EP0118340A2 - Hydraulische Notfallkontrollvorrichtung für einen Kran - Google Patents

Hydraulische Notfallkontrollvorrichtung für einen Kran Download PDF

Info

Publication number
EP0118340A2
EP0118340A2 EP84400241A EP84400241A EP0118340A2 EP 0118340 A2 EP0118340 A2 EP 0118340A2 EP 84400241 A EP84400241 A EP 84400241A EP 84400241 A EP84400241 A EP 84400241A EP 0118340 A2 EP0118340 A2 EP 0118340A2
Authority
EP
European Patent Office
Prior art keywords
power
hydraulic
load
valve
pressure
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.)
Withdrawn
Application number
EP84400241A
Other languages
English (en)
French (fr)
Other versions
EP0118340A3 (de
Inventor
William A Featherstone
Larry D. Shultz
Thomas C. Doan
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.)
Oil States Industries Inc
Original Assignee
Continental Emsco 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 Continental Emsco Co filed Critical Continental Emsco Co
Publication of EP0118340A2 publication Critical patent/EP0118340A2/de
Publication of EP0118340A3 publication Critical patent/EP0118340A3/de
Withdrawn legal-status Critical Current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
    • B66D1/28—Other constructional details
    • B66D1/40—Control devices
    • B66D1/42—Control devices non-automatic
    • B66D1/44—Control devices non-automatic pneumatic of hydraulic
    • 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
    • B66C23/88—Safety gear
    • B66C23/90—Devices for indicating or limiting lifting moment
    • 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

Definitions

  • the present invention relates to hydraulic systems for emergency shutdown and operation of a crane and more particularly to such hydraulic systems which are capable of controlling the load of a crane during an emergency control situation.
  • the whip hoist winch on cranes used for loading and discharging supply ships shall be equipped with a constant emergency release system with a hook capacity sufficient to keep a constant tension in the wire rope of approximately 1.5 tonnes.
  • the emergency release system shall work under all conditions, including power failure.
  • the emergency release switch or handle shall be effectively secured against inadvertent use, and the winch shall automatically, with a soft characteristic, return to normal hoisting, braking or holding conditions when the emergency release is disconnected".
  • item 5.11 requires that "the brakes shall be designed and constructed in such a way that it, within the shortest possible time, will be possible to lower and stop the full hook capacity manually and under full control in case of power failure or failure in the control system.
  • This invention provides a hydraulic control system for operation of a winding means having a drive means associated therewith.
  • the control system comprises a means for generating hydraulic power, conduit means capable of supplying hydraulic power to the drive means, a plurality of valving means capable of selectively supplying the hydraulic power to the drive means and a plurality of hand operable control means capable of effecting several operating modes of the control system by directing the hydraulic power to a select group of said conduit means and said valving means for a particular mode.
  • One of the operating modes besides normal operation, is a mode for letting out a load on the winding means when the normal hydraulic power is lost, while controlling the speed with which the load unwinds the winding means.
  • Additional operating modes for the control system include a means for letting out a load on the winding means when there is an accidental over-load, while maintaining a substantially constant tension from the winding means to the load; and a means for letting out a load on the winding means when there is an accidental over-load and there is total loss of normal hydraulic power.
  • a normal control mode an emergency non-powered load lowering mode for the main drum
  • an emergency non-powered load lowering mode for the auxiliary or whip drum an emergency release mode with and without constant tension for the auxiliary or whip drum (with the addition of some valves and minor modification to the circuit the emergency release could be used for the main drum or in combination on both drums).
  • the entire hydraulic system for the crane includes a number of components not represented in the hydraulic control system for the four modes of operation, shown in Figures 1-4, and for ease and simplification only those components of the overall crane hydraulic system necessary for the emergency control operating modes of the crane hydraulic system are referred to and shown in the following description.
  • the crane emergency control hydraulic system that is shown in figures 1 through 4 includes a pair of operator control elements: one for normal crane control and the other for emergency crane control, 2 pair of brakes: one for the main hoist drum, and one for the auxiliary or whip hoist drum; a pair of motors and their associates boxes: one for the main hoist drum and one for the auxiliary or whip hoist drum; a bank of four detented hand control valves for switching the crane hydraulic control system into one or another of its operating modes, a pressure make-up system for providing emergency power in the event of loss of power, such power make-up system being independent of the normal crane operating power system, and of several directional control valves controlling the direction of pressure flow generated either by the normal crane operating power system or the pressure make-up system, through the lines for effecting the different modes of operation.
  • the crane control system has been shown in each of its independently operating modes by highlighting those elements of the emergency hydraulic control system that are used in each of the individual operating modes.
  • the hydraulic control system will be described in terms of its several modes of operations.
  • the typical crane system is a Skagit Series Three Hundred Pedestal Crane powered by a two hundred and seventy horse power (270 h.p.) diesel engine operating at one thousand nine hundred and eighty (1980) rpm.
  • the system could also be employed with other types of prime movers such as an electric motor.
  • the horsepower rating of the prime mover is dependent on the hoist capacity and speed.
  • the engine supplies power to drive each of the four drive motors and their associated gear boxes, and supplies power to release the brakes associated therewith.
  • the engine power is controlled by means of a pair of operator controls that are operable in the normal crane operation condition.
  • the emergency control system can be activated in any of a variety of situations.
  • the primary purpose for engaging the emergency controls would be a loss of power, either total electrical power or a total or partial loss of hydraulic power, that results in a loss of power to the hydraulic controls, or accidental overload.
  • the first of the emergency control circuits to be described, the emergency non-powered load lowering system, is shown in Figures 1 and 2 for the auxiliary or whip drum and the main drum, respectively.
  • Both the main hoist drum and the auxiliary or whip hoist drum are provided with this system in order to allow the crane operator to lower a suspended load without power being supplied by the crane's diesel engine for powering the hydraulic circuitry and yet still enable the operator to handle the suspended load under full control.
  • the system provides a means for releasing the brakes for either the main hoist or the auxiliary or whip hoist, a means for controlling the speed with which the load suspended from either the main hoist or the auxiliary or whip hoist is lowered, and a means for stopping the load from lowering further, should that be necessary.
  • the non-powered load lowering system is primarily designed for operation where there is a loss of electrical power or a loss of the engine and the resulting loss of the hydraulic pressure necessary to operate the crane hydraulic control system to lower the load in normal operation.
  • use of the emergency non-powered load lowering system does require that the hydraulic motors of the main hoist or the auxiliary or whip hoist (which ever is being used) be in operational condition, i.e. the shutdown emergency can not have been caused by a failure of the hydraulic motors such that they are no longer functional as motors (or as pumps in a reverse direction). Should this be the case, then the non-powered load lowering system would not be able to function as anticipated.
  • the crane operator pulls one of the several detented hand valve control elements which are located in his cab console and which are positioned preferably near his right hand or within easy reach. There is a separate control valve handle to operate the NPLL system for the main hoist and to operate the NPLL system for the auxiliary or whip hoist.
  • the functioning of the non-powered load lowering system for each of the two modes of operation i.e. main hoist or the auxiliary or whip hoist, is identical and many common components are used in each system.
  • the operator activates the auxiliary or whip hoist non-powered load lowering mode by pulling the push-pull cable that triggers detented hand valve 20.
  • valve 20 When valve 20 is repositioned to the left hand port (herein after all references to valve ports are relative to the particular drawing Figure being described) pressure from accumulator 11 will flow via line 80 into line 82 and then through valve 20 and up to line 95 and 97. The accumulator pressure will then be directed via line 97 to shuttle valve 62 where it is directed via line 100 and energizes control valve 67, and to shuttle valves 38 and 39. From line 95 pressure is directed to shuttle valve 23 and then to the pilot positioning element on directional control valve 28 which allows relief valve 26 to become functional at a reduced pressure by venting relief valve 26 pilot port to the cranes hydraulic reservoir 68. The pressure that is directed to shuttle valve 38 goes via line 105 to the right hand pilot control element on directional valve 37.
  • valve 42 also serves to isolate the normal hydraulic system. Movement of valve 42 to the left serves to isolate any incoming pressure from the auxiliary or whip hoist motor. The auxiliary or whip hoist motor creates the pressure in line 117 when the brake (47) is released and speed control valve 29 is actuated by the crane operator activating the control valve 67.
  • the precharged accumulator 11 has (a) pressurized the control valve 67; (b) isolated the auxiliary or whip hoist normal hydraulic system controls, and (c) activated a special emergency make-up oil pressure system.
  • the control valve is a modulating joy stick of the dead-man type having two axes of operation.
  • the joy stick control handle is located to the front and right of the operator.
  • the joy stick control is used by the operator to release the auxiliary or whip hoist brake and to control the now non-powered crane load to lower the load at a controlled speed as determined by the crane operator's use of the joy stick.
  • the Series 300 Skagit Crane movement of the joy stick or operator control handle to the operator's left applies pressure to the hoist brake.
  • a variable pressure is directed to the auxiliary or whip hoist brake sufficient to release the brake. The operator therefor can start and stop load lowering as desired.
  • Movement of the operator control handle only in a forward direction will cause an increase in speed with which the load can be lowered. Combining the two movements, or moving the operator control handle at a forty-five degree angle, the operator can thereby release the brake and also start lowering or stop lowering the load.
  • the speed control line from valve 67, line 102 actually delivers its pressure to the left hand pilot positioning element of valve 29. This piloting allows the load induced pressure to enter line 108 and turn motor and pump 25.
  • This load-induced flow then travels via line 117 into directional control valve 37 which has already been positioned into its right hand valve position, through the right valve position into line 116, and then to directional control valve 35 which is still in its normal opened position, allowing pressure to travel directly through and onto line 113 to flow to control valve 30 and then on into and through the left hand port of directional control valve 29 and into line 108. From line 108 the pressure is directed to the make-up pump and motor 25. The incoming load-induced flow is directed into the pressure port of motor 25(a) causing motor 25(a) to rotate and drive pump 25(b) which draws hydraulic fluid from the crane hydraulic reservoir 68.
  • the pump 25b out-put pressure port is connected to the low pressure side of the auxiliary or whip hoist motor which is the suction port when the motor is acting as a pump.
  • output pressure and flow is sufficient to prevent the auxiliary or whip hoist motor (pump) from cavitating.
  • Pressurized fluid is forced to travel via line 87, via line 86, via line 94 to the auxiliary or whip hoist motor 45 completing the closed loop.
  • Pressurized fluid from line 86 also flows through check valve 17 to line 80 and into accumulator 11 or the control circuit. Any excess flow from the make-up pump and motor 25 is returned to the crane hydraulic reservoir 63 via relief valve 15.
  • flow control valve 30 which is set at a fixed flow and is pressure and temperature compensating to thereby limit the flow and the resulting maximum speed of the auxiliary or whip hoist drum when the auxiliary or whip hoist load is lowering.
  • flow through the modulating directional control valve 29 is controlled directly by the crane operator via the operator control handle in - the cab.
  • the pressure signal to the left hand pilot port, piloting the valve to the right, is related to the pilot pressure which in turn is related to the degree to which the operator control handle of valve 67 is moved in the forward direction.
  • the crane operator can control the speed with which a load is lowered to an infinite degree of variation by moving the operator control handle within the upper left hand quandrant of the operator control valve 67.
  • the crane operator merely moves the hoh-powered load lowering operator control valve 67 to its normal or centered position, This movement blocks the pressure porting on the operator cohtrol and serves to relieve the pressure on the modulating valve 29 (or speed control valve 29), and the pressure on the brake 47 allowing the brake 47 to reset and stop the load from continuing to lower.
  • the de-actlvation of the non-powered load lowering system is accomplished simply by having the crane operator replace the non-powered load lowering auxiliary or whip hoist handle of detented valve 20 to its normal position. This action isolates the non-powered load lowering system and allows the crane's normal operation to be reactivated. Therefore if power is later restored, the operator can proceed to operate the crane in a normal manner.
  • the design line speed for load lowering is in the range of from 0 feet per minute when the brake is set to approximately 60 feet per minute as determined by the flow control valve 30.
  • the loading required per line is approximately 1,000 pounds to provide this full line speed. Less of a load will reduce the maximum load lowering speed.
  • the non-powered load lowering system in the Skagit 300 Series Crane is designed to be capable of handling the crane's full rated capacity.
  • the line speeds and pulls given in this paragraph are typical of the Skagit 300 Series Cranes. However, the line speeds and pulls for a NPLL system used for another model or make crane may differ considerably from the above.
  • the accumulator hand pump is equipped with a hand pump element in order to feed pressure via line 83, through check valve 14 into line 80 and then into the accumulator.
  • This hand pump is primarily designed to provide a pressure build-up means should the pressure of the accumulator 11 be bled off prematurely.
  • the emergency non-powered load lowering system is also operable in a mode for operating the main hoist drum in a matter very similar to that as described above for the auxiliary or whip hoist drum.
  • the crane operator merely pulls the appropriate push-pull cable located in the cab to reposition detented valve 19 which serves a similar function to that of detented valve 20 for the auxiliary or whip hoist drum.
  • detented valve 19 When detented valve 19 is repositioned, the pressure flow is conducted from accumulator 11 via line 80 to line 82 and into and through the left hand port of detented valve 19. The pressure is then directed into line 96 and line 98.
  • Pressure from line 98 is also directed to shuttle va7 ve 62 and thence to operator control 67, activating the operator control in a manner similar to that for the auxiliary or whip hoist drum mode of the non-powered load lowering system.
  • the operator control 67 is used in this instance in the same matter as with the auxiliary or whip hoist drum mode forward movement of the operator control handle causes an increase in the speed with which the load is lowered by directing pressure to the left hand pilot positioning port of the modulating directional (speed) control valve 29. Movement to the left of the operator control handle, directs pressure via line 101 to directional control valve 51 which is in its upper most position, directing pressure into line 120 and into shuttle valve 48 and then into main hoist brake 46. Judicious movement of the operator control handle in the upper left hand quandrant of the control allows for controlled lowering of the load on the main hoist brake in a manner similar to that for the non-powered load lowering system mode for the auxiliary or whip hoist.
  • the load is allowed to start lowering thus causing the main hoist motor to rotate backwards and act as a pump. This creates a load-induced flow that travels to line 118. From line 118 the load-induced flow is directed to directional control valve 42 where it is ported to a blocked passage, since directional control valve 42 has been piloted to the right thereby blocking out crane normal circuit. From line 118 the load-induced flow is directed to directional control valve 37 which has been piloted to the right allowing load induced flow to directly transmit through the left hand position and into line 116 directing the load induced flow to directional control valve 35. Valve 35 is in its normal position and the load-induced flow enters line 113 and goes to flow control valve 30.
  • flow control valve 30 is set at a fixed flow and is pressure and temperature compensated to limit the maximum speed with which the main hoist drum is allowed to lower.
  • the load-induced flow is directed to repositioned modulating directional control valve 29, i.e. the speed control valve, which has been piloted to the right allowing the load induced flow to enter into line 108 which directs it to check valve 27 where it is blocked.
  • the load-induced flow enters the pressure port on the motor causing the motor 25a to rotate and drive the pump 25b which is directly coupled to the motor 25a.
  • the pump suction port is connected to the crane hydraulic reservoir 68 as with the auxiliary or whip hoist motor non powered load lowering mode.
  • the pressure flow is directed via line 87 to lines 85 and 86 and to check valve 24 where the flow is blocked.
  • the pressure flow in line 85 is directed to and through check valve 17 and into line 80 where it combines with the pressure flow from accumulator 11.
  • the flow in line 86 is directed to the main hoist motor 44 completing the closed loop, and line 94.
  • the flow entering the main hoist motor 44 serves to prevent the motor 44 from cavitating and the flow in 25b line 94 is blocked at motor 45 and eventually at check valve 52.
  • auxiliary or whip hoist non-powered load lowering mode to stop lowering the load the operator simply moves the non-powered load lowering operator control handle to its normal or centered position. This movement effectively blocks the pressure port on the operator control allowing the pressure on the speed control and brake release lines 101 and 102, respectively, to dump to the crane hydraulic reservoir 68.
  • the de-activation of the main drum non-powered load lowering mode is accomplished by simply placing the detented valve's 19 push pull handle back to its normal position. This return of detented valve 19 to its original position isolates the non powered load lowering system from the crane's normal operation and when power is eventually restored the operator can proceed to operate the crane in a normal manner.
  • auxiliary or whip hoist In addition to having the non powered load lowering system associated with the auxiliary or whip hoist there is also an emergency release system for the axuiliary or whip hoist.
  • a situation may occur wherein the hook on the auxiliary or whip hoist might become caught or fouled on some moving object, such as a work boat or barge requiring that the auxiliary or whip hoist line be effectively released in order to follow the direction of the moving object and to thereby avoid possible damage to either the moving object on which it is fouled or to the crane itself.
  • the crane operator is provided an additional push pull handle for the emergency release system. The crane operator pulls the push-pull handle to activate detented valve 21, as seen in Fig. 3.
  • the system is designed to operate with the crane hydraulic power unit still operating in order that the system will be constant tensioning. Once the operator has activated detented valve 21, automatically a preset line tension and a required line speed is maintained as the line associated with the auxiliary and whip hoist is hauled in or paid out as dictated by the requirements of the moving object to which it is caught or fouled.
  • the pressure that is directed from the precharged accumulator 11 and from the crane's normal control circuit pilot oil supply 103 assuming that the engine is still operating will (a) release the auxiliary or whip hoist brake through a series of shuttle valves; (b) isolate the crane's normal hydraulic speed and direction control circuit through a series of directional control valves; (c) engage the constant tension circuit, assuming that the engine is still operable, through directional control valves; and, (d) activate or engage the make-up circuit if and when it is detected that the engine is not operable, or loss of normal systems hydraulic pressure occur as highlighted in Fig. 4.
  • pressure from the crane's normal hydraulic system, generated by the diesel engine in the Skagit Series 300 crane is directed via line 103, the pilot oil supply line, to line 104 and to check valve 18.
  • Line 104 channels the crane's hydraulic pressure to the pilot port of directional control valve 36 repositioning valve 36 to the right.
  • the pressure that enters check valve 18 goes into the accumulator line 80 and then, along with accumulator pressure, is directed via line 80 to line 82 and thence through the repositioned detented control valve 21.
  • the pressure flow leaving valve 21 enters line 89 where the pressure is directed to line 90, 91 and 92.
  • Line 92 feeds the pressure flow to directional control valve 28 and to line 93.
  • the flow from valve 28 is directed to relief valve 26, piloting the relief valve 26 to a preset relief valve.
  • Line 93 channels the crane's hydraulic pressure to shuttle valve 50 and then to shuttle valve 49 and to the auxiliary or whip hoist brake 47, releasing the brake. With the release of the hoist brake 47 the auxiliary or whip hoist line is free to follow the load of the moving object and thus is able to pay out to to inhaul as required by the direction of the load of the object.
  • the auxiliary or whip hoist drum rotates backwards thus causing the auxiliary or whip hoist 45 to rotate backwards and acts as a pump thus creating its own flow and pressure.
  • this load-induced flow pressure generated by the auxiliary or whip hoist motor is proportional to the line tension created by the load of the moving object to which the hoist line is fouled. This load-induced flow acts directly on the hoist pump swash plate control.
  • the pressure directed to line 91 is directed into the left hand position of repositioned directional control valve 36 where it is blocked.
  • Line 91 also directs the pressure flow to the pilot port of directional control valve 35 porting it to the right, and to the pilot port of directional control valve 55 directing it to the right.
  • the pressure flow entering line 90 directs the pressure flow to directional control valves 58, 59 and 61.
  • the pressure directed to valve 61 enters the pilot port shifting directional control valve 61 downward and allowing the control pressure on operator control 66 to dump to crane hydraulic tank 68.
  • the pressure directed via line 90 to directional control valves 58 and 59 enters the lower pilot ports on the directional control valves 58 and 59 repositioning the valves 58, 59 upwardly. Having repositioned the directional control valves 58 and 59, the crane's pilot oil supply is allowed to enter, via line 121 through the center position on torque control valve 60.
  • the center position of valve 60 is divided into lines 124 and 125 which direct the pressure flow to.directional control valves 58 and 59, respectively.
  • the pressure flow from these two lines 124 and 125 is then directed through the valves 58 and 59, respectively, to the hoist pump swash plate control 56 via lines 126 and 127, respectively.
  • the directional control valve 60 is a torque limiting valve which has been installed adjacent to the hoist pump.
  • This valve 60 is a spool type with two pilot ports at each end, one pressure port, one tank port and two work ports.
  • the work ports are connected to the swash plate control ports 56a and 56b on the hoist pump through normally closed directional control valves 58 and 59 which are opened when the emergency release control is activated by the operator.
  • the high pressure port of the hoist pump is connected to the lower pilot port of torque valve 60.
  • the other two ports are ratio ports.
  • a reduced pressure signal is connected to the ratio pilot port on the in-haul or upper end of torque valve 60.
  • Pressure reducing valve 63 has been installed to provide this reduced signal from the crane's hydraulic control system.
  • the other pilot ratio port, on the outhaul end of torque valve 60, is connected to the tank return circuit or to the crane hydraulic tank 68.
  • the torque valve 60 is a valve with a 16:1 ratio - the area of the piston on the ratio port which is connected to the reduced pressure ratio port is 16 times larger than the piston on the lower pilot port.
  • This port senses the load induced pressure in line 157 and thus when the load induced pressure exceeds the predetermined reduced pressure by a factor of 16 the valve will shift and cause pressure to be directed to the opposite side of the pump swash plate causing the drum to rotate in the opposite direction allowing the line to payout, when induced pressure becomes less than 16 times the predetermined minimum pressure, the valve will shift back to the in-haul positions. Valves with different ratios are available.
  • the actual pressure of the reduced pressure signal is determined by the minimum line tension that is required by the Norwegian Maritime Directorate or other similar governmental or commercial regulations of standards or customer request, i.e. the reduced signal to the ratio port is set at approximately 100 psi. In other words, it would take a pressure in excess of 1600 psi to cause torque valve 60 to shift. With a fixed predetermined pilot signal at one end of torque valve 60 creating an imbalance, torque valve 60 will shift to the in-haul mode and control pressure will be transmitted through directional control valve 59 to the in-haul port of the hoist pump swash plate control. This causes the pump to go into the in-haul mode.
  • torque valve 60 Conversely with the opposite end of torque valve 60 sensing the load-induced pressure entering via line 123 and when the load-induced pressure exceeds the predetermined pressure, torque valve 60 will shift into the opposite direction. This allows control pressure to be transmitted through the directional control valve 58 to the pay-out port of the hoist pump swash plate control thus changing the direction of flow from in-haul to payout. Constant tension is therefore achieved and the pump will follow the load in any direction automatically.
  • the crane hydraulic system is capable of staying in this mode indefinately or until either the auxiliary or whip hoist line is stripped from the auxiliary or whip hoist drum when the line pay-out is greater than the line length (it should be noted that the length of line on the auxiliary or whip hoist will vary to fit the application) or the emergency situation is over and the operator deactivates the emergency release system and resets detented valve 21, or the engine or prime mover is lost or alternatively another partial loss of control pressure occurs. It should be noted that to de-activate the emergency release system the operator merely waits until the auxiliary or whip hoist is in the in-haul mode. The operator then places the normal crane hoist control on the in-haul position and returns the emergency release handle to its normal position. Transition to a normal operation under these conditions is designed to be smooth and to function without problems.
  • pressure from the accumulator 11 takes over and is capable of (a) maintaining pressure via shifting of directional control valves and shuttle valves to keep the hoist brake released, (b) able to lock-out the constant tension circuit system, and (c) able to open the make-up circuit and allow the load-induced flow generated by the motor acting as a pump when the load is lowering after the brake is released to drive the make-up circuit.
  • Pressure from line 90 splits into two sections and directs the pressure to the lower pilot ports of directional control valves 58, 59 and the pilot port of valve 61, should power return. If power does return then the directional control valves 58 and 59 are positioned to respond to the increased or reactivated pressure which would then flow as before to the swash plate of the hoist pump, valve 61 is positioned such that normal crane control functions remain locked out.
  • each of the three flow control valves 31, 32 and 33 used in the release mode without constant tension are installed with a fixed flow and are pressure and temperature compensated to limit the maximum speed that the auxiliary or whip hoist drum is capable of paying out, (paying out only in this instance, since there is no capability for controlling inhaul due to the loss of hydraulic power).
  • line 92 is connected to directional control valve 28, which is normally open and hence to the pilot port of relief valve 26, thus activating relief valve 26. Further, line 92 is connected to the auxiliary or whip brake 47 through line 93 and shuttle valves 49 and 50, thus maintaining pressure on auxiliary or whip brake 47, and keeping the brake in the release mode.
  • a high pressure relief valve 34 has been installed in the circuit to allow for momentary payout speeds in excess of the speeds set and normally limited by the flow control valves 31, 32 and 33.
  • Relief valve 40 is activated when the operator selects the emergency release mode. When the load-induced flow and pressure in line 17 exceeds the relief valve 40 setting excess flow generated.by the auxiliary or whip hoist motor acting as a pump will flow through relief valve 40 and discharge directly into line 86 through check valve 160 and into the low pressure port of the auxiliary or whip hoist motor 45. This bypasses the make-up circuit thus preventing auxiliary or whip hoist motor cavitation, and preventing overspeeding of the make - up pump and motor 25.
  • the hydraulic control system of the present invention also includes an emergency shut-down control system.
  • This emergency shut-down control is designed to completely shut the engine (or prime mover) down and set all of the brakes on the crane when it is activated by the operator.
  • the emergency shut-down is designed such that it automatically sets all of the brakes in the event of an electrical power failure. However, if the non-powered load lowering or either of the emergency release system has been activated, only those systems not part of these emergency systems will be affected.
  • the shut-down control is mechanically attached through a push pull cable and suitable linkage to a flapper valve on the engine air intake.
  • the flapper valve is provided as standard equipment on all diesel engines, such as those used on the Skagit cranes. However, if other engines are employed in other types of cranes, then similar valves or other devices could be employed to effect the same result.
  • the flapper valve on the Skagit diesel engine must be physically reset at the engine after emergency shut-down is activated in order to restart the engine.
  • the electrical switch is connected to a solenoid valve which is located in the crane's hydraulic control circuit.
  • the solenoid valve is also a part of the crane's hydraulic system along with the other emergency shut-down systems and is positioned as shown in figure 7. Pilot oil is supplied from line 103 via line 163 through energized solenoid valve 200 to line 129 through valve 61 to the operator control 66.
  • the emergency shut-down system is available for use with or without either of the two modes of the emergency release systems or the two modes of the emergency non-powered load lowering systems.
  • the preferred mode is that the hydraulic control circuit for the crane include all three of said circuits to maximize the safety of the crane.
EP84400241A 1983-02-03 1984-02-03 Hydraulische Notfallkontrollvorrichtung für einen Kran Withdrawn EP0118340A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US46345883A 1983-02-03 1983-02-03
US463458 1983-02-03

Publications (2)

Publication Number Publication Date
EP0118340A2 true EP0118340A2 (de) 1984-09-12
EP0118340A3 EP0118340A3 (de) 1985-12-27

Family

ID=23840156

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84400241A Withdrawn EP0118340A3 (de) 1983-02-03 1984-02-03 Hydraulische Notfallkontrollvorrichtung für einen Kran

Country Status (3)

Country Link
EP (1) EP0118340A3 (de)
AU (1) AU2406784A (de)
WO (1) WO1984003084A1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202008005035U1 (de) * 2008-04-11 2009-08-20 Liebherr-Hydraulikbagger Gmbh Arbeitsgerät und Notablasssystem
CN105489105A (zh) * 2016-01-04 2016-04-13 天津方兴石油工程技术有限公司 一种绞车系统教学演示平台
CN111362170A (zh) * 2020-03-31 2020-07-03 三一海洋重工有限公司 吊具电缆卷盘的控制方法、装置及起重机

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112340630B (zh) * 2020-11-18 2021-12-17 中船华南船舶机械有限公司 一种应急液压系统
CN114873503A (zh) * 2022-05-24 2022-08-09 重庆钢铁股份有限公司 一种起重机安全制动器控制系统及方法

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3180090A (en) * 1961-06-09 1965-04-27 Western Gear Corp Control for automatic tensioning of hydraulic winch
FR2075089A5 (de) * 1970-01-15 1971-10-08 Linde Ag
DE2146586A1 (de) * 1971-09-17 1973-03-22 Rexroth Gmbh G L Mit einer konstantzug-regelung versehener hydrostatischer antrieb
GB1352028A (en) * 1971-05-04 1974-05-15 Clarke Chapmen John Thompson L Fluid power transmissions
US3943713A (en) * 1974-11-25 1976-03-16 Eaton Corporation Control arrangement
US4043125A (en) * 1976-07-19 1977-08-23 Kubik Philip A Fluid system
US4187681A (en) * 1978-08-28 1980-02-12 Bucyrus-Erie Company Hydrostatic winch
US4188790A (en) * 1974-02-21 1980-02-19 A/S Bergens Mekaniske Verksteder Hydraulic system for operation of a winch
US4398698A (en) * 1981-05-29 1983-08-16 Fmc Corporation Freefall winch system and method of operation

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2349284A (en) * 1942-04-07 1944-05-23 Gerald W Kinzelman Safety device for hydraulic power transmission apparatus
US3378158A (en) * 1965-10-15 1968-04-16 Mccaffrey Ruddock Tagline Corp Hydraulically operated tagline rewind mechanism
DE2017272A1 (de) * 1970-04-10 1971-10-21 Linde Ag Überlastsicherung für einen hydrostatisch angetriebenen Kran

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3180090A (en) * 1961-06-09 1965-04-27 Western Gear Corp Control for automatic tensioning of hydraulic winch
FR2075089A5 (de) * 1970-01-15 1971-10-08 Linde Ag
GB1352028A (en) * 1971-05-04 1974-05-15 Clarke Chapmen John Thompson L Fluid power transmissions
DE2146586A1 (de) * 1971-09-17 1973-03-22 Rexroth Gmbh G L Mit einer konstantzug-regelung versehener hydrostatischer antrieb
US4188790A (en) * 1974-02-21 1980-02-19 A/S Bergens Mekaniske Verksteder Hydraulic system for operation of a winch
US3943713A (en) * 1974-11-25 1976-03-16 Eaton Corporation Control arrangement
US4043125A (en) * 1976-07-19 1977-08-23 Kubik Philip A Fluid system
US4187681A (en) * 1978-08-28 1980-02-12 Bucyrus-Erie Company Hydrostatic winch
US4398698A (en) * 1981-05-29 1983-08-16 Fmc Corporation Freefall winch system and method of operation

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202008005035U1 (de) * 2008-04-11 2009-08-20 Liebherr-Hydraulikbagger Gmbh Arbeitsgerät und Notablasssystem
US8061764B2 (en) 2008-04-11 2011-11-22 Liebherr-Hydraullikbagger GmbH Working machine and emergency lowering system
CN105489105A (zh) * 2016-01-04 2016-04-13 天津方兴石油工程技术有限公司 一种绞车系统教学演示平台
CN105489105B (zh) * 2016-01-04 2017-12-15 天津方兴石油工程技术有限公司 一种绞车系统教学演示平台
CN111362170A (zh) * 2020-03-31 2020-07-03 三一海洋重工有限公司 吊具电缆卷盘的控制方法、装置及起重机

Also Published As

Publication number Publication date
AU2406784A (en) 1984-08-09
WO1984003084A1 (en) 1984-08-16
EP0118340A3 (de) 1985-12-27

Similar Documents

Publication Publication Date Title
US5297019A (en) Control and hydraulic system for liftcrane
US3768263A (en) Hydraulic control system for two-speed winch
CN109292631B (zh) 一种起重机控制系统及控制方法
JP2009269683A (ja) タグボート用ロープウインチ
EP0041345B1 (de) Steuervorrichtung für das Hubwerk eines Schwimmkrans
EP0118340A2 (de) Hydraulische Notfallkontrollvorrichtung für einen Kran
US3934416A (en) Central hydraulic system for marine deck equipment
US4382360A (en) Unloading arrangement for hydraulic swing circuit or the like
US4610365A (en) Hoisting means including constant tension hoist wire
GB1559057A (en) Hoist drum drive system
JP3391382B2 (ja) ウインドラス用用途選択装置
US4598829A (en) Hydraulic circuit for crane
US3132622A (en) Two-sided hydraulic system
JPS6332709B2 (de)
US5806838A (en) Hydraulic system for driving a winch during quartering and lifting modes
CN114215798A (zh) 一种保护绞车的液压系统
CN109292653B (zh) 一种起重机液压变幅稳索系统
GB2132972A (en) Crane hoist protection system
KR100212218B1 (ko) 중장비의 다목적 유압제어장치
CN214935623U (zh) 液压控制系统以及缆绳张紧系统
EP0033239B1 (de) Hydraulisches Steuersystem für Krane
US4307678A (en) Hydraulic quick release system for tub/barge connections
NO20180204A1 (en) Pressurisation module and secondary-controlled hydraulic system
KR102532271B1 (ko) 유압장치 파손방지용 퀵릴리즈밸브
CN216691642U (zh) 一种绞车控制的液压系统

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): DE FR GB

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Designated state(s): DE FR GB

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 19860828

RIN1 Information on inventor provided before grant (corrected)

Inventor name: SHULTZ, LARRY D.

Inventor name: DOAN, THOMAS C.

Inventor name: FEATHERSTONE, WILLIAM A