US3895779A - Hoisting winch, in particular for a boring machine - Google Patents

Hoisting winch, in particular for a boring machine Download PDF

Info

Publication number
US3895779A
US3895779A US403004A US40300473A US3895779A US 3895779 A US3895779 A US 3895779A US 403004 A US403004 A US 403004A US 40300473 A US40300473 A US 40300473A US 3895779 A US3895779 A US 3895779A
Authority
US
United States
Prior art keywords
winch
fluid pressure
pipe means
motor
drum
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
US403004A
Other languages
English (en)
Inventor
Pierre Cassez
Claude Pelisson
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Application granted granted Critical
Publication of US3895779A publication Critical patent/US3895779A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • B66D2700/00—Capstans, winches or hoists
    • B66D2700/01—Winches, capstans or pivots
    • B66D2700/0125—Motor operated winches
    • B66D2700/0133—Fluid actuated

Definitions

  • a hydraulic drive motor is permanently coupled with the drum and comprises a stator and a rotor rotated by application of a main fluid pressure and capable of being rendered freely rotative relative to the stator by application of an auxiliary control fluid pressure.
  • a fluid supply device is adapted to supply in an alternating manner the main fluid pressure for raising the load and the auxiliary control pressure for allowing the load to fall freely.
  • the present invention relates to hoisting winches and more particularly to hoisting winches whereby it is possible to hoist a load and allow the load to fall freely.
  • winches are employed in boring machines which comprise a grab bucket of the percussion or hammer type which produces a bored hole by successive impacts on the bottom of the hole and by successive discharges of material which is broken up by the impacts of the bucket. The bucket thereafter brings the material to the surface of the ground.
  • An object of the invention is to provide a hoisting winch of the type indicated hereinbefore which avoids use of a mechanical clutch device between the drive motor and the winch shaft and which consequently facilitates the co-ordination of the various operations to be carried out.
  • the invention provides a winch for hoisting a load and allowing the load to fall freely and comprising a rotatably mounted drum around which drum a traction cable is wound, the cable being attached to the load, and a drive motor for driving the winch, wherein said motor is permanently coupled to the drum and comprises a hydraulic motor whose rotor is capable of rotating freely with respect to the stator, that is to say, is capable of free-wheeling with respect to the stator, upon application of an auxiliary control pressure, said winch further comprising a supply device adapted to supply in an alternating manner a main pressure for operating the motor for raising the load and the auxiliary control pressure for the free fall of this load.
  • FIG. I is a diagrammatic side elevational view of a boring machine comprising a percussion grab-bucket in which there is employed a hoisting winch according to the invention
  • FIG. 2 is a partial elevational view, partly in section, of a winch according to the invention.
  • FIG. 3 is a side elevational view, with parts cut away, of the winch shown in FIG. 2;
  • FIG. 4 is a hydraulic diagram of the winch according to the invention.
  • FIG. 5 shows a perspective diagrammatic view of a hydraulic motor used for the winch of FIG. 2-4.
  • the winch according to the invention permits raising a load and allowing the load to fall freely with possibility of a regulation of its speed of descent.
  • winches are employed in particular in boring machines employing a bucket or boring bit, in dredging machines for driving the bucket, in machines for cutting trenches by means of a bucket or boring bit, or like machines.
  • the boring machine comprises a vertical boring column A retained by guys B to a chassis C which may be mobile or stationary.
  • a chassis C which may be mobile or stationary.
  • Mounted on the chassis C is an internal combustion engine D and a hoisting winch E according to the invention which drives, through a cable F, the bucket in its up and down movement between the top G of the column A and the bottom of the bored hole.
  • the bucket is not visible and that the boring machine is only represented diagrammatically since it does not form part of the invention.
  • This winch is mounted on a base I from which vertically extend two supports 2 and 3. Mounted in these supports is a drum 4 which is adapted to receive a cable F shown in FIG. I and is rotatable about an axis XX.
  • the drum 4 comprises a cylinder 5 having at one end an attached end flange 6 secured to a housing 7 of a hydraulic motor 8.
  • the stator 9 of the motor 8 is located inside the rotor and secured to the support 2 so as to be prevented from rotating.
  • the cylinder 5 has at the end thereof opposed to the flange 6 an end wall 10 to which a wheel 11 is connected to rotate with the wall 10, the wheel having on its periphery a cylindrical braking surface 12 with which co-operates a brake band 13.
  • the wall 10 is integral with a journal 14 supported in a bearing 15 which is mounted in the support 3.
  • a protection disc 16 is provided and defines one end of the surface on which the cable F may be wound around the drum 4.
  • the brake band 13 is secured at one end to a tensioning device 17 (FIG. 3) which is pivoted at 18 to the base 1 of the winch.
  • the other end of the brake band 13 is pivoted to an arm 19 which is integral with a lever 20, the assembly comprising the arm 19 and the lever 20 being rotatable about a pivot 21 which is integral with the base 1 of the winch.
  • the free end of the lever 20 is connected to a rod 22 of a cylinder device 23 whose cylinder is pivoted at 24 to the base 1.
  • a spring 27 which acts on the lever 20in such manner that when the cylinder device 23 is not connected to a source of pressure, the brake band 16 is applied against the peripheral surface 12 of the wheel 11 and the brake device is in its applied position.
  • the hydraulic motor 8 is of the reversible type, its rotor and its stator being rotatable with respect to each other by application of the main hydraulic pressure so as to produce a driving torque. Moreover, the rotor and the stator are rotatable with respect to each other substantially without friction and at very high speed upon cessation of the main hydraulic pressure and application of a command pressure which produces of course no torque.
  • a motor of this type which is particularly appropriate for the winch according to the invention is that manufactured and sold by the Swedish firm Hagglunds under reference N 4150 and whose main hydraulic output is 4.71 litres/revolution.
  • Such a motor comprises (FIG. 5) a stator H in which are movable radial pistons l subjected to the main pressure.
  • Rotatable about this stator is a rotor K which is provided with a ring L having cams M. Rollers N integral with the pistons I undergo a radial to-and-fro movement while being in contact with the cam ring L. In the course of operation of the motor, the main pressure applied to the pistons l urges the rollers N to remain constantly in contact with the cam ring L of the rotor K so as to impart thereto a movement of rotation.
  • This motor also has a control port 80, which, when it is subjected to a second given auxiliary control pressure, causes the radial pistons I to move toward the axis Y Y of the motor and separates the rollers N from the cam ring L. Under these conditions, the rotor K of the motor free-wheels with respect to the stator H, the frictional forces being extremely low and resulting exclusively from the bearings of the motor.
  • this motor may be particularly appropriate for association with the winch according to the invention it is possible to employ other reversible hydraulic motors.
  • the motor CH 800 sold by the firm Tractel.
  • This motor comprises axial pistonswhich act on a moving plate, the pistons being capable of being separated from the plate so as to render the rotor freely rotatable with respect to the stator.
  • the winch is associated with a control device whose preferred construction is shown in FIG. 4.
  • the latter shows diagrammatically the hydraulic motor 8 shown in FIG. 2 and the flow ports 8a and 8b to which the main pressure is applied and the control or command port 8c which receives the control or command pressure for rendering the rotor K freely rotatable with respect to the stator H.
  • FIG. 4 there is also shown diagrammatically the cylinder device 23 and the brake band 13 acting on the wheel 11.
  • the reversible hydraulic motor 8 is supplied by a pump unit 28 comprising two pumps 29 and 30 having respectively a high output flow and a low output flow. These pumps 29 and 30 draw in the hydraulic fluid from a tank 31 through the filter-32.
  • the presence of the two pumps 29 and 30 enables the motor 8 to be driven at different speeds.
  • the pump 30 is connected to a pipe 33 which is connected through a back-pressure valve 34 to a control directional valve 35 having five ports a to e.
  • This valve can occupy three positions the intermediate position of which is the stable position shown in FIG. 4.
  • the backpressure valve 34 is connected to a pipe 36 which is connected to a pipe 37 constituting the main return circuit of the hydraulic fluid.
  • This pipe opens into the tank 31 through a back-pressure valve 38.
  • the valve 35 may be put into the other positions manually.
  • the port a of the valve 35 may be put in communication with a pipe 39 which is directly connected to the port 8a of the motor 8.
  • the port a is also connected to the safety valve 34 connected to the port I) of the valve 35.
  • the pipe 39 is connected to the port c and the pipe 36 is connected to the port d.
  • the valve 35 has a port e which is connected to a pipe 40 leading directly to the tank 31.
  • the motor 8 can be supplied with fluid by the pump 30 when the valve 35 is placed in the position in which the ports a and c are connected to each other.
  • a supply circuit to which the pump 29 delivers fluid at a high rate of flow.
  • the pump 29 is connected to a pipe 41 which leads to a second directional valve 42 having four ports a, b, c and d. It is by means of this valve 42 that the pipe 41 may be put in communication with the back-pressure valve 34 when the port a and the port c are manually connected to each other.
  • the valve 42 normally occupies the position shown in FIG. 4 in which the ports 12 and d are in communication with each other so that in its position of rest the valve 42 allows the pump 29 to deliver fluid directly to the return pipe 37 through a pipe 43.
  • the pumps 29 and 30 are shown connected to the return pipe 37 through safety valves 44 and 45 which are calibrated or set at pressures which have been calculated in accordance with the pressures furnished by the pumps so as to put them in short-circuit when the set pressures are reached.
  • the port 8b of the motor 8 is normally connected through a pipe 46 to a back-pressure valve 47 which is also connected to the pipe 37.
  • the pipe 46 is connected to a three-way valve 48 to which a pipe 49 subjected to the output pressure of the pump 29 is connected.
  • One way of the valve 48 is connected to a check valve 50 connected to the pipe 39.
  • the cylinder device 23 can receive a control pressure from a cylinder device-pilot valve 51 for releasing the brake controlled by a lever 52 accessible to the operator. This connection is established through a selector 53 having three ports a, b and c, the port 0 being connected to the pipe 39.
  • the cylinder device-pilot valve 51 is connected directly to the control port of the hydraulic motor 8 through a pipe 54 to which the outlet of an accumulator 55 is also connected.
  • the pipe 54 is connected to the tank through a return pipe 56 in which is inserted a valve 57 set or calibrated to open at a predetermined pressure.
  • the selector 53 is connected through a pipe 58 to a control port a of a piloted check valve 59 connected to the tank 31 and to the safety valves 44 and 45.
  • the latter are each provided with control ports a through which a control or command pressure may be applied so as to suppress the pressure setting of the valve.
  • a check valve 60 is inserted between thecheck valve 59 and the control port a of the safety valve 44.
  • the pipes 37 and 36 are connected to each other through a restriction 61 and a check valve 62 connected in series.
  • the hoisting winch just described operates in the following manner:
  • the brake band 13 When the boring machine is at rest, the brake band 13 is applied against the braking surface of the wheel 11 so as to prevent the winch from rotating, the braking force applied to the band 13 being determined solely by the tension of the spring 27 placed in the cylinder device 23.
  • the machine is completely safe in operation. If the hydraulic pressure applied to the cylinder device 23 disappears, for example owing to a broken pipe, rotation of the winch is immediately stopped.
  • the valve 335 permits a progressive control of the rate of flow of hydraulic fluid therethrough and therefore controls the speed of the motor 8, that is to say the speed of the load.
  • the motor 8 can rotate at two speeds.
  • the higher speed serves to furnish a normal hoisting force for hoisting the bucket and the lower speed permits applying to the traction cable F a higher hoisting force which may be necessary for extracting a bucket subjected to the suction effect in the bored hole, or for de-blocking a boring tool, or for carrying out auxiliary operations.
  • the two hoisting forces are determined by the different calibrations or settings of the safety valves 44 and 45.
  • the safety device precluding an accidental hoisting command during the free-wheeling of the motor 8.
  • valve 35 When the valve 35 is actuated so as to interconnect its ports a and c, the output flow from the pump 30 is applied to the pipe 39 and consequently to the inlet port 80 of the motor, the return being through the valve 47, the pipe 37 and the valve 38.
  • the accumulator 55 under a pressure of 0.5 kg/sq.cm which immediately returns its volume of oil stored in accordance with the pressure of the circuit which is' preferably 0.750 kg/sq.cm;
  • This motor housing pressurizing circuit supplied by way of the restriction 61 for a small part.
  • This motor housing pressurizing circuit comprises:
  • valve 57 set at about 0.750 kg/sq.cm and em ployed as pressure limiter;
  • check valve 62 which maintains the pressure in the circuit upon stoppage of the machine and the pump unit 28;
  • This pressurizing circuit which is constantly under pressure, maintains the motor constantly in a freewheeling condition in the absence of other commands given by the operator. Thus the motor is always ready to permit a free fall of the load.
  • the backpressure valve 38 ensures an additional pressure drop by its calibration or setting so as to obtain a pressure of l kg/sq.cm at the inlet of the restriction 61.
  • valve 35 which connects the port 8a of the motor to the tank 31 is in position of rest shown in FIG. 4.
  • the check valve 50 which connects the port 8b of the motor to the pipe 40. As the setting of the valve 50 is 0.050 kg/sq.cm there remains only a very low pressure at the port 8b. Without this valve, the port 8b would be under a retained pressure (2 kg/sq.cm) produced by the valve 47 and the free-wheeling of the motor could not be suitably achieved.
  • the accumulator 55 performs a second function.
  • the pistons l of the motor When the hoisting is commanded through the valve 35, the pistons l of the motor extend and bear against the cam ring L at the speed corresponding to the flow of the oil supply.
  • the accumulator then absorbs the volume of oil delivered from the housing of the motor which is equal to the output volume of the pistons l with a variation in pressure which does not exceed the maximum allowed pressure of l kg/sq.cm.
  • the valve 57 discharges to the tank 31 so as to re-establish the normal pressure of the circuit (0.750 kg/sq.cm).
  • the double control or command is effected by the selector 53.
  • a pressure is established in the cylinder device 23 which reduces or completely cancels out the force of the spring 27.
  • This variable hydraulic action brought about by the operator permits achieving a variable hydraulic pull on the brake band and affords a very sensitive progressivity in the braking.
  • the operator acts in the manner described hereinbefore by utilizing the complete travel of the cylinder device 51 so as to transmit the pressure and volume of the oil to the cylinder device 23 and compress the spring 27. The compression of the spring completely releases the brake band 13 and causes the free fall of the load.
  • the spring 27 immediately resumes its braking action as soon as the hydraulic pressure in the cylinder device 23 is released.
  • the selector 53 indeed permits the decompression and return of the oil from the port b to the port a in the first case and from the port b to the port 0 in the second case.
  • This brake device has two main advantages, namely the progressivity and the sensitivity in the manual release of the braking with possibility of allowing the free fall of the load and the safety of operation by brake action in the case of breakage of a hydraulic pipe.
  • the speed in the free falling of the load may reach 500600 rpm whereas the normal speed is 70 rpm.
  • the motor would act as a hydraulic pump and the high speed would produce the continuous percussion of the rollers N against the cam ring L without possibility of a coupling of the rotor K and stator l-l since the supply of oil would be very distinctly insufficient and the inertia of the moving parts would be excessive.
  • the safety device comprises the pipe 58 which connects the outlet of the cylinder devicepilot valve 51 to the control port a of the piloted valve 59, the check valve 60 and the back-pressure valve 34.
  • the piloted valve 59 When there is no brake release order, the piloted valve 59 is normally closed and permits the operation of the safety valves at the desired pressure settings. For this operation, the valve 60 isolates the internal piloting circuits of the safety valves 44 and 45 by avoiding the discharge from the valve 45 to the valve 44.
  • Actuation of the three-way valve 48 interconnects through its ports b and c the delivery side of the pump 29 and the outlet 8b of the hydraulic motor 8.
  • the residual pressure at the safety valves 44 and 45 employed at this moment as discharge valves, produces the reverse rotation of the motor by way of the port 8b.
  • the pressure ensuring the reverse rotation is maintained and limited by the back-pressure valve 47.
  • the pipe 49 may be connected to the port 0 of the valve 42 instead of putting it in communication with the safety valve 44. This connection is shown in dotted lines by the pipe 49A in FIG. 4.
  • the three-way valve 48 In order to once more effect the boring with the load falling freely, the three-way valve 48 must be returned to its initial position (intercommunication of the ports a and b).
  • a winch for hoisting a load and allowing the load to fall freely comprising a support, a drum which is rotatably mounted relative to the support, a traction cable wound round the drum for attaching to the load, a hydraulic drive motor permanently coupled to said drum for rotating the drum and comprising first and second main fluid pressure ports, a control fluid pressure port, a stator and a rotor, said winch further comprising a fluid supply device having pump means, a tank and a control device for selectively connecting said main fluid pressure ports to said pump means and said tank, said control device comprising first pipe means connecting said second main fluid pressure port to said tank and second pipe means connecting said first pipe means to said control fluid pressure inlet port for continuously applying thereto a control fluid pressure, whereby upon actuation of said control device, said rotor is drivable by application of main fluid pressure to said first inlet port and capable of rotating freely with respect to said stator from the moment of release of said control device by virtue of control fluid pressure remaining in said second pipe means.
  • control device comprises an accumulator connected to said second pipe means for providing the volume of fluid required by said motor when said rotor passes from its driven state to its freely rotating state.
  • control device further comprises a restriction and a check valve connected between said first and second pipe means.
  • a winch as claimed in claim 1, comprising a calibrated valve connected between said second pipe means and said tank for determining the maximum value of the control fluid pressure prevailing in said second pipe means.
  • a winch as claimed in claim 5, wherein said brake device comprises a brake member combined with said drum so as to be capable of braking and stopping the latter, resiliently yieldable means for biasing the brake member against the drum, a second hydraulic cylinder device for releasing the brake member and a selector connected to said first and second hydraulic cylinder devices and to said first main fluid pressure port of said motor and being so arranged as to selectively apply fluid pressure to said second hydraulic cylinder device or to said first main fluid pressure port depending respectively upon'whether said first hydraulic cylinder device or said control device is actuated.
  • control device comprises an accumulator connected to said second pipe'means for providing the volume of fluid required by said motor when said rotor passes from its'driven state to its freely rotating state.
  • control device further comprises a restriction and a check valve connected between said first and second pipe means.
  • control device comprises safety valve means connected to said pump means and to said tank for selectively shortcircuiting said pump means, said safety valve means being connected to said first hydraulic cylinder device so as to be actuated upon actuation of said first hydraulic cylinder device.
  • a winch as claimed in claim 1 comprising third pipe means connecting said main fluid pressure ports of said motor to each other, and a check valve connected in said third pipe means for isolating said ports when said motor is in the hoisting mode of operation by actuation of said control device.
  • connection between said high-flow pump and its associated safety valve comprises a branch pipe means connected to a three-way valve so arranged as to be selectively capable to apply residual pressure generated at said safety valve by virtue of shortcircuiting of said high-flow pump, to said second main fluid pressure port of said motor for ensuring inverse rotation of the latter.
  • a winch as claimed in claim 12, comprising a pipe for series connecting said two control directional valves and a branch connection on said pipe, said branch connection being connected to a three-way valve so arranged as to be selectively capable to apply a slight fluid pressure to said second main fluid pressure port of said motor for ensuring inverse rotation of the latter.
  • a winch for hoisting a load and allowing the load to fall freely comprising a support, a drum which is rotatably mounted relative to the support, a traction 'cable wound round the drum for attaching to the load,
  • a hydraulic drive motor permanently coupled to said drum for rotating the drum and comprising first and second main fluid pressure ports, a control fluid pressure port, a stator and a rotor
  • said winch further comprising a supply device having a high-flow pump, a lowflow pump, a tank and control device, said control device comprising series connected control directional valves respectively connecting the high-flow pump and the low-flow pump to said motor, first pipe means connecting said second main fluid pressure port to said tank and second pipe means connecting said first pipe means to said control fluid pressure inlet port, an accumulator connected to said second pipe means, safety valves connected respectively to each of said pumps and to said first pipe means for selectively shortcircuiting said pumps, said winch further comprising a brake member resiliently biased against said drum, a brake release cylinder for releasing said brake member from said drum and a pilot cylinder selectively connected to said brake release cylinder for progressively actuating the latter and permanently connected to said

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
US403004A 1972-10-03 1973-10-03 Hoisting winch, in particular for a boring machine Expired - Lifetime US3895779A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR7234951A FR2201241B1 (enrdf_load_stackoverflow) 1972-10-03 1972-10-03

Publications (1)

Publication Number Publication Date
US3895779A true US3895779A (en) 1975-07-22

Family

ID=9105107

Family Applications (1)

Application Number Title Priority Date Filing Date
US403004A Expired - Lifetime US3895779A (en) 1972-10-03 1973-10-03 Hoisting winch, in particular for a boring machine

Country Status (9)

Country Link
US (1) US3895779A (enrdf_load_stackoverflow)
JP (1) JPS49132750A (enrdf_load_stackoverflow)
BE (1) BE805542A (enrdf_load_stackoverflow)
CH (1) CH578482A5 (enrdf_load_stackoverflow)
DE (1) DE2349661A1 (enrdf_load_stackoverflow)
FR (1) FR2201241B1 (enrdf_load_stackoverflow)
GB (1) GB1439624A (enrdf_load_stackoverflow)
IT (1) IT999604B (enrdf_load_stackoverflow)
NL (1) NL7313610A (enrdf_load_stackoverflow)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3988008A (en) * 1975-10-23 1976-10-26 The Manitowoc Company, Inc. Power lowering system
US4046060A (en) * 1974-08-22 1977-09-06 Gewerkschaft Eisenhutte Westfalia Hydraulic control systems for use with mining apparatus
US4102248A (en) * 1976-03-08 1978-07-25 Westinghouse Electric Corp. Protective system for pneumatically operated devices
US4244276A (en) * 1979-07-16 1981-01-13 Teijin Seiki Company Limited Hydraulic circuit
US4510971A (en) * 1983-07-22 1985-04-16 Fmc Corporation Circuitry for operating an extendible boom and a service line
US4756366A (en) * 1987-03-10 1988-07-12 Crane Carrier, Co. Well servicing methods using a hydraulic actuated workover mast
US20130034390A1 (en) * 2009-10-26 2013-02-07 John Arthur Mair Reeling and unreeling an internally clad metal pipeline
US20140332204A1 (en) * 2011-12-02 2014-11-13 Schlumberger Technology Corporation Quick Drum Connect
US9688520B1 (en) * 2016-12-19 2017-06-27 Ellicott Dredges, Llc Winch assembly
US11136940B2 (en) * 2019-05-31 2021-10-05 Goodrich Actuation Systems Limited Hydraulic thrust reverser actuation system

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS56165696A (en) * 1980-05-26 1981-12-19 Komatsu Mfg Co Ltd Brake gear for oil pressure type crane winch
AT367162B (de) * 1980-08-12 1982-06-11 Oemv Ag Swabwinde zur verwendung bei der erdoel- bzw. erd- gasfoerderung
US4516755A (en) * 1982-06-02 1985-05-14 Kabushiki Kaisha Komatsu Seisakusho Hydraulic winch control system
JP7186641B2 (ja) * 2019-03-04 2022-12-09 住友重機械建機クレーン株式会社 クレーンのウインチ装置及びクレーン

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3283668A (en) * 1965-03-01 1966-11-08 Suomen Autoteollisuus Ab Oy Hydraulic motor with piston holding means
US3776513A (en) * 1971-05-10 1973-12-04 F Mosley Crane

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3283668A (en) * 1965-03-01 1966-11-08 Suomen Autoteollisuus Ab Oy Hydraulic motor with piston holding means
US3776513A (en) * 1971-05-10 1973-12-04 F Mosley Crane

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4046060A (en) * 1974-08-22 1977-09-06 Gewerkschaft Eisenhutte Westfalia Hydraulic control systems for use with mining apparatus
US3988008A (en) * 1975-10-23 1976-10-26 The Manitowoc Company, Inc. Power lowering system
US4102248A (en) * 1976-03-08 1978-07-25 Westinghouse Electric Corp. Protective system for pneumatically operated devices
US4244276A (en) * 1979-07-16 1981-01-13 Teijin Seiki Company Limited Hydraulic circuit
US4510971A (en) * 1983-07-22 1985-04-16 Fmc Corporation Circuitry for operating an extendible boom and a service line
US4756366A (en) * 1987-03-10 1988-07-12 Crane Carrier, Co. Well servicing methods using a hydraulic actuated workover mast
US20130034390A1 (en) * 2009-10-26 2013-02-07 John Arthur Mair Reeling and unreeling an internally clad metal pipeline
US8876433B2 (en) * 2009-10-26 2014-11-04 Subsea 7 Limited Method of reeling and unreeling an internally clad metal pipeline
US20140332204A1 (en) * 2011-12-02 2014-11-13 Schlumberger Technology Corporation Quick Drum Connect
US9688520B1 (en) * 2016-12-19 2017-06-27 Ellicott Dredges, Llc Winch assembly
US11136940B2 (en) * 2019-05-31 2021-10-05 Goodrich Actuation Systems Limited Hydraulic thrust reverser actuation system
EP3744963B1 (en) * 2019-05-31 2024-10-30 Goodrich Actuation Systems Limited Hydraulic thrust reverser actuation system

Also Published As

Publication number Publication date
CH578482A5 (enrdf_load_stackoverflow) 1976-08-13
NL7313610A (enrdf_load_stackoverflow) 1974-04-05
DE2349661A1 (de) 1974-04-18
BE805542A (fr) 1974-02-01
IT999604B (it) 1976-03-10
JPS49132750A (enrdf_load_stackoverflow) 1974-12-19
FR2201241A1 (enrdf_load_stackoverflow) 1974-04-26
GB1439624A (en) 1976-06-16
FR2201241B1 (enrdf_load_stackoverflow) 1977-09-02

Similar Documents

Publication Publication Date Title
US3895779A (en) Hoisting winch, in particular for a boring machine
JPS60236990A (ja) 水力つり揚げ装置
JPH02159474A (ja) 油圧変速装置
US4458791A (en) Brake control system with metering pump relief
US4644849A (en) Locking apparatus of inertial mass drive hydraulic circuit system
US4100973A (en) Side load protection arrangement for rotating equipment
US4136855A (en) Hoist drum drive control
JPS6145891A (ja) ウインチ装置
US3851739A (en) Hoist reversing transmission with centrifugal speed control
JPH0689848B2 (ja) 液圧システム
JP4198371B2 (ja) ウインチの駆動制御装置
EP0819646A1 (en) Method and system for controlling the speed of a winch
JPS6017760B2 (ja) ウインチ制御装置
JP2752595B2 (ja) 油圧式ウインチ装置
US3733813A (en) Speed control system for hydraulic motor
JP2738660B2 (ja) 油圧式ウインチ装置
JP3508757B2 (ja) 油圧ウィンチ
JPH0355398B2 (enrdf_load_stackoverflow)
US11905147B2 (en) Method for the operation of a forestry winch and forestry winch
JP2000169090A (ja) 油圧巻上装置
JP2009107833A (ja) ウインチ装置
SU1763350A1 (ru) Гидравлический привод лебедки
JPH0725589A (ja) クレーンの旋回用油圧駆動装置
JP2597503B2 (ja) クレーン巻胴の制御装置
JPH0682407U (ja) ウインチドラム駆動用流体回路