JP2003226487A - Brake device and clutch device of winch, and crane with the brake device and clutch device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To cool a disk of a winch efficiently and appropriately. <P>SOLUTION: The temperature T of an outer disk 13 is detected by a temperature sensor 42, and the free fall operation is detected based on a free fall switch 41 and a pressure switch 43. When the free fall switch 41 is on and the pressure switch 43 is off, an electromagnetic proportional valve 29 is switched according to the detected value of temperature T, and a pressure oil is fed from a hydraulic source 28 to a brake housing 11. When the free fall switch 41 is off or the pressure switch 43 is on, the supply of the pressure oil from the hydraulic source 28 for the brake housing 11 is prohibited. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a winch brake device for braking a freefall of a winch drum, a winch clutch device for transmitting power to a winch drum, and a brake device and a crane equipped with the clutch device.

[0002]

2. Description of the Related Art In a brake device of this type, a brake disc is pushed by operating a brake pedal during free fall of a winch drum, and a friction force is applied to the rotating disc to generate a braking force. (For example, JP-A-11-130381). When a frictional force is applied to the rotating disk in this way, the temperature of the disk surface rises due to frictional heat, which causes a decrease in the braking force. In order to avoid this, in the device described in the above publication, the hydraulic pump is driven by the downward rotation of the winch drum, and the cooling oil from this hydraulic pump is supplied to the disk.

[0003]

However, in the device described in the above publication, since the hydraulic pump is driven by the lowering rotation of the winch drum, the cooling oil is supplied even during the power lowering where the temperature rise of the disk is small, and Efficiency. Further, since the amount of cooling oil from the hydraulic pump is determined by the number of revolutions of the winch drum in the winding operation, it is difficult to supply a required amount of cooling oil to the disk to perform proper cooling.

An object of the present invention is to provide a winch braking device, a clutch device, and a hoisting device for a crane equipped with the braking device and the clutch device, which can cool the disk efficiently and appropriately.

[0005]

(1) A winch brake device according to a first aspect of the present invention is a winch brake device, which is driven by power to wind up and down and is free fall by a load of a suspended load, and rotation of the winch drum. The brake member for braking the brake, the freefall detecting means for detecting the freefall operation of the winch drum, the cooling oil supplying means for supplying the cooling oil from the hydraulic source to the braking member, and the freefall detecting means for detecting the freefall operation. When the free fall detection means detects a free fall stop, the cooling oil supply means is controlled so as to reduce the amount of cooling oil supplied to the braking member. With the oil control means, the above-described object is achieved. (2) A winch brake device according to a second aspect of the present invention includes a winch drum that is driven by hoisting and hoisting by power and is free fall by a load of a suspended load,
A braking member that brakes the rotation of the winch drum, a heat generation detection unit that detects a heat generation state of the braking member, a free fall detection unit that detects a free fall operation of the winch drum, and a cooling oil is supplied from a hydraulic power source to the braking member. When the free fall operation is detected by the cooling oil supply means and the free fall detection means, the amount of cooling oil supplied to the braking member is controlled according to the heat generation state detected by the heat generation detection means, and other than the free fall operation. With the cooling oil control means for reducing the amount of cooling oil supplied to the braking member to at least the amount of cooling oil supplied at the time of detecting the free fall operation, the above-mentioned object is achieved. (3) The winch brake device according to the third aspect of the present invention is provided in association with a plurality of winch drums that are hoisted and unwinded by power and are free fall by the load of a suspended load, and a plurality of winch drums. A plurality of braking members for braking the rotation of the winch drum, heat generation detecting means for detecting the heat generation states of the plurality of braking members, free fall detecting means for detecting the free fall motions of the plurality of winch drums, and a hydraulic power source When the free fall operation of a plurality of winch drums is detected by the cooling oil supply means for supplying and distributing the cooling oil to each of the plurality of braking members from the above, the heat generation state detected by the heat generation detection means is set. The amount of cooling oil distributed from the hydraulic power source to the multiple braking members is controlled in accordance with And a cooling oil control means for reducing the amount of cooling oil supplied to the braking member corresponding to the winch drum at least when the at least one of the systems is not in the free fall operation. By providing, the above-mentioned object is achieved. (4) According to the invention of claim 4, in the winch brake device according to any one of claims 2 to 4, a freefall command means for commanding a freefall operation and a winch drum winding or winding drive. The free fall detecting means detects the free fall operation based on the instructions from the free fall command means and the drum command means. (5) The invention according to claim 5 is the winch brake device according to any one of claims 2 to 4, wherein the heat generation state detecting means has a temperature detecting means for detecting the temperature of the braking member, and is detected. The heat generation state is detected according to the temperature. (6) The invention of claim 6 is the winch brake device according to any one of claims 2 to 4, wherein the heat generation state detection means has an oil temperature detection means for detecting the temperature of the cooling oil.
The heat generation state is detected according to the detected cooling oil temperature. (7) The invention according to claim 7 is the winch brake device according to any one of claims 2 to 4, wherein the heat generation state detection means detects a release pressure for releasing the braking by the braking member. And a rotation speed detection means for detecting the rotation speed of the winch drum, and detects the heat generation state according to the detected cooling oil pressure and the drum rotation speed. (8) A winch clutch device according to the invention of claim 8 is a winch drum according to claim 1, a braking member,
The above-described object is achieved by including the free fall detection means, the cooling oil supply means, and the cooling oil control means, and transmitting / non-transmitting the power to the winch drum via the braking member. (9) A winch clutch device according to a ninth aspect of the present invention is a winch drum according to any one of the second to seventh aspects, a braking member, a heat generation detection means, a free fall detection means, and a cooling oil supply means. And a cooling oil control means,
The above-described object is achieved by transmitting / non-transmitting the power to the winch drum via the braking member. (10) The crane according to the invention of claim 10 is the crane according to claim 1.
The above-described object is achieved by providing the brake device according to any one of items 1 to 7. (11) The crane according to the invention of claim 11 includes:
Alternatively, the object described above is achieved by providing the clutch device described in 9.

[0006]

BEST MODE FOR CARRYING OUT THE INVENTION First Embodiment Hereinafter, a first embodiment of a brake device according to the present invention will be described with reference to FIGS. 1 to 3 and 11. Figure 1
[Fig. 11] is a hydraulic circuit diagram of a winch having a brake device according to the first embodiment of the present invention, and Fig. 11 is a side view of a crane equipped with the brake device. As shown in FIG. 11, the crane includes a traveling body 101 and a traveling body 101.
Revolving revolving structure 102 mounted on the revolving structure and revolving structure 10
2 and a boom 103 supported so as to be capable of undulating. The winch drum 1 is mounted on the revolving structure 102, the wire rope 104 is hoisted or unwound by the drive of the winch drum 1, and the hanging load 106 is hoisted by the hook 105 connected to the wire rope 104. Further, a hoisting drum 107 is mounted on the revolving structure 102, and the hoisting rope 108 is hoisted or unwound by driving the hoisting drum 107 to hoist the boom 103.

As shown in FIG. 1, a winch includes a winch drum 1 and a hydraulic motor 2 for driving the winch drum 1.
And a hydraulic pump 3 that supplies driving pressure oil to the hydraulic motor 2.
A directional control valve 4 for controlling the flow of pressure oil from the hydraulic pump 3 to the hydraulic motor 2, a planetary reduction mechanism 5 for transmitting the driving force of the hydraulic motor 2 to the winch drum 1, and a rotation of the winch drum 1. Alternatively, it has a wet multi-plate type brake device 10 for transmitting and non-transmitting the drive of the hydraulic motor 2.

The output shaft 2a of the hydraulic motor 2 is connected to the sun gear 51 of the planetary reduction mechanism 5. A planetary gear 52 is meshed with the sun gear 51, and the planetary gear 52 is provided with a ring gear 53 provided inside the winch drum 1.
Are meshed. Planetary gear 52 is carrier shaft 5
4, the carrier shaft 54 is supported by the brake case 1
1 penetrates the side wall and reaches the inside of the case 11.

The main part inside the brake case 11 (mainly the lower part)
The structure is shown in FIG. A plurality of inner discs 12 are engaged with the carrier shaft 54 by spline coupling so as to be movable in the axial direction, and the inner disc 12 is rotatable integrally with the carrier shaft 54. A plurality of outer disks 13 are engaged with the inner peripheral surface of the brake case 11 by spline coupling so as to be movable in the axial direction. The outer discs 13 and the inner discs 12 are arranged alternately in the axial direction, and the outer discs 13 are arranged at both ends of these discs 12, 13, that is, the outermost portions in the axial direction. Brake piston 1 beside the discs 12 and 13
4 is arranged, and the brake piston 14 is slidable in the brake case 11 in the axial direction.

As shown in FIG. 1, the brake piston 14
A piston 16 of a hydraulic cylinder 15 is attached to the. A spring 17 that exerts a biasing force in the axial direction is interposed between the brake piston 14 and the brake case 11. The oil chamber 15a of the hydraulic cylinder 15 is connected to a hydraulic pump 24 via a conduit 21, a pressure reducing valve 22, and an electromagnetic switching valve 23. The pressure reducing valve 22 is a variable pressure reducing valve, and the degree of pressure reduction is changed according to the depression amount of the brake pedal 25. That is, the degree of pressure reduction is minimum (secondary pressure is maximum) when the pedal is not operated, the degree of pressure reduction increases (secondary pressure decreases) with an increase in pedal stroke, and the degree of pressure reduction increases when the pedal 25 is fully depressed. Maximum (secondary pressure is tank pressure). The figure shows a state in which the brake pedal 25 is fully depressed.

When the maximum secondary pressure acts on the oil chamber 15a, the piston 16 resists the urging force of the spring 17 and the disc 12,
It is pushed to the opposite side of 13. Disk 1
The pressure contact force acting on 2, 13 is removed, and the brake is released. On the other hand, when the oil chamber 15a is under tank pressure, the piston 16 is urged by the spring 17 so that the disks 12, 13
Pushed to the side. As a result, the inner disc 12 and the outer disc 13 are pressed and brought into close contact with each other, and the brake is activated.

The solenoid of the solenoid operated directional control valve 23 is connected to a free fall switch 41. The free fall switch 41 is switched by an operation in the driver's cab.
When the free fall switch 41 is turned on, the solenoid operated directional control valve 23 is switched to position b as shown. As a result, pressure oil can be supplied from the hydraulic pump 24 to the oil chamber 15a. When the free fall switch 41 is off,
The electromagnetic switching valve 23 is switched to the position a, and the supply of pressure oil to the oil chamber 15a is prohibited.

As shown in FIGS. 1 and 2, an oil supply hole 11a is provided at a side end portion of the brake case 11, and the disc 1
An oil drain hole 11b is provided at the bottom of the brake case 11 on the opposite side of the oil feed hole 11a with the oil tanks 2 and 13 interposed therebetween. The oil supply hole 11a is connected to a hydraulic pressure source (for example, a hydraulic pump) 28 via a pipe line 26 and a hydraulic pressure switching valve 27, and the oil discharge hole 11b is connected to a tank.

The pilot port of the hydraulic pressure switching valve 27 is connected to the pilot hydraulic pressure source 30 via the electromagnetic proportional pressure reducing valve 29, and the switching amount of the hydraulic pressure switching valve 27 is adjusted according to the degree of pressure reduction of the electromagnetic proportional valve 29. When the pilot pressure acts on the hydraulic pressure switching valve 29, the hydraulic pressure switching valve 29 is switched to the position B side. By this switching, the pressure oil from the hydraulic pressure source 28 is supplied to the oil supply hole 11
It is supplied into the brake case 11 via a. The supplied pressure oil passes through the inside of the brake case and is then returned to the tank through the oil drain hole 11b.
The disks 12 and 13 in 1 are cooled. Hydraulic pressure switching valve 2
When the supply of pilot pressure to 7 is stopped, the hydraulic pressure switching valve 27
Is switched to position a. As a result, the supply of pressure oil from the hydraulic power source 28 into the brake case 11 is blocked. The pressure oil from the hydraulic pressure source 28 is also supplied to other control valves via the hydraulic pressure switching valve 27. The degree of pressure reduction of the solenoid proportional valve 29 is controlled by a control signal from the controller 40 as described later.

The outer disk 13 is provided with a temperature sensor 42, and the temperature sensor 42 detects the temperature of the outer disk 13. The temperature detected here is a representative temperature indicating the heat generation state of the disks 12 and 13. A pressure switch 43 is connected to the hoisting and hoisting pilot lines of the directional control valve 4, and the operation of the operating lever 6 is detected by the pressure switch 43. The controller 40 takes in signals from the free fall switch 41, the temperature sensor 42, and the pressure switch 43, executes the following processing, and outputs a control signal to the solenoid of the solenoid proportional valve 29.

FIG. 3 is a flow chart showing an example of processing in the controller 40 according to the first embodiment.
This flowchart starts, for example, when the engine key switch is turned on. First, in step S1, it is determined whether the free fall switch 41 is on. When step S1 is affirmed, it progresses to step S2 and it is determined whether the pressure switch 43 is on. The free fall operation is performed when the free fall switch 41 is on and the operation lever 6 is in neutral, and the steps S1 and S2 are performed.
Then, it is determined whether or not the free fall operation is performed. If it is determined to be the free fall operation, step S2 is affirmed and the process proceeds to step S3.

In step S3, the controller 40 is previously set.
The pressure reduction degree corresponding to the detection value T of the temperature sensor 42 is calculated by using the relationship between the temperature detection value T and the pressure reduction degree of the solenoid proportional valve 29 stored in. In this case, the controller 40 stores a relationship in which the degree of pressure reduction decreases (the secondary pressure increases proportionally) as the temperature detection value T increases. Next, in step S4, the control signal I corresponding to the calculated pressure reduction degree is output to the solenoid of the solenoid proportional valve 29. As a result, the degree of pressure reduction of the solenoid proportional valve 29 is controlled to a value according to the detected temperature value T.

On the other hand, if either step S1 or step S2 is denied, it is determined that the free fall operation is not performed, and the routine proceeds to step S5. In step S5,
A predetermined control signal IL (low signal) is output to the solenoid of the solenoid proportional valve 29 so that the degree of pressure reduction of the solenoid proportional pressure reducing valve 29 is maximized. As a result, the solenoid proportional valve 29 is controlled to the maximum degree of pressure reduction, and the secondary pressure becomes, for example, the tank pressure.

The main operation of the brake device according to the first embodiment configured as described above will be described. (1) Free fall switch off When the free switch 41 is off, the electromagnetic switching valve 23 is switched to the position a. By this switching, the oil chamber 15a of the hydraulic cylinder 15 becomes the tank pressure regardless of the operation of the brake pedal 25, and the brake piston 14 is pushed toward the disks 12, 13 by the urging force of the spring 17. As a result, the outer disc 13 and the inner disc 12 are pressed against each other, a frictional force acts on the inner disc 12, and rotation of the inner disc 12 is blocked (brake operation).

When the brake device 10 operates in this manner, the rotation of the carrier shaft 54 is blocked, and the hydraulic motor 2
Can be transmitted to the winch drum 1 via the sun gear 51, the planetary gear 52, and the ring gear 53. If the pilot pressure oil is applied to the pilot port of the direction switching valve 4 by operating the operation lever 6 to wind up or down, the direction switching valve 4 is switched from the neutral position, and the pressure oil from the hydraulic pump 3 is used. The hydraulic motor 2 rotates in the winding direction or the winding direction. As a result, the winch drum 1 is driven to wind up or wind down, and a hoisting operation of a suspended load can be performed. When the operation lever 6 is returned to the neutral position, the direction switching valve 4 is returned to the neutral position, and the supply of pressure oil from the hydraulic pump 3 to the hydraulic motor 2 is stopped. As a result, the rotation of the winch drum 1 is stopped. The rotation of the winch drum 1 may be stopped by a brake device (not shown) other than the brake device 10 regardless of the neutral operation of the operation lever 6.

When the free fall switch 41 is off,
The solenoid proportional valve 29 is controlled to the maximum degree of pressure reduction by the above-described processing (step S5), and the minimum secondary pressure (tank pressure) acts on the pilot port of the hydraulic pressure switching valve 27. As a result, the hydraulic pressure switching valve 27 is switched to position A, and the hydraulic pressure source 28
The supply of pressure oil from the inside to the brake case 11 is blocked. As a result, power consumption is reduced and fuel economy is improved.

(2) Free fall switch on When the free fall switch 41 is turned on, the electromagnetic switching valve 2
3 is switched to position b. This allows the hydraulic pump 2
The pressure oil from No. 4 is supplied to the pressure reducing valve 22 via the electromagnetic switching valve 23, and the secondary pressure according to the operation amount of the brake pedal 25 acts on the oil chamber 15a. When the brake pedal 25 is not operated, the secondary pressure is maximum, and the hydraulic pressure acting on the piston 16 overcomes the biasing force of the spring 17 so that the brake piston 14 moves to the opposite side of the disks 12 and 13. As a result, the pressure contact force acting on the disks 12 and 13 is removed,
The inner disc 12 becomes rotatable (brake release).

When the rotation of the hydraulic motor 2 is stopped by the neutral operation of the operating lever 6 when the brake is released, the rotation of the carrier shaft 54 is allowed and the winch drum 1 is brought into a free rotation state by the load of the suspended load, so that the suspended load is free fall. can do. When the brake pedal 25 is depressed in this state, the secondary pressure decreases in accordance with the amount of the depression, and when the pedal 25 is depressed fully, the secondary pressure becomes the tank pressure. As a result, the brake piston 14 is pushed by the urging force of the spring 17, and the disks 12, 13
The two are pressed together. Thereby, the rotation of the winch drum 1 can be stopped during the free fall.

During free fall, the operating lever 6 is in the neutral position and the pressure switch 43 is turned off. As a result, the solenoid proportional valve 2 is processed by the above-described processing (step S4).
The pressure reduction degree of 9 is controlled, and the hydraulic pressure switching valve 27 is set to the temperature detection value T
The position is switched to the position b. By this switching, pressure oil is supplied from the hydraulic pressure source 28 into the brake case 11,
The disks 12, 13 are cooled. In this case, the higher the temperature T of the disk 13, the larger the amount of pressure oil supplied into the brake case 11. As a result, the disks 12, 13
Can be efficiently cooled.

When the free fall switch is turned on and the operating lever 6 is hoisted or hoisted while the brake pedal 25 is being depressed, the brake device 10 is activated and pressure oil from the hydraulic pump 3 is supplied to the hydraulic motor 2. Then, the drum 1 is driven to wind up or wind down. That is, if the freefall switch 41 is on but the pressure switch is not off, the hoisting or hoisting operation is possible. At this time, the solenoid proportional valve 29 reaches the maximum decompression degree and the hydraulic pressure switching valve 27 is switched to the position a by the above-described processing (step S2 → step S5), so that the brake case 11 is unnecessarily cooled except during the free fall. It is possible to prevent oil from being supplied.

In the above embodiment, when the free fall switch 41 is off, the tank pressure is applied to the pilot port of the hydraulic pressure switching valve 27 to cause the brake case 11 to operate.
Although the supply of pressure oil to the inside is prohibited, the maximum degree of pressure reduction of the solenoid proportional valve 29 is set so that the minimum secondary pressure becomes larger than the tank pressure, and a small amount of pressure oil from the hydraulic pressure source 28 is braked. It may be guided into the case 11.

As described above, according to the first embodiment, when the free fall switch 41 is on and the pressure switch 43 is off, it is determined that the work is a free fall work, and the cooling oil is supplied into the brake case 11. Therefore, when cooling of the disks 12 and 13 is not necessary, the cooling oil is not wastefully supplied, which is efficient. Further, since the amount of cooling oil is increased / decreased according to the temperature of the disks 13, the disks 12, 13 can be appropriately cooled. That is, when the disks 12 and 13 are at a high temperature, the cooling oil amount can be increased to immediately lower the temperature of the disks 12 and 13, and when the disks 12 and 13 are at a low temperature, the cooling oil amount can be decreased to cool the brake case 11 more than necessary. Supply can be prevented.

-Second Embodiment- A second embodiment of the brake device according to the present invention will be described with reference to FIGS. The second embodiment is the first
What is different from the embodiment is the method of adjusting the amount of cooling oil supplied into the brake case 11. That is, in the first embodiment, the amount of cooling oil is controlled based on the temperature of the outer disc 13, but in the second embodiment, the rotation speed of the winch drum 1 and the hydraulic cylinder 15 are supplied. The amount of cooling oil is controlled based on the brake release pressure. FIG. 4 is a hydraulic circuit diagram of a winch having a brake device according to the second embodiment. The same parts as those in FIG. 1 are designated by the same reference numerals, and the differences will be mainly described below.

As shown in FIG. 4, in the second embodiment, the oil supply hole 11a of the brake case 11 has the conduit 26.
It is connected to the hydraulic pump 32 via. The hydraulic pump 32 is connected to an output shaft of an engine (not shown) and is driven by the rotation of the engine. The hydraulic pump 32 is a variable displacement pump, and its tilt angle is changed by a tilt cylinder 33. The tilt cylinder 33 is connected to the hydraulic pump 24 via an electromagnetic switching valve 34.

The electromagnetic switching valve 34 is switched by a control signal I (low signal IL, high signal IH) from the controller 40, and the tilt cylinder 33 is driven in accordance with this switching. That is, when the high signal I is output to the solenoid of the electromagnetic switching valve 34, the electromagnetic switching valve 34 is switched to position B. This causes pressure oil to act on the tilt cylinder 33,
The pump tilt angle q increases. On the other hand, when the low signal IL is output to the solenoid of the electromagnetic switching valve 34, the electromagnetic switching valve 34
Is switched to position a. As a result, tank pressure acts on the tilt cylinder 33, and the pump tilt angle q decreases.

A drum rotation speed sensor 44 for detecting the rotation speed ND of the winch drum 1 is provided near the winch drum 1.
Is provided, and the engine is provided with an engine speed sensor 46 for detecting the engine speed NE. A pressure sensor 45 that detects a pressure (brake release pressure) P in the pipeline 21 is provided in the pipeline 21 that is connected to the oil chamber 15a of the hydraulic cylinder 15. The sensors 44 to 46, the free fall switch 41, and the pressure switch 43 are connected to the controller 40. The controller 40 takes in signals from these and executes the following processing,
The control signal I is output to the electromagnetic switching valve 34.

FIG. 5 is a flow chart showing an example of processing in the controller 40 according to the second embodiment.
The same processes as those in FIG. 3 are designated by the same reference numerals, and the differences will be mainly described below. As shown in FIG. 5, when both step S1 and step S2 are affirmed, the process proceeds to step S11. In step S11, the drum rotation speed ND detected by the drum rotation speed sensor 46 and the pressure sensor 4 are detected.
The brake heat generation amount H is calculated based on the brake release pressure P detected by 5. The brake heat generation amount is an estimated heat generation amount that is generated in the disks 12 and 13 when the drum 1 in free fall is stopped by operating the brake pedal 25. When stopping the drum 1 during free fall, increase of the drum speed ND and brake release pressure P
As the braking force increases, the braking force increases
Will increase. The amount of heat generated by the brake is, for example, H = A × ND /
It is calculated by P. Here, A is a constant.

In the next step S12, step S11
A required cooling flow rate Q corresponding to the brake heat generation amount H calculated in step 3 is calculated. The required cooling flow rate Q is the disk 12,1
3 is a cooling flow rate required per unit time for sufficiently cooling No. 3. The controller 40 stores in advance a relationship (for example, a proportional relationship) in which the required cooling flow rate Q increases with an increase in the brake heating value H. Using this relationship, the required cooling flow rate according to the brake heating value H is stored. Calculate Q. Next, in step S13, the required cooling oil amount Q is divided by the signal ND from the engine speed sensor 46, that is, the pump speed to calculate the target pump tilt angle qA.

In step S14, the control signal I is output to the electromagnetic switching valve 34 so that the pump displacement angle q becomes the target pump displacement angle qA, and the electromagnetic switching valve 34 is switched. As a result, the pressure acting on the tilt cylinder 33 is adjusted, and the pump tilt angle q is controlled to the target pump tilt angle qA. In controlling the pump tilt angle q, for example, the pressure of the tilt cylinder 33 may be detected, and the electromagnetic switching valve 34 may be feedback-controlled so that this pressure becomes a value corresponding to the target pump tilt angle qA. . On the other hand, if either step S1 or step S2 is denied, the process proceeds to step S15, and the control signal IL to the electromagnetic switching valve 34 is stopped. As a result, the electromagnetic switching valve 34 is switched to the position a, the tank pressure acts on the tilt cylinder 33, and the pump tilt angle q becomes the minimum tilt.

Next, the main operation of the second embodiment will be described. Note that the differences from the first embodiment will be mainly described below. When the free fall switch 41 is off or the pressure switch 43 is on, the tilt angle q of the hydraulic pump 32 is determined by the above-described processing (step S15).
Is the smallest. As a result, the amount of cooling oil supplied from the hydraulic pump 32 into the brake case 11 is minimized, and the power consumption can be reduced.

When the free fall switch 41 is on and the pressure switch 43 is off, the pump tilt angle q is set to the target pump tilt angle qA by the above-described processing (step S14).
Is controlled to the required cooling oil amount Q in the brake case 11.
Is supplied. In this case, the brake is released when the brake pedal 25 is not operated, and the brake release pressure P in the conduit 21 is the maximum, so the brake heat generation amount H is small. As a result, the required cooling oil amount Q calculated in the controller 40 is small, and the power consumption can be reduced.

When the brake pedal 25 is operated during free fall, the brake release pressure P increases and the brake operates. As a result, the brake heat generation amount H increases and the required cooling oil amount Q increases. As a result, the brake case 11
The amount of cooling oil supplied therein also increases, and heat generation of the disks 12 and 13 during brake operation can be suppressed. In this case, the larger the rotational speed ND of the drum 1 and the smaller the brake release pressure P, the larger the brake heat generation amount H, so the required cooling oil amount Q becomes large, and the disc 12,
13 can be cooled efficiently. The cooling flow rate may not be immediately decreased to the minimum value when the drum is stopped (ND = 0), but may be decreased after a predetermined time has elapsed or gradually.

As described above, according to the second embodiment, the drum rotation speed ND and the brake release pressure P are set during the free fall.
Since the brake heat generation amount H is calculated based on the above, and the cooling oil amount Q corresponding to this brake heat generation amount H is supplied into the brake case 11, an appropriate amount of cooling oil is supplied into the case 11, 12, 13 can be cooled efficiently. Further, since the minimum amount of cooling oil is supplied into the brake case 11 even at times other than the free fall, the disks 12 and 13 can be cooled even if the drum 1 is stopped after the free fall.

In the second embodiment, the tilt angle q of the hydraulic pump 32 is controlled. However, as in the first embodiment, the hydraulic line switching valve 27 is provided in the pipe line 26 and the electromagnetic switching valve 27 is provided. The required cooling oil amount Q may be supplied into the brake case 11 by controlling the degree of pressure reduction of the proportional valve 29. Further, the minimum amount of cooling oil is supplied to the brake case 11 other than during the free fall, but the supply of the cooling oil may be prohibited except during the free fall.

Third Embodiment With reference to FIG. 6, a third embodiment of the brake device according to the present invention will be described. The third embodiment differs from the first embodiment in the method of adjusting the amount of cooling oil supplied into the brake case 11. FIG. 6 is a hydraulic circuit diagram of a winch having a brake device according to the third embodiment. The same parts as those in FIG. 1 are designated by the same reference numerals, and the differences will be mainly described below.

As shown in FIG. 6, in the third embodiment, the temperature sensor 42 is not used, and the free fall switch 41 and the pressure switch 43 are connected to the delay relay 47. The delay relay 47 is configured so that the relay contact is turned on when the free fall switch 41 is turned on and the pressure switch 43 is turned off, and turned off under other conditions. Then, when the on condition of the relay is satisfied, the relay contact is immediately turned on, and when the off condition is satisfied, the relay contact is turned off with a delay of a predetermined time t (for example, 20 to 30 seconds). The signal from the delay relay 47 is output to the solenoid proportional valve 29, which changes the degree of pressure reduction of the solenoid proportional valve 29.

The characteristic operation of the third embodiment will be described. When the free fall switch 41 is turned on and the pressure switch 43 is turned off, the delay relay 47 is turned on immediately, and the high signal IH is output to the solenoid of the solenoid proportional valve 29. As a result, the pilot pressure from the hydraulic pressure source 30 acts on the pilot port of the hydraulic pressure switching valve 27, and the hydraulic pressure switching valve 27 is switched to position b. As a result, the pressure oil from the hydraulic pressure source 28 is supplied into the brake case 11, and the disks 12 and 13 are cooled during the free fall.

On the other hand, when the free fall switch 41 is turned off or the pressure switch 43 is turned on, the delay relay 47 is turned off after a predetermined time t. When the delay relay 47 is turned off, the low signal IL is output to the solenoid proportional valve 29. As a result, the hydraulic pressure switching valve 27 is switched to position A, and the supply of pressure oil into the brake case 11 is blocked. In this case, the cooling oil is supplied into the brake case for a predetermined time t after the brake is released due to the delay in switching the relay contacts. As a result, immediately after releasing the brake, the disc 1
Even if the temperature of 2 and 13 is high, the disks 12 and 13 can be cooled.

As described above, according to the third embodiment, the signals of the free fall switch 41 and the pressure switch 43 are taken into the delay relay 47, and the relay 47 is turned on at the time of free fall to supply the cooling oil into the brake case 11. Since this is done, the controller 40 is not necessary and the configuration can be made at low cost. Further, since the relay 47 is turned off after a predetermined time t other than during the free fall, cooling oil is supplied into the controller 11 even after the free fall, and the disks 12 and 13 can be sufficiently cooled. The hydraulic power source 28 may be configured by a variable pump as in the second embodiment, and the pump tilt angle q may be changed by a signal from the relay 47.

-Fourth Embodiment- A fourth embodiment of the brake system according to the present invention will be described with reference to FIGS. The fourth embodiment is the first
What is different from the embodiment is the method of adjusting the amount of cooling oil supplied into the brake case 11. FIG. 7 is a hydraulic circuit diagram of a winch having a brake device according to the fourth embodiment. The same parts as those in FIG. 1 are designated by the same reference numerals, and the differences will be mainly described below.

As shown in FIG. 7, in the fourth embodiment, the pilot port of the hydraulic pressure switching valve 27 is connected to the hydraulic power source 30 via the electromagnetic switching valve 35. The electromagnetic switching valve 35 is switched by a control signal (low signal IL, high signal IH) from the controller 40. That is, when the low signal IL is output to the solenoid of the electromagnetic switching valve 35, the electromagnetic switching valve 35 is switched to position A, and when the high signal IH is output, the electromagnetic switching valve 35 is switched to position B.

FIG. 8 is a flowchart showing an example of processing executed in the controller 40 according to the fourth embodiment. The same parts as those in FIG. 3 are designated by the same reference numerals, and the differences will be mainly described below. As shown in FIG. 8, when both step S1 and step S2 are affirmed, the process proceeds to step S21. In step S21, it is determined whether the detected value T of the temperature sensor 42 is larger than a predetermined value Ts set in advance. Here, the predetermined value Ts means the disc 1
This is a reference value for determining whether cooling of Nos. 2 and 13 is necessary, and is determined in consideration of the heat resistance of the disks 12 and 13 and the temperature characteristics of the cooling oil.

When step S21 is affirmed, step S
22, the low signal I is sent to the solenoid of the electromagnetic switching valve 35.
Output L. As a result, the electromagnetic switching valve 35 is switched to position A, and the pilot pressure from the hydraulic pressure source 30 acts on the pilot port of the hydraulic switching valve 27. On the other hand, if any of step S1, step S2, or step S21 is denied, the routine proceeds to step 23, where the high signal IH is output to the solenoid of the electromagnetic switching valve 35. As a result, the electromagnetic switching valve 35 is switched to the position b, and the supply of pilot pressure from the hydraulic power source 30 is blocked.

In the fourth embodiment, when the free fall switch 41 is on and the pressure switch 43 is off, if the temperature of the disk 13 exceeds a predetermined value Ts, the electromagnetic switching valve is processed by the above-mentioned processing (step S22). 35
Is switched to the position a, and the hydraulic pressure switching valve 27 is connected to the hydraulic power source 30.
Pilot pressure from acts. As a result, the hydraulic switching valve 27 is switched to the position B as shown in FIG. 7, cooling oil is supplied from the hydraulic source 28 into the brake case 11, and the disks 12 and 13 are cooled. When the temperature of the disk 13 becomes equal to or lower than the predetermined value Ts, the electromagnetic switching valve is switched to the position B by the above-mentioned processing (step S23),
The supply of pilot pressure from the hydraulic power source 30 is stopped. As a result, the hydraulic pressure switching valve 27 is switched to position A, and the supply of cooling oil into the brake case 11 is blocked.

As described above, in the fourth embodiment, when the free fall switch 41 is on and the pressure switch 43 is off and the temperature of the disk 13 exceeds the predetermined value Ts, the cooling oil is supplied into the brake case 11. Since the cooling oil is supplied, the cooling oil can be efficiently supplied and the control is easy. Even when the temperature is not equal to the free fall, the switching amount of the hydraulic pressure switching valve 27 is adjusted so that the minimum flow rate from the hydraulic pressure source 28 is supplied into the brake case 11 when the temperature detection value T is equal to or higher than the predetermined value Ts. May be.

-Fifth Embodiment- Referring to FIGS. 9 and 10, a fifth embodiment of the brake apparatus according to the present invention.
The embodiment will be described. In the first to fourth embodiments, the cooling oil is supplied to one brake device, but in the fifth embodiment, the cooling oil is supplied to each of the two brake devices. That is, the winch according to the fifth embodiment has the main winding winch drum 1A and the auxiliary winding winch drum 1B.
The main winding winch brake device 10A and the auxiliary winding winch brake device 10B are provided in 1B, respectively.

FIG. 9 is a hydraulic circuit diagram of a winch having a brake system according to the fifth embodiment. Note that FIG.
The same parts as those of the above are denoted by the same reference numerals, and the differences will be mainly described below. As shown in FIG. 8, the oil supply hole 11a of the main winding brake device 10A has a conduit 26A and an electromagnetic switching valve 3a.
6, connected to a hydraulic pressure source 38 via an electromagnetic switching valve 37, and the oil supply hole 11a of the auxiliary winding brake device 10B has a conduit 26B,
It is connected to a hydraulic pressure source 38 via an electromagnetic switching valve 36 and an electromagnetic switching valve 37.

The electromagnetic switching valve 36 is a three-position switching valve and is switched by a control signal from the controller 40. When the electromagnetic switching valve 36 is switched to the position a, the pressure oil that has passed through the electromagnetic switching valve 37 is guided to the pipeline 26A. When the electromagnetic switching valve 36 is switched to position B, the pressure oil that has passed through the electromagnetic switching valve 37 is guided to the pipe line 26B. When the electromagnetic switching valve 10A is switched to the neutral position, the electromagnetic switching valve 3
The pressure oil that has passed through 7 is equally distributed to the pipelines 26A and 26B. The electromagnetic switching valve 37 is switched by a control signal from the controller 40.

The electromagnetic switching valve 37 is switched by a control signal from the controller 40. When the electromagnetic switching valve 37 is switched to position A, the pressure oil from the hydraulic pressure source 38 is guided to the electromagnetic switching valve 36. When the electromagnetic switching valve 37 is switched to position B, the pressure oil from the hydraulic pressure source 38 is transferred to the electromagnetic switching valve 36.
It is returned to the tank without being guided to.

FIG. 10 is a flow chart showing an example of processing executed in the controller 40 according to the fifth embodiment. First, in step S31, the signals from the main-winding winch free fall switch 41A and the pressure switch 43A are read to determine whether the free fall switch 41A is on and the pressure switch A is off. This is a process of determining the free-fall operation of the main winding winch, and if step S31 is positive, step S32
Proceed to. In step S32, the signals from the auxiliary fall winch free fall switch 41B and the pressure switch 43B are read to determine whether the free fall switch 41B is on and the pressure switch 43B is off. This is the process of determining the fall operation, and if the result at step S32 is affirmative, the routine proceeds to step S33.

In step S33, the signals from the main-winding winch temperature sensor 42A and the auxiliary-winding winch temperature sensor 42B are read, and the detected value TA of the temperature sensor 42A is read.
Then, it is determined whether or not at least one of the detected values TB of the temperature sensor 42B is larger than a predetermined value TS that is set in advance.
Here, the predetermined value TS is a reference value for determining whether cooling of the disks 12 and 13 is necessary. If the result at step S33 is affirmative, the routine proceeds to step S34. If the result at step S33 is negative, that is, when the temperature detection values TA and TB are both below the predetermined value TS, the routine proceeds to step S39.

In step S34, it is determined whether or not the absolute value │TA-TB│ of the difference between the detected temperature values is larger than a predetermined value Ta. The predetermined value Ta in this case is the temperature difference | TA-
TB | is the allowable value, and the temperature difference | TA-TB | is the allowable value Ta.
If the following is determined, step S34 is denied and the process proceeds to step S35. In step S35, the electromagnetic switching valve 36
To output the control signal to the solenoid to switch the electromagnetic switching valve 36 to the neutral position, and to output the control signal to the solenoid of the electromagnetic switching valve 37 to switch the electromagnetic switching valve 37 to the position a. As a result, the pressure oil from the hydraulic pressure source 38
A and 26B are supplied respectively.

On the other hand, if it is determined that the temperature difference | TA-TB | exceeds the allowable value Ta, the affirmative decision is made in step S34 and the operation proceeds to step S36. In step S36, the detected temperature value T
The magnitudes of A and TB are determined, and if TA is greater than TB, step S36 is affirmed and the process proceeds to step S37. In step S37, a control signal is output to the solenoid of the solenoid operated directional control valve 36 to switch the solenoid operated directional control valve 36 to position A, and a control signal is output to the solenoid of the solenoid operated directional control valve 37 to switch the solenoid operated switching valve 37 to position A. As a result, the pressure oil from the hydraulic pressure source 38 is supplied to the pipeline 26A.

If the detected temperature value TA is less than TB, step S36 is denied and the routine proceeds to step S38. In step S38, a control signal is output to the solenoid of the electromagnetic switching valve 36 to switch the electromagnetic switching valve 36 to the position B, and
A control signal is output to the solenoid of the electromagnetic switching valve 37 to switch the electromagnetic switching valve 37 to position a. As a result, the hydraulic power source 3
The pressure oil from No. 8 is supplied to the pipe line 26B.

When step S31 is negative, that is, when at least the main-winding winch free fall switch 41A is off or the pressure switch 43A is on, step S4 is performed.
Go to 0. In step S40, similar to step S32,
It is determined whether the free fall switch 41B is on and the pressure switch 43B is off. Step S
If 40 is affirmed, the process proceeds to step S41, and if not, the process proceeds to step S39. In step S41, it is determined whether or not the detected value TB of the auxiliary winding winch temperature sensor 42B is larger than the above-described predetermined value TS. If the result is affirmative, the process proceeds to step S38, and if the result is negative, the process proceeds to step S39. In step S39, a control signal is output to the electromagnetic switching valve 36 to switch the electromagnetic switching valve 36 to the neutral position, and a control signal is output to the electromagnetic switching valve 37 to switch the electromagnetic switching valve to the position b. As a result, from the hydraulic power source 38 to the pipelines 26A, 2
The supply of pressure oil to 6B is blocked.

On the other hand, step S32 is negative, that is, at least the auxiliary winding winch free fall switch 41B.
Is off or the pressure switch 43B is on, the routine proceeds to step S42. In step S42, it is determined whether or not the detected value TA of the main winding winch temperature sensor 42A is larger than the predetermined value Ts described above. If the result is affirmative, the process proceeds to step S37, and if the result is negative, the process proceeds to step S39.

The operation of the fifth embodiment configured as above will be described. Free fall switch 41
When both A and 41B are off, the braking device 10A, 1
0B is actuated, and the operation of the operation lever 6 enables the winding or winding operation of the drums 1A and 1B. Even if the free fall switches 41A and 41B are turned on, the brake pedal 2 is turned on when the pressure switches 43A and 43B are turned on.
The brake devices 10A and 10B can be operated by the operation of 5, so that the winding or lowering work of the drums 1A and 1B becomes possible. In this state, the electromagnetic switching valve 36 is switched to the neutral position and the electromagnetic switching valve 37 is switched to the position b by the above-described processing (step S39). As a result, the supply of pressure oil from the hydraulic pressure source 38 to the pipelines 26A, 26B is blocked, and it is possible to prevent wasteful supply of cooling oil into the brake case 11.

Free fall switch 4 for main winding winch
When only 1A is on and the pressure switch 43A is off, the main winding winch brake device 10A is released, and the free fall of the suspended load by the main winding winch becomes possible. At this time, when the temperature TA of the disk 13 is higher than the predetermined value TS, the above-mentioned processing (step S42 → step S3)
By 7), the pressure oil from the hydraulic power source 38 is supplied into the brake case 11 of the main winding winch via the pipe 26A. As a result, the disks 12, 13 can be cooled when the rake device 10A is operated by operating the brake pedal 25 after free-falling the suspended load, and heat generation of the disks 12, 13 can be suppressed. On the other hand, when the temperature TA of the disk 13 is equal to or lower than the predetermined value TS, the supply of the pressure oil from the hydraulic power source 38 into the pipe line 26A is blocked by the above-described processing (step S42 → step S39).
As a result, it is possible to prevent the cooling oil from being unnecessarily supplied into the brake case 11, which contributes to the improvement of fuel consumption.

Free fall switch 4 for auxiliary winding winch
When only 1B is on and the pressure switch 43B is off, the brake device 10B for the auxiliary winding winch is released, and the free fall of the suspended load by the auxiliary winding winch becomes possible. At this time, when the temperature TB of the brake disc is equal to or higher than the predetermined value TS, the above-described processing (step S41 → step S41)
38), the pressure oil from the hydraulic power source 38 is supplied into the brake case 11 of the auxiliary winding winch via the pipe line 26B.
As a result, the disks 12, 13 can be cooled when the brake device 10B is operated by operating the brake pedal 25 after free-falling the suspended load, and the heat generation of the disks 12, 13 can be suppressed. On the other hand, when the temperature TB of the disk 13 is below the predetermined value TS,
By the above-described processing (step S41 → step S39), the supply of pressure oil from the hydraulic power source 38 into the pipe line 26B is blocked. As a result, it is possible to prevent the cooling oil from being unnecessarily supplied into the brake case 11, which contributes to the improvement of fuel consumption.

When both the free-fall switches 41A and 41B are on and the pressure switches 43A and 43B are both off, the main-winding winch and the auxiliary-winding winch can simultaneously free-fall. At this time, the temperature detection value T
At least one of A and TB is larger than a predetermined value TS, and
When the difference between the detected temperature values | TA-TB | is less than or equal to the predetermined value Ta,
By the above-described processing (step S35), the pressure oil from the hydraulic pressure source 28 is equally distributed to the respective brake cases 11 via the pipelines 26A and 26B. As a result, it is possible to cool the disks 12 and 13 for the main winding winch and the auxiliary winding winch with the pressure oil from one hydraulic power source 38, respectively.

The difference between the detected temperatures │TA-TB│ is the predetermined value Ta.
In the above case, the pressure oil from the hydraulic pressure source 38 is supplied into the brake case 11 of the winch on the higher temperature side by the above-described processing (step S37 or step S38). In this case, the amount of cooling oil supplied to the case 11 is larger than that of the case where cooling oil is supplied to both the main winding winch and the auxiliary winding winch. Can be cooled rapidly and the temperature difference | TA-TB | can be reduced. When the temperature difference | TA-TB | becomes less than or equal to the predetermined value Ta,
Through the above-described process (step S35), the cooling oil from the hydraulic power source 38 is supplied into the brake cases 11 of the main winding winch and the auxiliary winding winch, respectively. On the other hand, when both the temperature detection values TA and TB are less than or equal to the predetermined value Ts, the supply of the cooling oil from the hydraulic pressure source 38 is blocked by the above-described processing (step S39). As a result, the power consumption of the hydraulic power source 38 can be reduced.

As described above, according to the fifth embodiment, the temperatures of the disks 13 of the main-winding winch brake device 10A and the auxiliary-winding winch brake device 10B are respectively detected, and an electromagnetic wave is detected according to the detected values TA and TB. Switching valve 36, 37
Is switched to control the flow of pressure oil from the hydraulic pressure source 38. That is, when the temperature detection value difference | TA-TB | is less than or equal to the predetermined value Ta, cooling oil is supplied into the brake case 11 of the main winding winch and the auxiliary winding winch respectively, and the temperature detection value difference | TA-TB | Is larger than the predetermined value Ta, the cooling oil is supplied only into the brake case 11 of the winch on the high temperature side. Thereby, the cooling oil from the single hydraulic power source 38 can be efficiently distributed to the brake cases 11 of the plurality of winches. In this case, the cooling oil is supplied on condition that the free fall switches 41A and 41B are on, the pressure switches 43A and 43B are off, and the temperature detection values TA and TB are larger than the predetermined value Ts. It is possible to prevent wasteful supply of fuel and improve fuel efficiency.

In the fifth embodiment, the cooling oil is equally distributed in the brake cases 11 of the main winch and the auxiliary winch, but one brake case 11 is used.
The distribution ratio may be changed so that more cooling oil is supplied therein. Further, the predetermined value Ts to be compared with the temperature detection values TA and TB may be set separately for the main winding winch and the auxiliary winding winch. The electromagnetic switching valve 36 or the electromagnetic switching valve 37 may be configured as an electromagnetic proportional valve, and the amount of cooling oil supplied into the pipelines 26A, 26B may be changed according to the temperature detection values TA, TB. In this case, the higher the temperature detection values TA and TB are, or the larger the temperature detection value difference | TA-TB | is, the larger the flow rate may be made to flow. Further, the hydraulic power source 38 may be configured by a variable pump, and the pump capacity may be changed according to the temperature detection value. The electromagnetic switching valve 36 may be changed to a hydraulic switching valve, an electromagnetic switching valve may be provided in the pilot line, and the hydraulic switching valve may be switched by switching control of the electromagnetic switching valve.

Although one winch has been described in the first to fourth embodiments, a plurality of winches are provided as in the fifth embodiment, and depending on the disk temperature T or the heat generation amount H of each winch. Alternatively, the cooling oil from the hydraulic power source 28 and the hydraulic pump 32 may be distributed.

Although the temperature of the disk 13 is detected in the first, fourth and fifth embodiments, the return temperature of the cooling oil flowing out from the brake case 11 may be detected. Good. This allows the disks 12, 13
Can detect the average temperature of the disk 12,
Even if there is a temperature difference between 13, the disc 12,
13 can be cooled. Further, fine control is possible by controlling the fluctuation of the oil temperature.

As described above, the brake device according to this embodiment functions as a brake device for stopping the rotation of the drum 1 at the time of free fall, and the hydraulic motor 2
It also functions as a clutch device that transmits / non-transmits the rotation of the above to the winch drum 1.

The above-described embodiment is applied to the wet multi-plate brake device, but if it is of a type that supplies the cooling oil to the contact surfaces of the disks 12 and 13, for example, the inner disk 12 is a single plate type. The same applies to disc brakes. For one inner disc 12,
The outer disc 13 and the brake piston 14 may be integrated. Further, in the above embodiment, the planetary reduction mechanism 5 is used.
Although the brake device and the clutch device are both used by using, the invention can be similarly applied to a brake-dedicated device or a clutch-dedicated device that does not have the planetary speed reduction mechanism 5.

In the correspondence between the above embodiment and the claims, the inner disk 12 and the outer 13 serve as a braking member, the temperature sensor 42, the drum rotation speed sensor 44 and the pressure sensor 4.
5 is heat generation detecting means, and freefall switch 41 and pressure switch 43 are freefall detecting means.
The hydraulic pressure switching valve 27 and the electromagnetic proportional valve 29, the tilt cylinder 33 and the electromagnetic switching valve 34, the hydraulic pressure switching valve 27 and the electromagnetic switching valves 35, and the electromagnetic switching valves 36 and 37 respectively serve as cooling oil supply means, and the controller 40 and the delay relay 47. Is the cooling oil control means, the free fall switch 41 is the drum command means,
The operation lever 6 constitutes a drum command means, the temperature sensor 42 constitutes a temperature detection means, the pressure sensor 45 constitutes a pressure detection means, and the drum rotation speed sensor 44 constitutes a rotation speed detection means.

[0074]

As described above in detail, according to the invention of claim 1, when the free fall operation is detected, the amount of cooling oil supplied to the braking member is increased, and when the free fall stop is detected. The amount of cooling oil was reduced. Also. According to the inventions of claims 2 and 3, when the free fall operation is detected, the amount of cooling oil supplied to the braking member is controlled according to the heat generation state of the braking member, and is supplied during the free fall operation other than the free fall operation. The amount of cooling oil is set to be smaller than the amount of cooling oil that is generated. As a result, the disk can be cooled efficiently and appropriately.

[Brief description of drawings]

FIG. 1 is a hydraulic circuit diagram of a winch having a brake device according to a first embodiment of the present invention.

FIG. 2 is a diagram showing a structure of a main part inside a brake case which constitutes the brake device according to the first embodiment of the present invention.

FIG. 3 is a flowchart showing an example of processing by the controller according to the first embodiment of the present invention.

FIG. 4 is a hydraulic circuit diagram of a winch having a brake device according to a second embodiment of the present invention.

FIG. 5 is a flowchart showing an example of processing in a controller according to the second embodiment of the present invention.

FIG. 6 is a hydraulic circuit diagram of a winch having a brake device according to a third embodiment of the present invention.

FIG. 7 is a hydraulic circuit diagram of a winch having a brake device according to a fourth embodiment of the present invention.

FIG. 8 is a flowchart showing an example of processing by the controller according to the fourth embodiment of the present invention.

FIG. 9 is a hydraulic circuit diagram of a winch having a brake device according to a fifth embodiment of the present invention.

FIG. 10 is a flowchart showing an example of processing by the controller according to the fifth embodiment of the present invention.

FIG. 11 is a side view of a crane to which the present invention is applied.

[Explanation of symbols]

6 Operation Lever 12 Inner Disc 13 Outer Disc 14 Brake Piston 27 Hydraulic Switching Valve 28 Hydraulic Source 29 Electromagnetic Proportional Valve 32 Hydraulic Pump 33 Tilt Cylinder 36, 37 Electromagnetic Switching Valve 40 Controller 41 Freefall Switch 42 Temperature Sensor 43 Pressure Switch 44 Drum Rotation speed sensor 45 Pressure sensor 47 Delay relay

Claims (11)

[Claims] 1. A winch drum driven by power to wind up and down, freefalling by a load of a suspended load, a braking member for braking rotation of the winch drum, and a freefall detecting a freefalling motion of the winch drum. Fall detection means, cooling oil supply means for supplying cooling oil from the hydraulic pressure source to the braking member, and increasing the amount of cooling oil supplied to the braking member when the free fall operation is detected by the free fall detection means. A cooling oil control means for controlling the cooling oil supply means so as to reduce the amount of cooling oil supplied to the braking member when the free fall detection means detects a free fall stop. Winch braking system. 2. A winch drum which is driven by power to wind up and down and freefalls by a load of a suspended load, a braking member which brakes rotation of the winch drum, and a heat generation detection which detects a heat generation state of the braking member. Means, a free fall detecting means for detecting a free fall operation of the winch drum, a cooling oil supplying means for supplying a cooling oil from a hydraulic pressure source to the braking member, and a free fall operation is detected by the free fall detecting means. And the amount of cooling oil supplied to the braking member is controlled according to the heat generation state detected by the heat generation detecting means, and at least the free fall operation is detected for the amount of cooling oil supplied to the braking member except for the free fall operation. Cooling oil control means for reducing the amount of cooling oil supplied at times. Inch of the brake system. 3. A plurality of winch drums, which are driven by power to wind up and down and free fall by a load of a suspended load, and a plurality of winch drums provided corresponding to the plurality of winch drums, respectively, for braking rotation of the winch drums. Braking member, heat generation detecting means for detecting heat generation states of the plurality of braking members, free fall detecting means for detecting free fall operation of the plurality of winch drums, and hydraulic pressure source to the plurality of braking members. When the free-fall operation of the plurality of winch drums is detected by the cooling-oil supply means that distributes and supplies the cooling oil respectively, and the free-fall detection means detects the free-fall operation of the winch drum, The amount of cooling oil distributed from the hydraulic power source to the plurality of braking members is controlled to control the plurality of wins. Cooling oil control means for reducing the amount of cooling oil supplied to the braking member corresponding to the winch drum at least when the at least one of the drums is not in the free fall operation, at least below the amount of cooling oil supplied when the free fall operation is detected. A winch brake device comprising: 4. The winch braking device according to claim 1, wherein a freefall command means for commanding a freefall operation and a drum command for commanding hoisting or lowering drive of the winch drum. Means for detecting a free fall operation based on commands from the free fall commanding means and the drum commanding means. 5. The winch brake device according to claim 2, wherein the heat generation state detection means has a temperature detection means for detecting the temperature of the braking member, and the detected temperature A winch brake device characterized by detecting a heat generation state in accordance with the above. 6. The winch brake device according to claim 2, wherein the heat generation state detection means has an oil temperature detection means for detecting a temperature of the cooling oil, and the detected cooling oil is included. A winch brake device characterized by detecting a heat generation state according to temperature. 7. The winch brake device according to any one of claims 2 to 4, wherein the heat generation state detection means detects a release pressure for releasing braking by the braking member, and the winch. A winch brake device, comprising: a rotation speed detecting means for detecting a rotation speed of a drum, and detecting a heat generation state according to the detected cooling oil pressure and the drum rotation speed. 8. The winch drum according to claim 1, a braking member, a free fall detection means, a cooling oil supply means, and a cooling oil control means, and the power is supplied to the winch drum via the braking member. A winch clutch device characterized in that transmission / non-transmission is performed. 9. A winch drum according to any one of claims 2 to 7, a braking member, a heat generation detection means, a free fall detection means, a cooling oil supply means, and a cooling oil control means. A winch clutch device, wherein power is transmitted / not transmitted to the winch drum via the braking member. 10. A crane provided with the brake device according to claim 1. 11. A crane provided with the clutch device according to claim 8.