US3780990A - Brake controlling device - Google Patents

Brake controlling device Download PDF

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Publication number
US3780990A
US3780990A US00220133A US3780990DA US3780990A US 3780990 A US3780990 A US 3780990A US 00220133 A US00220133 A US 00220133A US 3780990D A US3780990D A US 3780990DA US 3780990 A US3780990 A US 3780990A
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Prior art keywords
pressure
brake
motor
valve
load
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Expired - Lifetime
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US00220133A
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English (en)
Inventor
S Edlund
B Sodersten
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Haegglund and Soener AB
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Haegglund and Soener AB
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/02—Driving gear
    • B66D1/08—Driving gear incorporating fluid motors
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D5/00—Braking or detent devices characterised by application to lifting or hoisting gear, e.g. for controlling the lowering of loads
    • B66D5/02—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes
    • B66D5/24—Operating devices
    • B66D5/26—Operating devices pneumatic or hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003—Systems with load-holding valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D2700/00—Capstans, winches or hoists
    • B66D2700/01—Winches, capstans or pivots
    • B66D2700/0125—Motor operated winches
    • B66D2700/0133—Fluid actuated
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D2700/00—Capstans, winches or hoists
    • B66D2700/03—Mechanisms with latches or braking devices in general for capstans, hoists or similar devices as well as braking devices actuated electrically or by fluid under pressure
    • B66D2700/035—Fluid operated braking devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/321—Directional control characterised by the type of actuation mechanically
    • F15B2211/324—Directional control characterised by the type of actuation mechanically manually, e.g. by using a lever or pedal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary output members
    • 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
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/3023—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure
    • F16H63/3026—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure comprising friction clutches or brakes
    • F16H2063/3033—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure comprising friction clutches or brakes the brake is actuated by springs and released by a fluid pressure
    • 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
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/4157—Control of braking, e.g. preventing pump over-speeding when motor acts as a pump

Definitions

  • ABSTRACT The present invention relates to a device for controlling the brake in winches which are driven by a hydraulic motor and have a brake which is engaged when not actuated and arranged to disengage when a pressure medium is delivered to a hydraulic cylinder connected to the brake.
  • the invention is chiefly characterized by a brake controlling unit which is connected to the high pressure side of the motor and is arranged to regulate the supply of pressure medium to the brakes hydraulic cylinder, depending on the size of the motor load, so that during a lifting operation, the brake releases only after the pressure on the motors high pressure side substantially corresponds to the pressure required to balance the load.
  • a brake controlling unit which is connected to the high pressure side of the motor and is arranged to regulate the supply of pressure medium to the brakes hydraulic cylinder, depending on the size of the motor load, so that during a lifting operation, the brake releases only after the pressure on the motors high pressure side substantially corresponds to the pressure required to balance the load.
  • means are provided to release the brake at a pressure during lowering of the load, independent of the size of the load.
  • the present invention relates to a device for controlling the brake in winches which are driven by a hydraulic motor and have a brake which is engaged when not actuated and arranged to disengage when a pressure medium is delivered to a hydraulic cylinder connected to the brake.
  • pressure medium is usually supplied to the brake cylinder directly from the feeder of the pump; the brakes releasing pressure lies in the magnitude of 30 kp/cm depending on size of the motor.
  • a pressure of this magnitude ensures that the brake disengages before the motor is started without a load.
  • a hydraulic pressure on the high pressure side of the motor is required in the magnitude of 150 200 kp/cm.
  • the purpose of the present invention is to produce a device for brake control whereby the above mentioned drawbacks are totally eliminated.
  • This is achieved according to the invention by means of a brake control unit connected to the high pressure side of the motor, which unit is arranged to regulate the supply of pressure medium to the brakes hydraulic cylinder, depending on the size of the motor load, so that during lifting the brake releases only when the pressure on the high pressure side of the motor substantially corresponds to the pressure required to balance the load.
  • Means are provided to release the brake during lowering at a pressure independent of the size of the load.
  • the brake control unit comprises a hydraulic pressure accumulator, which is connected with the motors high pressure connection over a non-return valve opening away from the motor, and a spring-loaded control valve which is arranged in a pressure medium supply line to the brake cylinder.
  • the control valve communicates with the accumulator and is actuated by the pressure in the accumulator against the effect of the spring force towards a first position at whichthe pressure medium supply to the brake cylinder is interrupted; on the other side, the control valve communicates with the motors high pressure line and is actuated by the pressure in said line towards a second position where it is open to allow free passage of pressure medium to the brake cylinder.
  • the accumulator During lifting, the accumulator is charged to the pressure in the system, which depends on the size of the load, required for the lifting operation. If the motor is then stopped so that the hydraulic system has no pressure and the brake engages, due to the non-return valve connected in front of the accumulator the latter will maintain the pressure prevailing during lifting and hold the control valve closed with a force corresponding to said pressure.
  • the accumulator serves as a memory which stores information concerning the pressure required for lifting the load.
  • the control valve will open the connection with the brake when the pressure on the control valves opposite side, connected to the feeder of the motor on the high pressure side, exceeds the pressure in the accumulator minus the pressure corresponding to the force of the spring built in to said control valve.
  • the brake will hereby release only when the pressure on the high pressure side of the motor is sufficient to balance the load so that there will be no risk of the load sinking first.
  • the means which cause the brakes to release independent of the size of the load during the lowering operation consist preferably of a reverse valve arranged in the pressure medium line between the control valve and the brake cylinder.
  • This reverse valve communicates with the low pressure side of the motor and a short-circuit valve coupled over the accumulator and the non-return valve.
  • the short-circuit valve is arranged to be controlled by the pressure on the low pressure side of the motor.
  • the pressure medium is delivered via the reverse valve to the brake cylinder from the motors low pressure side, independent of the pressure in the accumulator which is shortcircuited by the short-circuit valve.
  • the accumulator is discharged since the motor is unloaded when the next lifting movement begins.
  • FIG. 1 is a wiring diagram of a control system for a hydraulic winch motor with conventionally regulated brakes.
  • FIG. 2 is a wiring diagram corresponding to the system in FIG. 1, but with a brake control device according to the invention.
  • the hydraulic system is fed oil by a pump 1 from a tank 2 to a hand valve, indicated by 3.
  • This valve communicates via a line 4 with the low pressure side 5 of a hydraulic winch motor 6, and via a line 7 with the high pressure side 8 of said motor 6.
  • a back-pressure valve 9 which communicates with the low pressure line 4 and is controlled by the pressure in said line 4.
  • a filter 10 in the return line from the hand valve 3 to the tank 2.
  • a brake 11 is provided.
  • the brake which is preferably a strap brake, is of the type which, when not actuated, is kept engagedby means of a powerful spring and is made to'release by the supply of oil to a hydraulic cylinder which is connected to the brake and acts against the force of the spring.
  • the spring and the brake are built together as one unit 12 which is fed oil via a line 13 connected with the feeder of the pump 1.
  • FIG. 2 the brake line 13 of FIG. 1 has been replaced by a brake controlling device according to the invention in order to remove the above mentioned drawbacks. Otherwise the two figures are identical; thus corresponding components have the same reference numerals.
  • the brake controlling device comprises a hydraulic pressure accumulator 14 which is connected directly to the high pressure side 8 of the motor 6 over a nonreturn valve 15 opening away from the motor 6.
  • the accumulator is also connected to one side of a pilotcontrolled two-position valve 16 so that the pressure in the accumulator actuates one side of a pilot piston displaceable in the valve 16 and tends to move the piston to the right in the figure in response to the effect of a spring 17.
  • the valve 16 assumes the position I indicated in the figure.
  • the opposite side of the valve 16 communicates via a line 18 with the high pressure line 7 of the motor 6 so that the pressure in the line 18, together with the spring 17, strives to displace the pilot piston to the left towards a valve position II.
  • the valve 16 is arranged between a line 19, which is connected to the high pressure line 7 via the line 18, and a line which, via a reverse valve 21, is connected to the brake cylinder 12.
  • a line 19 which is connected to the high pressure line 7 via the line 18, and a line which, via a reverse valve 21, is connected to the brake cylinder 12.
  • connection is made between the lines 19 and 20 so that pressure medium can flow freely from the high pressure line 7 via the valve 16 and the valve 21 to the brake cylinder 12 to release the brake 11.
  • the line 19 is closed and the line 20 communicates with the tank 2 so that the brake cylinder is drained for application of the brake.
  • the above described system relates to the high pressure side of the motor 6.
  • a line 22 which, via a reverse valve 21, connects the brake cylinder 12 with the motors low pressure line 4.
  • a short-circuit valve 23 is coupled over the non-return valve 15 and the accumulator 14 to shortcircuit the non-return valve and discharge the accumulator 14.
  • the valve 23 communicates with the low pres sure line 4 and is controlled by the pressure in said line.
  • valve 16 When the valve 3 is moved to the lifting position, oil is fed to the high pressure side of the motor 6 over the line 7 and simultaneously over the lines 18 and 19 to the valve 16. Since the pressure accumulator 14 is discharged, the valve 16 may be arranged so that the force of the spring 17 will be sufficient to keep said valve 16 open so that the oil can flow freely from the high pressure side via the lines 19 and 20 to the brake cylinder 12. The brake 11 thus disengages even at a'low pressure. This is advantageous since the motor first operates with low pressure only to take up the slack in the line before the load is lifted from the ground.
  • Corresponding pressure will prevail in the accumulator 14 which is thus kept continuously charged to a pressure equal to the pressure required to lift the load. Corresponding pressure also prevails on both sides of the pilot piston, on one side by the influence of the pressure in the accumulator l4, and on the other side by the pressure in the line 18 which is equal to the pressure on the high pressure side 8 of the motor.
  • the valve 16 is therefore kept in position II in open position by the spring 17 so that the brake is kept disengaged.
  • the pressure in the line 18 sinks.
  • the pressure in the accumulator 14 remains the same as during the lifting because of the non-return valve 15 which prevents discharging of the accumulator.
  • the pressure in the accumulator then acts to displace the pilot piston to the right so that the valve 16 assumes the position indicated by I. In this position, the line 19 is closed and the line 20 is connected to the tank. Thus the brake cylinder 12 is drained and the brake is applied.
  • the brake cylinder will instead be supplied with pressure medium over a line 22 which is connected with the low pressure line 4 of the motor and communicates, viathe reverse valve 21, with the brake cylinder 12. Since the line 20 is coupled to the tank over the valve 16, and is thus pressureless, the pressure in the line 22 will move the ball-shaped valve body in the valve 21 to the right in the figure and open the connection between the line 22 and the brake cylinder 12 at the same time as the line 20 is blocked. Thus, the brake is already released at a low pressure which is independent of the size of the load.
  • the pressure on the motors high pressure side 8 is determined by the backpressure valve 9 connected with the low pressure side 5. This pressure will now depend on the size of the load. This means that even during lowering the accumulator 14 will be kept charged with a pressure dependent on the size of the load so that, during a subsequent lifting, the brake releases only once the pressure on the high pressure side 8 of the motor 6 is sufficient to balance the load.
  • the non-return valve is short-circuited by the short-circuit valve 23, which is controlled from the low pressure side, so that the accumulator 14 can be discharged when the load is lowered to the ground since the winch starts without the load at the beginning of the next lifting movement.
  • Device for brake control in winches driven by a hydraulic motor said winches having a brake which is engaged when not actuated, said brake being arranged to release by means of the delivery of pressure medium to a hydraulic cylinder connected to the brake, characterize by a brake controlling unit which is connected to the high pressure side of the motor and is arranged to regulate the supply of pressure medium to the brakes hydraulic cylinder, depending on the size of the motor load, so that during a lifting operation, the brake releases only after the pressure on the motors high pressure side substantially corresponds to the pressure required to balance the load, means being arranged in order to release the brake at a pressure, during lowering of the load, independent of the size of the load, said brake control unit comprises a hydraulic pressure accmmulator, which is connected with the motors high pressure line over a non-return valve that opens away from said motor, and a spring-loaded control valve which is arranged in a pressure medium supply line to the brake cylinder and which, on the one side, communicates with the accumulator and is actuated 'by

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
US00220133A 1971-01-28 1972-01-24 Brake controlling device Expired - Lifetime US3780990A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
SE01029/71A SE353297B (de) 1971-01-28 1971-01-28

Publications (1)

Publication Number Publication Date
US3780990A true US3780990A (en) 1973-12-25

Family

ID=20257474

Family Applications (1)

Application Number Title Priority Date Filing Date
US00220133A Expired - Lifetime US3780990A (en) 1971-01-28 1972-01-24 Brake controlling device

Country Status (5)

Country Link
US (1) US3780990A (de)
JP (1) JPS5430170B1 (de)
DE (1) DE2203860C2 (de)
GB (1) GB1370736A (de)
SE (1) SE353297B (de)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3934856A (en) * 1973-06-14 1976-01-27 Fullerton, Hodgart & Barclay Ltd. Mine hoists
US3986703A (en) * 1973-06-21 1976-10-19 Evershed Power-Optics Limited Movement of scenery in theaters and studios
US4047311A (en) * 1974-09-23 1977-09-13 Kelley Charles S Automatic grab bucket with pressure responsive solenoid control
US4053999A (en) * 1974-09-23 1977-10-18 Kelley Charles S Automatic grab crane
US4074891A (en) * 1974-12-20 1978-02-21 Kopat Gesellschaft Fur Konstruktion, Entwicklung Und Patentverwertung M.B.H. & Co. Kg Winding mechanism-drive, particularly for construction cranes or like hoisting devices
US4441691A (en) * 1982-01-22 1984-04-10 Kabushiki Kaisha Komatsu Seisakusho Hoisting winch mounted on crane or the like
US4447044A (en) * 1980-05-26 1984-05-08 Kabushiki Kaisha Komatsu Seisakusho Clutching and braking control for hydraulically driven crane winches
US4462570A (en) * 1982-08-25 1984-07-31 Ingersoll-Rand Company Hoist overload limiter
US4516755A (en) * 1982-06-02 1985-05-14 Kabushiki Kaisha Komatsu Seisakusho Hydraulic winch control system
US5735506A (en) * 1993-12-30 1998-04-07 Thomson-Csf Winch with hydraulic motor especially for helicopter equipped with sonar
US5806838A (en) * 1995-11-30 1998-09-15 Kalve; Atle Hydraulic system for driving a winch during quartering and lifting modes
US6012707A (en) * 1995-05-19 2000-01-11 Tamrock Oy Arrangement for controlling tension in a winch cable connected to rock drilling equipment
CN105019881A (zh) * 2015-07-24 2015-11-04 上海中联重科桩工机械有限公司 旋挖钻机、旋挖钻机的防溜杆控制系统及控制方法
CN113148884A (zh) * 2021-04-20 2021-07-23 徐州重型机械有限公司 应急动力装置及起重机卷扬应急液压控制系统
WO2022247003A1 (zh) * 2021-05-25 2022-12-01 三一重机有限公司 马达总成、行走驱动系统及作业机械

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2467284A1 (fr) * 1979-10-10 1981-04-17 Rexroth Sigma Dispositif de commande d'un moteur a fluide, notamment hydraulique, et installation equipee d'un tel dispositif
NO151129C (no) * 1980-07-14 1985-02-13 Bryne Mek Verksted Ventilanordning, saerlig for bremsing av hydrauliske motorer med mekanisk bremse
GB2082227B (en) * 1980-08-15 1984-03-07 Coal Industry Patents Ltd Brake equipment for underground mining machines
FR2547569B1 (fr) * 1983-06-20 1987-03-06 Sern Dispositif de controle hydraulique ou pneumatique d'un moteur hydraulique d'entrainement d'un treuil de fune a bord des bateaux de peche
DE3608536C1 (de) * 1986-03-14 1987-09-24 Boecker Albert Gmbh & Co Kg Steuervorrichtung fuer die Betaetigung eines hydraulischen Seilwindenantriebes fuer einen Schraegaufzug
DE102008024512B4 (de) * 2008-05-21 2010-08-12 Manitowoc Crane Group France Sas Elektrohydraulische Leck-Kompensation
CN114212715B (zh) * 2021-11-09 2024-04-05 中船华南船舶机械有限公司 一种吊机的液压系统的控制方法

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1406914A (fr) * 1964-09-07 1965-07-23 Landsverk Ab Dispositif de commande pour les grues mobiles, les excavatrices, ou autres machines analogues
FR1531600A (fr) * 1967-05-16 1968-07-05 Richier Sa Perfectionnement aux transmissions hydrostatiques pour treuils de levage

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3934856A (en) * 1973-06-14 1976-01-27 Fullerton, Hodgart & Barclay Ltd. Mine hoists
US3986703A (en) * 1973-06-21 1976-10-19 Evershed Power-Optics Limited Movement of scenery in theaters and studios
US4047311A (en) * 1974-09-23 1977-09-13 Kelley Charles S Automatic grab bucket with pressure responsive solenoid control
US4053999A (en) * 1974-09-23 1977-10-18 Kelley Charles S Automatic grab crane
US4074891A (en) * 1974-12-20 1978-02-21 Kopat Gesellschaft Fur Konstruktion, Entwicklung Und Patentverwertung M.B.H. & Co. Kg Winding mechanism-drive, particularly for construction cranes or like hoisting devices
US4447044A (en) * 1980-05-26 1984-05-08 Kabushiki Kaisha Komatsu Seisakusho Clutching and braking control for hydraulically driven crane winches
US4441691A (en) * 1982-01-22 1984-04-10 Kabushiki Kaisha Komatsu Seisakusho Hoisting winch mounted on crane or the like
US4516755A (en) * 1982-06-02 1985-05-14 Kabushiki Kaisha Komatsu Seisakusho Hydraulic winch control system
US4462570A (en) * 1982-08-25 1984-07-31 Ingersoll-Rand Company Hoist overload limiter
US5735506A (en) * 1993-12-30 1998-04-07 Thomson-Csf Winch with hydraulic motor especially for helicopter equipped with sonar
US6012707A (en) * 1995-05-19 2000-01-11 Tamrock Oy Arrangement for controlling tension in a winch cable connected to rock drilling equipment
US5806838A (en) * 1995-11-30 1998-09-15 Kalve; Atle Hydraulic system for driving a winch during quartering and lifting modes
CN105019881A (zh) * 2015-07-24 2015-11-04 上海中联重科桩工机械有限公司 旋挖钻机、旋挖钻机的防溜杆控制系统及控制方法
CN105019881B (zh) * 2015-07-24 2017-11-07 上海中联重科桩工机械有限公司 旋挖钻机、旋挖钻机的防溜杆控制系统及控制方法
CN113148884A (zh) * 2021-04-20 2021-07-23 徐州重型机械有限公司 应急动力装置及起重机卷扬应急液压控制系统
CN113148884B (zh) * 2021-04-20 2022-11-29 徐州重型机械有限公司 应急动力装置及起重机卷扬应急液压控制系统
WO2022247003A1 (zh) * 2021-05-25 2022-12-01 三一重机有限公司 马达总成、行走驱动系统及作业机械

Also Published As

Publication number Publication date
JPS5430170B1 (de) 1979-09-28
DE2203860A1 (de) 1972-08-17
SE353297B (de) 1973-01-29
GB1370736A (en) 1974-10-16
DE2203860C2 (de) 1983-04-28

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