EP1172325A2 - Dispositif de commande pour un treuil hydraulique - Google Patents

Dispositif de commande pour un treuil hydraulique Download PDF

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Publication number
EP1172325A2
EP1172325A2 EP01302982A EP01302982A EP1172325A2 EP 1172325 A2 EP1172325 A2 EP 1172325A2 EP 01302982 A EP01302982 A EP 01302982A EP 01302982 A EP01302982 A EP 01302982A EP 1172325 A2 EP1172325 A2 EP 1172325A2
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EP
European Patent Office
Prior art keywords
winding
hydraulic
pressure
free fall
control valve
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Withdrawn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
EP01302982A
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German (de)
English (en)
Other versions
EP1172325A3 (fr
Inventor
Yoshio Nabco Seishin Plant Nishimoto
Takahiro Okubo Plant Kobaysahi
Taisuke Okubo Plant Tsunoo
Etsujiro Kobe Corporate Research Labs. Imanishi
Satoshi Kobe Corporate Research Labs. Yonezawa
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.)
Kobelco Cranes Co Ltd
Original Assignee
Kobelco Construction Machinery Co Ltd
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
Priority claimed from JP2000212746A external-priority patent/JP3893857B2/ja
Priority claimed from JP2001025132A external-priority patent/JP3767389B2/ja
Application filed by Kobelco Construction Machinery Co Ltd filed Critical Kobelco Construction Machinery Co Ltd
Publication of EP1172325A2 publication Critical patent/EP1172325A2/fr
Publication of EP1172325A3 publication Critical patent/EP1172325A3/fr
Withdrawn legal-status Critical Current

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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
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/28—Other constructional details
    • B66D1/40—Control devices
    • B66D1/48—Control devices automatic

Definitions

  • the present invention relates to a control device for a hydraulic drive winch for controlling rotation of a winch drum driven by a hydraulic motor.
  • a conventional control device for a hydraulic drive winch is shown in Japanese Patent Application Laid-Open No. 63-35555 Publication. That is, in the aforesaid device, a winch drum is provided with a clutch, and both negative and positive brakes. These clutch and brakes are on/off controlled according to the operating conditions of drum drive and stop, and fee fall (free fall of suspended load). For the free fall, the clutch, the positive brake and a control system for them are necessary. This poses a problem that the device constitution becomes complicated, and the cost is high.
  • a hydraulic pump which is a hydraulic source for a hydraulic motor, is not exclusively used for a winch but is used in common as a hydraulic source for a plurality of actuators. Therefore, the engine speed is changed by the total of loads of the actuators. The pump flow rate is changed by the change of the engine speed. The motor flow rate is changed accordingly. The motor flow rate is changed at a position of the same control valve during the free fall operation. Therefore, when the engine speed is risen, the motor speed exceeds the allowable speed so that there sometimes possibly occurs the situations such that the winding-down speed is excessively high, and the random winding occurs.
  • the present inventors have provided, separately from the first winding-down operating means for normal winding-down, the second winding-down operating means for free fall operation.
  • the second winding-down operating means controls the passage flow rate of the control valve so that the flow rate of the hydraulic motor does not exceed the allowable flow rate at the minimum valve of the motor capacity.
  • the passage flow rate of the valve (motor flow rate) is controlled by operating the control valve by the second winding-down operating means during the free fall operation.
  • the winch drum is wound down and rotated at high speeds by setting the motor to a small capacity during the free fall operation, the speed when winding-down starts becomes quick as the load of a hanging load increases. Where a rapid lever operation is carried out, a shock possibly occurs in the vehicle body. Furthermore, when the initial speed is high, the movement of a counter balance valve cannot follow the hanging load, and hunting possibly occurs.
  • the control device for a hydraulic drive winch has the following fundamental constitution. That is, the control device comprises a winch drum, a variable capacity type hydraulic motor for driving the winch drum, a hydraulic pump as a hydraulic source, a control valve for controlling supply and discharge of pressure oil to the hydraulic motor, winding-up side for operating the control valve on the winding-up operating means, motor capacity control means for controlling capacity of the hydraulic motor, and free fall instructing means for outputting free fall instructions.
  • the motor capacity control means is operated on the basis of the free fall instructions from the free fall instructing means to set the hydraulic motor to a small capacity, in which state the winding-down operating means is operated whereby the winch drum is wound down and rotated at high speeds to carry out the free fall operation.
  • control valve controlling means is provided in addition to the above-described fundamental constitution.
  • the control valve controlling means controls an opening degree of the control valve relative to the operating amount of the winding-down operating means to be smaller than that of the normal winding-down operation without the free fall instructions so that at the time of the free fall operation, the supply flow rate to the hydraulic motor is less than the allowable flow rate of the hydraulic motor.
  • the motor capacity control means in the above-described fundamental constitution may employ the following constitution.
  • the motor capacity is increased on the high engine speed side according to the engine speed for driving the hydraulic pump, whereby at the time of the free fall operation, the hydraulic motor speed is controlled to no more than the allowable speed of the hydraulic motor.
  • the control device for a hydraulic drive winch may comprise, in addition to the above-described fundamental constitution, free fall control means.
  • the free fall control means changes the capacity of the hydraulic motor from a large capacity to a small capacity in proportional to the operating amount of the winding-down operating means.
  • a tilting angle of the variable capacity motor is controlled, for example.
  • the capacity of the variable capacity motor is set from a large capacity to a small capacity in proportional to the winding-down operating amount. So, when the winding-down operation is carried out using the operating means which is common in operation to the free fall operation, the initial speed of the free fall gets slow since at the time of starting free fall operation, the capacity of the variable capacity motor is large. Accordingly, the free fall operation can be carried out safely.
  • a control device for a hydraulic winch to enable free fall operation has the following constitutions:
  • a winch drum A hydraulic motor for driving the winch drum.
  • a hydraulic pump as a hydraulic source for the hydraulic motor, the hydraulic pump and the hydraulic motor being connected by the closed circuit.
  • a motor speed switching means for switching modes between a high speed rotation mode for winding-down rotating the hydraulic motor at relatively high speeds and a low speed rotation mode for winding-down rotating the hydraulic motor at relatively low speeds.
  • a winding-down operation means for outputting a winding-down instruction signal.
  • a pump control means for controlling a discharge direction and a discharge flow rate of the hydraulic pump.
  • the pump control means is constituted so that in the state that the motor speed switching means is set to the high speed rotation mode and the winding-down operation means is winding-down operated, when a winding-down side holding pressure of the closed circuit is lowered to a level below a set value of winding-down stop, the rotation of the hydraulic motor stops to control the hydraulic pump in the direction of stopping the winding-down operation.
  • Reference numeral 1 denotes a winch drum.
  • Arotational shaft 1a of the winch drum 1 is connected directly or through a reduction unit to a hydraulic motor 2 for a winch of a variable capacity type.
  • the winch drum 1 is rotated and driven by the motor 2.
  • Both winding-up and winding-down pipes 3, 4 constituting a driving circuit of the hydraulic motor 2 are connected to a hydraulic pump 6 through a hydraulic pilot switching type control valve 5 provided with three positions a, b and c, i.e., neutral, winding-up and winding-down.
  • Supply and discharge (drive, stop, and rotating direction and speed at the time of drive) of pressure oil to the motor is controlled by the control valve 5.
  • Reference numeral 7 denotes a winding-up side remote control valve as winding-up operating means for operating the control valve 5 on the winding-up side.
  • Reference numeral 8 denotes a winding-down side remote control valve as winding-down operating means for operating the control valve 5 on the winding-down side at the time of power winding-down. Pilot pressure according to the operating amount of both the remote control valves 7, 8 is fed to both pilot ports 5a, 5b on the winding-up side and winding-down side of the control valve 5.
  • the both the remote control valves 7, 8 on the winding-up side and the winding-down side normally, are integrally formed and selectively operated by a single lever.
  • Reference numeral 11 denotes a counter-balance valve as a brake valve for generating a hydraulic brake force in the winding side pipe 3 at the time of power winding-down rotation.
  • Reference character E denotes an engine for driving the hydraulic pump 6.
  • Reference numeral 12 denotes a cylinder (hereinafter referred to as a capacity regulating cylinder) as a motor capacity regulating actuator for changing a tilting angle of the hydraulic motor 2 to thereby change the motor capacity.
  • the hydraulic motor 2 is set to a large capacity in a state that the cylinder 12 is contracted, and set to a small capacity in a state that the cylinder is extended.
  • An oil chamber 12a on the contracted side of the capacity regulating cylinder 12 is connected to the winding-up side pipe 3 through a cylinder control valve (an actuator control valve) 13 of a hydraulic pilot switching type.
  • the cylinder control valve 13 has a large capacity position (a) and a small capacity position (b). At the large capacity position (a), an oil chamber 12a on the extended side of the cylinder is communicated with a tank T so that the capacity regulating cylinder 12 is contracted (the hydraulic motor 2 is set to a large capacity).
  • a small capacity pilot port 13a of the cylinder control valve 13 is connected to an output port of a free fall valve (an electromagnetic switching valve) 15 as free fall instruction means through a motor capacity switching line 14.
  • the free fall valve 15 is set to a non-operation position (a) shown in FIG. 1 at the time of normal operation except the free fall operation. In this state, the cylinder control valve 13 is maintained at a large capacity position (a) shown.
  • the free fall switch 16 When from that position, the free fall switch 16 is operated, the free fall valve 15 is switched to the operating position (b). Thereby, oil pressure of a pilot hydraulic source Pp is supplied to the small capacity side pilot port 13a of the cylinder control valve 13 so that the control valve 13 is switched to a small capacity position (b). Accordingly, the capacity regulating cylinder 12 is operated to be extended, and the hydraulic motor 2 is set to a small capacity.
  • the large capacity side pilot port 13b of the cylinder control valve 13 is connected to the winding-up side pipe 3 by a winding-up side pressure detecting line 17.
  • the cylinder control valve 13 is operated with respect to the large capacity position (a) side so that the motor capacity increases.
  • Reference numeral 18 denotes a variable relief valve as pump pressure setting means for setting pump pressure.
  • a pump pressure-switching valve 19 of a hydraulic pilot type To a spring side pressure port of the relief valve 18 are directly connected a pump pressure-switching valve 19 of a hydraulic pilot type, and a pump pressure setting valve 20.
  • the pump pressure-switching valve 19 is switched to a closed position (a) and an open position (b), vice versa.
  • a pilot port 19a of the pump pressure-switching valve 19 is connected to a pump pressure control line 21.
  • the pump pressure control line 21 is connected to an output port of the free fall valve 15.
  • set pressure of the relief valve 18, that is, pump pressure is set to a value determined by set pressure of the pump pressure setting valve 20.
  • the pump pressure determined by the pump pressure setting valve 20 is set to a value at which a relationship between the pump pressure and the winding-down rotating force > drum rotating resistance is established.
  • the free fall valve 15 is set to a non-operation opposition (a).
  • the motor capacity and the pump pressure are set to a large capacity and a high pressure, respectively.
  • the hydraulic motor 2 is driven at a speed corresponding to the operating amount (stroke of the control valve 5) of both winding-up side and winding-down side remote control valves 7, 8, and normal winding-up and winding-down operation are carried out.
  • the free fall switch 16 is operated to switch the free fall valve 15 to the operation position (b).
  • the winding-down side remote control valve 8 When in that state, the winding-down side remote control valve 8 is operated, the motor capacity and the pump pressure are set to a small capacity and a low pressure, respectively. Thereby, the hydraulic motor 2 is wound down and driven at high speeds to effect the free fall operation.
  • an opening degree of the control valve 5 is changed according to the operating amount of the winding-down side remote control valve 8 to change the motor capacity. Therefore, the free fall speed can be adjusted or stopped by the remote control valve 8.
  • the motor capacity can be set to a small capacity to thereby wind down and drive the hydraulic motor 2 at high speeds to obtain the free fall function. Therefore, a clutch and a positive brake for the free fall, and a control system therefor are eliminated.
  • the pump pressure is set to low pressure simultaneously, the motor speed will not be excessively high. Therefore, it is possible to carry out operation near the original free fall, which is free from looseness of a rope and random winding.
  • the hydraulic pump 6 is not exclusively used for the hydraulic motor 2 for a winch, as described above, but is used in common as the hydraulic source for one or more actuators not shown. Because of this, engine speed changes with variation of the total load. The pump flow rate is changed by the change of engine speed to change the motor flow rate. Therefore, excessive speed of the motor 2 possibly occurs.
  • the winding-down side pilot port 5b of the control valve 5 is of a 2-port construction comprising a normal winding-down side port 5b1 having a relatively large pressure receiving area, and a free fall side port 5b2 having a small pressure receiving area. Pilot pipes 10a, 10b derived from both the ports 5b1, 5b2 are connected to a winding-down side pilot line 10 through a mode-switching valve 22 of a hydraulic pilot type.
  • a pilot port 22a of the mode-switching valve 22 is connected to an output port of the free fall valve 15. As shown in FIG. 1, when the free fall valve 15 is at a non-operation position (a), the mode-switching valve 22 is set to a normal winding-down position (a).
  • control valve 5 operates without receiving any restriction at the stroke according to the operating amount (pilot pressure) of the winding-down side remote control valve 8. Thereby, an opening degree of the valve 5 is changed.
  • the mode-switching valve 22 is switched to the free fall position (b).
  • pilot pressure from the remote control valve 8 is supplied to the free fall side port 5b2 in the winding-down side pilot port 5b of the control valve 5.
  • the normal winding-down side port 5b is communicated with the tank T.
  • a pressure receiving area of the free fall side port 5b2 is smaller than that of the normal winding-down side port 5b1.
  • a flow rate control valve 23 is provided on the pump line as shown in FIG. 1 in order to return surplus flow rate to the tank T.
  • the motor flow rate is suppressed within the allowable flow rate Qs irrespective of variation of engine speed. Therefore, there is no possible occurrence that the hydraulic motor 2 exceeds the allowable speed resulting in excessive speed state or random winding occurs due to the increase in engine speed.
  • the free fall operation can be carried out by the operating means (remote control valve 8) common to normal operation. Because of this, there is no possible occurrence that the operation where the free fall operation from the winding-up operation is continuously carried out becomes complicated or an erroneous operation is brought forth, as in the case where both the operations are carried out by separate operating means.
  • the winding-up side pilot port 5a is formed with an auxiliary port 5a1.
  • a stopper 24 is provided movably forward and backward opposing to a spool 5c.
  • oil pressure of the pilot hydraulic source Pp is supplied to the auxiliary port 5a1 in the winding-up side pilot port 5a through a stopper hydraulic line 25.
  • the stopper 24 is moved forward toward the spool 5c (in a right direction in the figure) to limit the stroke.
  • the winding-down pilot line 10 is divided into a non-reduction pipeline 26 and a reduction pipeline 28.
  • the non-reduction pipeline 26 causes pilot pressure from the winding-down side remote control valve 8 to pass to the pilot port 5b without modification.
  • the reduction pipeline 28 reduces pilot pressure by a reducing valve 27.
  • a hydraulic pilot type mode-switching valve 29 is provided between both the pipelines 26, 28 and the pilot port 5b. Thereby, in the state that the switching valve 29 is set to the normal winding-down position (a), the non-reduction pipeline 26 is communicated with the pilot port 5b. As shown by the solid line in FIG. 8, normal pilot pressure (in the figure, Pf denotes the maximum pilot pressure) corresponding to the operating amount of the remote control valve 8.
  • FIG. 9 shows a relationship between the pilot pressure set in this embodiment and the control valve stroke.
  • the allowable flow rate (allowable speed) of the motor 2 is obtained by the maximum stroke Ss obtained by the maximum pilot pressure Ps at the time of free fall operation.
  • the pilot pressure is introduced into the free fall side port having a small pressure receiving area in the winding-down side pilot port of the control valve, whereby the stroke of the control valve is suppressed to throttle its opening degree. Further, the pilot pressure is introduced into the auxiliary port of the winding-down side pilot port and the stopper is actuated, whereby the stroke of the control valve is suppressed to throttle its opening degree. Further, the pilot pressure from the winding-down operating means (remote control valve) is reduced and is introduced into the pilot port of the control valve, whereby the stroke of the control valve is suppressed to throttle its opening degree.
  • adjustment and change of the motor allowable flow rate can be done easy by setting the reduction valve 27.
  • An electromagnetic proportional type-reducing valve 31 controlled by a controller is provided in the winding-down side pilot line 10.
  • the control valve 30 will not output a signal when the free fall switch 16 is turned off (at the time of normal winding-down operation). In this state, the reducing valve 31 is set to high pressure.
  • the reducing valve 31 is set to low pressure by a signal from the controller 30.
  • examples 1 to 4 there is employed the constitution that at the time of free fall operation, the stroke toward the winding-down side of the control valve is controlled to thereby control the motor flow rate.
  • the present embodiment employs the constitution that when the engine speed rises during the free fall operation, the motor capacity is increased to limit the motor rotation.
  • an electromagnetic proportional type-reducing valve 32 is provided in a motor capacity switching line 14 for switching the motor capacity. Thereby, the reducing valve 32 is controlled by the controller 33.
  • the controller 33 changes an output current according to the engine speed detected by a speed sensor 34.
  • a speed sensor 34 As shown in FIG. 12, at not more than the engine speed (hereinafter referred to as the allowable engine speed) at which flow rate Qs corresponding to the motor allowable speed at the time of small capacity of the motor is discharged, full current I max is output. At the engine speed region in excess of the former, it is set so that an output current is reduced in inverse proportion to the engine speed.
  • the winding-down initial speed is reduced at the start time of free fall operation, and the winding-down speed can be accelerated according to the operating amount.
  • remote control pressure Pi of the winding-down side remote control valve (operating means) 8 is detected by a pressure sensor 40.
  • a signal output from the pressure sensor 40 is given to a controller 41.
  • a selecting switch (free fall instruction means) 42 is connected to the controller 41.
  • the selecting switch 42 is provided with a normal operating button 42a for carrying out normal winding-up and winding-down, and a free fall operating button 42b.
  • a free fall instruction is given to the controller 41.
  • the controller 41 sets capacity of the hydraulic motor 2 by preset motor capacity characteristics.
  • FIG. 16 shows the motor capacity characteristics (a relationship between remote control pressure Pi and a motor capacity Mq) set when the free fall instructions are output. As shown in the figure, The motor capacity characteristics M is large when the remote control pressure Pi is small. On the other hand, it is small as the remote control pressure Pi increases.
  • the controller 41 causes the secondary pressure of a reducing valve 43 (input pressure of the cylinder control valve 13) to lower.
  • the cylinder control valve 13 is operated toward the large capacity position (a).
  • the motor capacity is set to a large level.
  • the controller 41 causes the free fall valve 15a from position (a) to position (b). Thereby, variable remote control pressure Pi in place of fixed pressure Pc is supplied to the pilot oil passage 44.
  • the remote control pressure Pi is introducing into a set pressure control valve 45 and a holding pressure control valve 46 separately.
  • the set pressure control valve 45 has a switching position switched from communication to cutoff (in the figure, shown by switching positions a to c conveniently). In the state that the winding-down side remote control valve 8 is not operated when the free fall valve 15 is switched to the position (b), the set pressure control valve 45 is at the position (a). When the winding-down lever 8a is operated, the position is switched from the position (b) to position (c).
  • the pressure control valve 18 is changed in set pressure from minimum to maximum. Accordingly, the winding-down pressure (pressure of the winding-down side pipeline 4) changed from minimum to maximum.
  • the holding pressure control valve 46 is switched to the communication position by the remote control pressure Pi when the free fall operation is selected.
  • the motor capacity Mq is made large and the winding-down pressure is made low.
  • the motor capacity Mq is large, much oil is required for the drive of the hydraulic motor 2 whereby the initial speed is slow.
  • the shock generated immediately after the start of free fall winding-down is extremely small.
  • it is designed so that the winding-down speed at the time of free fall becomes quick in proportion to the operating amount of the operating lever 8a. Therefore, the state can be shifted to the stationary operating state in a stable manner. Accordingly, operation in conformity with an operator's can be carried out.
  • the controller 41, the free fall valve 15, the set pressure control valve 45 and the pressure control valve 18 function as free fall operation control means.
  • FIG. 17A shows the change of the lever-operating amount.
  • FIG. 17B shows the state when the winch drum 1 starts to move.
  • control valve 5 is switched by either remote control pressure Pi from the winding-down side remote control valve 8 or pilot pressure Pj from a pilot pressure supply valve (control valve switching means) provided separately from the winding-down side remote control valve 8.
  • Reference numeral 51 denotes a shuttle valve for selecting a high level of the remote control pressure Pi and the pilot pressure Pj.
  • the controller 41 switches the pilot pressure supply valve 50 from a position (a) to a position (b). Then, when the pilot pressure Pj is derived from the pilot pressure supply valve 50, the shuttle valve 51 selects a high level of the pilot pressure Pj and the remote control pressure Pi. Next, the pilot pressure Pj is given to the pilot port 5b of the control valve 5 due to Pj>Pi. Thereby, the control valve 5 is switched to the winding-down position (c) in preference to the operation of the winding-down side remote control valve 8.
  • control valve 5 can be quickly switched to the winding-down position without waiting the remote control pressure Pi from the winding-down side remote control valve 8 at the time of the free fall operation. Accordingly, the time from the start of winding-down to the maximum speed. Thereby, acceleration can be promoted.
  • the pilot pressure Pj is not derived.
  • the remote control pressure Pi derived from the winding-down side remote control valve 8 is introduced into the pilot port 5b of the control valve 5.
  • the winding-up and winding-down operation can be done at normal speeds.
  • a relief valve 55 provided on the bypass oil passage 4a is directly controlled by the controller 41.
  • the relief pressure characteristics for changing the relief pressure of the electromagnetic relief valve 55 from low pressure to high pressure in a predetermined pattern according to the lever stroke (remote control pressure Pi) of the operating lever 8a is stored in advance in a memory. Thereby, a relief pressure is read out of the memory according to the remote control pressure Pi detected by the pressure sensor 40. Thereby, a relief pressure signal is given to the electromagnetic relief valve 55.
  • FIG. 20 shows the above-described relief pressure characteristics.
  • a relief pressure P1 is constant when the remote control pressure Pi is from P0 to PA. As the remote control pressure increases from PA to PB, the relief pressure P1 increases from P1 to P2.
  • the relief pressure characteristics can be suitably set. Furthermore, there is an advantage that the speed responsiveness is high, and the operation feeling is excellent.
  • the stroke of the control valve can be suppressed to contract an opening degree thereof by the following means:
  • the free fall operation can be carried out by the same operating means (remote control valve) common to the normal operation. Therefore, the continuous operation particularly where the free fall operation is continuously carried out from the winding-up operation as in the case where both the operations are carried out by separate operating means is not complicated or erroneous operation is possibly brought forth.
  • the second embodiment has the following effects. That is, when the free fall operation is selected by the free fall instruction means, the tilting angle of the variable capacity type hydraulic motor is controlled. Thereby, the capacity of the hydraulic motor is set to a small capacity from a large capacity in proportional to the winding-down operating amount. Thus, the winding-down operation is carried out using the operating means common in operation to the free fall operation. Since the capacity of the hydraulic motor is large at the time of starting the free fall operation, the initial speed of the free fall is slow. Thereby, the free fall operation can be carried out safely.
  • the pressure of the winding-down side oil passage is set to be low. Therefore, even if the hanging load is large, no shock occurs when the winding-down starts.
  • the winding-down side oil passage is risen in pressure in proportional to the operating amount of the operating means. Therefore, increasing and decreasing of the hook falling speed can be done according to the operating amount. For example, if the winding-down operating amount is increased in the state that the capacity of the variable capacity type hydraulic motor is set to be small, the free falling can be done at high speeds.
  • control valve switching means independently switches the control valve to the winding-down side. Therefore, the time required from the start of free falling to the maximum winding-down speed in the state that the hanging load is applied is shortened. Accordingly, the responsiveness can be enhanced.
  • reference numeral 101 denotes a hydraulic motor of a variable capacity type for driving a winch drum not shown.
  • Both pipelines 102, 103 on the winding-up side and winding-down side, respectively, of the motor 101 are directly connected to both discharge ports of a hydraulic pump 104 of a variable capacity type and a 2-directional discharge type.
  • a motor closed circuit A is constituted.
  • the discharge direction and the discharge flow rate of the hydraulic pump 104 are controlled to control the rotational directions (winding-up and winding-down) and the rotational speed of the hydraulic motor 101.
  • a tilting cylinder 105 for operating the tilting of the pump 104 on either the winding-up side or the winding-down side is connected to a hydraulic source 106 for the cylinder 105 and a tank T through a cylinder control valve 107 which is a hydraulic pilot type servo valve.
  • the control valve 107 and the tilting cylinder 105 are controlled by pressure (remote control pressure) from both remote control valves 109, 110 on the winding-up side and winding-down side operated by a lever 108.
  • the remote control pressure corresponding to the lever operating amount from the remote control valve 109 on the winding-up side or the remote control valve 110 on the winding-down side is output.
  • the cylinder control valve 107 is switched from a neutral position x to a winding-up position y on the right-hand in the figure or a winding-down position z on the left-hand in the figure.
  • Oil pressure corresponding to the remote control valve operating amount are fed to either an oil chamber 105a on the winding-up side of the tilting cylinder 105 at the winding-up position y or an oil chamber 105b on the winding-down side thereof at the winding-down position z, respectively.
  • the cylinder 105 is driven on the winding-up side or the winding-down side to change the tilting.
  • Oil corresponding to the tilting is fed to the pipeline 102 on the winding-up side or the pipeline 103 on the winding-down side to rotate the motor 101.
  • tilting control circuit 112 on the winding-down side is provided with a hydraulic pilot-type switching valve 113.
  • the switching valve 113 has a winding-down stop position a for communicating the oil chamber 105b on the winding-down side of the tilting cylinder 105 with the tank T, and a winding-down position b for feeding oil from the hydraulic source 106 to the oil chamber 105.
  • the switching valve 113 has, as a pilot port for receiving pilot pressure, a first pilot port 114 for introducing pressure (holding pressure on the winding-down side) P1 of the pipe line 103 on the winding-down side, and a second pilot port 115 for introducing remote control pressure (winding-down instruction pressure) P2 by operation the remote control valve 110 on the winding-down side.
  • both the pilot ports 114, 115 are provided pistons 116, 117 as a pressure receiving part operated by receiving the pilot pressure so that the pistons move together.
  • the total pressure of a winding-down side holding pressure P1 and a winding-down instruction pressure P2 exerting on both the pistons 116, 117 can switch the switching-valve 113.
  • the pressure receiving area for the first piston 16, which receives relatively high pressure (the winding-down side holding pressure P1) is set to be small, and that for the second piston 17, which receives relatively low pressure (the winding-down instruction pressure P2) is set to be large.
  • Reference numeral 118 denotes a spring resisting to the pilot pressure.
  • Reference numeral 119 denotes a capacity-regulating cylinder for changing the motor capacity by changing the tilting of the motor 101.
  • the motor 101 is set to a large capacity in the state that the cylinder 119 is contracted, while being set to a small capacity in the state that the cylinder is expanded.
  • An expanded side oil chamber 119a of the capacity-regulating cylinder 119 is connected to the winding-up side pipeline 102 and the tank T through a hydraulic pilot switching type capacity control valve 120.
  • the capacity control valve 120 has a large capacity position x and a small capacity position y. At the large capacity position x, the expanded side oil chamber 119a is communicated with the tank T so that the capacity regulating cylinder 119 contracts (the motor 101 is set to a large capacity).
  • a small capacity pilot port 120a of the capacity control valve 120 is connected to an output port of a free fall valve (an electromagnetic switching valve) 122 constituting a mode switching means through a motor capacity switching line 121.
  • the free fall valve 122 is set to a non-operating position x in the figure at the time of normal operation (at the time of winding-up and normal winding-down). In this state, the capacity control valve 120 is held at a large capacity position x shown.
  • a free fall switch 123 constituting the mode switching means When, from this state, a free fall switch 123 constituting the mode switching means is turned on, the free fall valve 122 is switched to an operating position y. Oil pressure of a pilot hydraulic source 124 is supplied to the small capacity pilot port 120a of the capacity control valve 120 so that the control valve 120 is switched to a small capacity position y.
  • the capacity-regulating cylinder 119 is operated to be expanded, and the motor 101 is set to a small capacity.
  • the free fall valve 122 is set to the non-operating position x, and the motor capacity is set to a large capacity.
  • the motor 101 is rotated at the speed (lower than that at the time of free fall operation) corresponding to the operating amount, by the action of the cylinder control valve 107 and the tilting cylinder 105 on the basis of the operation of both the remote control valves 109, 110 on the winding-up side or winding-down side, and the winding-up operation or the normal winding-down operation is carried out.
  • the free fall valve 122 is set to the operating position y, and the motor capacity is set to a small capacity. Because of this, the winding-down operation at the high speed is enabled.
  • the total pressure of the winding-down side holding pressure P1 and the winding-down instruction pressure P2 is applied as a pilot pressure to the switching valve 113, as described above.
  • the total pressure reaches a set valve at which winding-down starts, the position is switched to the winding-down position b.
  • the switching valve 113 is at the winding-down stop position a. Even if the cylinder side control valve 107 should be switched to the winding-down position z by the operation of the winding-down side remote control valve 110, the pump 104 assumes a neutral (tilting 0) state. Accordingly, the discharge flow amount of oil from the pump 104 is 0, and the motor 101 is not rotated.
  • the switching valve 113 is switched to the winding-down position b.
  • the winding-down side tilting of the pump 104 is set to the value corresponding to the operating amount of the remote control valve so that the motor 101 takes winding-down rotation at the high speed, and the free fall operation is carried out.
  • the switching characteristic of the switching valve 113 is set so that when the winding-down side holding pressure P1 lowers to a value less than a certain value (pressure at the time of landing), the switching valve 113 is switched to the winding-down stop position a.
  • the free fall operation provided with two functions, that is, the high-speed winding-down rotation and the winding-down stop at the time of landing becoming enabled.
  • the pump tilting changes corresponding to the operating amount (the winding-down instruction pressure P2) of the remote control valve 110. Therefore, the free fall speed can be suitably controlled outside the diagonal area of FIG. 22 by operation of the lever.
  • the pressure receiving areas of both the pistons 116, 117 of the switching valves 113 are set to be small on the first piston 116 side and to be large on the second piston 117 side. Therefore, the change in speed with respect to the change of the winding-down instruction pressure P2 becomes large, and the speed controllability caused by the lever operation is improved.
  • the free fall operation is started and the winding-down speed changes corresponding to the winding-down instruction pressure, the free fall speed can be freely controlled by an operator. Therefore, the operatability at the time of free fall operation is improved.
  • a hydraulic pilot type-switching valve is used as a switching valve. Since the whole hydraulic control becomes enabled, equipment for electric control (a controller or a pressure detection means) is unnecessary as compared with a case using an electro-magnetic switching valve. Accordingly, the circuit can be constituted merely by hydraulic equipment.
  • the switching valve it is set so that the pressure receiving area of the first port into which is introduced high winding-down side holding pressure is small, and the pressure receiving area of the second port into which is introduced low winding-down instruction pressure is large, and therefore, the winding-down speed control corresponding to the winding-down operating amount can be easily carried out. Further, since the spring force resisting to the winding-down side holding pressure can be weakened, the switching valve can be constituted compact.
  • EXAMPLE 9 employs the constitution in which when the winding-down side holding pressure P1 assumes a value less than a set value at the time of winding-down, the switching valve 113 is always switched to the winding-down stop position a and the winding-down operation automatically stops.
  • the present example employs the constitution in which by switching the mode, even if the winding-down side holding pressure P1 lowers to a value less than a set value, the winding-down operation can be continued.
  • an electro-magnetic switching control valve 126 between a second pilot port 115 of a switching valve 113, a winding-down side remote control valve 110 and a pilot hydraulic source 124. Further, there are provided a controller 127 for controlling the control valve 126, a pressure gage 128 for detecting a wining-down instruction pressure P2 to input it into the controller 127, and a mode switching switch 129 as a mode switching means for switching a winding-down mode between an automatic stop mode for automatically stopping the wining-down operation and a normal mode not to effect automatic stop.
  • the switching control valve 126 has a first position x for feeding the winding-down instruction pressure P2 to the second pilot port 115 by the operation of the winding-down side remote control valve 110, and a second position y for feeding pressure of the pilot hydraulic source 124 directly to the port 115 without decreasing the pressure.
  • the switching control valve 126 is set to the first position x shown when the mode switching switch 129 is turned off. In this state, when the winding-down side holding pressure P1 lowers to a value less than a set value as described in EXAMPLE 9, the winding-down operation automatically stops.
  • the switching control valve 126 is switched to the second position y by a signal from the controller 127. In this state, pressure from the hydraulic source 124 is supplied to the second pilot port 115 of the switching valve 113. Therefore, the switching valve 113 is held at the winding-down position b irrespective of the change in magnitude of the winding-down side holding pressure P1.
  • the winding-down operation can be continued corresponding to the winding-down operating amount as long as the winding-down operation is carried out.
  • Such an operating mode as described can be used where for example, in the work in which a crushing rod is free fallen to crush rocks in water, winding-down operation is continued to crush them positively for a fixed time even after the crushing rod arrives at the rocks.
  • the winding-down operation can be continued irrespective of the change in magnitude of the winding-down side holding pressure, as necessary.
  • an electromagnetic switching type switching valve 130 is used in place of the hydraulic pilot-type switching valve 113 in EXAMPLES 9 and 10.
  • the switching valve 130 is controlled by a signal from a controller 131.
  • Into the controller 131 is input the winding-down side holding pressure P1 by a pressure gage 132, and the winding-down instruction pressure P2 by a pressure gage 133.
  • a switching signal is output from the controller 131 to the switching valve 130 so that the switching valve 130 is switched to the winding-down position b.
  • a switching signal form the controller 131 stops so that the switching valve 130 returns to the winding-down stop position a.
  • a general electromagnetic valve can be used as compared with a case using the special switching valve 113 provided with both the first and second pilot ports 114, 115 as in EXAMPLES 9, 10. Therefore, the cost of parts is low, and the constitution of a device can be simplified.
  • the switching characteristic of the switching valve 130 can be freely selected in a wide range.
  • the electromagnetic switching valve is used as a switching valve, the switching valve can be controlled directly by an electric signal. Since the general valve can be used as compared with a case using a hydraulic switching valve provided with a special pilot port, the cost of parts is low, and the constitution of a device can be simplified.
  • the switching characteristic of the switching valve 130 can be freely selected in a wide range.
  • the tilting cylinder 105 is controlled indirectly through the cylinder control valve 107 by the remote control valves 109, 110, whereas in the present example, the cylinder control valve 107 is omitted, and remote control pressure from the remote control valves 109, 110 is fed directly (via the switching valve 113 on the winding-down side) to the tilting cylinder 105.
  • the tilting cylinder 105 is controlled directly by the operation of the remote control valves 109, 110.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
EP01302982A 2000-07-13 2001-03-29 Dispositif de commande pour un treuil hydraulique Withdrawn EP1172325A3 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2000212746A JP3893857B2 (ja) 1999-11-25 2000-07-13 油圧駆動ウインチの制御装置
JP2000212746 2000-07-13
JP2001025132A JP3767389B2 (ja) 2001-02-01 2001-02-01 油圧ウィンチの制御装置
JP2001025132 2001-02-01

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EP1172325A2 true EP1172325A2 (fr) 2002-01-16
EP1172325A3 EP1172325A3 (fr) 2002-04-17

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Cited By (7)

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Publication number Priority date Publication date Assignee Title
FR2956105A1 (fr) * 2010-02-10 2011-08-12 Payant Ets Dispositif de traction
CN103287999A (zh) * 2013-06-18 2013-09-11 中联重科股份有限公司 工程机械及其卷扬变幅液压系统、作业方法
WO2016138865A1 (fr) * 2015-03-04 2016-09-09 徐州重型机械有限公司 Soupape de commutation, système hydraulique de commutation et grue
CN106185662A (zh) * 2016-07-18 2016-12-07 华中科技大学 一种适用于履带起重机的卷扬液压系统
CN107795538A (zh) * 2017-12-01 2018-03-13 徐工集团工程机械有限公司 行走马达换挡阀、行走马达和工程机械
CN109555638A (zh) * 2017-09-25 2019-04-02 马尼托意大利有限责任公司 用于供应和改变液压发动机的气缸立体容积的设备
CN112777503A (zh) * 2021-02-23 2021-05-11 三一汽车起重机械有限公司 卷扬装置及其液压系统、使用方法及作业机械

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Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2956105A1 (fr) * 2010-02-10 2011-08-12 Payant Ets Dispositif de traction
CN103287999A (zh) * 2013-06-18 2013-09-11 中联重科股份有限公司 工程机械及其卷扬变幅液压系统、作业方法
CN103287999B (zh) * 2013-06-18 2015-08-05 中联重科股份有限公司 工程机械及其卷扬变幅液压系统、作业方法
WO2016138865A1 (fr) * 2015-03-04 2016-09-09 徐州重型机械有限公司 Soupape de commutation, système hydraulique de commutation et grue
US10233060B2 (en) 2015-03-04 2019-03-19 Xuzhou Heavy Machinery Co., Ltd. Switching valve, switching hydraulic system and crane
CN106185662A (zh) * 2016-07-18 2016-12-07 华中科技大学 一种适用于履带起重机的卷扬液压系统
CN109555638A (zh) * 2017-09-25 2019-04-02 马尼托意大利有限责任公司 用于供应和改变液压发动机的气缸立体容积的设备
CN109555638B (zh) * 2017-09-25 2022-03-29 马尼托意大利有限责任公司 用于供应和改变液压发动机的气缸立体容积的设备
CN107795538A (zh) * 2017-12-01 2018-03-13 徐工集团工程机械有限公司 行走马达换挡阀、行走马达和工程机械
CN107795538B (zh) * 2017-12-01 2023-09-08 江苏徐工工程机械研究院有限公司 行走马达换挡阀、行走马达和工程机械
CN112777503A (zh) * 2021-02-23 2021-05-11 三一汽车起重机械有限公司 卷扬装置及其液压系统、使用方法及作业机械

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