JP2005520998A - Control mechanism - Google Patents

Abstract

A control mechanism for a hydraulically operated consumer, particularly a control mechanism for a winch, is disclosed. The consumer's hydraulic drive mechanism can be connected to a pump or tank by a continuously adjustable main valve. The control mechanism includes hydraulically actuated brake means for fixing the consumer. The main valve can be actuated by manual pilot control means or remote control means. According to the present invention, the lifting of the brake means applies the same brake pulling pressure to the brake means, preferably released upstream of the main valve, using a pilot control similar to the operation by the manual pilot control means. Achieved by brake lift valve.

Description

  The present invention relates to a control mechanism for a hydraulically actuated consumer according to the preamble of claim 1, and in particular to a control mechanism for a winch.

  Such a control mechanism is used in particular for controlling a winch for hoisting and feeding a ship hawser. WO00 / 57067A1 discloses a winch control mechanism, and a winch for winding and unwinding a rope is driven by a hydraulic motor. The hydraulic motor is driven with the aid of a variable displacement pump, and the flow of pressure medium from the variable displacement pump to the hydraulic motor is proportional to the flow of pressure medium from the hydraulic motor to the return (tank) ( Proportionally) controlled via an adjustable main valve. This main valve is designed with manual pilot control means that can adjust the operating status of "hoisting", "easing", and any "mooring" .

  The known winch control mechanism further has a port for remote control, through which the main valve can be controlled even when the pilot control means is not operating. In the neutral position of the main valve, that is, when the winch is not in operation, the rotational position of the winch is fixed via the hydraulically operated brake means, and the hydraulically operated brake means is braked in the brake engagement direction. Having a hydraulic cylinder biased in The brake is lifted by applying a pressure acting in the opposite direction to the spring to the pressure chamber of the hydraulic cylinder.

  In this known structure, the pressure of the hydraulic cylinder to raise the brake is between the maximum value and zero during hoisting of the rope in the no-load state (load pressure is almost zero) and when the main valve is suddenly operated by remote control. Fluctuate between. Such fluctuations in the brake lifting pressure are shown in FIG. Surprisingly, brake lift pressure fluctuations only occur when using remote control. When the main valve was operated by the manual pilot control means, such fluctuation was not observed.

  On the other hand, the present invention is based on the object of providing a control mechanism for a hydraulically operated consumer, particularly a control mechanism for a winch, and is combined with a winch even when the load pressure is small. The raised brake means can be lifted without substantially causing the above-described fluctuations.

  This object is achieved by a control mechanism having the features of claim 1.

  According to the present invention, the control mechanism includes the brake pull-up valve, and when the main valve is operated by the remote control means and the pilot control means, the brake control chamber of the brake means acting in the brake pull-up direction has the main valve A brake lifting pressure that is released upstream can be applied.

  According to the present invention, the brake control is performed regardless of the operation mode (remote control / manual), regardless of the pressure drop in the main valve or the control land of the pilot control means or the adjustment of the main valve. Is done by.

  In contrast to the solution according to the invention, in the known solution, the brake lifting pressure was released downstream of the main valve for control by the remote control means. Surprisingly, it has been found that the above-mentioned fluctuation does not occur when the brake pressure is released upstream of the main valve.

  According to the present invention, it is preferable that the brake control pressure necessary for operating the brake pull-up valve corresponds to the control pressure for controlling the main valve. That is, the control pressure applied by the remote control means or the pilot control means is used to switch the brake pull-up valve.

  The brake lift valve is preferably designed as a 3 / 2-way control valve, which releases the control chamber of the brake means acting in the brake lift direction in the basic position biased by the spring. To do. Further, the 3 / 2-way control valve can be switched to a position where the brake lifting pressure is applied to the brake control chamber by the above-described brake control pressure.

  In a particularly preferred embodiment, the brake lifting pressure substantially corresponds to the pump pressure applied via the variable displacement pump.

  If the control pressure for controlling the drive mechanism, which has the form of a hydraulic motor with a variable suction volume, corresponds to the control pressure for operating the brake lift valve and the main valve It becomes particularly easy to control each element of the winch control mechanism.

  In an advantageous variant of the invention, the pilot control means comprises a directional control valve known per se, which directional control valve is connected to each control chamber of the main valve via a control passage, at least 2 Has two pilot control ports. A higher control pressure present at the pilot control port or applied by the remote control means is released through the shuttle valve assembly as a control pressure for controlling the brake control pressure and / or hydraulic motor.

  The limit pressure when the brake lift valve for raising the brake means is switched can be adjusted to various operating conditions via an adjustable control spring of the brake lift valve.

  The directional control valve of the pilot control means can preferably be set to the unwind / windup and mooring positions, and all three operating states can be set manually, whereas in remote control the “winding” Only the “up” and “feed” operating states can be set.

  Other advantages of the invention are the subject of further subclaims.

  Hereinafter, preferred embodiments of the present invention will be described in more detail with reference to schematic drawings.

  FIG. 2 shows a circuit diagram of a winch control mechanism capable of controlling a winch for winding up the hawser or feeding out the hawser. The basic concept of the winch control mechanism shown in FIG. 2 corresponds to the winch control mechanism described in WO00 / 57067A1, and only the components essential for understanding will be described below. Reference is made to the disclosure of WO 00/57067 A1.

  The drive of the winch 2 is achieved by the hydraulic motor 4 having a variable suction capacity connected to the winch 2 via the transmission 6. The latter can be fixed at a predetermined rotational position for holding the rope via the brake means 8. According to the invention, the brake means 8 includes a hydraulic cylinder 10, which is biased in the brake engagement direction by a spring and operates in the brake pull-up direction by exposing the annular chamber 12 to the pressure medium. can do.

  The connection between the ports 14 and 16 of the hydraulic motor 4 and the pressure line 19 or the tank (return) line 21 for transmitting the pressure of a variable displacement pump (not shown) is via a pilot-controlled main valve 18. The valve body of the main valve 18 is continuously moved from the basic position biased by the spring to the right (see FIG. 2) to “hoisting” and to the left to “easing”. Can be adjusted. The main valve 18 includes two tank ports 20 and 22, a pressure port 24, an operation port 26 connected to the hydraulic motor port 14, an operation port 28 connected to the hydraulic motor port 16, and a control port 30. Have.

  The tank port 22 is connected to the tank line 21 via a meter-out valve 32. The meter-out valve 32 receives the spring force and the control pressure present in the control line 34 in the closing direction, and the pressure present in the port 14 of the hydraulic motor in the opening direction.

  A pressure compensator 38 is provided in the meter inline 36 connecting the pressure port 24 to the pressure line 19, and this pressure compensator 38 is upstream of the throttle throttle formed by the main valve 18 in the closing direction. Under pressure, the pressure of the control port 30 is received in the opening direction. The pressure of the control port 30 corresponds to the pressure downstream of the throttle throttle.

  The two control chambers of the main valve 18 are connected to the outlet ports of the shuttle valves 44, 46 via control passages 40, 42, which are connected via a third shuttle valve 48 and a motor control line 50. , Connected to the control port 52 of the hydraulic motor 4. The motor control valve 54 of the hydraulic motor 4 is controlled by the control pressure of the motor control line 50 in order to change the suction capacity.

  The inlet ports of the two shuttle valves 44 and 48 are connected to the two remote control ports 56 and 58, respectively, and are also connected to the two pilot control ports 60 and 62 of the directional control valve 64. The direction control valve 64 can be moved by the actuating lever 66 from the basic position biased by the spring to the “feed”, “winding”, and “tethered” switching positions.

  The directional control valve 64 has an inlet port 70 and an outlet port 72. The inlet port 70 is connected to the meter inline 36 via a pressure reducing valve 74 and a pressure passage 76. The pressure passage 76 is provided with a flow governor 78, a check valve 80 that opens toward the pressure reducing valve 74, and another pressure reducing valve 82. The pressure reducing valve 82 is operated by the output pressure of the pressure reducing valve 74 in the opening direction, and is operated by the spring force in the closing direction. The pressure reducing valve 74 is adjusted via the radial cam 84 of the actuating lever 66, and the outlet port of the pressure reducing valve 74 is connected to the discharge line 88 via the discharge passage 86 in the neutral position.

  A pressure passage 90 is branched between the flow governor 78 and another pressure reducing valve 82, and is connected to the port 92 of the brake lift valve 94. The brake lift valve 94 is designed as a 3 / 2-way control valve, which shuts off the port 92 in the basic position biased by the spring and communicates with the annular chamber 12. The brake pull-up line 96 is connected to the discharge passage 88 or the tank line 21 via the relief line 98. The control chamber acting in the opposite direction to the spring of the brake lift valve 94 receives the pressure of the motor control line 50 via the passage 100, thereby controlling the motor control valve 54, which pressure is controlled by the two shuttle valves 44. , 48 corresponds to the higher pressure.

  As shown in FIG. 2, the directional control valve 64 may also be designed to have no “tethered” switching position. In the case of such a modification, the flow governor 78 and the check valve 80 can also be omitted.

  In another variation of the winch control mechanism, an internal discharge line 86 ′ can be used instead of the external discharge line 86.

  When winding the rope, the actuating lever 66 is turned to the right in the hatch hoisting range, and the piston of the direction control valve 64 moves to the right accordingly. At the same time, the pressure reducing valve 74 is actuated via a radial cam 84 and the inlet port 70 is connected via a further pressure reducing valve 82 to the pressure passage 76 and the pressure line 19 which transmits the pump pressure. In the hoisting position, the pressured inlet port 70 is connected to the pilot control port 62, while the pilot control port 60 is connected to the outlet port 72 and the discharge line 86. A control pressure corresponding to the pressure at the inlet port 70 is released through the shuttle valve 46 and the control passage 42 and applied to the right control chamber of the main valve 18 shown in FIG. The main valve 18 moves to the left from the illustrated position to the hoisting position according to the applied control pressure, and the throttle throttle is opened accordingly. In the hoisting position, the pressure port 24 is connected to the operating port 28, the operating port 26 is connected to the tank port 20, the port 16 of the hydraulic motor 4 functions as a meter import, and the port 14 functions as a meter-out port. . The control pressure existing in the pilot control port 62 is sent to the motor control line 50 via the two shuttle valves 46 and 48, and the suction capacity of the hydraulic motor 4 is adjusted according to the control pressure via the motor control valve 54. Is done. The pressure in the motor control line 50 also acts on the control chamber of the brake lift valve 94 via the passage 100. With this control pressure, the brake lift valve 54 is displaced from the illustrated basic position to a switching position where the port 92 is connected to the brake pull-up line 96. Correspondingly, a brake lifting pressure corresponding to the pump pressure is applied to the annular chamber 12 of the hydraulic cylinder 10, the brake means 8 is released from engagement, and the winch 2 is driven according to the direction of rotation of the hydraulic motor 4. Is controlled to wind up the rope.

  When using remote control, the actuating lever 66 remains in the illustrated basic position. The two remote control ports 56, 58 receive a differential control pressure via a remote control device, with higher control pressures being shuttle valves 44, 46, 48 for controlling the main valve 18, motor control valves 54 and the brake lift valve 94. When hoisting the ropes by remote control, higher control pressure is applied to the remote control port 58 and is routed through the shuttle valve 46 and control passage 52 to the control chamber on the right side of the main valve 18. The valve body of the main valve 18 moves to the left in the hoisting position in the manner described above, and the hydraulic motor is controlled accordingly. The pressure at the outlet of the shuttle valve 46 is sent to the motor control line 50 via another shuttle valve 48, and the motor control valve 54 is controlled to change the suction capacity. Further, as in the case of manual control, the brake pull-up valve 94 moves to the switching position, and the brake pull-up line 96 is connected to the brake pull-up valve 54, the brake pressure passage 90, the flow governor to raise the brake. 78, check valve 80, and meter inline 36 are connected to pressure line 19.

  Adjustment of the operating states of “feeding” and “mooring” is performed in the same manner.

  Whether using the brake lifting valve 94 to which the same brake lifting pressure is applied during both remote control use and manual operation, does not cause fluctuations when winding the above-mentioned unloaded general rules, Alternatively, the variation can be reduced at least to an acceptable degree.

  FIG. 3 shows the brake lifting pressure generated when the remote control is used when the unloaded general rope is drawn by the winch 2. When the above-mentioned control pressure is applied by remote control, the brake pull-up pressure rises to the desired maximum value (approximately pump pressure) in a very short time, and after a very short transition time, a constant brake pull-up pressure and Become. The characteristic line of the brake lifting pressure is almost the same as the characteristic line when the main valve 18 is operated by the operating lever 66.

  According to the solution according to the invention, the response of the winch 2 is improved even when the load pressure is low and the control pressure is applied very rapidly and suddenly by remote control.

  In the embodiment shown in FIG. 2, the brake lift valve 94 is biased by a control spring to a position where the annular chamber 12 is connected to the discharge line 88 or the tank line 21. By designing this control spring to have means for changing the bias, the travel point of the brake lift valve 94 can be changed.

  A control mechanism for a hydraulically operated consumer, particularly a control mechanism for a winch, is disclosed. The consumer's hydraulic drive mechanism can be connected to a pump or tank by a continuously adjustable main valve. The control mechanism has hydraulically operated brake means for fixing the consumer. The main valve can be actuated by manual pilot control means or remote control means. According to the invention, the lifting of the brake means applies the same brake lifting pressure, preferably released upstream of the main valve, to the brake means using a pilot control similar to the operation by the manual pilot control means. Achieved by brake lift valve.

FIG. 1 shows the brake pressure versus time when winding a no-load haul using a conventional winch control mechanism. FIG. 2 shows a circuit diagram of a winch control mechanism according to the present invention provided with a brake lift valve. FIG. 3 shows the brake pressure versus time in the winch control mechanism according to the present invention.

Explanation of symbols

2 winch 4 hydraulic motor 6 transmission 8 brake means 10 hydraulic cylinder 12 annular chamber 14 port 16 port 18 main valve 19 pressure line 20 tank port 21 tank line 22 tank port 24 pressure port 26 operation port 28 operation port 30 control port 32 Meter-out valve 34 Control line 36 Meter inline 38 Pressure compensator 40 Control passage 42 Control passage 44 Shuttle valve 46 Shuttle valve 48 Third shuttle valve 50 Motor control line 52 Control port 54 Motor control valve 56 Remote control port 58 Remote control port 60 pilot control port 62 pilot control port 64 directional control valve 66 actuating lever 70 inlet port 72 outlet port 74 pressure reducing valve 76 pressure passage 78 flow governor 80 check valve 82 another pressure reducing valve 84 radial cam 86 Discharge passage 88 Discharge line 90 Brake pressure passage 92 Port 94 Brake pull-up valve 96 Brake pull-up line 98 Relief line 100 Passage

Claims (8)

Control mechanism for hydraulic control consumer, especially winch,
A pump for supplying a pressure medium to the drive mechanism (4) of the consumer (2), a main valve (18) for controlling the flow of the pressure medium between the drive mechanism (4), and the consumer Hydraulically actuated brake means (8) for (2),
Pilot control means (64) that can be adjusted via a manipulator (66) to apply a control pressure to the control chamber of the main valve (18), and as an alternative to the pilot control means (64) the main valve ( Remote control means capable of controlling 18) is combined with the main valve (18),
When the main valve (18) is controlled by the remote control means and the pilot control means (64), the brake control chamber (12) of the brake means (8) acting in the brake pulling-up direction is preferably provided in the main control valve (18). A control mechanism comprising a brake lift valve (94) that applies a brake lift pressure released upstream of the valve (18). In claim 1,
The brake pull-up valve (94) is a control mechanism that operates to raise the brake by a brake control pressure corresponding to the control pressure for controlling the main valve (18). In claim 2,
The brake lift valve is a 3/2 direction control valve (94);
The 3 / 2-way control valve (94) releases the brake control chamber (12) in a basic position biased by a spring, and the brake control pressure causes the brake control chamber (12) to release the brake. A control mechanism that can be switched to a position where an upper pressure is applied. In any of claims 1 to 3,
A control mechanism in which the brake pull-up pressure substantially corresponds to the pump pressure. In any of claims 1 to 4,
The brake control pressure corresponds to the control pressure for controlling the drive mechanism,
The drive mechanism is a control mechanism having the form of a hydraulic motor (4) having a variable suction capacity. In any of claims 1 to 5,
The pilot control means includes a directional control valve (64),
The directional control valve (64) has at least two pilot control ports (60, 62) connected via control passages (40, 42) to each control chamber of the main valve (18);
The higher control pressure present at the pilot control port (60, 62) or applied by the remote control means is released through the shuttle valve assembly (44, 46, 48) as a brake control pressure. Control mechanism. In any one of Claims 1 thru | or 6.
The control mechanism of the brake lift valve is designed to be adjustable. In claim 6,
The said direction control valve (64) is a control mechanism which can be set to a feeding position, a winding position, and arbitrary mooring positions via an actuating lever (66).

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