US3815478A - Pipelayer hydraulic drawworks with free-fall - Google Patents

Pipelayer hydraulic drawworks with free-fall Download PDF

Info

Publication number
US3815478A
US3815478A US00084978A US8497870A US3815478A US 3815478 A US3815478 A US 3815478A US 00084978 A US00084978 A US 00084978A US 8497870 A US8497870 A US 8497870A US 3815478 A US3815478 A US 3815478A
Authority
US
United States
Prior art keywords
motor
hydraulic
fluid
pressure
free
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US00084978A
Other languages
English (en)
Inventor
E Axelsson
D Collier
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Caterpillar Inc
Original Assignee
Caterpillar Tractor Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Caterpillar Tractor Co filed Critical Caterpillar Tractor Co
Priority to US379759A priority Critical patent/US3893572A/en
Application granted granted Critical
Publication of US3815478A publication Critical patent/US3815478A/en
Assigned to CATERPILLAR INC., A CORP. OF DE. reassignment CATERPILLAR INC., A CORP. OF DE. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: CATERPILLAR TRACTOR CO., A CORP. OF CALIF.
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/18—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes specially adapted for use in particular purposes
    • B66C23/36—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes specially adapted for use in particular purposes mounted on road or rail vehicles; Manually-movable jib-cranes for use in workshops; Floating cranes
    • B66C23/44—Jib-cranes adapted for attachment to standard vehicles, e.g. agricultural tractors
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0425—Disconnecting the pistons from the actuated cam
    • 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
    • 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
    • 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
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F15B2211/20584—Combinations of pumps with high and low capacity
    • 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
    • F15B2211/32—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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/61—Secondary circuits
    • F15B2211/611—Diverting circuits, e.g. for cooling or filtering
    • 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
    • F15B2211/615—Filtering means
    • 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
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • 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
    • 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
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7114—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators
    • F15B2211/7128—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators the chambers being connected in parallel
    • 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
    • F15B2211/715—Output members, e.g. hydraulic motors or cylinders or control therefor having braking means
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/865—Prevention of failures
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/875—Control measures for coping with failures
    • F15B2211/8755—Emergency shut-down

Definitions

  • ABSTRACT In cable winding gear driven by a hydraulic motor of the kind having radial pistons driving a surrounding cam ring, a control is provided for applying differential pressure to the motor pistons so that they are disengaged from the cam ring which can then rotate freely. This provision enables the cable to be run out freely, so that, for example, in a crane free fall of the load can be allowed while avoiding damage to the m0- tor. Pipe-laying equipment including the free-fall provision is described.
  • this invention is concerned with systems embodying a hydraulic motor of the kind including a stationary cylinder having a number of radial bores in each of which a piston is displaceable, and a cam ring which is rotatably driven by the pistons.
  • the cam faces of the cam ring are engaged by driving means.
  • driving means such as rollers mounted on the radially outward ends of the pistons, or the outer end faces of the pistons, and hydraulic fluid is selectively supplied to the bores to radially displace the pistons in a predetermined sequence whereby the pressure engagement of the driving means with the cam faces rotates the cam ring from which the drive is obtained in any suitable manner.
  • Such hydraulic motors as above described are herein referred to as of the kind specified.
  • Hydraulic motors of the kind specified are already well known and they are used for driving winches, hoists, windlasses or the like. Although in such applications hydraulic motors of the kind specified are very satisfactory, it is most desirable to be able to operate the winch or the like in the conventional manner in which the drive can be disengaged so as to allow the winch drum or the like to rotate freely or over-run the drive. For example, it is desirable to provide an operating condition such that the load supported by the winch can fall freely under gravity, or such that the cable or drag line can run out freely.
  • Further objects of this invention are to provide an improved hydraulic system for operating and controlling a winch, hoist or the like driven by a hydraulic motor of the kind specified, and to provide a winch, hoist or the like operated and controlled by such improved hydraulic system.
  • valve means for controlling the flow of hydraulic fluid and which valve means on actuation is arranged to produce in the hydraulic motor a hydraulic pressure differential acting on the pistons to displace them radially inwards to an extent such that the driving means are maintained out of contact with the cam faces of the cam ring which can then rotate freely.
  • One of the preferred ways of obtaining the hydraulic pressure differential in the hydraulic motor is to arrange for the valve means to reduce hydraulic pressure in the cylinder bores and to maintain a low hydraulic pressure in the motor casing so as to develop a pressure differential sufficient to displace the pistons radially inwards. In this manner a relativey low hydraulic pressure in the motor casing can be utilised to displace the pistons,and when the drive is to be restored, hydraulic fluid can be supplied to the cylinder to re-engage the driving means with the cam ring, and then hydraulic fluid for driving the motor may be supplied at the required flow rate.
  • valve means merely to control the flow of hydraulic fluid into the motor casing so as to develop therein a hydraulic pressure acting on the radially outer parts of the pistons greater than the hydraulic pressure in the cylinder bores as applied to the radially inner parts of the pistons
  • this has the disadvantage that the motor casing, including the cam ring will have to be designed to withstand very high bursting loads due to the high hydraulic pressures involved.
  • the flow capacity of the pump means and overheating of the hydraulic fluid may lead to further problems.
  • a hydraulic motor of the kind specified is designed to operate with no or very low hydraulic pressure in the motor casing, and thus where it is desired merely to apply our invention to existing hydraulic motors of the kind specified the aforementioned preferred way of developing the hydraulic pressure differential can most conveniently be adopted.
  • valve means has to be arranged to act, on actuation. in concert with the other essential operational controls of the winch or the like which must be maintained either inoperative or functional, for instance when the load is released the winch brake must be held off.
  • these considerata will be fully understood from an embodiment of the invention which is described later herein.
  • This invention is also deemed to include a winch
  • One application of this invention is in a hydraulic systern for operating and controlling pipe-laying apparatus adapted for attachment to, or incorporation in a tractor, preferably of the tracked type.
  • FIG. 1 is a front-elevation of pipe-laying apparatus according to the invention mounted on a tractor;
  • FIG. 2V is a diagrammatic view of a hydraulic motor of the kindvspecifled
  • FIG. 3 is aidiagram of the hydraulic operation and control system for the boom of the pipe-laying apparatus of FIG. I and;
  • FIG'. 4' is a diagram of the hydraulic operation and control system for counterweights and a hoist of the pipe-laying-apparatus.
  • the principal components of the pipe-laying apparatus which are mounted on the tractor comprise a saddle l on one side of which are carried a set of hydraulically controlled counterweights 2 and two winches 3 each adapted to be driven by a hydraulic motor of the kind specified and of which further details will be given later.
  • a saddle l On the other side of the saddle is mounted the boom 4 which is raised and lowered by one of the winches 3, and the other end of the boom carries the hoist 5 which is raised and lowered by the other winch 3.
  • the hoist 5 and boom 4 can be operated independently or simultaneously.
  • the hydraulic motors driving the winches 3 are each of the kind shown in FIG. 2 and including a stationary cylinder block6 having a number of radial bores in each of which a piston 7 is displaceable, and a cam ring 8 which is rotatably driven by the pistons.
  • the cam faces of the cam ring 8 are engaged by driving means, such as rollers 9 mounted on the radially outward ends of the pistons, or the outer end faces of the pistons, and hydraulic'fluid is selectively supplied to the bores to displace the pistons 7 radially in a predetermined sequence whereby the pressure engagement of the driving means with the cam faces rotates the cam ring from which the drive is obtained in any suitable manner.
  • the hydraulic system depicted in FIGS. 3 and 4 is for operating and controlling the foregoing apparatus and its ancillary parts.
  • the power is derived from. the tractor engine independently of drive transmission, and it is arranged to drive the fixed displacement hydraulic pumps which supply hydraulic fluid to the three parts of the hydraulic system for actuating:
  • FIGS. 3 and 4 are in the form of circuit diagrams with all the control valves shown in the neutral position.
  • the Boom System A fixed displacement hydraulic pump 10 driven from the engine draws hydraulic fluid through a suction filter 12 from an open or low pressure reservoir II. Hydraulic fluid supply from the output line 13 of the pump [0 is controlled by a three position open-centre valve 14 which is shown in the neutral position. By means ofthe valve 14 hydraulic fluid may be supplied to a reversible hydraulic motor 15 of the kind specified which is connected directly tothe winch drum, and the hydraulic fluid may be returned to the reservoir 11.
  • valve 14 For raising the boom 4, the valve 14 is displaced to a second position, which corresponds to moving it to the extreme right in the accompanying drawing. In this second position the motor 15 is rotated in one sense by hydraulic fluid supplied through line 16 to the motor 15 and discharged through the line 17 through the valve 14, to line 18 returning to the reservoir 11. Hydraulic fluid is also drained from the motor casing through line 19 back to the reservoir 11.
  • valve 20 Associated with line 16 is a valve 20 which is normally closed, but which on actuation serves to connect the line 16 with line 21 leading to the reservoir 11.
  • the valve 20 is actuated by the engagement of a spring loaded abutment 22 which is arranged to be engaged by the boom if his raised to an over-centre position, or other predetermined attitude of elevation in relation to the tractor.
  • the supply of hydraulic fluid through line 16 to the motor 15 is prevented as the line 16 is connected through valve 20 to the reservoir return line 2l,.and further elevation of the boom is prevented.
  • the motor 15 is rotated in the opposite sense by changing the direction of flow of the hydraulic fluid supplied to the motor 15.
  • the motor 15 is provided with a counterbalance valve arrangement as depicted in the rectangular out-- line referenced 23.
  • This counterbalance valve arrangement is adapted only to open when a predetermined high pressure is exceeded so that the motor can operate with full back pressure.
  • the boom winch is provided with a conventional spring operated band brake that is arranged to be held in the off" position by a hydraulic brake cylinder 25 which is connected to the valve 14 by a line 26. Hydraulic pressure is maintained in the brake cylinder 25 whilst the motor 15 is driven in either sense. When no hydraulic fluid is supplied to the motor 15, namely when valve 14 is in the neutral position as depicted, the brake line 26 is open to the reservoir return line 18 and the hydraulic cylinder 25 is released so that the brake is applied. Additionally, if there should be a loss of hydraulic fluid with consequent reduction in pressure in any of the supply lines aforementioned the brake is automatically applied.
  • the control valve 14 when in the neutral position shown, blocks lines 16 and 17 from lines 13 and 18 and communicates flow from pump totank 11 via conduits l3 and 18.
  • the brake 25 is in communication with the tank via the conduit 26 which is a branch of conduit 13.
  • Brake 25, which is normally applied by spring force, is allowed to be applied to restrict movement of the boom. Release of the brake is accomplished by pressurization of the brake cylinder to overcome the spring bias when desired.
  • the selector control valve 14 is shifted to position 92 in which it allows pump flow to be communicated to motor 15 via the conduit 17 and to the counter-balance valve 93 via the conduit 94.
  • the orifice choke 96 modulates pilot flow to the counter-balance valve 93 and prevents over sensitive operation thereof.
  • the valve 93 will shift to an open position in which is allowed communication between the motor ports 102 and the tank 11 via conduits the 97,98,99,16 and 18.
  • the counter-balance valve 93 maintains a minimum back pressure range of 300-500 psi in the motor which pressure assures the release of the brake prior to the lowering of the boom and prevents cavitation in the motor 15.
  • the two-way relief valve 100 protects the motor circuitry by directing flow back to the motor inlet via the conduits 101 and 17 at such times that the load is excessive and back pressure in the motor reaches the 3,000 psilevel. This provision also reduces cavitation in the motor by supplying make-up fluid to the inlet ports when the load becomes excessive.
  • Check valves 104 and 105 are provided to block flow in the direction'indicated and to maintain fluid in the respective associated conduits and also to block flow to the motor 15 until after the brake spring force is overcome by pressurized fluid and the brake is released.
  • the Counterweight System The lateral position of the counterweights (not shown) relative to the tractor is hydraulically controlled by a three position valve 27 similar to valve 14. Two hydraulic cylinders 28, 29 are arranged to move the counterweights transversely of the tractor centreline by means of hydraulic fluid supplied through line 30 from the small section of a double hydraulic pump 31 of the fixed displacement type drawing hydraulic fluid through a suction filter 83 from the reservoir 11.
  • valve 27 When the valve 27 is in the central neutral position as depicted, the supply of hydraulic fluid is straight through is straight through the open-centre of valve 27 into line 36 connected to the hoist system which is described later. If the valve 27 is displaced into either a second or third position, then hydraulic fluid is supplied to one end of the hydraulic cylinders 28, 29
  • a counterbalance valve arrangement 34 is provided in line 33.
  • a pressure relief valve 35 is associated with valve 27 and is connected to line 36.
  • the Hoist System The supply of hydraulic fluid to the hoist system is derived from the large section of the double hydraulic pump 31. Hydraulic fluid in output line 37 is directed through line 39 to a three-position valve 38, through line 40 to a two-position valve 41 with the output line 37 including a bypass filter 42.
  • valve 38 is for controlling a two speed hydraulic motor 43 of the kind specified.
  • Valve 38 is substantially the same as the other three position valves 27 and 14, except that it includes a restrictor 44 which serves to throttle flow to the reservoir 11 through line 45 when the valve 38 is in its second or third position.
  • the valve 41 is provided for operating the valve 46 of the hydraulic motor 43 that controls, in known manner, the speed of the motor.
  • the valve 41 is connected to a line 47 leading to the reservoir 11, and in either operative position provides a through passage for hydrau- Iic fluid to the brake cylinder 48 of the spring-operated band'type winch brake (not shown) that is held off by the brake cylinder 48.
  • valve 38 With reference to the operation of the brake cylinder 48, when the valve 38 is in the neutral position depicted in the drawing there is no hydraulic fluid supplied to the brake cylinder 48'and the brake is in the applied position.
  • the hydraulic fluid in line 39 flows through the open centre of valve 38 to the reservoir 11 via return line 45.
  • the brake cylinder line 52 is also open to the reservoir 11 through shuttle valve 51, line 54 through shuttle valve 50, and the line 49, valve 41 to line 40 and thence to the reservoir 11 through opencentred valve 38.
  • valve 38 When the valve 38 is in either its second or third positions, that is when the hydraulic motor 43 is being driven, hydraulic fluid is supplied to the brake cylinder 48 to hold the winch brake in the off" position.
  • hydraulic fluid flows through line 40 through port p to port a of valve 41. Flow is then through line 49, through shuttle valve 50 into line 54 to actuate shuttle valve 51 and into the brake line 52. The actuation of the shuttle valve 51 prevents the return flow of hydraulic fluid to the reservoir 11 through line 57.
  • the motor speed control valve 41 When the motor speed control valve 41 is in its other position, the hydraulic fluid flows through line 40, through port p to port b of valve 41, through line 53 to actuate shuttle valve 50 to close line 60. The flow is then to the brake line 52 through line 54 and shuttle valve 51 which is actuated in the same way as just described.
  • the speed of the hydraulic 43 is controlled in known manner by the actuation of spool valve 46 to which hydraulic fluid is supplied through line when the conis either through line 58,-or through line 59 dependingon the position of valve 38.
  • the return'flow of hydraulic fluid from the motor 43 is through either line 59 or 58.
  • the crux of this invention is that the hydraulic motor 43 can be operated so that free fall of the hoist load can be obtained, andcontrolled without risk of damage to the motor 43. This operation and control will now be explained having regard to the foregoing description and explanation.
  • the free-fall hydraulic system associated with control valve 56 is arranged so that it can only be effective I when the hoist control valve 38 is in the neutral central position, that is when the hydraulic motor is not being driven, such as when a load is suspended on the hoist in mid-air.- This is done by providing a drain valve 64 which is mechanically coupled by a suitable linkage to the operating linkage of valve 38. When valve 38 is in either its second or third position, the line 66 leading to valve 64 is open to the reservoir 11' through drain line 65 and. thus pressure cannot be developed in line 67 which is in the free fall system. Accordingly, free fall of the load can only be obtained when the hoist valve 38 and drain'valve 64 are in the operative positions depicted in the accompanying drawing; 1
  • the free fall of the hoist load is controlled by the control valve 56 to which hydraulic fluid flows from the control valve 27 of the counterweight system, through line 36 including by -pass filter 61.
  • the free fall control valve 56 is depicted in the inoperative position whereby the brake line 52 is open to the reservoir 11, flow being through line 55, line '62 including restrictor 63, through port B to port T of the valve 56 to' the reservoir return line 57.
  • the hydraulic fluid flows through port P to port Aof valve 56, through line'68 to a non-return valve 69 in'line 70, to a line 71 and thus to anopen reservoir 72 to which flow is controlled by a non-return valve 73 having a predetermined opening pressure.
  • the line 71 also includes a pressure relief valve 74 for relieving the pressure in line 36, but under normal conditions as now being described, this relief valve 74 merely acts as a non-return valve in line 71.
  • the open reservoir 72 which may be integral with reservoir 11, is also connected to the motor casing bycylinder 48. Hydraulic fluid also flows from the line 62 to line 67 connected to a pair of spool valves 76, 77,
  • the lower hydraulic pressure which is present in the idle hydraulic motor 43 and which is determined by the valves 78, 79 is vented to an open reservoir through the valves 76, 77 on their actuation, and thus the pressure maintained in the motor casing by the valve 73 is greater than that in the motor cylinder bores and the pistons are displaced radially inwards by the hydraulic pressure in the motor casing so that the driving means as aforedescribed is moved out of engagement with the cam ring.
  • valves 80, 81- are set lower than the non-return valve 69, thus the minimum operating pressure determined by the arrangement of valves 78 and 79 is quickly restored. Hydraulic fluid also flows to the reservoir ll from the brake line 52, through shuttle 'valve 51 through line 55,-through the restrictor 63 in'line 62, and through valve 56 to line 57. This exhausts the brake cylinder 48 which'is releasedand the brake is applied.
  • the spool valves 76 and 77 are also released again by the pressure drop in line 67, buta throttle non-return valve 84 in line 67 the restrictor 63 provides a restriction which delays the release of the spool valves 76, 77 for a short time to ensure that the brake is applied slightly before the motor pistons are displaced outwards to re-engage the driving means.
  • the hoist winch is then ready for operation under the control of valve 38.
  • valves I4. 27 and 38 are of the open-centre kind so that when any of these valves are maintained in the neutral position. such as when the tractor is idling, the hydraulictluid is returned directly to the reservoir 11] without passing through the associated hydraulic circuits. This arrangement is most advantageous because excessive heating of the hydraulic fluid is prevented and the provision of additional oil coolers can be avoided.
  • the actuation of the hoist-winch brake is synchronised with the readiness of the hydraulic motor, and this provides a fail-safe feature. Additionally, the coupling of the drain valve 164 to the hoist winch motor control valve 138 provides another fail-safe feature.
  • Each of the manually operable control valves are of the dead-man type biased to return to the neutral position,
  • a v 1 In a system for'operating and controlling a winding gear driven by a rotary hydraulic motor of the kind including a first member having a plurality of radial bores, a motor element displaceable in each of the bores and each having an associated driving means, a cam ring having cam faces engaged by the driving means and means for selectively supplying hydraulic fluid to the bores to displace the motor elements radially in a predetermined sequence and by pressure-engagement of the driving means with the cam faces to produce relative rotation between the cam ring and said first member, the system includingpump means for supplying hydraulic fluid to the hydraulic motor, normally applied brake means for said winding gear, fluid pressure means including fluid communication means for releasing said brake means, the improvement comprising; free-run means including fluid communication means for applying to the motor elements of the hydraulic motor a hydraulic pressure differential to displace the motor elements radially inwardly and withdraw the associated driving means from contact with the cam faces of the cam ring whereby the cam ring can rotate freely, said free-run means including means for
  • the invention of claim 1 including a casing for said hydraulic motor and means for applying, on actuation of the free-run means, a hydraulic pressure inthe interior of said casing of the motor higher than that obtain ing in said bores.
  • the invention of claim 1 including means for re ducing, on actuation of the free-run means, standing hydraulic pressure in said bores.
  • the invention of claim 4 including a casing for said hydraulic motor and wherein said valve means are adapted, on actuation. to connect a source of hydraulic pressure to the interior of said casing.
  • the invention-of claim 5 further including means for maintaining a standing pressure in the bores when the motor is idle and wherein said valve means, on actuation, operate means for releasing said standingpressure from the bores of the motor.
  • a system for operating and controlling a winding gear driven by a rotary hydraulic motor of the kind including a first member having a plurality of radial bores, a motor element displaceable in each of the bores and each having an associated driving means, a cam. ring having cam faces engaged by the driving means and means for selectively supplying hydraulic fluid to the bores todisplace the motor elements radially in a predetermined sequence and by pressure engagement of the driving means with the cam faces to produce relative rotation between the cam ring and said first member, .the system including pump means for-supplying hydraulic fluid to 'the hydraulic motor.
  • said free-run means including means for preventingsaid fluid pressure means from releasing said brake'means until said pressuredifferential has been developed to condition said motor elements and associated driving means to move radially'inwardlyv away from contact with said cam faces of'said cam ring, valve means forac'tuating the free-run means, a casing for hydraulic motor and wherein said'valve means are adapted, on actuating, to connect a source of hydraulic pressure to the interior of said casing, means for maintaining a standing pressure in the bores when the motor is idle and wherein said valve means, on actuation, operate means for releasing said standing pressure from the bores of the motor, said valve means, on restoration to its normal position after actuation, acting to connect a source of hydraulic pressure to the bores of the motor to restore the standing pressure.
  • valve means on restoration of its normal position after actuation. connect a source of hydraulic pressure to the bores of the motor to restore the standing pressure, said means for preventing brake means release being also provided for ensuring that the brake means is applied before the standing pressure is restored.
  • driving means for selectively supplying hydraulic fluid to said rotary hydraulic motor to rotate said hydraulic motor and said winding gear
  • said driving means including first supply means for supplying hydraulic pressure fluid to said hydraulic motor, normally applied brake means for said winding gear, fluid pressure means including fluid communication means for releasing said brake means, free-run means including fluid communication means for applying to a portion of the hydraulic motor a hydraulic pressure to allow said hydraulic motor to rotate freely without load
  • said free-run means including second supply means for supplying said hydraulic motor portion, said second supply means including a source of hydraulic fluid separate from the source of hydraulic fluid for said drive means, said freerun means including means for preventing said fluid pressure means from releasing said brake means until said hydraulic pressure has been supplied to said portion of said motor to condition said motor to rotate freely without load
  • said driving means for said reversible rotary hydraulic motor further including a motor control valve for controlling flow of hydraulic fluid to said hydraulic motor for driving rotation thereof, said control valve having a first portion for
  • driving means for selectively supplying hydraulic fluid to said rotary hydraulic motor to rotate said hydraulic motor and said winding gear
  • said driving means including first supply means for supplying hydraulic. pressure fluid to said hydraulic motor, normally applied brake means'for said winding gear, fluid pressure means including fluid communication means for releasing said brake means, free-run means including fluid communication rneans for applying to a portion of the hydraulic motor a hydraulic pressure to allow said hydraulic motor to rotate freely without load, said free-run means including second supply means for supplying said hydraulic motor portion, said second supply means including a sourceof hydraulic fluid separate from the source of hydraulic fluidfor said drive means, said freerun means including means for preventing said fluid pressure means from releasing said brake means until said hydraulic pressure has been supplied to said portion of said motor to condition said motor to rotate freely without load, said free-run means further including tertiary valve means for preventing said rotary hydraulic motor from returning from the freely rotating condition to the driving condition prior to the reapplication of said brake means
  • a winding gear driven by a rotary hydraulic motor of the kind including a first member having a plurality of radial bores, 21 motor element displaceable in each of the bores and each having an associated driving means, a cam ring having cum l'aces engaged by the driving means and means for selectively supplying hydraulic fluid to the bores to displace the motor elements radially in a predetermined sequence and by pressure engagement of the driving means with the cam faces to produce relative rotation between the cam ring and said first member
  • the system including pump means for supplying hydraulic fluid to the hydraulic motor, normally applied brake means for said winding gear, fluid pressure means including fluid communication means for releasing said brake means
  • the improvement comprising; free-run means including fluid communication means for applying to the motor elements of the hydraulic motor a hydraulic pressure differential to displace the motor elements radially inwardly and withdraw the associated driving means from contact with the cam faces of the cam ring whereby the cam ring can rotate freely, said free-run means including means for preventing said fluid pressure means from
  • driving means for selectively supplying hydraulic fluid to said rotary hydraulic motor to rotate said hydraulic motor and said winding gear
  • said driving means including first supply means for supplying hydraulic pressure fluid to said hydraulic motor, normally applied brake means for said winding gear, fluid pressure means including fluidcommunication means for releasing said brake means, free-run means including fluid communication means for applying to a portion of the hydraulic motor a hydraulic pressure to allow said hydraulic motor. to rotate freely without load.
  • said free-run means including second supply means for supplying said hydraulic motor portion, said second supply means including a source of hydraulic fluid separate from the source of hydraulic fluid for said drive means, said freerun means including means for preventing said fluid pressure means from releasing said brake means until said hydraulic pressure has been supplied to said portion of said motor to condition said motor to rotate freely without load.
  • said hydraulic motor drive means further includes a motor control valve for controlling flow of hydraulic fluid to said hydraulic motor for driving rotation thereof, said control valve having a first position for supplying fluid to cause said motor to rotate in a first direction, a second position for supplying fluid to cause said motor to rotate in the reverse direction, and a neutral position in which fluid flow to and from said hydraulic motor is blocked and a hydraulic fluid lock is created which retards rotation of said hydraulic motor in either of said first or reverse directions.
  • numerals 90, 91, 92, 93, 94, 96, 97, 98, 99', 100', 101, 102, 103, 10M, 1o5 and 106 are added along with lead lines where indicated;

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Agronomy & Crop Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Hydraulic Motors (AREA)
US00084978A 1970-06-26 1970-10-29 Pipelayer hydraulic drawworks with free-fall Expired - Lifetime US3815478A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US379759A US3893572A (en) 1970-06-26 1973-07-16 Systems for operating and controlling hydraulically driven winches, hoists, windlasses and the like

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB3107870 1970-06-26

Publications (1)

Publication Number Publication Date
US3815478A true US3815478A (en) 1974-06-11

Family

ID=10317622

Family Applications (1)

Application Number Title Priority Date Filing Date
US00084978A Expired - Lifetime US3815478A (en) 1970-06-26 1970-10-29 Pipelayer hydraulic drawworks with free-fall

Country Status (5)

Country Link
US (1) US3815478A (cs)
DE (1) DE2101750A1 (cs)
FR (1) FR2096496B1 (cs)
GB (1) GB1335386A (cs)
SE (1) SE377103B (cs)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3995973A (en) * 1975-09-04 1976-12-07 Deere & Company Variable displacement hydraulic system
US4381701A (en) * 1979-09-06 1983-05-03 Regie Nationale Des Usines Renault Servomotor featuring a servovalve controlling a hydraulic drum motor
US6644562B2 (en) * 2000-10-13 2003-11-11 Maquinas Agricolas Jacto S.A. Dynamic counterweight mechanism for one-sided sprayers
US20130205762A1 (en) * 2011-11-29 2013-08-15 Vanguard Equipment, Inc. Auxiliary flow valve system and method for managing load flow requirements for auxiliary functions on a tractor hydraulic system
US20140338317A1 (en) * 2013-05-20 2014-11-20 Komatsu Ltd. Pipelayer
WO2015162229A1 (de) * 2014-04-23 2015-10-29 Putzmeister Engineering Gmbh Steuerungssystem für eine hydraulische arbeitsmaschine
US20160207744A1 (en) * 2013-10-31 2016-07-21 Komatsu Ltd Winch for pipelayer and pipelayer equipped with same
NO20160714A1 (en) * 2016-04-28 2017-01-16 Mhwirth As A winch system
US9663335B2 (en) 2014-08-27 2017-05-30 Caterpillar Inc. Hydraulic winch control system and method
US9739495B2 (en) 2013-04-05 2017-08-22 Siang Teik Teoh Coaxial ventilator
US9890964B2 (en) 2013-04-05 2018-02-13 Siang Teik Teoh Coaxial ventilator
US20190337776A1 (en) * 2018-05-07 2019-11-07 Caterpillar Inc. Pipelayer machine having hoisting system with pivotable fairlead
US20190352148A1 (en) * 2018-05-21 2019-11-21 Caterpillar Inc. Machine having hoisting system with instrumented fairlead
US11148915B2 (en) * 2019-09-19 2021-10-19 Caterpillar Inc. Boom assembly and method of assembly thereof
US11247879B2 (en) 2015-07-14 2022-02-15 Mhwirth As Winch system
US11946372B2 (en) 2021-09-16 2024-04-02 Vermeer Manufacturing Company Horizontal directional drill with freewheel mode
US12110753B2 (en) 2022-03-28 2024-10-08 Vermeer Manufacturing Company Horizontal directional drill with freewheel mode

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1486978A (en) * 1975-02-28 1977-09-28 Coal Ind Mineral-mining machine
EP0238356B1 (en) * 1986-03-20 1992-12-16 Monyana Engineering Services Control system for a fluid actuated motor

Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2453309A (en) * 1939-12-29 1948-11-09 Oilgear Co Vane type hydraulic motor
US2789542A (en) * 1953-09-23 1957-04-23 New York Air Brake Co Hydraulic motor control system
US2831554A (en) * 1951-07-30 1958-04-22 Ingersoll Rand Co Control device for hoists
US3036435A (en) * 1955-04-25 1962-05-29 Tubular Structures Corp Of Ame Portable builder's hoist
US3184018A (en) * 1962-12-14 1965-05-18 Gearmatic Co Ltd Reversible drive assembly including fluid-powered prime mover
GB1004080A (en) * 1961-11-14 1965-09-08 Alvis Ltd Piston pump having a variable stroke
US3230715A (en) * 1964-01-24 1966-01-25 Alfred Teves K G Hydraulic-machine system with idling mode
US3244405A (en) * 1964-02-17 1966-04-05 Aro Corp Cable hoist brake
US3283668A (en) * 1965-03-01 1966-11-08 Suomen Autoteollisuus Ab Oy Hydraulic motor with piston holding means
US3323779A (en) * 1965-09-13 1967-06-06 Ingersoll Rand Co Overhead hoist and brake therefor
US3396666A (en) * 1965-12-13 1968-08-13 Borg Warner Transmission with variable volume vane pump
US3416452A (en) * 1966-12-29 1968-12-17 Gen Signal Corp Controls for variable displacement pumps
US3527144A (en) * 1967-01-27 1970-09-08 Nat Res Dev Hydraulic motors and pumps
US3662551A (en) * 1970-08-19 1972-05-16 Nutron Corp Fluid pressure controlling
US3685290A (en) * 1970-04-10 1972-08-22 Linde Ag Overload system for a hydrostatic-drive apparatus

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3039576A (en) * 1959-12-30 1962-06-19 Clark Equipment Co Fluid system for a windlass
FR1425800A (fr) * 1965-02-27 1966-01-24 Suomen Autoteollisuus Ab Oy Moteur hydraulique destiné spécialement aux véhicules
US3511131A (en) * 1968-06-24 1970-05-12 Deere & Co Hydraulic motor

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2453309A (en) * 1939-12-29 1948-11-09 Oilgear Co Vane type hydraulic motor
US2831554A (en) * 1951-07-30 1958-04-22 Ingersoll Rand Co Control device for hoists
US2789542A (en) * 1953-09-23 1957-04-23 New York Air Brake Co Hydraulic motor control system
US3036435A (en) * 1955-04-25 1962-05-29 Tubular Structures Corp Of Ame Portable builder's hoist
GB1004080A (en) * 1961-11-14 1965-09-08 Alvis Ltd Piston pump having a variable stroke
US3184018A (en) * 1962-12-14 1965-05-18 Gearmatic Co Ltd Reversible drive assembly including fluid-powered prime mover
US3230715A (en) * 1964-01-24 1966-01-25 Alfred Teves K G Hydraulic-machine system with idling mode
US3244405A (en) * 1964-02-17 1966-04-05 Aro Corp Cable hoist brake
US3283668A (en) * 1965-03-01 1966-11-08 Suomen Autoteollisuus Ab Oy Hydraulic motor with piston holding means
US3323779A (en) * 1965-09-13 1967-06-06 Ingersoll Rand Co Overhead hoist and brake therefor
US3396666A (en) * 1965-12-13 1968-08-13 Borg Warner Transmission with variable volume vane pump
US3416452A (en) * 1966-12-29 1968-12-17 Gen Signal Corp Controls for variable displacement pumps
US3527144A (en) * 1967-01-27 1970-09-08 Nat Res Dev Hydraulic motors and pumps
US3685290A (en) * 1970-04-10 1972-08-22 Linde Ag Overload system for a hydrostatic-drive apparatus
US3662551A (en) * 1970-08-19 1972-05-16 Nutron Corp Fluid pressure controlling

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3995973A (en) * 1975-09-04 1976-12-07 Deere & Company Variable displacement hydraulic system
US4381701A (en) * 1979-09-06 1983-05-03 Regie Nationale Des Usines Renault Servomotor featuring a servovalve controlling a hydraulic drum motor
US6644562B2 (en) * 2000-10-13 2003-11-11 Maquinas Agricolas Jacto S.A. Dynamic counterweight mechanism for one-sided sprayers
US20130205762A1 (en) * 2011-11-29 2013-08-15 Vanguard Equipment, Inc. Auxiliary flow valve system and method for managing load flow requirements for auxiliary functions on a tractor hydraulic system
US9739495B2 (en) 2013-04-05 2017-08-22 Siang Teik Teoh Coaxial ventilator
US9890964B2 (en) 2013-04-05 2018-02-13 Siang Teik Teoh Coaxial ventilator
US20140338317A1 (en) * 2013-05-20 2014-11-20 Komatsu Ltd. Pipelayer
US9021796B2 (en) * 2013-05-20 2015-05-05 Komatsu Ltd. Pipelayer
US20160207744A1 (en) * 2013-10-31 2016-07-21 Komatsu Ltd Winch for pipelayer and pipelayer equipped with same
US9617126B2 (en) * 2013-10-31 2017-04-11 Komatsu Ltd. Winch for pipelayer and pipelayer equipped with same
WO2015162229A1 (de) * 2014-04-23 2015-10-29 Putzmeister Engineering Gmbh Steuerungssystem für eine hydraulische arbeitsmaschine
US10267343B2 (en) 2014-04-23 2019-04-23 Putzmeister Engineering Gmbh Control system for a hydraulic work machine
US9663335B2 (en) 2014-08-27 2017-05-30 Caterpillar Inc. Hydraulic winch control system and method
US11247879B2 (en) 2015-07-14 2022-02-15 Mhwirth As Winch system
NO20160714A1 (en) * 2016-04-28 2017-01-16 Mhwirth As A winch system
US10807839B2 (en) * 2018-05-07 2020-10-20 Caterpillar Inc. Pipelayer machine having hoisting system with pivotable fairlead
US20190337776A1 (en) * 2018-05-07 2019-11-07 Caterpillar Inc. Pipelayer machine having hoisting system with pivotable fairlead
US10773934B2 (en) * 2018-05-21 2020-09-15 Caterpillar Inc. Machine having hoisting system with instrumented fairlead
US20190352148A1 (en) * 2018-05-21 2019-11-21 Caterpillar Inc. Machine having hoisting system with instrumented fairlead
US11148915B2 (en) * 2019-09-19 2021-10-19 Caterpillar Inc. Boom assembly and method of assembly thereof
US11946372B2 (en) 2021-09-16 2024-04-02 Vermeer Manufacturing Company Horizontal directional drill with freewheel mode
US12371947B2 (en) 2021-09-16 2025-07-29 Vermeer Manufacturing Company Horizontal directional drill with freewheel mode
US12110753B2 (en) 2022-03-28 2024-10-08 Vermeer Manufacturing Company Horizontal directional drill with freewheel mode
US12281531B2 (en) 2022-03-28 2025-04-22 Vermeer Manufacturing Company Horizontal directional drill with freewheel mode
US12320219B2 (en) 2022-03-28 2025-06-03 Vermeer Manufacturing Company Horizontal directional drill with freewheel mode
US12371946B2 (en) 2022-03-28 2025-07-29 Vermeer Manufacturing Company Horizontal directional drill with freewheel mode

Also Published As

Publication number Publication date
GB1335386A (en) 1973-10-24
SE377103B (cs) 1975-06-23
DE2101750A1 (de) 1972-01-05
FR2096496B1 (cs) 1976-04-16
FR2096496A1 (cs) 1972-02-18

Similar Documents

Publication Publication Date Title
US3815478A (en) Pipelayer hydraulic drawworks with free-fall
US2316926A (en) Power transmission
US3685290A (en) Overload system for a hydrostatic-drive apparatus
US3249336A (en) Hydraulic winch control mechanism
US3780990A (en) Brake controlling device
US3768263A (en) Hydraulic control system for two-speed winch
US3776518A (en) Winch and control means therefor
JPS58146702A (ja) 油圧制御システム
US3578787A (en) Control system
US3893572A (en) Systems for operating and controlling hydraulically driven winches, hoists, windlasses and the like
US3972185A (en) Hydraulic system for a pipelayer
US4100973A (en) Side load protection arrangement for rotating equipment
US4382360A (en) Unloading arrangement for hydraulic swing circuit or the like
US3988008A (en) Power lowering system
US3458053A (en) Cable control apparatus
US3253683A (en) Safety circuit
US3972186A (en) Speed override control for hydraulic motors
US3132622A (en) Two-sided hydraulic system
US4126082A (en) Travel-brake control system
JPH0227522B2 (ja) Fukusukonoyuatsumootanoseigyokairosochi
JPS58174702A (ja) 動力伝達装置
US2655000A (en) Pump and motor hydraulic system and control valve means therefor
SU1763350A1 (ru) Гидравлический привод лебедки
US3592346A (en) Winching with greater speed downwardly
JP2009107833A (ja) ウインチ装置

Legal Events

Date Code Title Description
AS Assignment

Owner name: CATERPILLAR INC., 100 N.E. ADAMS STREET, PEORIA, I

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:CATERPILLAR TRACTOR CO., A CORP. OF CALIF.;REEL/FRAME:004669/0905

Effective date: 19860515

Owner name: CATERPILLAR INC., A CORP. OF DE.,ILLINOIS

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:CATERPILLAR TRACTOR CO., A CORP. OF CALIF.;REEL/FRAME:004669/0905

Effective date: 19860515