JP7258695B2 - Braking devices for track-running machines - Google Patents

Description

The present invention relates to a braking device for a track-running machine.

FIG. 6 shows an example of a container crane as a general track traveling machine, 1 is a container crane, 2 is a port where the container crane 1 is deployed, 3 is a quay in the port 2, and 4 is a quay 3. A traveling device 8 having traveling wheels 7 that can freely roll along the rails 4 on the supporting legs 6 of the crane body 5 of the container crane 1. is installed.

If the container crane 1 is hit by a strong wind during cargo handling work, it may not stop traveling against the will of the driver and may run away, resulting in collision with adjacent machines or adjacent structures or collapse. .

For this reason, conventionally, there is a clamping device as disclosed in Patent Document 1, for example, as a device for preventing runaway of the track traveling type machine as described above. The clamping device includes a pinching mechanism in which a pair of contactors having pinching portions formed at their distal ends are connected so that their substantially intermediate portions are rotatable about an axis, and a proximal end of the contactor in the pinching mechanism. a spring mechanism which is provided at the base of the contactor and narrows the distance between the base ends of the contactor so as to rotate the contactor in a closing direction in which the pinching portion always sandwiches the rail; and a rotating cam for driving the cam receiving portion formed in the inner side of the cam receiving portion in a direction to open the rail to release the clamping portion of the rail.

However, since the clamping device disclosed in Patent Document 1 employs a method of clamping the rail from both sides, the contact surface on the side of the clamping device may be provided with jagged teeth in order to increase the coefficient of friction with the rail surface. Or, if the contact surface is hardened and made like a file, there is a possibility that the side surface of the rail will be damaged. In addition, when the precision of the side surface of the rail is low and the dimension from the center line to the side surface in the width direction varies from left to right, or when the rail is corroded, etc. There is also a possibility that the tightening force is greatly reduced because the tightening is not performed uniformly, and sufficient holding force cannot be obtained.

In order to solve such a problem, a braking device has been developed that has a fluid pressure cylinder, such as a hydraulic cylinder, that can freely press and separate a brake pad in a direction perpendicular to the rolling surface of the running wheel of the rail (see, for example, Patent Documents 2).

JP-A-6-72690 JP 2015-58805 A

By the way, in recent years, there is an increasing demand for a track traveling type machine such as the container crane 1 to be able to provide a braking device under the traveling device 8 . In particular, when modifying an existing track traveling machine, a braking device cannot be provided under the lower frame extending along the rail 4 so as to connect the support legs 6 between the support legs 6 of the crane body 5. This is to deal with such cases.

However, in the conventional braking device as described in Patent Document 2, the length of the fluid pressure cylinder cannot be shortened, so it has been difficult to provide the braking device in the lower part of the traveling device 8.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a braking device for a track traveling machine that eliminates restrictions on installation locations during modification and increases the degree of freedom in installation.

The present invention comprises an upper equalizer beam, which is swingably arranged at the lower part of a support leg that runs on a rail and whose intermediate part is supported by a rocker pin that extends in a horizontal direction perpendicular to the running direction; and the upper equalizer beam. At least one stage of equalizer devices consisting of a pair of lower equalizer beams, which are swingably arranged with intermediate portions supported by rocker pins extending in the horizontal direction perpendicular to the running direction, In a braking device for a track traveling machine having a traveling device in which traveling wheels capable of rolling along rails are arranged at both ends of the lower equalizer beam in the traveling direction of the lower equalizer device,
a pressing frame disposed between the lower equalizer beam and the rail of the lowermost equalizer device so as to protrude in the horizontal direction orthogonal to the rail; both ends of the pressing frame in the horizontal direction orthogonal to the rail; A braking mechanism having a fluid pressure cylinder interposed between both side surfaces of the lower equalizer beam in the lowermost equalizer device and raising and lowering the pressing frame, and a brake pad attached to the lower surface of the pressing frame,
The fluid pressure cylinder relates to a braking device for a track traveling machine fixed via an elastic member that absorbs a bending force acting on a piston rod of the fluid pressure cylinder.

In the braking device for the track traveling type machine, the elastic member includes a lower surface of a support bracket projecting from the lower equalizer beam and a cylinder body of the fluid pressure cylinder fixed to the lower surface of the support bracket with a fastening member. It is interposed between the back and
It is preferable that the tip of the piston rod of the fluid pressure cylinder is screwed into the pressing frame.

Moreover, the braking device for the track traveling type machine may further comprise a metal plate interposed between the elastic member and the back surface of the cylinder main body of the fluid pressure cylinder.

According to the braking device of the track traveling type machine of the present invention, it is possible to obtain an excellent effect of eliminating restrictions on the installation location at the time of remodeling and increasing the degree of freedom of installation.

1 is a front view showing an embodiment of a braking device for a track traveling machine according to the present invention; FIG. 1 is a schematic configuration diagram showing an embodiment of a braking device for a track traveling machine according to the present invention, showing a state in which braking is released; FIG. FIG. 3 is a view taken along line III-III in FIG. 2; 1 is a schematic configuration diagram showing an embodiment of a braking device for a track traveling machine of the present invention, showing a state in which braking is being performed; FIG. 1 is a schematic configuration diagram showing a reference example of a braking device for a track traveling machine according to the present invention, showing a state in which braking is released; FIG.

1 is an overall side view showing an example of a container crane as a track traveling machine; FIG.

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

1 to 4 show an embodiment of a braking device for a track traveling machine according to the present invention, and in the figures, the same reference numerals as in FIG. 6 represent the same parts.

In a container crane 1 as a rail traveling machine shown in FIG. A plurality of (two in the example of FIG. 1) traveling devices 8 are provided on the bottom surface side.

The traveling device 8 includes an upper equalizer beam 9a, an intermediate equalizer beam 9b, a lower equalizer beam 9c, and traveling wheels 7. As shown in FIG.

The upper equalizer beam 9a is swingably arranged on the bottom side of the lower frame 6a with its intermediate portion supported by a rocker pin 10a extending in the horizontal direction perpendicular to the running direction. The middle portion of the equalizer beam 9b is swingably supported by rocker pins 10b extending in the horizontal direction perpendicular to the running direction at both ends of the upper equalizer beam 9a in the running direction. The lower equalizer beam 9c is oscillatably supported at its intermediate portion by rocker pins 10c extending in the horizontal direction perpendicular to the running direction at both ends of the intermediate equalizer beam 9b in the running direction.

The running wheels 7 are arranged so as to be free to roll along the rails 4 at both ends of the lower equalizer beam 9c in the running direction.

In the example shown in FIG. 1, an equalizer device 9A consisting of an upper equalizer beam 9a and an intermediate equalizer beam 9b, and an equalizer device 9B consisting of an intermediate equalizer beam 9b and a lower equalizer beam 9c are formed in two upper and lower stages. It is Incidentally, the upper equalizer beam 9a in the upper equalizer device 9A becomes an upper equalizer beam, and the intermediate equalizer beam 9b becomes a lower equalizer beam. In the lower equalizer device 9B, the intermediate equalizer beam 9b relatively becomes the upper equalizer beam, and the lower equalizer beam 9c relatively becomes the lower equalizer beam. However, according to the scale of the container crane 1 as the track traveling machine, only one stage of the equalizer device 9A is formed, and the traveling wheels 7 are arranged on the lower equalizer beam (in this case, the intermediate equalizer beam 9b). You can Also, the equalizer devices may be arranged in three or more stages, and running wheels 7 that can freely roll along the rails 4 may be arranged at both ends of the lower equalizer beam in the running direction of the lowermost equalizer device.

The lower equalizer beam 9c (lower equalizer beam) is composed of a plurality of (two in the example of FIGS. 2 and 3) plate members 9cp arranged at predetermined intervals in the width direction of the rail 4. It is configured by arranging a plate member 9cq that connects the .

A braking mechanism 40 is arranged in each of the traveling devices 8 . However, it is not always necessary to arrange the braking mechanism 40 in each of the traveling devices 8, and the number of the braking mechanism 40 may be one as long as a sufficient braking force can be obtained.

The braking mechanism 40 is attached to the lower equalizer beam 9c (lower equalizer beam) on which the traveling wheels 7 are arranged, and as shown in FIG. have.

The pressing frame 50 of the braking mechanism 40 is arranged between the lower equalizer beam 9c (lower equalizer beam) and the rail 4 so as to protrude in the horizontal direction perpendicular to the rail 4. As shown in FIG.

The hydraulic cylinders 13 of the braking mechanism 40 move the pressing frame 50 between both horizontal ends perpendicular to the rails 4 of the pressing frame 50 and both side surfaces of the lower equalizer beam 9c (lower equalizer beam). It is interposed so that it can be raised and lowered.

A fixed frame 51 is attached to the lower equalizer beam 9c (lower equalizer beam), and an elastic member 60 (for example, urethane rubber or the like) and a metal plate 70 ( The cylinder main body 13a of the fluid pressure cylinder 13 is fixed by a fastening member 80 such as a bolt via a steel plate or the like.

The tip of the piston rod 13b suspended from the cylinder body 13a is screwed into the pressing frame 50 and fixed by a nut 90. As shown in FIG.

The fixed frame 51 is provided with stopper portions 51a opposed to both end surfaces of the pressing frame 50 in the longitudinal direction of the rail 4, and the stopper portions 51a restrict the movement of the pressing frame 50 in the longitudinal direction of the rail 4. (see FIGS. 2 and 3).

As shown in FIG. 3, two fluid pressure cylinders 13 are arranged on one side, but the number can be set to one or three or more as required.

A brake pad 12 of the braking mechanism 40 is attached to the lower surface of the pressing frame 50 .

A fluid pressure unit 14 is connected to the fluid pressure cylinder 13 .

The fluid pressure unit 14 can supply and discharge a working fluid such as oil to and from the cap side chamber 13c and the rod side chamber 13d of the fluid pressure cylinder 13 and expand and contract the fluid pressure cylinder 13. will be described in detail.

The fluid pressure unit 14 includes a pressure feed line 16 extending from a tank 15 in which working fluid is stored, and a cap side line 17 connected to the cap side chamber 13c of the fluid pressure cylinder 13 (the chamber on the side where the piston rod 13b does not protrude). , a rod-side line 18 connected to the rod-side chamber 13 d of the fluid pressure cylinder 13 (the chamber on the side where the piston rod 13 b protrudes), and a return line 19 leading to the tank 15 . A pump 21 driven by a motor 20 and a check valve 22 for preventing reverse flow of the working fluid pressure-fed by the pump 21 are provided in the pressure-feeding line 16 . The pressure-feeding line 16 and return line 19, and the cap-side line 17 and rod-side line 18 are connected via a solenoid valve 23. An accumulator 25 is connected to the branched pressure accumulation line 24 .

The solenoid valve 23 has a brake application position 23A and a brake release position 23B. At the brake operating position 23A, the pressure-feeding line 16 and the cap-side line 17 are communicated to introduce the working fluid pressure-fed by the pump 21 into the cap-side chamber 13c of the fluid pressure cylinder 13, and the rod-side line. 18 and the return line 19 are communicated with each other to discharge the working fluid in the rod-side chamber 13d of the fluid pressure cylinder 13 to the tank 15. At the brake release position 23B, the pressure-feeding line 16 and the rod-side line 18 are communicated to introduce the working fluid pressure-fed by the pump 21 into the rod-side chamber 13d of the fluid pressure cylinder 13, and This is the position where the working fluid in the cap-side chamber 13c of the fluid pressure cylinder 13 is discharged to the tank 15 by connecting the line 17 and the return line 19 to each other. In addition, the solenoid valve 23 is switched to the brake operation position 23A mechanically by the spring force when the solenoid valve 23 is de-energized during an emergency stop (when the power supply is intentionally cut off in an emergency) or during a power failure. there is

A relief line 26 leading to the tank 15 is branched and connected in the middle of the pressure-feeding line 16 between the pump 21 and the check valve 22, and the pressure of the working fluid in the pressure-feeding line 16 is applied to the middle of the relief line 26. A relief valve 27 is provided that opens to return the working fluid to the tank 15 when the pressure exceeds a set pressure.

In the middle of the pressure accumulation line 24, there is a high pressure switch 28H that operates when the pressure of the working fluid in the pressure accumulation line 24 reaches the high set pressure, and the pressure of the working fluid in the pressure accumulation line 24 reaches the low set pressure. A low-level pressure switch 28L, which is actuated when the high-level pressure switch 28H is actuated, and a shut-off valve 28V which is normally open and closed when the high-level pressure switch 28H is actuated are provided. As a result, when the pressure of the working fluid in the pressure accumulation line 24 reaches the set pressure of the accumulator 25, the high pressure switch 28H is actuated and the motor 20 of the pump 21 is stopped by a control device (not shown). While the shut-off valve 28V is closed when the command is output, when the pressure drops below the set pressure of the accumulator 25, the low pressure switch 28L operates and the motor 20 of the pump 21 is controlled. The shut-off valve 28V is opened when a drive command is output from the device.

A drain line 29 for draining the working fluid from the accumulator 25 to the tank 15 at the time of maintenance or the like is connected to the middle of the pressure accumulation line 24. The drain line 29 is provided with a manual on-off valve that is opened and closed by an operator. 30 are provided.

Next, the operation of the above embodiment will be described.

As shown in FIG. 2, when the solenoid valve 23 of the fluid pressure unit 14 is switched to the brake release position 23B, the pressure-feeding line 16 and the rod-side line 18 communicate with each other, so that the working fluid pressure-fed by the pump 21 becomes a fluid. The working fluid in the cap side chamber 13 c of the fluid pressure cylinder 13 is discharged to the tank 15 by connecting the cap side line 17 and the return line 19 while being introduced into the rod side chamber 13 d of the pressure cylinder 13 . As a result, the piston rod 13b moves in the direction of contraction inside the fluid pressure cylinder 13, the pressing frame 50 is lifted upward, and the brake pad 12 integrated with the pressing frame 50 moves against the running wheel rolling surface 4a of the rail 4. , the braking is released, and the container crane 1 can travel.

On the other hand, when the solenoid valve 23 of the fluid pressure unit 14 is switched from the state shown in FIG. 2 to the brake operating position 23A as shown in FIG. While the working fluid pressure-fed by the pump 21 is introduced into the cap-side chamber 13c of the fluid pressure cylinder 13, the rod-side line 18 and the return line 19 are communicated with each other, whereby the working fluid in the rod-side chamber 13d of the fluid pressure cylinder 13 flows. It is discharged to tank 15 . As a result, the piston rod 13b of the fluid pressure cylinder 13 moves in a projecting direction to push down the pressing frame 50, and the brake pad 12 integrated with the pressing frame 50 is pressed against the traveling wheel rolling surface 4a of the rail 4. Braking takes place.

When the pressure of the working fluid in the pressure accumulation line 24 reaches the high set pressure of the accumulator 25, the high pressure switch 28H is actuated and the motor 20 of the pump 21 is controlled by a control device (not shown). A stop command is output and the shutoff valve 28V is closed. On the other hand, when the pressure drops below the low-level set pressure of the accumulator 25, the low-level pressure switch 28L is actuated, and a drive command is output from the control device to the motor 20 of the pump 21, and the shutdown is performed. Off valve 28V opens. As a result, the accumulator 25 is constantly accumulated at a pressure between the high set pressure and the low set pressure. Moreover, the solenoid valve 23 is switched to the brake operating position 23A mechanically by spring force when the solenoid is de-energized at the time of emergency stop or power failure. The shut-off valve 28V is normally open and is open during an emergency stop and power failure. Therefore, during an emergency stop or a power failure, the working fluid accumulated in the accumulator 25 is guided from the pressure accumulation line 24 through the cap side line 17 to the cap side chamber 13c of the fluid pressure cylinder 13, and the piston rod 13b protrudes. , and the brake pad 12 is pressed against the running wheel rolling surface 4 a of the rail 4 . As a result, even if the pump 21 stops during an emergency stop or power failure, the brake can be operated.

Here, in general, the fluid pressure cylinder 13 is configured such that the back side of the cylinder main body 13a is pin-connected to the base member, and the tip of the piston rod 13b is pin-connected to the member to be driven. . However, such a pin connection structure inevitably increases the total length, which inevitably increases restrictions on the installation location.

On the other hand, in the case of the present embodiment, the rear side of the cylinder main body 13a of the fluid pressure cylinder 13 is fixed to the lower surface of the support bracket 52 by the fastening member 80, although the elastic member 60 and the metal plate 70 are interposed therebetween. The tip of the piston rod 13b suspended from the cylinder main body 13a is screwed into the pressing frame 50 and fixed by a nut 90, and a pin connection structure is not adopted. Therefore, the structure is very advantageous in terms of shortening the overall length.

As a result, when modifying a track traveling machine such as an existing container crane 1, under the lower frame 6a (see FIG. 1) connecting the support legs 6 of the crane body 5, as described in Patent Document 2, Even if a conventional braking device cannot be provided, it is possible to provide a braking mechanism 40 in the lower portion of the travel device 8 .

On the other hand, if the pin connection structure is not employed, a bending force acts on the piston rod 13b of the fluid pressure cylinder 13 when the braking mechanism 40 is actuated. However, since the bending force acting on the piston rod 13b of the fluid pressure cylinder 13 is absorbed by the elastic member 60, the fluid pressure cylinder 13 does not malfunction, and the service life of the fluid pressure cylinder 13 is prevented from being shortened. be done. Further, by providing the metal plate 70 between the elastic member 60 and the fluid pressure cylinder 13 , the load acting on the fluid pressure cylinder 13 can be uniformly distributed and transmitted to the elastic member 60 . Furthermore, since the bending force is absorbed by the elastic member 60 and the mounting accuracy of the fluid pressure cylinder 13 to the support bracket 52 is no longer strictly required, machining of the surface of the support bracket 52 becomes unnecessary, leading to cost reduction. It will happen.

In this way, restrictions on the installation location during remodeling can be eliminated, and the degree of freedom in installation can be increased.

FIG. 5 shows a reference example of a braking device for a track traveling machine according to the present invention. 1 to 4, respectively.

In the case of this reference example, a pedestal 65 made of an elastic member such as chloroprene rubber is provided on the upper surface side of the support bracket 52, and the fluid pressure cylinder 13 is secured by tightening the fastening member 80 through the pedestal 65. It is fixed to the lower surface of the support bracket 52 .

Next, the operation of the reference example will be described.

In this reference example, although the overall length is increased by the amount of the pedestal 65, the elastic member 60 absorbs the bending force acting on the piston rod 13b of the fluid pressure cylinder 13 when the braking mechanism 40 is actuated. At the same time, the pedestal 65 also absorbs it, and the movable range of the fluid pressure cylinder 13 is expanded.

Since the other functions are the same as those of the embodiment shown in FIGS. 1 to 4, description thereof will be omitted.

In the embodiment shown in FIGS. 1 to 4, the elastic member 60 includes the lower surface of the support bracket 52 projecting from the lower equalizer beam 9c as the lower equalizer beam, and the fastening member attached to the lower surface of the support bracket 52. The piston rod 13b of the fluid pressure cylinder 13 is interposed between the rear surface of the cylinder body 13a of the fluid pressure cylinder 13 and fixed at 80, and the tip end of the piston rod 13b of the fluid pressure cylinder 13 is screwed into the pressing frame 50. With this configuration, it is possible to eliminate the need to employ a pin connection structure for installing the fluid pressure cylinder 13 , shorten the overall length, and provide the brake mechanism 40 in the lower portion of the travel device 8 .

1 to 4, a metal plate 70 is interposed between the elastic member 60 and the back surface of the cylinder main body 13a of the fluid pressure cylinder 13. As shown in FIG. With this configuration, the load acting on the fluid pressure cylinder 13 can be uniformly distributed and transmitted to the elastic member 60 .

The brake system for a track traveling machine according to the present invention is not limited to the above-described embodiments, and can be modified in various ways without departing from the scope of the present invention.

1 Container crane (orbital traveling machine)
2 Harbor 3 Quay 4 Rail 4a Traveling Wheel Rolling Surface 5 Crane Main Body 6 Supporting Leg 6a Lower Frame 7 Traveling Wheel 8 Traveling Device 9A Equalizer Device 9B Equalizer Device 9a Upper Equalizer Beam (Upper Equalizer Beam)
9b middle equalizer beam (lower equalizer beam (upper equalizer beam))
9c lower equalizer beam (lower equalizer beam)
9cp plate material 9cq plate material 10a rocker pin 10b rocker pin 10c rocker pin 12 brake pad 13 fluid pressure cylinder 13a cylinder body 13b piston rod 13c cap side chamber 13d rod side chamber 14 fluid pressure unit 15 tank 16 pumping line 17 cap side line 18 rod side line 19 Return line 20 Motor 21 Pump 22 Check valve 23 Solenoid valve 23A Brake application position 23B Brake release position 24 Pressure accumulation line 25 Accumulator 26 Relief line 27 Relief valve 28H High pressure switch 28L Low pressure switch 28V Shutoff valve 29 Drain line 30 Manual opening/closing Valve 40 Braking mechanism 50 Pressing frame 51 Fixed frame 51a Stopper 52 Support bracket 60 Elastic member 65 Base 70 Metal plate 80 Fastening member 90 Nut

Claims (3)

An upper equalizer beam, which is swingably arranged at the lower part of a support leg that runs on the rail and whose intermediate part is supported by a rocker pin that extends in a horizontal direction perpendicular to the running direction, and both ends of the upper equalizer beam in the running direction. At least one equalizer device consisting of a pair of lower equalizer beams arranged swingably with the middle portion supported by rocker pins extending in the horizontal direction perpendicular to the running direction, and the equalizer device at the lowest stage. A braking device for a track traveling machine equipped with a traveling device in which traveling wheels that can freely roll along rails are arranged at both ends of the lower equalizer beam in the traveling direction in
a pressing frame disposed between the lower equalizer beam and the rail of the lowermost equalizer device so as to protrude in the horizontal direction orthogonal to the rail; both ends of the pressing frame in the horizontal direction orthogonal to the rail; A braking mechanism having a fluid pressure cylinder interposed between both side surfaces of a lower equalizer beam in the lowermost equalizer device and for raising and lowering the pressing frame, and a brake pad attached to the lower surface of the pressing frame,
A braking device for a track traveling machine, wherein the fluid pressure cylinder is fixed via an elastic member that absorbs a bending force acting on a piston rod of the fluid pressure cylinder. The elastic member is interposed between the lower surface of the support bracket projecting from the lower equalizer beam and the back surface of the cylinder body of the fluid pressure cylinder fixed to the lower surface of the support bracket with a fastening member,
2. A braking device for a track traveling machine according to claim 1, wherein a tip portion of a piston rod of said fluid pressure cylinder is screwed into said pressing frame. 3. A braking device for a track traveling machine according to claim 2, further comprising a metal plate interposed between said elastic member and a back surface of a cylinder body of said fluid pressure cylinder.

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