略低于外油缸回油孔C，回油阀芯27顶端的环形槽上端的圆柱使输出轴控制板19的外环形槽不能通过外油缸回油孔C与输出轴控制板19外侧相通。
输出轴25由轴承III23和轴承IV24支撑，轴承III23和轴承IV24安装在右轴承座26内；输出轴25开有压力油进油孔A，与输出轴控制板19的径向油孔相通；输入轴1开有内摩擦片组润滑油进油孔D和外摩擦片组润滑油进油孔E。壳体4安装在左轴承座2和右轴承座26之间，内摩擦片组7、外摩擦片组12等均安装在壳体4内。
开始起动时，输入轴1在外部电机带动下开始转动，压力油进油孔A通入压力油，内摩擦片组润滑油进油孔D和外摩擦片组润滑油进油孔E均通入润滑油；进油阀芯20在进油阀芯弹簧18作用下，使由压力油进油孔A进入的压力油进入外油缸，作用在外活塞15上，外活塞15推动外摩擦片组12开始接合，提供输出轴25开始输出起动扭矩，起动扭矩的大小通过调节压力油进油孔A进入的压力油的压力来控制；此时回油阀芯27在回油阀芯弹簧28作用 下，切断外油缸的回油通路。
起动过程完成，输出轴的转速升高至额定转速，在离心力作用下进油阀芯20压缩进油阀芯弹簧18外移，切断外油缸的进油通路，而内油缸的进油通路打开，压力油进入内油缸，推动内活塞21压向内摩擦片组7，内摩擦片组7开始接合，提供输出轴25所需的扭矩；同时，在离心力作用下回油阀芯27压缩回油阀芯弹簧28外移，打开外油缸的回油通路，切断内油缸的回油通路。即正常运行时由内摩擦片组7提供扭矩。
由于外摩擦片组12直径较大，可提供起动时所需的大扭矩，以克服静摩擦力完成起动过程；而内摩擦片组7直径较小，能提供正常运行所需的扭矩即可，方便于运行过程中的速度调节。
本发明的液粘调速装置能根据输出轴25的运行速度自动切换外摩擦片组12和内摩擦片组7的接合状态，提供所需的扭矩，能满足满载荷超载等重载起动工况的需求，且结构紧凑、性能可靠、造价低，具有广泛的实用性。
以上所述仅是本发明的优选实施方式，应当指出：对于本技术领域的普通技术人员来说，在不脱离本发明原理的前提下，还可以做出若干改进和润饰，这些改进和润饰也应视为本发明的保护范围。

Claims (4)

  1. 一种用于带式输送机重载起动的液粘调速装置，包括输入轴(1)、内摩擦片组(7)、外摩擦片组(12)、内活塞(21)、外活塞(15)、进油阀芯(20)、回油阀芯(27)、输出轴(25)；
    其特征在于：输入轴端盘(6)与输入轴(1)中部的圆环凸起固定联接，与输入轴花键筒(8)固定联接；输入轴花键筒(8)的内花键与内摩擦片组(7)中的外摩擦片通过花键形成动联接，输入轴花键筒(8)的外花键与外摩擦片组(12)中的内摩擦片通过花键形成动联接；内摩擦片组(7)中的内摩擦片通过花键与输出轴(25)左端大直径圆筒的外花键形成动联接，外摩擦片组(12)中的外摩擦片通过花键与输出轴花键筒(11)的内花键形成动联接；外挡板(9)与输出轴花键筒(11)的左端面固定联接；输出轴端盘(34)与输出轴(25)左端的圆筒固定联接；输出轴花键筒(11)与输出轴控制板(19)固定联接；输出轴控制板(19)左端面靠近外圆柱面和靠近内孔区域分别开有外环形槽和内环形槽，外活塞(15)和内活塞(21)分别安装在外环形槽和内环形槽内；输出轴花键筒(11)右侧端面开有圆孔，外活塞弹簧(13)装在圆孔内，外活塞弹簧(13)右端面作用在外活塞(15)端面；输出轴(25)左端大直径圆筒右侧端面靠近外圆柱面处开有圆孔，内活塞弹簧(22)安装在圆孔内，内活塞弹簧(22)右端面作用在内活塞(21)端面；输出轴控制板(19)与输出轴(25)左端的大直径圆筒固定联接；
    输出轴控制板(19)在内圆柱表面开有一径向油孔(36)，在输出轴控制板(19)外圆柱面与该径向油孔(36)平行位置开有一径向孔I(37)，所述径向孔I(37)内安装有进油阀芯(20)；在输出轴控制板(19)的内外两个环形槽处各开有一横向油孔(38)，使径向油孔(36)横穿过径向孔I(37)与两个环形槽相通；进油阀芯(20)顶端安装有进油阀芯弹簧(18)，弹簧压板I(17)与输出轴控制板(19)固定联接，把进油阀芯弹簧(18)压在进油阀芯(20)顶端；进油阀芯(20)顶部直径小于径向孔I(37)的直径，使径向油孔(36)与输出轴控制板(19)外环形槽相通；进油阀芯(20)底部封住径向油孔(36)通往输出轴控制板(19)内环形槽的横向油孔(38)；
    输出轴控制板(19)上与径向孔I(37)关于输出轴(25)轴对称的位置开有与径向孔I(37)同样大小的径向孔II(39)，径向孔II(39)内安装有回油阀芯(27)；所述回油阀芯(27)的顶端安装有回油阀芯弹簧(28)，弹簧压板II(30)与输出轴控制板(19)固定联接，把回油阀芯弹簧(28)压在回油阀芯(27)顶端；输出轴控制板(19)上开有内油缸回油孔B和外油缸回油孔C，所述内油缸回油孔B和外油缸回油孔C分别横穿内外两个环形槽和径向孔II(39)；回油阀芯(27)上开有上下两个环形槽，回油阀芯(27)的下环形槽使输出轴控制板(19)的内环形槽通过内油缸回油孔B与输出轴控制板(19)外侧相通；回油阀芯(27)上环形槽略低于外油缸回油孔C，回油阀芯(27)上环形槽上端的圆柱使输出轴控制板(19)的外环形槽不能通过外油缸回油孔C与输出轴控制板(19)外侧相通。
  2. 根据权利要求1所述的一种用于重载起动的液粘调速装置，其特征在于：所述输出轴(25)由轴承III(23)和轴承IV(24)支撑，轴承III(23)和轴承IV(24)安装在右轴承座(26)内；输出轴(25)开有压力油进油孔A，与输出轴控制板(19)的径向油孔相通；输入轴(1)开有内摩擦片组润滑油进油孔D和外摩擦片组润滑油进油孔E。
  3. 根据权利要求1所述的一种用于重载起动的液粘调速装置，其特征在于：所述液粘调速装置还包括壳体(4)，所述壳体(4)安装在左轴承座(2)和右轴承座(26)之间，内摩擦片组(7)、外摩擦片组(12)等均安装在壳体(4)内。
  4. 根据权利要求1所述的一种用于重载起动的液粘调速装置，其特征在于：所述输入轴 (1)通过轴承I(3)和轴承II(5)支撑，轴承I(3)安装在左轴承座(2)内，轴承II(5)安装在输出轴端盘(34)的内孔中。
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