JP2003002587A - Braking device for winch, clutch device therefor, and hoist gear for crane provided with the braking device and the clutch device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a prescribed braking characteristic irrespective of a manufacturing tolerance. SOLUTION: In a wet type multiple disk brake device provided alternately with inner disks 12 and outer disks 13, a brake disk 14 press-moved by a hydraulic cylinder 20 is provided on the side of the disks 12, 13. A plate-like spring 5 is connected to the brake disk 14, and one end of the spring 15 is fixed to a push plate 16. The push plate 16 is movable by screwing a bolt 17 in, and an initial contraction amount of the spring 15 is changed to thereby obtain the prescribed braking characteristic.

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 permitting and prohibiting the rotation of a winch drum, a clutch device, and a hoisting device for a crane including the brake device and the clutch device.

[0002]

2. Description of the Related Art A wet multi-plate brake device is known as a brake device of this type (for example, Japanese Patent Laid-Open No. 9-21).
6793). In the device described in this publication, an inner plate spline-coupled to the rotary shaft so as to be movable in the axial direction and an outer plate spline-coupled to the brake case so as to be movable in the axial direction are pressed against each other by a pressing force of a brake cylinder and a spring, As a result, the rotation of the rotary shaft is blocked and a braking force is generated. In this case, the pressing force from the brake cylinder changes according to the amount of depression of the brake pedal.

[0003]

In the above-mentioned device, the spring is incorporated in the brake case, and the braking characteristic, that is, the relationship between the braking force and the depression amount of the brake pedal is determined according to the initial length of the spring. . However, since there are manufacturing tolerances in the dimensions of the spring and the brake case, if the spring is incorporated without taking this into consideration, an error may occur in the initial length of the spring, and it may not be possible to obtain a predetermined braking characteristic.

An object of the present invention is to provide a winch brake device, a clutch device, and a hoisting device for a crane equipped with the clutch device, which can obtain predetermined characteristics regardless of manufacturing tolerances of springs and brake cases. To provide.

[0005]

(1) A brake system for a winch according to a first aspect of the present invention comprises a winch drum, a brake member for braking rotation of the winch drum, and a braking force applied to the winch drum by driving the brake member. The above-described object is achieved by providing a driving device that exerts a spring force, a spring member that applies a spring force to the brake member to increase or decrease the braking force by the driving device, and an adjusting unit that adjustably fixes the position of one end of the spring member. To do. (2) A winch brake device according to a second aspect of the present invention includes a hydraulic power source, a winch drum, a brake member that brakes the rotation of the winch drum, and a brake cylinder that drives the brake member to exert a braking force on the winch drum. ,
A control device for controlling the hydraulic pressure from the hydraulic source to the brake cylinder, a spring member for exerting a spring force on the brake member to increase or decrease the braking force by the brake cylinder, and an adjusting means for fixing the position of one end of the spring member so as to be adjustable. The above-described object is achieved by including (3) A brake system for a winch according to a third aspect of the present invention provides a hydraulic power source, a winch drum, a rotating body that rotates in correlation with the winch drum, a case member that houses the rotating body, and an outer periphery of the rotating body. A plurality of first friction plates axially movably engaged with the surface, and axially movably engaged with the inner peripheral surface of the case member, and alternating with the first friction plates axially. A plurality of second friction plates, and a brake member that axially pushes the first friction plate and the second friction plate to press the first friction plate and the second friction plate into pressure contact with each other. , A brake cylinder that drives a brake member to apply a braking force to a winch drum, a control device that controls hydraulic pressure from a hydraulic source to the brake cylinder, and a spring force to the brake member to increase or decrease the braking force by the brake cylinder. Spring member and one end of the spring member To achieve the object described above by providing an adjustment means for adjustably fixing the position. (4) A winch clutch device according to a fourth aspect of the present invention includes the brake device according to any one of the first to third aspects, and is configured to transmit / non-transmit power through the brake device. By doing so, the above-mentioned object is achieved. (5) A hoisting device for a crane according to a fifth aspect of the invention achieves the above-mentioned object by including the brake device according to any one of the first to third aspects. (6) The crane hoisting device according to the invention of claim 6 achieves the above-mentioned object by including the clutch device of claim 4.

[0006]

BEST MODE FOR CARRYING OUT THE INVENTION First Embodiment Hereinafter, a first embodiment of a winch brake device according to the present invention will be described with reference to FIGS. 1 to 3 and 9. FIG. 1 is a hydraulic circuit diagram of a winch having a brake device according to a first embodiment of the present invention, and FIG.
Sectional view of a brake case that constitutes this brake device,
FIG. 9 is a side view of a crane in which the brake device is used. As shown in FIG. 9, the mobile crane includes a traveling body 1
01, a revolving revolving structure 102 mounted on the traveling structure 101, and a boom 103 supported by the revolving structure 102 so as to be capable of hoisting. Then, the wire rope 104 is hoisted or unwound by driving the winch drum 1 mounted on the revolving structure 102, and the hanging load 106 is hoisted by the hook 105 connected to the wire rope 104. Further, by driving the hoisting drum 107, the hoisting rope 108 is hoisted or lowered, and the boom 103 is hoisted.

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, and a planetary speed reduction mechanism 5 for transmitting or not transmitting the driving force of the hydraulic motor 2 to the winch drum 1.
A wet multi-plate brake device 10 that controls the drive of the winch drum 1 is provided.

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. As shown in FIG. 2, a plurality of inner disks 12 are engaged with the carrier shaft 54 by spline coupling so as to be movable in the axial direction, and the inner disks 12 are rotatable integrally with the carrier shaft 54. A plurality of outer discs 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, and the outer discs 13 and the inner discs 12 are alternately arranged in the axial direction.

A brake disc 14 is slidable on the inner peripheral surface of the brake case 11 on the side of the discs 12 and 13.
, And a push plate 16 is disposed laterally of the brake disc 14 via a disc-shaped spring 15 so as to be movable in the axial direction. The disc-shaped spring 15 has a groove portion 14 a formed on the end surface of the brake disc 14 and the outer peripheral surface 1 at the tip of the push plate 16.
It is positioned by 6a. The side plate 11a of the brake case 11 has a screw hole 11b penetrating therethrough, and the screw hole 11b
A bolt 17 is screwed into the. The tip of the bolt 17 contacts the push plate 16 and regulates the position of the push plate 16. A loosening prevention nut 18 is screwed onto the bolt 17.

As shown in FIG. 1, the brake case 11 is provided with a hydraulic cylinder 20, and the piston 20p of the cylinder 20 is connected to the brake disc 14. As a result, when pressure oil acts on the bottom chamber 20a of the hydraulic cylinder 20, the brake disc 14 is pushed in the direction a in the figure, and the inner disc 12 and the outer disc 13 are pressed against each other. When pressure oil acts on the rod chamber 20b of the hydraulic cylinder 20, the brake disc 14 is pushed in the direction of b in the figure against the spring force, and the pressure of the discs 12 and 13 is released. In FIG. 2, oil chambers 20a and 20b of the cylinder 20 are provided on both sides of the brake disc 14, respectively.
The brake disc 14 also serves as the piston 20p.
The disc 1 is placed on the phase (not shown) of the brake case 11.
An oil supply hole and an oil discharge hole communicating with the storage chambers 11c of 2 and 13 are provided, and oil flows through the case 11 through the oil supply hole and the oil discharge hole to cool the disks 12 and 13.

The rod chamber 20b of the cylinder 20 has a conduit 2
It is connected to the hydraulic power source 6 via 1. The bottom chamber 20 a of the cylinder 20 is connected to the hydraulic pressure source 6 via a pipe line 22, a high pressure selection valve 23, a pressure reducing valve 24 or an electromagnetic switching valve 25. Assuming that the primary pressure from the hydraulic pressure source 6 is P1 and the secondary pressure after passing through the pressure reducing valve is P2, the degree of pressure reduction of the pressure reducing valve 24 (P1-P
2) / P1 is maximum (2 when the brake pedal 26 is not operated.
The secondary pressure P2 is the minimum) and decreases as the depression amount of the brake pedal 26 increases (the secondary pressure P2 increases). The electromagnetic switching valve 25 is switched by operating a free fall switch 25a that commands a free fall.

The operation of this embodiment configured as described above will be described. (1) Free fall switch off When the free switch 25a is off, as shown in FIG. 1, the electromagnetic switching valve 25 is switched to the position a and the hydraulic power source 6
The pressure oil from the electromagnetic switching valve 25, the high pressure selection valve 23, the pipeline 2
The pressure oil from the hydraulic pressure source 6 is supplied to the bottom chamber 20a of the cylinder 20 via 2 as well as to the rod chamber 20b via the conduit 21. This makes the piston 20p
The hydraulic pressure acting on the
Is pushed in the direction a in the figure by the urging force of the disc-shaped spring 15. 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 disc 12 is blocked (brake operation).

When the brake device operates in this manner, the rotation of the carrier shaft 54 is blocked, and the rotation of 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. Here, when a control lever (not shown) is hoisted or hoisted to apply pilot pressure oil to the pilot port of the direction switching valve 4, the direction switching valve 4 is switched from the neutral position, and the hydraulic motor 2 is hoisted. Or rotate in the unwinding 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. The winch drum 1 is stopped by a brake device (not shown) provided separately from the wet multi-plate brake device 10.

(2) When the free fall switch-on operation lever is operated to the neutral position to switch the directional control valve 4 to the neutral position, the supply of pressure oil to the hydraulic motor 2 is cut off and the rotation of the hydraulic motor 2 is stopped. To do. When the free fall switch 25a is turned on in this state, the electromagnetic switching valve 25 is switched to position b, and the bottom chamber 20a of the cylinder 20 communicates with the tank. Thereby, the rod chamber 20
The hydraulic pressure acting on b overcomes the urging force of the disc-shaped spring 15, and the brake disc 14 moves in the b direction in the figure.
As a result, the pressure contact force acting on the disks 12 and 13 is removed, and the inner disk 12 becomes rotatable away from the outer disk 13 (brake release).

When the brake device is released in this way, the carrier shaft 54 is allowed to rotate, and the winch drum 1 is brought into a free rotation state by the load of the suspended load, and the suspended load can be free fall. When the brake pedal 26 is depressed in this state, the secondary pressure P2 after passing through the pressure reducing valve increases as the pedal stroke amount increases, and this secondary pressure P2 acts on the bottom chamber 20a of the cylinder 20. As a result, as shown by the characteristic A in FIG. 3, the pressing force on the brake disc 14 increases as the pedal stroke amount increases. When the pressing force becomes larger than the hydraulic pressure in the rod chamber 20b, the brake disc 14 is pushed in the a direction, and the discs 12 and 13 are pressed against each other.
As a result, the brake device operates and the winch drum 1 can be stopped. In the characteristic A of FIG. 3, the braking force can be finely adjusted in a region where the pedal stroke amount is small, and the slope of the brake characteristic is changed from the middle so that the brake is surely applied when the pedal stroke amount is a predetermined amount or more. Making it big.

(3) Adjustment of Brake Force When the initial length of the disc-shaped spring 15 is set to deviate from an appropriate value, the brake force characteristics are, for example, the characteristics B1 and B2 shown in FIG.
Shift as shown in. As a result, the brake pedal 2
An appropriate braking force cannot be obtained for the depression amount of 6. That is, for example, the pedal stroke amount S1
B of the characteristic A in FIG. 4 and the brake force FB1 of the characteristic B1 or the characteristic A in the pedal stroke amount S2
The braking force FA2 of the characteristic B2 and the braking force FB2 of the characteristic B2 differ greatly with respect to the predetermined pedal stroke amounts S1, S2. As a result, an appropriate braking force cannot be obtained with respect to the pedal stroke, resulting in poor usability. Therefore, the initial length of the spring 15 is adjusted as follows.

In adjusting the initial length of the spring 15,
When assembling the brake system, check the braking force against the pedal stroke amount. If the value checked at this time is different from the proper value, loosen the nut 18 and tighten the bolt 17
Change the screwing amount of. As a result, the position of the push plate 16 is moved, and the initial length of the disc-shaped spring 15 is changed. The brake force is checked against the pedal stroke amount not only at the time of assembly but also periodically.
The initial length of may be adjusted. This allows
Even if the braking force characteristic changes due to some cause (for example, wear of the disks 12 and 13), it can be easily dealt with.

As described above, according to the first embodiment, the spring 15 for pushing the brake disc 14 is supported from the push plate 16, and the position of the push plate 16 is adjusted by screwing the bolt 17. The initial length of the spring 15 can be set to an appropriate value. As a result, proper braking characteristics can be obtained regardless of manufacturing tolerances and the like.
In addition, since the wet multi-plate type brake device is used as the braking device, the contact area between the disks 12 and 13 is increased, and since the disks 12 and 13 are cooled by oil, the friction coefficient is increased and a large braking force is obtained. You can

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

-Second Embodiment- A second embodiment of the present invention will be described with reference to FIGS. In the first embodiment, the brake pedal 26 is depressed to apply the hydraulic pressure to the cylinder 20 to generate the braking force. However, in the second embodiment, the brake pedal 26 is depressed to release the hydraulic pressure. To generate braking force. FIG. 4 is a hydraulic circuit diagram of a winch having a brake device according to the second embodiment, and FIG. 5 is a cross-sectional view of a brake case 11 that constitutes this brake device. The same parts as those in FIGS. 1 and 2 are designated by the same reference numerals, and the differences will be mainly described below.

As shown in FIG. 5, in the second embodiment, a screw 31a is provided on the outer peripheral surface of the push plate 31.
The side plate 11a of the brake case 11 is provided with a screw hole 11c corresponding to the screw 31a.
It is screwed to a. Accordingly, if the screwing amount of the push plate 31 is adjusted, the position of the disc-shaped spring 15 is moved, and the initial length of the spring 15 is changed. As shown in FIG. 4, the rod chamber 30 a of the hydraulic cylinder 30 includes a conduit 21 and a pressure reducing valve 32.
It is connected to the hydraulic power source 6 via. Note that the illustration of the free fall switch 25a and the like is omitted in FIG.

FIG. 6 is a diagram showing the valve characteristics of the pressure reducing valve 32. As shown in FIG. 6, the secondary pressure P2 after passing through the pressure reducing valve is maximum when the pedal is not operated, and decreases as the pedal stroke amount increases. As a result, the maximum pressure acts on the rod chamber 30a of the cylinder 30 when the pedal is not operated, the brake disc 14 is pushed in the direction b against the spring force, and the brake device is released. When the brake pedal 26 is depressed, the rod chamber 3 increases as the pedal stroke increases.
The hydraulic pressure acting on 0a decreases and the brake disc 14
Is pushed in the direction a by the spring force, and the brake device is activated.

As described above, in the second embodiment, the push plate 3
Since the screw 31a is provided on the screw 1 to adjust the screwing amount of the pressing plate 31 itself, it is not necessary to separately provide the bolt 17 and the like, and the number of parts is reduced. Further, since the hydraulic pressure acting on the rod chamber 30a is released by the depression of the brake pedal 26 to operate the brake device, the brake device can be operated even when the pipeline 21 is damaged. it can.

-Third Embodiment- A third embodiment of the present invention will be described with reference to FIGS. In the first embodiment, the bolt 17 is screwed into the brake case 11 to adjust the position of the push plate 16, but in the third embodiment, hydraulic pressure is exerted on the push plate 16 to adjust the position of the push plate 16. Adjust the position. FIG. 7 is a hydraulic circuit diagram of a winch having a brake device according to the third embodiment, and FIG. 8 is a sectional view of a brake case 11 which constitutes the brake device. The same parts as those in FIGS. 1 and 2 are designated by the same reference numerals, and the differences will be mainly described below.

As shown in FIG. 7, a rod chamber 40a and a bottom chamber 40b are formed on both sides of the disc-shaped spring 15 in the hydraulic cylinder 40, respectively. The rod chamber 40a is connected to the hydraulic pressure source 6 via the pipe line 21 and the pressure reducing valve 41, and the bottom chamber 40b is connected to the hydraulic pressure source 6 via the pipe line 27 and the pressure reducing valve 42. In FIG. 8, the rod chamber 40a is formed between the brake disc 14 and the brake case 11, and the bottom chamber 40b is formed between the brake case 11 and the push plate 16. The structure of the pressure reducing valve 41 is the same as that of the pressure reducing valve 32 in FIG. 4, and the secondary pressure after passing through the pressure reducing valve decreases as the pedal stroke amount increases. The pressure reducing valve 42 is a variable pressure reducing valve, and the degree of pressure reduction is changed by adjusting the set spring force of the spring 42a.

In this structure, the bottom chamber 40b of the cylinder 40 is constantly acted on by the hydraulic pressure according to the degree of pressure reduction of the pressure reducing valve 42. As a result, the push plate 16 is pushed, and the position of the disc-shaped spring 15 is regulated. Here, when the characteristic of the braking force with respect to the pedal stroke deviates from an appropriate value, the set spring force of the spring 42a is adjusted. As a result, the pressure in the bottom chamber 40b changes, and an appropriate braking force can be obtained.

In the third embodiment, since the push plate 16 is moved by the hydraulic pressure from the pressure reducing valve 42, it is not necessary to provide the brake case 11 with the bolt 17 for moving the push plate. As a result, the pressure reducing valve 4 is placed at a position where workability is good.
The provision of 2 facilitates adjustment of the initial length of the dish-shaped spring 15.

In the above embodiment, the dish-shaped spring 1 is used.
Although 5 is used, a coiled spring may be used. Further, although the above-described embodiment is applied to the wet multi-plate type brake device, the brake disc 14 is provided by the hydraulic cylinder.
It can be similarly applied to a device other than the wet multi-plate type brake device (for example, a drum brake) as long as it drives the. Further, the invention can be similarly applied to a device that transmits the operation of the brake pedal 26 to the brake disc 14 via a wire or the like without using the hydraulic cylinders 20, 30, 40. Furthermore, in the above-described embodiment, the braking force is generated according to the depression operation of the brake pedal 26, but an operating member other than the brake pedal may be operated to generate the braking force.

In the correspondence between the above embodiment and the claims, the brake disc 14 serves as a brake member, the hydraulic cylinders 20, 30, 40, the brake pedal 26, and the pressure reducing valve 2.
4, 32, 41 and the like are drive devices, the dish-shaped spring 15 is a spring member, the pressing plates 16, 31, the bolt 17 and the variable pressure reducing valve 42.
Adjusts the brake pedal 26 and the pressure reducing valves 24, 32,
41 and the like are control devices, the carrier shaft 54 is a rotating body, the brake case 11 is a case member, and the inner disc 12
Constitutes a first friction plate, and the outer disk 13 constitutes a second friction plate.

[0030]

As described in detail above, the present invention can be applied to any one of claims 1 to 3.
According to the invention, since the brake member is provided with the spring member for increasing and decreasing the braking force and the position of one end of the spring member is adjustably fixed, the initial contraction amount of the spring is adjusted. Therefore, it is possible to obtain a predetermined braking characteristic regardless of manufacturing tolerances of the spring and the brake case. Further, according to the invention of claim 4, since the brake device is used as the clutch device, the free fall work or the like can be favorably performed.

[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 cross-sectional view of a brake case that constitutes the brake device according to the first embodiment of the present invention.

FIG. 3 is a diagram showing one characteristic of the brake device 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 sectional view of a brake case that constitutes a brake device according to a second embodiment of the present invention.

FIG. 6 is a diagram showing one characteristic of a brake device according to a second embodiment of the present invention.

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

FIG. 8 is a sectional view of a brake case that constitutes a brake device according to a third embodiment of the present invention.

FIG. 9 is a side view of a crane to which the present invention is applied.

[Explanation of symbols]

1 Winch Drum 2 Hydraulic Motor 6 Hydraulic Source 10 Wet Multi-plate Brake Device 11 Brake Case 12 Inner Disc 13 Outer Disc 14 Brake Disc 15 Disc Spring 16,31 Push Plate 17 Bolt 20,30,40 Hydraulic Cylinder 24,32, 41 pressure reducing valve 15 electromagnetic switching valve 26 brake pedal 42 variable pressure reducing valve

─────────────────────────────────────────────────── ─── Continuation of front page (51) Int.Cl. ⁷ Identification code FI theme code (reference) F16D 65/18 F16D 65/18 Z F16H 57/10 F16H 57/10 F term (reference) 3J058 AA44 AA48 AA53 AA58 AA70 AA73 AA77 AA83 AA88 BA61 CC03 CC07 CC72 CC78 FA11 3J063 AA16 AB12 AB62 BA01 BB21 BB48 CA10 CB02 CC33 CD14 CD16 CD24 CD33 CD34

Claims (6)

[Claims] 1. A winch drum, a brake member for braking rotation of the winch drum, a drive device for driving the brake member to exert a braking force on the winch drum, and a spring force for exerting a spring force on the brake member. A winch brake device comprising: a spring member that increases or decreases a braking force by a drive device; and an adjusting unit that adjustably fixes a position of one end of the spring member. 2. A hydraulic pressure source, a winch drum, a brake member for braking the rotation of the winch drum, a brake cylinder for driving the brake member to exert a braking force on the winch drum, and the brake from the hydraulic pressure source. A control device for controlling hydraulic pressure to the cylinder; a spring member for exerting a spring force on the brake member to increase or decrease the braking force by the brake cylinder; and an adjusting means for fixing the position of one end of the spring member so as to be adjustable. A winch brake device comprising: 3. A hydraulic power source, a winch drum, a rotating body that rotates in correlation with the winch drum, a case member that houses the rotating body, and an axially movable outer peripheral surface of the rotating body. A plurality of first friction plates engaged with the plurality of first friction plates, and a plurality of first friction plates axially movably engaged with the inner peripheral surface of the case member, and arranged alternately in the axial direction with the first friction plates. A second friction plate, a brake member that axially pushes the first friction plate and the second friction plate, and presses the first friction plate and the second friction plate into pressure contact with each other; A brake cylinder that drives a member to exert a braking force on the winch drum, a control device that controls hydraulic pressure from the hydraulic pressure source to the brake cylinder, and a braking force by the brake cylinder that exerts a spring force on the brake member. Spring member to increase or decrease And a brake device for a winch, comprising: an adjusting unit that adjustably fixes the position of one end of the spring member. 4. A winch clutch device comprising the brake device according to any one of claims 1 to 3, wherein power is transmitted / non-transmitted via the brake device. 5. A hoisting device for a crane, comprising the brake device according to claim 1. 6. A hoisting device for a crane, comprising the clutch device according to claim 4.