JP3944969B2 - Hydraulic winch control device - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to braking GoSo location of the hydraulic winch for driving a winch drum by a hydraulic motor.
[0002]
[Prior art]
The prior art is shown in FIG.
[0003]
In the figure, 1 is a winch drum, and 2 is a hydraulic motor (hereinafter referred to as a winch motor) as a drive source for the winch drum 1, and transmits power between the output shaft 2 a of the winch motor 2 and the winch drum 1. A planetary gear mechanism 3 is provided.
[0004]
4 is a sun gear of the planetary gear mechanism 3, 5 is a planetary gear, 6 is a ring gear provided on the inner periphery of the winch drum 1, 7 is a carrier for supporting the planetary gear 5, and 8 is a carrier shaft. A multi-plate clutch 9 is provided, and the winch drum 1 is connected to the motor output shaft 2a by the multi-plate clutch 9, a piston 10 that is pressed against and separated from the clutch 9, and a cylinder 11 that drives the piston 10. On the other hand, a hydraulic brake 12 that is connected and disconnected and brakes the rotation of the drum 1 is configured.
[0005]
Reference numeral 13 denotes a spring that pushes the piston 10 in a direction in which it is pressed against the multi-plate clutch 9.
[0006]
The extension side pipe line 14 connected to the extension side oil chamber 11 a of the cylinder 11 is connected to the secondary side of the brake valve (pressure reducing valve) 16 operated by the brake pedal 15.
[0007]
The reduction side pipe line 17 connected to the reduction side oil chamber 11b of the cylinder 11 is connected to a hydraulic pressure source 19 and a tank T via an electromagnetic switching valve 18 as a switching means.
[0008]
The electromagnetic switching valve 18 is in the normal operation position a on the left side in the normal operation, and the cylinder reduction side oil chamber 11b communicates with the tank T in this state.
[0009]
On the other hand, at the time of the free fall operation in which the winch drum 1 is rotated down by a load (suspended load), the switch 20 is turned on, whereby the electromagnetic switching valve 18 is switched to the free fall operation position b on the right side of the figure. In this state, the cylinder reduction side oil chamber 11 b is connected to the hydraulic pressure source 19.
[0010]
This device operates as follows.
[0011]
(A) During normal hoisting / lowering operation At this time, the electromagnetic switching valve 18 is in the normal operating position a in the figure, and no pressure is generated in the cylinder reduction side oil chamber 11b.
[0012]
At this time, since the brake pedal 15 is not operated, no secondary pressure is generated in the brake valve 16, and no pressure is generated in the cylinder extension side oil chamber 11a.
[0013]
Therefore, since the piston 10 is pressed against the clutch 9 by the force of the spring 13 and the clutch 9 is fixed to the fixed portion, the carrier shaft 8 is fixed so as not to rotate.
[0014]
In this state, the planetary gear 5 of the planetary gear mechanism 3 performs only rotation, the rotational force of the winch motor 2 is decelerated by the planetary gear mechanism 3 and transmitted to the winch drum 1, and normal power hoisting and lowering operations are performed. Done.
[0015]
When the rotation of the winch motor 2 is stopped, the winch drum 1 is fixed by the planetary gear mechanism 3 so as not to rotate.
[0016]
(B) During free fall operation At this time, with the winch motor 2 stopped, the switch 20 is operated to switch the electromagnetic switching valve 18 to the free fall operation position b, and pressure is applied to the cylinder reduction side oil chamber 11b. .
[0017]
As a result, the cylinder 11 is contracted, the piston 10 is separated from the clutch 9 , and the carrier shaft 8 is freed (the hydraulic brake 12 is released), so that the winch drum 1 is retracted at a speed corresponding to the load. Free to rotate.
[0018]
At this time, when the brake pedal 15 is operated and a secondary pressure is generated in the brake valve 16, the cylinder extension side oil chamber 11a is pressurized and the piston 10 is pressed against the clutch 9, and the above-described power hoisting and lowering operations are performed. It becomes the same state (clutch on state) as the hour.
[0019]
Thereby, the braking force according to the operation amount of the brake pedal 15 acts on the winch drum 1, and the free fall speed is adjusted by the operator.
[0020]
On the other hand, the suspended load lowering speed at the time of this free fall operation is considerably faster than that at the time of power lowering, and the speed is adjusted while applying the braking force by the hydraulic brake 12 as described above. A friction portion of the clutch 9 (hereinafter referred to as a brake heat generating portion) generates heat.
[0021]
Therefore, the oil discharged from the hydraulic pump 21 driven by an engine (not shown) is sent to the brake heat generating portion to be cooled.
[0022]
[Problems to be solved by the invention]
However, according to the above prior art, the speed adjustment operation by the operator is required during the free fall operation, and this operation has to be performed carefully, so that the operation burden on the operator is large.
[0023]
Moreover, there is a possibility that the suspended load may fall freely without restriction against the operator's intention due to an operator's brake operation mistake.
[0024]
Therefore, as a countermeasure against this point, as shown in JP-A-8-12280, a hydraulic brake circuit is configured by connecting a brake hydraulic pump to the winch drum 1 and connecting a relief valve to the pump. In addition, a technique has been proposed in which the pump is rotated by a winch drum during free fall operation, and the rotational load is applied to the winch drum by the hydraulic load circuit to regulate the free fall speed.
[0025]
However, according to this known technique, a large pump is required to obtain a sufficient load resistance even for a large load, and the set pressure of the relief valve needs to be relatively high.
[0026]
For this reason, there occurs a situation in which the winch drum 1 does not rotate down (cannot be free-falled) when there is a small load, including when the hook is empty.
[0027]
For this reason, this known technique has been considered impossible in practice.
[0028]
Therefore, the present invention provides a hydraulic winch control method and apparatus capable of regulating the free fall speed while ensuring the original free fall function.
[0029]
[Means for Solving the Problems]
The inventions of claim 1, and the winch drum, and a hydraulic motor as a drive source for the winch drum, and a planetary gear mechanism for power transmission between the output shaft of the winch drum and the hydraulic motor, the multi-plate clutch A hydraulic brake that is driven to switch between a clutch-on state that fixes the carrier shaft of the planetary gear mechanism and a clutch-off state that releases the carrier shaft; and a normal hoisting operation in which the winch drum is rotationally driven by the hydraulic motor. A switching means for switching between a lowering operation and a free fall operation in which the winch drum is rotated downward by a load, and the hydraulic brake includes a piston that is pressed against and separated from the multi-plate clutch, and the piston And a brake valve, and a hydraulic pressure corresponding to the amount of operation of the brake valve is applied to the cylinder. The hydraulic winch that is configured to brake rotation of the winch drum as the clutch-on state by causing the brake actuation for pressing the piston to the multi-plate clutch, the winch hydraulic pump brake, at least when the free fall operation Discharge line of the pump is provided so that the hydraulic pressure generated in the discharge line of the brake hydraulic pump during free fall operation is applied to the cylinder of the hydraulic brake in the brake operation direction. Is provided with a throttle as a pressure generating means, the same pipe line is connected to the cylinder of the hydraulic brake, and the discharge oil of the brake hydraulic pump is supplied as cooling oil for cooling the heat generating part of the hydraulic brake. Between the discharge line of the pump and the heat generating part of the hydraulic brake. In which the cooling pipe is connected to.
[0030]
According to a second aspect of the present invention, in the configuration of the first aspect, a variable throttle with a variable set pressure is used as the throttle .
[0031]
According to a third aspect of the present invention, in the configuration of the first or third aspect, as the hydraulic pump for a brake, a bidirectional discharge type pump that discharges oil by rotation in either the forward or reverse direction is used. The oil discharged from the brake hydraulic pump is supplied to the heat generating part of the hydraulic brake during both unwinding and rotation .
[0032]
According to a fourth aspect of the present invention, in the configuration of any one of the first to third aspects, the cooling oil can be supplied in parallel to the brake hydraulic pump so that the cooling oil can be supplied to the heat generating portion of the hydraulic brake even when the rotation of the winch drum is stopped. A cooling hydraulic pump is provided .
[0033]
According to the above configuration, during the free fall operation, the discharge oil of the brake hydraulic pump driven by the winch drum is added to the drive portion of the hydraulic brake, and the braking force acts on the winch drum.
[0034]
Thereby, the rotational speed (free fall speed) of the winch drum is regulated. For this reason, the safety of the free fall operation is ensured and the operation burden on the operator is reduced.
[0035]
In addition, the pump discharge oil amount changes in proportion to the drum rotation speed, and the pump discharge line pressure (braking force) changes, so that the original free fall function is reliably maintained regardless of the load size, and a small load There is no risk of freefall sometimes being lost.
[0036]
Further, in order to supply as cooling oil to the brake heat generating portion in parallel discharge oil of the hydraulic pump for brake and hydraulic brake, cooling only pump becomes unnecessary.
[0037]
In addition, as described above, the pump discharge oil amount changes in proportion to the drum rotation speed, and the cooling oil amount increases as the drum rotation speed increases and the heat generation amount increases. For this reason, cooling efficiency is further improved.
[0038]
In the prior art shown in FIG. 5, it is necessary to use a large capacity pump for the cooling pump 21 in order to secure a sufficient amount of cooling oil even in the low idle state of the engine. Since the amount of cooling oil commensurate with the rotational speed, that is, the amount of heat generation is secured, the pump capacity can be reduced.
[0039]
On the other hand, according to the configuration of the second aspect , since the discharge line pressure (braking force) of the brake hydraulic pump is variable, it is possible to select the braking action according to the suspended load amount, the work content, the operator's preference, and the like. .
[0040]
According to the third aspect of the present invention, since the hydraulic motor type bidirectional discharge pump is used as the brake hydraulic pump, the cooling oil is supplied to the brake heat generating portion not only during free fall but also during winding. For this reason, the cooling performance can be enhanced by cooling the brake heat generating portion that has been heated at the time of free fall even when it is hoisted.
[0041]
Further, according to the fourth aspect of the present invention, the cooling action is performed even when the rotation of the winch drum is stopped. In this case, the cooling hydraulic pump requires less capacity than the conventional cooling hydraulic pump.
[0042]
DETAILED DESCRIPTION OF THE INVENTION
An embodiment of the present invention will be described with reference to the drawings.
[0043]
1st Embodiment (refer FIG. 1)
In this embodiment, the same parts as those in the prior art shown in FIG.
[0044]
A ring gear 21 is provided on the outer periphery of the flange of the winch drum 1, and a rotating shaft of a brake hydraulic pump (hereinafter referred to as a brake pump) 24 is connected to an output shaft of a spur gear 22 meshing with the ring gear 21 via a one-way clutch 23. Are connected.
[0045]
Accordingly, the brake pump 24 is rotationally driven by the drum 1 when the winch drum 1 is rotated downward (when the free fall and when the power is lowered).
[0046]
A discharge pipe 25 of the brake pump 24 is branched and connected to the extension side pipe 14 of the cylinder 11, and a shuttle valve 26 is provided at this branch connection portion.
[0047]
A cooling pipe 27 is branchedly connected to the pump discharge pipe 25, and the tip of the cooling pipe 27 is connected to the heat generating portion of the hydraulic brake 12.
[0048]
The cooling pipe 27 is provided with a fixed throttle 28 as pressure generating means, and the pressure generated on the inlet side of the fixed throttle 28 becomes the pressure of the pump discharge pipe 25, that is, the pressure of the hydraulic brake 12.
[0049]
The operation of this apparatus will be described.
[0050]
During the free fall operation, the electromagnetic switching valve 18 is switched to the free fall position b by the operation of the switch 20 as described above, the reduction side oil chamber 11b of the cylinder 11 is pressurized, and the piston 10 is separated from the multi-plate clutch 9.
[0051]
As a result, the hydraulic brake 12 is turned off, and in this state, the winch drum 1 rotates down by the amount of the suspended load, and the free fall operation is performed.
[0052]
During this free fall operation, the brake pump 24 is driven by the winch drum 1 and the discharged oil is supplied to the extension side oil chamber 11a of the cylinder 10 via the shuttle valve 26, and the pressure in the extension side oil chamber 11a is reduced. When the pressure in the chamber 11b becomes higher, the piston 10 is pressed against the multi-plate clutch 9.
[0053]
As a result, the carrier shaft 8 is braked, and a braking force determined by the opening area of the fixed throttle 28 acts on the winch drum 1.
[0054]
Thus, the rotational speed of the winch drum 1, that is, the free fall speed is regulated to a predetermined value or less, so that there is no possibility that the suspended load falls freely without regulation, and safety during free fall operation is ensured.
[0055]
If the operator operates the brake pedal 15 during the free fall operation, a pressure corresponding to the operation amount is applied to the cylinder extension side oil chamber 11a, so that the speed can be adjusted within the regulation speed.
[0056]
On the other hand, the oil discharged from the brake pump 24 is supplied as cooling oil to the brake heat generating part through the cooling pipe 27 in parallel with the cylinder 11. Thus, during the free fall operation, the brake heat generating portion is cooled and the brake performance is maintained.
[0057]
In this case, the rotational speed of the brake pump 24 is proportional to the rotational speed of the winch drum 1, and the amount of cooling oil increases as the drum rotational speed increases and the heat generation amount increases, so that the cooling efficiency is improved.
[0058]
Moreover, since the amount of cooling oil commensurate with the amount of heat generation is secured, the capacity of the brake pump 24 can be reduced.
[0059]
The brake pump 24 is driven even when the power is down. At this time, the electromagnetic switching valve 18 is set to the normal operation position a, and no pressure is generated in the reduction-side oil chamber 11b of the cylinder 11, and the piston 10 is originally provided. Is pressed against the multi-plate clutch 9 by the force of the spring 13, and even if oil is supplied from the brake pump 24, the operation does not change.
[0060]
Further, at the time of hoisting, the brake pump 24 is disconnected from the winch drum 1 by the action of the one-way clutch 23, so that no oil discharge action is performed.
[0061]
Incidentally, a variable aperture may be used instead of the fixed aperture 28. In this way, the regulation speed can be made variable according to the amount of suspended load, work content, operator preference, and the like.
[0062]
Further, instead of the variable throttle, a switching valve operated by an operator may be used so that the regulation speed can be arbitrarily set by adjusting the stroke of the switching valve.
[0063]
Second embodiment (see FIG. 2)
In the following embodiments, only differences from the first embodiment will be described.
[0064]
In the second embodiment, as the brake pump 24 driven by the winch drum 1, a bidirectional discharge pump of a hydraulic motor type that discharges oil by rotation in either forward or reverse direction as shown in the figure is used.
[0065]
In this case, the one-way clutch 23 is omitted and the brake pump 24 is directly connected to the spur gear 22.
[0066]
Discharge pipes 25a and 25b are provided on both sides of the brake pump 24, and the both side discharge pipes 25a and 25b are connected to a shuttle valve 26 or a tank T via a check valve block 29 in which four check valves are combined. Connected to.
[0067]
According to this configuration, the brake pump 24 is driven not only during the lowering rotation of the winch drum 1 but also during the uppering rotation, and the pump discharge oil is supplied to the brake heat generation unit. The cooling performance is enhanced by being able to cool even during winding.
[0068]
At the time of winding, since the electromagnetic switching valve 18 is in the normal operation position a and the piston 10 is originally pressed against the multi-plate clutch 9, even if the discharge oil of the brake pump 24 is further supplied, the operation is not affected. Absent.
[0069]
3rd Embodiment (refer FIG. 3)
In this embodiment, a cooling pump 30 driven by an engine (not shown) is provided separately from the brake pump 24, and a discharge pipe 31 of the cooling pump 30 is branched and connected to the cooling pipe 27.
[0070]
32 is a check valve that regulates the flow direction of the oil discharged from the pump 30 to the brake heat generating part side.
[0071]
According to this configuration, the oil discharged from the cooling pump 30 merges with the oil discharged from the brake pump 24 when the winch drum 1 rotates and is supplied to the brake heat generating unit, and is supplied to the brake heat generating unit independently when the drum rotation is stopped.
[0072]
In other words, the cooling oil is supplied to the brake heat generating portion even when the drum is stopped, and the cooling action is performed.
[0073]
In this case, the cooling pump 30 requires a smaller capacity than the cooling hydraulic pump of the prior art.
[0074]
Fourth embodiment (see FIG. 4)
In each of the first to third embodiments, the secondary pressure of the pressure reducing valve (brake valve) 16 is supplied to the cylinder 11 by the operation of the brake pedal 15, but the brake pedal 15 of the fourth embodiment is used. A known configuration in which the hydrostatic pressure from the master cylinder 33 is sent to the cylinder 11 by an operation may be adopted. Reference numeral 34 denotes a reservoir of the master cylinder 33.
[0075]
This configuration can also provide basically the same effects as the other embodiments.
[0076]
Further, as shown in FIG. 4, a relief valve 35 as a safety valve that regulates the maximum pressure may be connected to the discharge pipe 25 of the brake pump 24 through each embodiment.
[0077]
Incidentally, in the above SL embodiments, a clutch disposed between the brake pump 24 and spur gear 22, during free fall, velocity regulating action the brake pump 24 is separated from the winch drum 1 by the clutch as desired You may comprise so that the complete free fall operation which does not have can be performed.
[0078]
【The invention's effect】
As described above, according to the present invention, during the free fall operation, the brake hydraulic pump is driven by the winch drum, and the brake oil is applied to the winch drum by adding the oil discharged from the pump to the hydraulic brake drive unit. Since the free fall speed is regulated, the free fall speed can be regulated to ensure work safety while ensuring the original free fall function.
[0079]
Further, in order to supply as cooling oil to the brake heat generating portion in parallel discharge oil of the hydraulic pump for brake and hydraulic brake, cooling only pump becomes unnecessary.
[0080]
In addition, as described above, the pump discharge oil amount changes in proportion to the drum rotation speed, and the cooling oil amount increases as the drum rotation speed increases and the heat generation amount increases. For this reason, cooling efficiency is further improved.
[0081]
In addition, since the amount of cooling oil corresponding to the drum rotation speed, that is, the amount of heat generated in the brake heat generating portion is secured, the pump capacity can be reduced.
[0082]
On the other hand, according to the invention of claim 2 , since the discharge line pressure (braking force) of the brake hydraulic pump is variable, it is possible to select the braking action according to the suspended load amount, the work content, the operator's preference, and the like. .
[0083]
According to the invention of claim 3 , since the bidirectional discharge pump of the hydraulic motor type is used as the brake hydraulic pump, the cooling oil is supplied to the brake heat generating portion not only during free fall but also during winding. For this reason, the cooling performance can be enhanced by cooling the brake heat generating portion that has been heated at the time of free fall even when it is hoisted.
[0084]
Furthermore, according to the invention of claim 4, since the cooling action is performed even when the rotation of the winch drum is stopped, it is suitable for a winch where brake heat generation is intense. In this case, the cooling hydraulic pump requires less capacity than the conventional cooling hydraulic pump.
[Brief description of the drawings]
FIG. 1 is a hydraulic circuit diagram showing a first embodiment of the present invention.
FIG. 2 is a hydraulic circuit diagram showing a second embodiment of the present invention.
FIG. 3 is a hydraulic circuit diagram showing a third embodiment of the present invention.
FIG. 4 is a hydraulic circuit diagram showing a fourth embodiment of the present invention.
FIG. 5 is a hydraulic circuit diagram showing a conventional technique.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Winch drum 2 Hydraulic motor for driving the same drum 12 Hydraulic brake 9 Multi-plate clutch constituting hydraulic brake 10 Same piston 11 Same cylinder 13 Same spring 18 Electromagnetic switching valve 20 constituting switching means 20 Same switch 24 Brake hydraulic pump 21, 22 Gear for connecting the pump and winch drum 23 One-way clutch 25 Discharge line 27 for brake hydraulic pump 27 Cooling line 28 Fixed throttle as pressure generating means 30 Hydraulic pump for cooling

Claims (4)

A winch drum, a hydraulic motor as a drive source of the winch drum, a planetary gear mechanism for transmitting power between the winch drum and an output shaft of the hydraulic motor, a multi-plate clutch to drive the planetary gear mechanism A hydraulic brake that switches between a clutch-on state for fixing the carrier shaft and a clutch-off state for releasing the carrier shaft, and a normal winch / unwind operation in which the winch drum is rotationally driven by the hydraulic motor and a winch by the load. Switching means for switching between free fall operation for rotating the drum down, and the hydraulic brake includes a piston that is pressed against and separated from the multi-plate clutch, a cylinder that drives the piston, and a brake valve The hydraulic pressure corresponding to the amount of operation of the brake valve is applied to the cylinder, and the piston is The hydraulic winch that is configured to brake rotation of the winch drum as the clutch-on state by causing a braking for pressing the latch, the hydraulic pump for a brake is driven to rotate by the winch drum at least the free fall time of operation As a pressure generating means in the discharge line of the pump so that the hydraulic pressure generated in the discharge line of the brake hydraulic pump during free fall operation is applied to the cylinder of the hydraulic brake in the brake operating direction. And the pipe is connected to the cylinder of the hydraulic brake, and the discharge oil of the brake hydraulic pump is supplied as cooling oil for cooling the heat generating part of the hydraulic brake. A cooling line is connected between the discharge line and the heat generating part of the hydraulic brake. Control device for a hydraulic winch, characterized in that it is. 2. The hydraulic winch control device according to claim 1 , wherein a variable throttle with a variable set pressure is used as the throttle . As the cooling hydraulic pump, a bi-directional discharge type pump that discharges oil by rotating in either forward or reverse direction is used, and the oil discharged from the cooling hydraulic pump is hydraulic brake when the winch drum rotates both up and down. 3. The hydraulic winch control device according to claim 1, wherein the hydraulic winch control device is supplied to the heat generating portion . 4. The cooling hydraulic pump is provided in parallel with the brake hydraulic pump so that the cooling oil can be supplied to the heat generating part of the hydraulic brake even when the rotation of the winch drum is stopped . The control apparatus of the hydraulic winch of any one of Claims .

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