JP2002323072A - Multiplate brake device, multiplate clutch device, and hoist gear of crane equipped with the brake and the clutch devices - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a multiplate brake device having multiplate discs in which multiplate discs are sufficiently separated from each other when releasing a break. SOLUTION: Ring-shaped hydrostatic grooves 40 and through holes 40a passing through the hydrostatic grooves 40 are respectively provided on the surfaces on an inner disc 12 engaged with a carrier shaft 54 in such a way as to be movable in the axial direction and an outer disc 13 engaged with brake case 11 in such a way as to be movable in the axial direction. At free fall, pressure oil is led in the inside 28 of the brake case 11 through an oil filler port 29. While shrinking a cylinder 15, the pressure oil is led in the hydrostatic grooves 40 on the surface of the disc through an oil filler port 27. By so doing, the pressure which separates the discs 12 and 13 from each other in the axial direction is activated on the surfaces of the discs 12 and 13.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a multi-layer disc in which a multi-plate disc provided on a rotating body and a multi-plate disc provided on a fixed body are pressed against or separated from each other to inhibit or allow rotation of the rotating body. The present invention relates to a plate type brake device, a multi-plate type clutch device, and a hoisting device of a crane provided with the brake device and the clutch device.

[0002]

2. Description of the Related Art A multi-plate type brake apparatus of this type is disclosed in, for example, Japanese Patent Application Laid-Open No. H11-130381. According to this, the multi-plate disc supported by the rotating body and the multi-plate disc supported by the fixed body are alternately arranged, and the hydraulic brake cylinder is arranged beside the multi-plate disc to extend the brake cylinder. The multi-disc disc is pushed by the operation. As a result, the multiple discs are pressed against each other, the rotation of the rotating body is prohibited, and the brake device is operated. Further, the pressure contact force from the cylinder is removed by the contraction of the brake cylinder, the rotation of the rotating body is permitted, and the brake device is released. Further, cooling oil is supplied to the multi-plate disc to prevent the multi-plate disc from becoming high temperature due to frictional heat.

[0003]

However, the above-mentioned conventional multi-disc brake system has the following problems. (A) When the brake device is released, a force for positively separating the multi-disc disk does not act simply by removing the pressing force due to the contraction of the cylinder. Therefore, the multi-plate disks are not completely separated from each other, and a braking force is applied by the frictional force. (B) In a state where the multiple discs are in close contact with each other, the cooling oil does not sufficiently reach the surface of each disc. As a result, when the multiple discs are pressed against each other, the friction coefficient of the friction surface is reduced, and the braking force is reduced. Or a so-called fade phenomenon may occur.

A first object of the present invention is to provide a multi-disc type brake device, a multi-disc type clutch device, a crane provided with this brake device and a clutch device, which can sufficiently separate the multi-disc disks when the brake device is released. To provide a hoisting device. A second object of the present invention is to provide a multi-plate type brake device, a multi-plate type clutch device, and a hoisting device of a crane including the brake device and the clutch device, which can effectively cool the multi-plate disk. is there.

[0005]

A description will be given with reference to the drawings showing an embodiment. (1) The multiple disc brake device according to the first aspect of the present invention is movably engaged with the outer peripheral surface of the rotating body 54 in the axial direction, and the static pressure groove 40 is formed on the surface thereof.
A plurality of first friction plates 12 each having a through-hole 40a penetrating through the first friction plate 0 in the axial direction, the first friction plate 12 being engaged with the inner peripheral surface of the fixed body 11 movably in the axial direction, and The grooves are alternately arranged in the axial direction, and the static pressure grooves 40 are formed on the surface thereof.
Are formed, and the second friction plate 13 having the through holes 40a penetrating the static pressure groove 40 in the axial direction, and the first friction plate 12 and the second friction plate 13 are pushed and moved in the axial direction. , First
A cylinder member 15 for pressing the friction plate 12 and the second friction plate 13 against each other, a cylinder control device 21 for driving and controlling the cylinder member 15, a first friction plate 12 and a second friction plate 13, And the hydraulic pressure source 40
The above-described object is achieved by providing the supply control devices 25, 61, 81, and 83 for controlling oil supply from the first and the 63 to the static pressure groove 40. (2) According to a second aspect of the present invention, in the multiple disc brake device according to the first aspect, the static pressure groove 40 has a substantially ring shape. (3) The invention of claim 3 is the multi-disc brake device according to claim 2, wherein the first friction plate 12 and the second friction plate 1
3 is a substantially ring-shaped drain groove 41, 42 formed on at least one of the outer peripheral side and the inner peripheral side of the static pressure groove 40, and a cutout groove 41a extending from the drain groove 41, 42 to the outer peripheral end face or the inner peripheral end face. , 42a. (4) In the multi-plate type brake device according to the first or second aspect, the first friction plate 12 and the second friction plate 13 are at least the outer peripheral end surface or the inner peripheral surface of the static pressure groove 40. Each has a cutout groove 43 reaching the end face. (5) The invention according to claim 5 is the multiple disc brake device according to any one of claims 1 to 4, wherein the supply control device controls the static pressure groove 40 according to the operation of the brake operation means 23a.
Operation supply control device 2 that controls the supply of pressure oil to the vehicle
3 is provided. (6) According to a sixth aspect of the present invention, in the multiple disc brake device according to any one of the first to fifth aspects, the first friction plate 1 is provided.
The supply control devices 81 and 83 control oil supply to the static pressure groove 40 in accordance with the value detected by the temperature detection means 82. The temperature detection means 82 detects the heat generation state of the second and second friction plates 13. Things. (7) According to a seventh aspect of the present invention, in the multiple disc brake device according to any one of the first to sixth aspects, the working actuator 2 driven by pressurized oil from the hydraulic source 63 and the work from the hydraulic source 63. And a directional control valve 4 for controlling the flow of pressure oil to the actuator 2 for supplying the return oil from the directional control valve 4 to the static pressure groove 40. (8) According to an eighth aspect of the present invention, there is provided the multi-plate type brake device according to any one of the first to seventh aspects, wherein the multi-plate type clutch device is configured to transmit / non-transmit power via the brake device. It is composed. (9) The hoisting device for a crane according to the ninth aspect of the present invention achieves the above object by including the multiple disc brake device according to any one of the first to seventh aspects. (10) A hoisting device for a crane according to the tenth aspect of the present invention achieves the above object by including the multi-plate clutch device according to the eighth aspect.

[0006] In the section of the means for solving the above-mentioned problems, which explains the configuration of the present invention, the drawings of the embodiments of the present invention are used to make the present invention easy to understand. However, the present invention is not limited to this.

[0007]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS First Embodiment A first embodiment of a multiple disc brake device according to the present invention will be described below with reference to FIGS. FIG.
FIG. 10 is a hydraulic circuit diagram of a winch having the multi-plate brake device according to the first embodiment of the present invention, and FIG. 10 is a side view of a crane using the multi-plate brake device.
As shown in FIG. 10, the mobile crane includes a traveling body 101.
And a revolvable revolving structure 10 mounted on a traveling structure 101
2 and a boom 10 supported up and down by the revolving superstructure 102
3 The wire rope 104 is wound up or down by driving the winch drum 1 mounted on the revolving structure 102, and the suspended load 106 is lifted by the hook 105 connected to the wire rope 104. Also,
The driving of the undulating drum 107 causes the undulating rope 108 to be raised or lowered, and the boom 103 to be undulated.

As shown in FIG. 1, the winch includes a winch drum 1 and a hydraulic motor 2 for driving the winch drum 1.
And a hydraulic pump 3 for supplying drive hydraulic oil to the hydraulic motor 2
A direction control valve 4 for controlling the flow of hydraulic oil from the hydraulic pump 3 to the hydraulic motor 2, a planetary reduction mechanism 5 for transmitting or not transmitting the driving force of the hydraulic motor 2 to the winch drum 1,
Multi-plate type brake device 1 for controlling operation of planetary reduction mechanism 5
0.

The output shaft 2a of the hydraulic motor 2 is connected to a sun gear 21 of the planetary reduction mechanism 5. A planetary gear 52 is meshed with the sun gear 51, and a ring gear 53 provided inside the winch drum 1 is meshed with the planetary gear 52.
Are meshed. The planetary gear 52 is a carrier shaft 5
4 and the carrier shaft 54 is connected to the brake case 1
One of the side walls 11a penetrates and reaches the inside of the case 11.
A plurality of inner disks 12 are axially movably engaged with the carrier shaft 54 by spline coupling, and the inner disk 12 is rotatable integrally with the carrier shaft 54. A plurality of outer disks 13 are axially movably engaged with the inner peripheral surface of the brake case 11 by spline coupling.
2 are alternately arranged in the axial direction.

[0010] A brake piston 14 is disposed on the side of the disks 12 and 13. The brake piston 14 is connected to a piston rod 15 a of a brake cylinder 15 and a spring 16 provided on a side end of the brake case 11. Supported by. In the rod chamber of the brake cylinder 15, an electromagnetic switching valve 21, a pipeline 22, a brake valve 23,
The hydraulic pressure source 31 is connected via the pipeline 24. The downstream line 22 of the electromagnetic switching valve 21 includes a hydraulic switching valve 25 and a line 2
6, as described later, is connected to an oil supply hole 27 provided in the brake case 11, and a pilot port of the hydraulic switching valve 25 is in contact with a downstream side pipe line 24 of the brake valve 23.

The electromagnetic switching valve 21 is switched by operating a free fall switch 21a for instructing a free fall, and the degree of pressure reduction of the brake valve 23 is adjusted according to the operation of a brake pedal 23a. FIG. 2 shows the relationship between the stroke amount S of the brake pedal 23a when the pressure oil from the hydraulic pressure source 31 is supplied to the brake valve 23 via the electromagnetic switching valve 21 and the secondary pressure P after passing through the brake valve, and FIG. 4 is a diagram showing a relationship between a switching amount of a hydraulic switching valve 25 and a switching amount. As shown in FIG. 2, the secondary pressure P after passing through the brake valve is constant at the maximum value P0 when the pedal stroke amount S is equal to or less than a predetermined value S0. As the pressure increases, the secondary pressure P decreases proportionally. When the pedal stroke S = S1, the secondary pressure P = P1, and when the stroke S = S2, the secondary pressure P = P2. On the other hand, when the pedal stroke amount S is equal to or less than a predetermined value S1, that is, when the secondary pressure P is equal to or greater than P1, the hydraulic switching valve 25 becomes the maximum switching amount, the valve opening is fully opened, and the stroke amount S1 ≦ S ≦ S2. In the range, the switching amount decreases proportionally with the increase of the stroke amount S. Then, the pedal stroke amount S is equal to or more than a predetermined value S2,
That is, when the secondary pressure P is equal to or less than P2, the switching amount becomes minimum and the hydraulic switching valve 25 is fully closed.

FIG. 3 is a sectional view showing the internal structure of the brake case 11, and FIG. 4 is a view showing the shape of the main parts of the disks 12, 13. As shown in FIG. Note that in FIG.
13 shows the press contact state. As shown in FIG. 4, on one surface of the inner disk 12 and the outer disk 13,
A ring-shaped static pressure groove 40 having the same shape is formed, and the static pressure groove 40 is formed at four locations (every 90 degrees) in the circumferential direction.
A through hole 40a having a diameter smaller than the width of the through hole 40a is formed. As shown in FIG. 3, a static pressure groove 40 having the same shape is also formed on the surface of the brake piston 14.

An oil supply hole 27 connected to the pipe 26 penetrates the brake case 11 and opens from the inner surface of the side wall 11a toward the static pressure groove 40. The brake piston 14 is slidably fitted to the inner peripheral surface of the brake case 11, and a gap 28 is provided in the axial direction between the outer end surface of the brake piston 14 and the side end surface of the brake case 11. ing. An oil supply hole 29 (dotted line) connected to the pipeline 24 is provided in a phase (not shown) of the brake case 11, and the oil supply hole 29 is opened in a gap 28 between the brake piston 14 and the brake case 11. Also, brake case 1
1 is provided with a discharge hole 30, and the discharge port 30 is connected to the tank.

The operation of the present embodiment configured as described above will be described. (1) Free fall switch off When the free switch 21a is off, as shown in FIG.
The pressure oil from 1 is shut off by the electromagnetic switching valve 21. As a result, the hydraulic switching valve 25 is switched to the position A, the pipeline 22 and the pipeline 26 are cut off, the bottom chamber of the brake cylinder 15 communicates with the tank, and the cylinder 15 is actuated by the urging force of the spring 16 in FIG. It extends in the a direction. Due to the extension of the cylinder 15, the disks 12, 13 are pushed toward the case-side end 11a, and are pressed between the case-side end 11a and the brake piston 14, as shown in FIG. As a result, a frictional force acts on the inner disk 12, and the rotation of the disk 12 is prevented (brake operation).

When the brake device operates in this manner, the rotation of the carrier shaft 54 is prevented, and the rotation of the hydraulic motor 2 is transmitted to the winch drum 1 via the sun gear 51, the planetary gear 52, and the ring gear 53. here,
When a pilot pressure oil is applied to the pilot port of the direction switching valve 4 by operating the operation lever (not shown) to wind up or down, the direction switching valve 4 is switched from the neutral position, and the hydraulic motor 2 is wound up or down. Rotate in the direction. This allows
The winch drum 1 is driven to hoist or lower to perform a hoisting operation of a suspended load. The driving of the winch drum 1 is stopped by the operation of a brake device (not shown) provided separately from the multiple disc brake device 10.

(2) Free fall switch on When the free fall switch 21a is turned on while the operation lever is operated to the neutral position and the direction switching valve 4 is switched to the neutral position, the electromagnetic switching valve 22 is switched to the position B. . Here, when the brake pedal 23a is not depressed, the pressure oil from the hydraulic pressure source 31 is supplied to the electromagnetic switching valve 21,
The brake piston 14 and the brake case 1 are provided through the brake valve 23 and the oil supply hole 29 in the brake case 11
1 flows into the gap 28. As a result, the brake cylinder 15 contracts in the direction a in FIG. 2 against the spring force, and the pressing force acting on the disks 12, 13 is removed. At the same time, the pressure oil that has passed through the brake valve 23 also acts on the pilot port of the hydraulic switching valve 25, and the hydraulic switching valve 25 is switched to the position B side. Accordingly, the pressure oil from the hydraulic pressure source 31 is pressed against the case side wall 11a via the electromagnetic switching valve 21, the hydraulic switching valve 25, and the oil supply hole 27 in the brake case 11 (the outer disk 13 in FIG. 3). Flows into the static pressure groove 40, and the pressure oil flows through the through hole 40a.
Are guided to the static pressure grooves 40 of the respective disks 12 and 13 via the. As a result, a static pressure corresponding to the amount of hydraulic pressure acts on the disks 12 and 13, and the static pressure causes the respective disks 12 and 13 to operate.
13 are separated from each other, and a predetermined oil film thickness is formed on both sides of the disks 12, 13 (brake release). The oil flowing into the brake case 11 is discharged from the discharge hole 40 to the tank.

When the brake device is released, the inner disk 12 becomes rotatable, and the rotation of the carrier shaft 54 is permitted. As a result, when a rotational force due to the load of the suspended load acts on the winch drum 1, the carrier shaft 54 is in a free rotation state, and the suspended load can fall free. When the brake pedal 23a is depressed in this state, the secondary pressure P after passing through the brake valve decreases as the pedal stroke amount S increases as shown in FIG. 2, and the brake cylinder 15 expands accordingly. Then, when the pedal stroke amount S = S2, the hydraulic pressure switching valve 25 is fully closed, and the supply of the pressure oil to the oil supply hole 27 is cut off. As a result, the discs 12 and 13 are
Is pressed, and the disks 12, 13 are pressed against each other,
The brake device operates. As a result, winch drum 1
Can be stopped.

As described above, according to the first embodiment, ring-shaped static pressure grooves 40 are provided on the surfaces of the inner disk 12 and the outer disk 13 installed in the brake case 11, respectively. A through-hole 40a is provided to guide the pressure oil to each static pressure groove 40 when a free fall command is issued. As a result, an axial oil pressure acts on the surfaces of the disks 12, 13, and the disks 12, 13 are separated from each other by the oil pressure. That is, since the disks 12 and 13 are stuck as they are, a large force is required to separate them, but the separation is easy if hydraulic pressure is used. Such separation of the disks 12, 13 removes the braking force due to the contact resistance between the disks 12, 13 and allows the suspended load to free-fall efficiently. Further, since the pressure oil flows in the brake case 11, the disks 12, 13 are cooled.

Further, when the oil supply to the static pressure groove 40a is stopped by operating the brake pedal 23a or the like, the disk 12,
A separation force in the axial direction is no longer applied to the disc 13, and the discs 12 and 13 can be easily pressed against each other by the extension of the brake cylinder 15. That is, the adjacent disk 1
In the case where a spring is provided between the discs 12 and 13 and the discs 12 and 13 are separated by the spring force, when the discs 12 and 13 are pressed against each other, the brake cylinder 15 which resists the spring force is used.
However, if the disks 12, 13 are separated by hydraulic pressure as in the present embodiment, the pressing force of the brake cylinder 14 does not need to be so large. Further, since the brake device is operated in response to the operation of the brake pedal 23a during the free fall, the driving of the drum 1 during the free fall can be arbitrarily stopped, and the free fall operation can be performed satisfactorily. .

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

-Second Embodiment- A second embodiment of the present invention will be described with reference to FIG. FIG. 5 is a diagram showing the main part shapes of an inner disk 12 and an outer disk 13 constituting the multiple disc brake device according to the second embodiment. In FIG. 5, the same portions as those in FIG. 4 are denoted by the same reference numerals, and the differences will be mainly described below. The difference between the second embodiment and the first embodiment lies in the shape of the static pressure grooves provided in the disks 12 and 13. As shown in FIG. 5, in addition to the static pressure grooves 40 on the surfaces of the disks 12 and 13, ring-shaped static pressure grooves 41 and 42 are provided on the inner diameter side and the outer diameter side of the static pressure grooves 40, respectively. . A plurality of notches 41a are radially formed in the static pressure groove 41 toward the inner diameter end face, and a plurality of notches 42a are radially formed in the static pressure groove 42 toward the outer diameter end face.

In the second embodiment configured as described above, when the pressure oil is supplied to the static pressure groove 40 through the oil supply hole 27 at the time of the free fall, the same as in the first embodiment,
Hydraulic pressure acts on the surfaces of the disks 12, 13 to separate the disks 12, 13 and release the brake device. At this time, the static pressure grooves 41 and 4 pass through the gaps between the disks 12 and 13.
2 is also supplied with oil, but since the static pressure grooves 41, 42 are provided with a plurality of notches 41a, 42a radially, the oil flows out from the notches 41a, 42a. Therefore, a large static pressure does not act on the static pressure grooves 41 and 42. By adjusting the widths of the static pressure grooves 41 and 42 and the notches 41a and 42a,
13 can be adjusted.

When the oil supply to the oil supply hole 27 is stopped, the first
As in the case of the first embodiment, the brake cylinder 15 extends,
The discs 12 and 13 are pressed against each other to operate the brake device. In this case, notches 41a, 4 are formed in the static pressure grooves 41, 42.
2a, the notches 41a, 42
The pressure oil in the static pressure grooves 41 and 42a can be quickly discharged from the disk surface via the a, and the responsiveness of the brake device operation is improved.

Third Embodiment A third embodiment of the present invention will be described with reference to FIGS. In the third embodiment, the configuration is such that the cooling effect of the disks 12, 13 is further enhanced during free fall. FIG. 6 is a hydraulic circuit diagram of a winch having a multiple disc brake device 60 according to the third embodiment.
FIG. 3 is a diagram showing the shape of a main part of an inner disk 12 and an outer disk 13 constituting the brake device 60. 6 and 7, the same parts as those in FIGS. 1 and 4 are denoted by the same reference numerals, and the differences will be mainly described below.

As shown in FIG. 6, in the third embodiment, a hydraulic switching valve 61 is provided instead of the hydraulic switching valve 25. The inlet side port of the hydraulic switching valve 61 is connected to a line 62.
Is connected to the tank port (T port) of the directional control valve 4 via a port, and the outlet side port is connected to the pipe 26 connected to the oil supply hole 27 and the tank, respectively. Since the return pressure of the hydraulic pump 63 does not rise more than necessary, the relief valve 6
4 are connected. The pilot port of the hydraulic switching valve 61 is connected to the downstream pipeline 22 of the electromagnetic switching valve 21. A cooler 66 is interposed in a conduit 65 for guiding the return oil from the brake case 11 to the tank. As shown in FIG. 7, the static pressure grooves 40 of the disks 12 and 13
A plurality of through holes 40a are opened, and between each through hole 40a, a notch 43 is provided radially from the inner peripheral surface to the outer peripheral surface of the disk.

In the third embodiment, the directional control valve 4
When the free fall switch 21a is turned on at the time of neutralization, the hydraulic oil from the hydraulic pressure source 31 is supplied to the brake cylinder 15 via the electromagnetic switching valve 21 and the brake valve 23, and the brake cylinder 15 contracts and the electromagnetic switching valve 21
The pressure oil that has passed through acts on the pilot port of the hydraulic switching valve 61, and the electromagnetic switching valve 61 is switched to position B. With this switching, the pressure oil from the hydraulic pump 63 flows into the static pressure groove 40 of the disk 13 through the direction switching valve 4, the hydraulic switching valve 61, and the oil supply hole 27 in the brake case 11, and passes through the through hole 40a. Through the static pressure grooves 40 of the respective disks 12 and 13. Thereby, the disks 12, 13
Hydraulic pressure acts on the surface of the disk 12 and the disks 12 and 13 are separated from each other, and the pressure oil guided to the static pressure groove 40 passes through the surface of the disks 12 and 13 through the notch 43. As a result, the cooling effect of the disks 12, 13 is promoted, and the temperature rise of the disks 12, 13 can be suppressed. The pressure oil in the brake case 11 flows to a cooler 66 via a pipe 65, is cooled by the cooler 66, and is returned to the tank. Since the notches 43 are provided on the surfaces of the disks 12 and 13 in the circumferential direction so as to cross the static pressure grooves 40, the static pressure acting on the surfaces of the disks 12 and 13, that is, the disks 12 and 13 are separated from each other. The force for separating is smaller than in the first and second embodiments described above.

During free fall, the brake pedal 23a
Is operated, the brake cylinder 1
The hydraulic pressure acting on the hydraulic cylinder 5 decreases, and the brake cylinder 15 is extended by the spring force. At this time, the hydraulic switching valve 61 is still switched to the position B, and the pressure oil from the hydraulic pump 63 is guided to the static pressure grooves 40 of the disks 12 and 13.
In this case, since the static pressure acting on the surfaces of the disks 12 and 13 does not become so large as described above, when the brake pedal 23a is operated by a predetermined amount or more, the pressing force of the spring 16 on the brake cylinder 15 becomes larger than the static pressure. The pressure becomes larger than the oil pressure acting on the groove 40, and the disks 12, 13 are pressed against each other. At this time, since the disks 12 and 13 are sufficiently cooled, the friction coefficient of the surfaces of the disks 12 and 13 is large, and therefore, the disks 12 and 13 can be pressed against each other with a correspondingly small force. As long as the free fall switch 21a is on, cooling oil is continuously flown over the surfaces of the disks 12, 13 to cool the disks 12, 13 for a long time.

As described above, according to the third embodiment, the disk 1 traverses the static pressure grooves 40 of the disks 12 and 13 and
Since the radial notches 43 are provided from the inner peripheral surface to the outer peripheral surface of the disks 2 and 13, the surfaces of the disks 12 and 13 are effectively cooled by the cooling oil passing through the notches 43. As a result, the temperature rise of the disks 12, 13 is suppressed, and the occurrence of the fade phenomenon can be prevented, and the wear life of the disks 12, 13 can be extended. Further, since the pressure oil from the hydraulic pump 63 is used as the cooling oil, it is not necessary to add a cooling pump, and the increase in the number of parts can be suppressed. When the amount of cooling oil to the disks 12, 13 is insufficient, the pump flow rate may be increased.

-Fourth Embodiment- A fourth embodiment of the present invention will be described with reference to FIGS. In the fourth embodiment, the cooling oil amount is adjusted according to the temperatures of the disks 12 and 13. FIG. 8 is a hydraulic circuit diagram of a winch having a multiple disc brake device 80 according to the fourth embodiment. The same parts as those in FIG. 6 are denoted by the same reference numerals, and the differences will be mainly described below.
As shown in FIG. 6, in the fourth embodiment, the hydraulic pressure switching valve 61 is changed to an electromagnetic proportional valve 81. A temperature sensor 82 for detecting the oil temperature is provided in the upstream pipe 65 of the cooler 66, and the temperature of the disks 12 and 13 is indirectly detected by the temperature sensor 82. Free fall switch 2
The solenoid 1a, the temperature sensor 82 and the solenoid of the electromagnetic proportional valve 81 are connected to a controller 83.

FIG. 9 is a flowchart showing an example of processing executed by the controller 83. First, step S
At 1, it is determined whether the free fall switch 21a is on. If it is determined that the switch is off, the process proceeds to step S2, in which a control signal for switching the electromagnetic proportional valve 81 to the position A is output, and the process returns. Thereby, the oil supply hole 2
7 is shut off, and the disks 12, 13 are pressed against each other by the extension of the brake cylinder 15.

On the other hand, if it is determined that the switch is on, the process proceeds to step S3, where the detection value from the temperature sensor 82 is read. Next, in step S4, a control signal is output to the solenoid of the electromagnetic proportional valve 81 based on preset characteristics so that the electromagnetic proportional valve 81 has a valve opening corresponding to the detected temperature value, and the process returns. In this case, the valve characteristic of the electromagnetic proportional valve 81 is set so that the opening degree communicating between the pipelines 62 and 26 increases as the detection value of the temperature sensor 82 increases, as shown in step S4. Thereby, the disk 1
The higher the temperature of 2,13, the higher the temperature of disks 12,13
The amount of cooling oil supplied to the cooling water increases, and the cooling effect increases.
Note that instead of controlling the electromagnetic proportional valve 81, the amount of cooling oil may be adjusted by controlling the tilt angle of the hydraulic pump 63 and the engine speed.

As described above, according to the fourth embodiment, the valve opening of the electromagnetic proportional valve 81 is controlled in accordance with the temperature of the disks 12 and 13 so that the amount of cooling oil supplied to the disks 12 and 13 is optimized. Was controlled. Thereby, it is possible to prevent a fading phenomenon and abnormal wear due to a rise in the temperature of the disks 12 and 13 and to make the cooler 6 warm up during the warm-up operation.
6 can be minimized (for example, 0), and the warm-up operation time is not prolonged.

In the above embodiment, the static pressure grooves 40 to
Although 42 is formed in a ring shape, the shape is not limited to this, and may be another shape (for example, a triangle, a square, or a staggered shape).
Further, the number of the static pressure grooves 40 to 42 and the notches 41a, 4
The shape and number of 2a and 43 are not limited to the above embodiment. The static pressure grooves 40 to 42 provided in each of the disks 12 and 13 need not be on the same circumference.

In the correspondence between the above embodiment and the claims, the carrier shaft 54 is a rotating body, the brake case 11 is a fixed body, the first friction plate 12 is an inner disk,
The friction plate 13 of the outer disc and the brake cylinder 1
5 is a cylinder member, the electromagnetic switching valve 21 is a cylinder control device, the hydraulic switching valves 25 and 61, the electromagnetic switching valve 81 and the controller 83 are a supply control device, the static pressure grooves 41 and 42 are a drain groove, and a notch 41a. , 42a, 43 are notched grooves,
The brake pedal 23a functions as a brake operation means, the brake valve 23 functions as a brake operation supply control device, and the temperature sensor 82
Constitute the temperature detecting means, and the hydraulic motor 2 constitutes the working actuator.

[0035]

As described above, according to the present invention, the following effects can be obtained. (1) According to the first aspect of the invention, the first friction plate engaged with the rotating body and the second friction plate alternately arranged with the first friction plate and engaged with the fixed body In the multi-disc brake device having: a first friction plate and a second friction plate, a static pressure groove is provided on each of the surfaces thereof, and a through-hole is provided through the static pressure groove, so that the hydraulic pressure source can move from the hydraulic pressure source to the static pressure groove. Refueling was controlled. This makes it possible to apply an oil pressure to the surfaces of the friction plates in such a manner as to be spaced apart from each other in the axial direction according to the shape and the number of the static pressure grooves, and to effectively cool the surface of the disk. (2) According to the third aspect of the invention, a substantially ring-shaped drain groove is provided on the surface of the friction plate, and a cutout groove is provided from the drain groove to the outer peripheral surface or the inner peripheral surface of the friction plate. The pressure oil in the groove quickly flows out of the friction plate surface through the notch groove, and the responsiveness of the brake device operation is improved. (3) According to the invention of claim 4, since the notch groove is provided from the static pressure groove to the outer peripheral surface or the inner peripheral surface of the friction plate, the cooling oil flows on the surface of the disk through the notch groove, The cooling efficiency of the disk is improved. (4) According to the sixth aspect of the invention, the oil supply to the static pressure groove is controlled according to the heat generation state of the friction plate, so that the friction plate can be cooled optimally. (5) According to the invention of claim 7, since the return oil from the direction control valve is supplied to the static pressure groove, it is not necessary to newly add a hydraulic pressure source. (6) According to the invention of claim 8, the multi-plate type brake device is applied to the multi-plate type clutch device, so that the free fall operation can be performed satisfactorily.

[Brief description of the drawings]

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

FIG. 2 is a view showing characteristics of a brake valve and a hydraulic switching valve that constitute the multi-plate brake device according to the first embodiment.

FIG. 3 is an essential part cross-sectional view of the multiple disc brake device according to the first embodiment;

FIG. 4 is a view showing the shapes of an inner disk and an outer disk constituting the multiple disc brake device according to the first embodiment.

FIG. 5 is a view showing the shapes of an inner disk and an outer disk constituting a multiple disc brake device according to a second embodiment.

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

FIG. 7 is a view showing the shapes of an inner disk and an outer disk constituting a multiple disc brake device according to a third embodiment.

FIG. 8 is a hydraulic circuit diagram of a winch having a multiple disc brake device according to a fourth embodiment of the present invention.

FIG. 9 is a flowchart illustrating an example of a process performed by a controller included in the brake device according to the fourth embodiment;

FIG. 10 is a side view of a crane to which the present invention is applied.

[Explanation of symbols]

2 Hydraulic motor 4 Directional control valve 12 Inner disk 13 Outer disk 15 Brake cylinder 23 Brake valve 23a Brake pedal 31 Hydraulic source 40-42 Static pressure groove 41a, 42a, 43
Notch 61 Hydraulic switching valve 63 Hydraulic pump 81 Solenoid switching valve 82 Temperature sensor 83 Controller

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI theme coat ゛ (reference) F16D 25/0638 F16D 65/12 S 65/12 25/063 K F term (reference) 3J057 AA04 BB04 DB03 GA65 GB22 GC02 HH04 JJ01 3J058 AA44 AA48 AA53 AA59 AA70 AA77 AA79 AA88 BA34 CC03 CC07 CC72 CC78 FA39

Claims (10)

[Claims] 1. A plurality of rotating bodies are axially movably engaged with an outer peripheral surface of the rotating body, a static pressure groove is formed on the surface thereof, and a plurality of through holes each penetrating the static pressure groove in the axial direction. A first friction plate, axially movably engaged with an inner peripheral surface of the fixed body, and
A plurality of second friction plates, each of which is alternately arranged in the axial direction with the first friction plate, has a static pressure groove formed in the surface thereof, and has through holes each penetrating the static pressure groove in the axial direction; Pushing the first friction plate and the second friction plate in the axial direction,
A cylinder member for pressing the first friction plate and the second friction plate against each other, a cylinder control device for driving and controlling the cylinder member, and a supply control device for controlling oil supply from a hydraulic pressure source to the static pressure groove. A multi-plate type brake device comprising: 2. The multiple disc brake device according to claim 1, wherein the static pressure groove has a substantially ring shape. 3. The multiple disc brake device according to claim 2, wherein the first friction plate and the second friction plate are formed on at least one of an outer peripheral side and an inner peripheral side of the static pressure groove. A multi-plate brake device comprising: a ring-shaped drain groove; and a cutout groove extending from the drain groove to an outer peripheral end surface or an inner peripheral end surface. 4. The multi-plate type brake device according to claim 1, wherein the first friction plate and the second friction plate have a notch groove extending from the static pressure groove to at least an outer peripheral end surface or an inner peripheral end surface. A multi-plate type brake device characterized by having each. 5. The multi-plate type brake device according to claim 1, wherein the supply control device controls the supply of pressurized oil to the static pressure groove in accordance with an operation of a brake operation unit. A multi-disc type brake device comprising a brake operation supply control device that performs the operation. 6. The multiple disc brake device according to claim 1, further comprising: a temperature detecting unit that detects a heat generation state of the first friction plate and the second friction plate. The supply control device controls oil supply to the static pressure groove in accordance with a value detected by the temperature detection means. 7. The multi-plate brake device according to claim 1, wherein a working actuator driven by pressure oil from the hydraulic source, and a pressure from the hydraulic source to the working actuator. A directional control valve for controlling a flow of oil, wherein return oil from the directional control valve is supplied to the static pressure groove. 8. A multi-plate clutch comprising the multi-plate brake device according to claim 1, wherein power is transmitted / non-transmitted via the brake device. apparatus. 9. A hoisting device for a crane provided with the multi-plate type brake device according to claim 1. Description: 10. A crane hoisting device provided with the multi-plate clutch device according to claim 8.