JP7042070B2 - Braking device for orbiting machines - Google Patents

Description

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

FIG. 10 shows an example of a container crane as a general track-traveling machine, where 1 is a container crane, 2 is a port where a container crane 1 is deployed, 3 is a quay in a port 2, and 4 is a quay 3. It is a rail laid so as to extend in a direction orthogonal to the paper surface of FIG. 10, and a traveling device 8 having traveling wheels 7 that can roll along the rail 4 on the support legs 6 of the crane body 5 of the container crane 1. Is attached.

If the container crane 1 is blown by a strong wind during cargo handling work, the traveling of the container crane 1 does not stop against the intention of the driver and runs away, which may cause a collision or collapse with an adjacent machine or a nearby structure. ..

Therefore, as a device for preventing the escape of the track traveling machine as described above, there is a clamp device as disclosed in, for example, Patent Document 1 in the past. The clamp device includes a pinching mechanism in which a pair of contacts having a pinching portion formed at the tip thereof are connected so that a substantially intermediate portion thereof is rotatable about an axis, and a base end of the contact in the pinching mechanism. A spring mechanism provided in the portion and narrowing between the base ends of the contacts so that the sandwich always rotates the contact in the closing direction in which the rail is sandwiched, and the base end of the pair of contacts. It is provided with a rotary cam for driving the cam receiving portion formed in the above in a direction of pushing open from the inside thereof and releasing the pinching of the rail by the sandwiching portion.

However, since the clamp device disclosed in Patent Document 1 employs a method of sandwiching the rail from both sides, jagged teeth may be provided on the contact surface on the clamp device side in order to increase the coefficient of friction with the rail surface. Or, if the contact surface is hardened to make it look like a friction, there is a possibility that the side surface of the rail will be scratched. In addition, if the accuracy of the side surface of the rail is low and the dimensions from the center line to the side surface in the width direction vary from side to side, or if the rail is corroded, it is pinched by the pinching portion. However, the tightening force may be significantly reduced and a sufficient holding force may not be obtained.

In order to solve such a problem, a braking device equipped with a fluid pressure cylinder such as a hydraulic cylinder capable of pressing and separating the brake pad in a direction orthogonal to the rolling surface of the traveling wheel of the rail has been developed (for example, Patent Document). 2).

Japanese Unexamined Patent Publication No. 6-72690 JP-A-2015-58805

By the way, in recent years, in an orbital traveling machine such as the container crane 1, there is an increasing demand for a braking device to be provided below the traveling device 8. This is because the load input point by the fluid pressure cylinder and the position where the braking force is generated are brought close to each other to reduce the generation of the moment with respect to the fluid pressure cylinder and to make the structure advantageous in terms of strength.

Here, when a braking device is to be provided in the lower part of the traveling device 8, the fluid is applied to the lower surface of a flat plate-shaped base plate attached so as to hang over the bottom surface side of the lower equalizer beam composed of two plates. A cylinder body of the pressure cylinder is attached, and a brake pad is connected to the piston rod of the fluid pressure cylinder so as to be freely pressed and separated from the traveling wheel rolling surface of the rail 4 in a direction orthogonal to the rail 4. Become.

However, when the fluid pressure cylinder is extended and driven so that the brake pad is pressed against the rolling surface of the traveling wheel of the rail 4 in a direction orthogonal to the rail 4, the base plate is bent by the reaction force, and the above-mentioned The axis of the fluid pressure cylinder may be displaced from the vertical direction, a load may be applied to the fluid pressure cylinder, and the fluid pressure cylinder may malfunction.

The present invention has been made in view of the above-mentioned conventional problems. Braking of a track-traveling machine capable of reducing the generation of a moment with respect to a fluid pressure cylinder to form a structure advantageous in terms of strength and facilitating operation. It is intended to provide a device.

In order to achieve the above object, in the braking device of the track-traveling machine of the present invention, the intermediate portion is supported by a rocker pin extending in the horizontal direction perpendicular to the traveling direction at the lower part of the support leg traveling on the rail and shaken. A pair of movably arranged upper equalizer beams and a pair of swingably arranged upper equalizer beams whose intermediate portions are supported by rocker pins extending in a horizontal direction perpendicular to the traveling direction at both ends of the traveling direction. It has at least one stage of an equalizer device consisting of a lower equalizer beam, and is equipped with a traveling device in which traveling wheels that can roll along a rail are arranged at both ends of the lower equalizer beam in the traveling direction in the lowermost equalizer device. It is a braking device for orbital traveling machines.
The lower equalizer beam in the lowermost equalizer device is configured by arranging a plurality of plate members at required intervals in the width direction of the rail.
A fixed frame provided on the lower surface of the lower equalizer beam and a plurality of fluid pressure cylinders arranged on the lower surface side of the fixed frame so as to correspond to a position directly under the plate material of the lower equalizer beam can be freely moved up and down. It is provided with a provided pressing frame and a transmission frame suspended from the lower surface side of the pressing frame and having a brake pad attached to the lower surface.
The pressing frame may be formed of a tensile rigid member on the upper surface side and a compressive rigid member on the lower surface side , the tensile rigid member may be made of carbon fiber reinforced plastic, and the compressive rigid member may be made of steel or ceramics. can.

In the braking device of the track traveling machine, a curved concave surface is formed on the lower surface of the pressing frame, and the curved convex surface to which the curved concave surface is in close contact when the pressing frame is deformed by applying a load from the fluid pressure cylinder is the transmission frame. It can be formed on the upper surface.

In the braking device of the track-traveling machine, an absorption mechanism that allows the axis of the fluid pressure cylinder to tilt when the pressing frame is deformed and absorbs the load on the fluid pressure cylinder.
A braking release mechanism interposed between the fixed frame and the pressing frame and urging the pressing frame in a direction in which the brake pad separates from the rail.
A fluid pressure unit that can freely supply and discharge the working fluid to the cylinder chamber of the fluid pressure cylinder and that extends the fluid pressure cylinder against the urging force of the braking release mechanism when the working fluid is supplied can be provided.

In the braking device of the track-traveling machine, the absorption mechanism is
A convex spherical surface formed on the end face of the cylinder body of the fluid pressure cylinder and the end face of the piston,
The fixed frame and the concave spherical surface formed on the pressing frame may be provided so that the convex spherical surface is slidably engaged.

In the braking device of the track-traveling machine, the braking release mechanism is
A connecting rod that connects the pressing frame to the fixed frame so that it can move close to and away from each other.
The connecting rod may be provided with a compression spring that is flexibly fitted and urges the fixed frame in a direction that brings the pressing frame closer to the fixed frame.

According to the braking device of the orbital traveling machine of the present invention, it is possible to reduce the generation of a moment with respect to the fluid pressure cylinder to form a structure advantageous in terms of strength, and it is possible to exert an excellent effect of facilitating the operation.

It is a front view which shows the 1st Embodiment of the braking device of the track traveling type machine of this invention. It is a schematic block diagram which shows the 1st Embodiment of the braking device of the track traveling type machine of this invention, and is the figure which shows the state which the braking is released. It is a top view which shows the 1st Embodiment of the braking device of the track traveling type machine of this invention, and is the figure corresponding to the arrow III-III of FIG. It is sectional drawing which shows the joining structure of the transmission frame with respect to the pressing frame of the pressing mechanism in the 1st Embodiment of the braking device of the track traveling type machine of this invention. It is a schematic block diagram which shows the 1st Embodiment of the braking device of the track traveling type machine of this invention, and is the figure which shows the state which brake is performed. It is a schematic block diagram which shows the 2nd Embodiment of the braking device of the track traveling type machine of this invention, and is the figure which shows the state which the braking is released. It is a top view which shows the 2nd Embodiment of the braking device of the track traveling type machine of this invention, and is the VII-VII arrow-viewing equivalent view of FIG. It is sectional drawing which shows the joining structure of the transmission frame with respect to the pressing frame of the pressing mechanism in the 2nd Embodiment of the braking device of the track traveling type machine of this invention. It is a schematic block diagram which shows the 2nd Embodiment of the braking device of the track traveling type machine of this invention, and is the figure which shows the state which brake is performed. It is an overall side view which shows an example of a container crane as an orbital traveling machine.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

1 to 5 are the first embodiments of the braking device of the track-traveling machine of the present invention, and in the drawings, the parts with the same reference numerals as those in FIG. 10 represent the same objects.

In the container crane 1 as a track traveling machine shown in FIG. 1, a lower frame 6a extending along a rail 4 so as to connect the support legs 6 is provided between the support legs 6 of the crane main body 5, and the lower frame 6a is provided with a lower frame 6a. A plurality of traveling devices 8 (two in the example of FIG. 1) 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.

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

The traveling wheels 7 are arranged at both ends of the lower equalizer beam 9c in the traveling direction so as to be rollable along the rail 4.

In the example shown in FIG. 1, an equalizer device 9A composed of an upper equalizer beam 9a and an intermediate equalizer beam 9b, and an equalizer device 9B composed of an intermediate equalizer beam 9b and a lower equalizer beam 9c are formed in two upper and lower stages. Has been done. Incidentally, the upper equalizer beam 9a in the equalizer device 9A in the upper stage becomes the upper equalizer beam, and the intermediate equalizer beam 9b becomes the lower equalizer beam. Further, the intermediate portion equalizer beam 9b in the lower equalizer device 9B is a relatively upper equalizer beam, and the lower equalizer beam 9c is a lower equalizer beam. However, depending on the scale of the container crane 1 as the track traveling machine, the equalizer device 9A is formed in only one stage, and the traveling wheels 7 are arranged on the lower equalizer beam (in this case, the intermediate equalizer beam 9b). You may. Further, the equalizer device may be formed in three or more upper and lower stages, and traveling wheels 7 capable of rolling along the rail 4 may be arranged at both ends of the lower equalizer beam in the traveling direction in the lowermost equalizer device.

The lower equalizer beam 9c (lower equalizer beam) is configured by arranging a plurality of plates (two in the examples of FIGS. 2 and 3) 9 cp of plate materials at required intervals in the width direction of the rail 4. ing.

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 braking mechanism 40 may be one as long as a sufficient braking force can be obtained.

The braking mechanism 40 is attached to a lower equalizer beam 9c (lower equalizer beam) in which the traveling wheel 7 is arranged, and has a fluid pressure cylinder 13 and a frame 50 as shown in FIG.

The frame 50 of the braking mechanism 40 includes a fixed frame 51, a pressing frame 52, and a transmission frame 53.

The fixed frame 51 is provided on the lower surface of the lower equalizer beam 9c (lower equalizer beam) in the lowermost equalizer device.

The pressing frame 52 is arranged on the lower surface side of the fixed frame 51 so as to be able to move up and down via the fluid pressure cylinder 13. The upper surface side of the pressing frame 52 is formed of the tensile rigidity member 52A, and the lower surface side of the pressing frame 52 is formed of the compression rigidity member 52B. As the tensile rigidity member 52A, for example, carbon fiber reinforced plastics (CFRP: Carbon Fiber Reinforced Plastics) can be adopted, and as the compression rigidity member 52B, for example, a steel material or ceramics can be adopted.

The transmission frame 53 is suspended from the lower surface side of the pressing frame 52, and the brake pad 12 is attached to the lower surface side. As shown in FIG. 3, holes 53b are formed in the four corners of the transmission frame 53, and the reamer pin 54 is loosely fitted into the holes 53b as shown in FIG. 4, and the tip screw portion of the reamer pin 54 is fitted. By screwing 54b into the lower surface of the pressing frame 52, the transmission frame 53 is supported so as to be suspended from the lower surface side of the pressing frame 52 by the head 54a located at the lower end of the reamer pin 54. Incidentally, the reason for this configuration is that if the pressing frame 52 is formed of the tensile rigid member 52A and the compressive rigid member 52B, it is possible to suppress the deformation of the pressing frame 52 when the fluid pressure cylinder 13 is operated. However, since the amount of deformation is not completely eliminated, the deformation of the pressing frame 52 can be tolerated.

Further, an absorption mechanism 60 is provided between the fixed frame 51 and the pressing frame 52 of the braking mechanism 40 and the fluid pressure cylinder 13. The absorption mechanism 60 forms convex spherical surfaces 61 and 62 on the end surface of the cylinder body 13a of the fluid pressure cylinder 13 and the end surface of the piston 13b, and the convex spherical surfaces 61 and 62 are slidably engaged with each other. It has a structure in which concave spherical surfaces 63 and 64 are formed on the pressing frame 52 and the fixed frame 51. Incidentally, the reason for this configuration is the same as described above, because the amount of deformation of the pressing frame 52 during operation of the fluid pressure cylinder 13 is not completely eliminated, so that the absorption mechanism 60 deforms the pressing frame 52. This is to allow the axis of the fluid pressure cylinder 13 to tilt at times so that the load on the fluid pressure cylinder 13 can be absorbed.

A braking release mechanism 70 is interposed between the fixed frame 51 and the pressing frame 52. The braking release mechanism 70 includes a connecting rod 71 and a compression spring 72. The connecting rod 71 is adapted to connect the pressing frame 52 to the fixed frame 51 so as to be close to and detachable from each other. The compression spring 72 is flexibly fitted to the connecting rod 71 and is urged in a direction in which the pressing frame 52 is brought close to the fixed frame 51. As a result, the braking release mechanism 70 urges the pressing frame 52 in a direction in which the brake pad 12 separates from the rail 4. As shown in FIG. 3, the connecting rod 71 is loosely fitted in the four corners of the fixed frame 51 and the pressing frame 52. Incidentally, the reason for this configuration is also the same as described above, since the amount of deformation of the pressing frame 52 during operation of the fluid pressure cylinder 13 is not completely eliminated, so that the deformation of the pressing frame 52 can be tolerated. Because.

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

The fluid pressure unit 14 is capable of supplying and discharging the working fluid to the cylinder chamber 13c of the fluid pressure cylinder 13, and extends the fluid pressure cylinder 13 against the urging force of the braking release mechanism 70 when the working fluid is supplied. The configuration is described in detail below.

The fluid pressure unit 14 includes a pressure feed line 16 extending from a tank 15 in which the working fluid is stored, a supply / discharge line 17 connected to a cylinder chamber 13c of the fluid pressure cylinder 13, and a return line 19 leading to the tank 15. And have. A pump 21 driven by the motor 20 and a check valve 22 for blocking the backflow of the working fluid pumped by the pump 21 are provided in the middle of the pressure feeding line 16. The pressure feed line 16 and the return line 19 and the supply / discharge line 17 are connected via a solenoid valve 23, and a pressure accumulator line branched from the middle of the pressure feed line 16 between the check valve 22 and the solenoid valve 23. An accumulator 25 is connected to 24.

The solenoid valve 23 has a brake operating position 23A and a brake releasing position 23B. As shown in FIG. 5, the brake operating position 23A introduces the working fluid pumped by the pump 21 into the cylinder chamber 13c of the fluid pressure cylinder 13 by communicating the pressure feeding line 16 and the supply / discharge line 17. It is a position. As shown in FIG. 2, the brake release position 23B operates the cylinder chamber 13c of the fluid pressure cylinder 13 by communicating the supply / discharge line 17 and the return line 19 while sealing the pressure feed line 16. It is a position to discharge the fluid to the tank 15. The solenoid valve 23 is stopped from being energized to the solenoid during an emergency stop (during an urgent intentional power failure) and during a power failure, and is mechanically switched to the brake operating position 23A by a spring force. ing.

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

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

A drain line 29 for draining the working fluid of the accumulator 25 to the tank 15 is connected in the middle of the accumulator line 24, and a manual on-off valve opened / closed by an operator is connected to the drain line 29. 30 is provided.

Next, the operation of the first 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 supply / discharge line 17 and the return line 19 communicate with each other, and the urging force of the compression spring 72 of the braking release mechanism 70 causes the supply / discharge line 17 to communicate with each other. The pressing frame 52 moves in a direction closer to the fixed frame 51 (in an ascending direction), and the working fluid in the cylinder chamber 13c of the fluid pressure cylinder 13 is discharged to the tank 15. As a result, the piston 13b of the fluid pressure cylinder 13 moves in the contracting direction, and the brake pad 12 integrated with the transmission frame 53 suspended from the pressing frame 52 separates from the traveling wheel rolling surface 4a of the rail 4. The braking is released and the container crane 1 can run. The pumping line 16 of the fluid pressure unit 14 is sealed by the solenoid valve 23 switched to the brake release position 23B, and the working fluid pumped by the pump 21 is sent from the relief line 26 via the relief valve 27. It is returned to the tank 15 and circulated.

On the other hand, when the solenoid valve 23 of the fluid pressure unit 14 is switched to the brake operation position 23A from the state shown in FIG. 2, as shown in FIG. 5, the pumping line 16 and the supply / discharge line 17 communicate with each other. The working fluid pressure-fed by the pump 21 is introduced into the cylinder chamber 13c of the fluid pressure cylinder 13. As a result, the piston 13b of the fluid pressure cylinder 13 moves in the protruding direction, the pressing frame 52 is pushed down against the urging force of the compression spring 72 of the braking release mechanism 70, and the brake pad 12 integrated with the transmission frame 53. Is pressed against the traveling wheel rolling surface 4a of the rail 4, and braking is performed.

Here, when the brake pad 12 is pressed against the traveling wheel rolling surface 4a of the rail 4, the pressing frame 52 tries to bend, but the upper surface side of the pressing frame 52 is a tensile rigid member such as carbon fiber reinforced plastic. Since it is formed of 52A and the lower surface side is formed of a compression rigid member 52B such as a steel material or ceramics, the load is transmitted from the fluid pressure cylinder 13 to the brake pad 12 while the deformation of the pressing frame 52 is minimized. To.

When the pressure of the working fluid in the accumulator line 24 reaches the high set pressure of the accumulator 25, the high pressure switch 28H is activated to operate the motor 20 of the pump 21 from a control device (not shown). A stop command is output and the shutoff valve 28V closes. On the other hand, when the pressure drops below the low set pressure of the accumulator 25, the low pressure switch 28L is activated, a drive command is output from the control device to the motor 20 of the pump 21, and the shut is shut. The off valve 28V opens. As a result, the accumulator 25 is constantly stored in a pressure between the high set pressure and the low set pressure. Moreover, the solenoid valve 23 is adapted to mechanically switch to the brake operating position 23A by a spring force by stopping the energization of the solenoid during an emergency stop or a power failure. Further, the shut-off valve 28V is always open (normally open) and is open at the time of emergency stop and power failure. Therefore, in the event of an emergency stop or a power failure, the working fluid accumulated in the accumulator 25 is guided from the accumulator line 24 to the cylinder chamber 13c of the fluid pressure cylinder 13 via the supply / discharge line 17 in the direction in which the piston 13b protrudes. The brake pad 12 moves and is pressed against the traveling wheel rolling surface 4a of the rail 4. As a result, even if the pump 21 is stopped during an emergency stop or a power failure, the brake can be operated.

In the case of the first embodiment, even if the fluid pressure cylinder 13 is extended and driven and the brake pad 12 is operated so as to be pressed against the traveling wheel rolling surface 4a of the rail 4 in a direction orthogonal to the rail 4, the fluid is fluidized. As shown in FIGS. 2 and 3, a plurality (two) of the pressure cylinders 13 are arranged so as to correspond to the positions directly below the plate material 9cp of the lower equalizer beam 9c (lower equalizer beam), and therefore the reaction force thereof. The base plate 11 does not bend. As a result, it is possible to prevent the axis of the fluid pressure cylinder 13 from being displaced from the vertical direction, the load is not applied to the fluid pressure cylinder 13, and there is a concern that the fluid pressure cylinder 13 operates smoothly and causes malfunction. Is gone.

Further, although the pressing frame 52 is inevitably bent, the upper surface side of the pressing frame 52 is formed of a tensile rigid member 52A such as carbon fiber reinforced plastic, and the lower surface side is formed of a compressive rigid member 52B such as steel material or ceramics. Since it is formed, the load is transmitted from the fluid pressure cylinder 13 to the brake pad 12 while the deformation of the pressing frame 52 is minimized, so that the influence of the bending of the pressing frame 52 is transmitted to the brake pad 12. It is difficult, and it is difficult for the brake pad 12 to hit the rail 4 on one side.

Further, even if the pressing frame 52 is deformed, the convex spherical surfaces 61 and 62 of the absorption mechanism 60 formed on the end surface of the cylinder body 13a of the fluid pressure cylinder 13 and the end surface of the piston 13b are fixed to the pressing frame 52. It slides on the concave spherical surfaces 63 and 64 formed on the frame 51. Therefore, tilting of the axis of the fluid pressure cylinder 13 is allowed by the absorption mechanism 60, and it is possible to avoid applying a load to the fluid pressure cylinder 13.

As a result, it is possible to meet the demand for providing a braking device at the lower part of the traveling device 8 in the track traveling type machine such as the container crane 1 in recent years, and the load input point and the braking force are generated by the fluid pressure cylinder 13. By moving the positions closer to each other, it is possible to reduce the generation of a moment with respect to the fluid pressure cylinder 13 and to form a structure advantageous in terms of strength.

In this way, the generation of a moment with respect to the fluid pressure cylinder 13 can be reduced to form a structure advantageous in terms of strength, and the operation can be facilitated.

6 to 9 show the second embodiment of the braking device of the track-traveling machine of the present invention, and in the drawings, the parts with the same reference numerals as those in FIGS. 1 to 5 represent the same objects, and are basic. The configuration is the same as that of the first embodiment shown in FIGS. 1 to 5.

In the second embodiment, the curved concave surface 52a is formed on the lower surface of the pressing frame 52 formed by the tensile rigid member 52A and the compressive rigid member 52B, and the load from the fluid pressure cylinder 13 is formed on the upper surface of the transmission frame 53. It is characterized in that a curved convex surface 53a is formed in which the curved concave surface 52a is in close contact when the pressing frame 52 is deformed by the application.

Since the other basic configurations are the same as those of the first embodiment shown in FIGS. 1 to 5, the description thereof will be omitted.

Incidentally, since the pressing frame 52 is formed of the tensile rigid member 52A and the compressive rigid member 52B, the actual amount of deformation of the pressing frame 52 is smaller than that of the case where the pressing frame 52 is formed of a single member. However, for the sake of explanation, FIG. 9 exaggerates the deformation of the pressing frame 52.

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

As shown in FIG. 6, when the solenoid valve 23 of the fluid pressure unit 14 is switched to the brake release position 23B, the supply / discharge line 17 and the return line 19 communicate with each other, and the urging force of the compression spring 72 of the braking release mechanism 70 causes the supply / discharge line 17 to communicate with each other. The pressing frame 52 moves in a direction closer to the fixed frame 51 (in an ascending direction), and the working fluid in the cylinder chamber 13c of the fluid pressure cylinder 13 is discharged to the tank 15. As a result, the piston 13b of the fluid pressure cylinder 13 moves in the contracting direction, and the brake pad 12 integrated with the transmission frame 53 suspended from the pressing frame 52 separates from the traveling wheel rolling surface 4a of the rail 4. The braking is released and the container crane 1 can run. The pumping line 16 of the fluid pressure unit 14 is sealed by the solenoid valve 23 switched to the brake release position 23B, and the working fluid pumped by the pump 21 is sent from the relief line 26 via the relief valve 27. It is returned to the tank 15 and circulated.

On the other hand, when the solenoid valve 23 of the fluid pressure unit 14 is switched to the brake operating position 23A from the state shown in FIG. 6, as shown in FIG. 9, the pumping line 16 and the supply / discharge line 17 communicate with each other. The working fluid pressure-fed by the pump 21 is introduced into the cylinder chamber 13c of the fluid pressure cylinder 13. As a result, the piston 13b of the fluid pressure cylinder 13 moves in the protruding direction, the pressing frame 52 is pushed down against the urging force of the compression spring 72 of the braking release mechanism 70, and the brake pad 12 integrated with the transmission frame 53. Is pressed against the traveling wheel rolling surface 4a of the rail 4, and braking is performed.

Here, when the brake pad 12 is pressed against the traveling wheel rolling surface 4a of the rail 4, the pressing frame 52 tries to bend, but the upper surface side of the pressing frame 52 is a tensile rigid member such as carbon fiber reinforced plastic. Since it is formed of 52A and the lower surface side is formed of a compression rigidity member 52B such as a steel material or ceramics, deformation of the pressing frame 52 is minimized. However, since the amount of deformation of the pressing frame 52 during operation of the fluid pressure cylinder 13 is not completely eliminated, when the brake pad 12 is pressed against the traveling wheel rolling surface 4a of the rail 4, the pressing frame 52 is very small. However, it bends so that the curved concave surface 52a of the pressing frame 52 comes into close contact with the curved convex surface 53a of the transmission frame 53. Therefore, the load is transmitted from the fluid pressure cylinder 13 to the brake pad 12 while the deformation of the pressing frame 52 is absorbed.

In the case of the second embodiment, even if the fluid pressure cylinder 13 is extended and driven and the brake pad 12 is operated so as to be pressed against the traveling wheel rolling surface 4a of the rail 4 in a direction orthogonal to the rail 4, the fluid is fluidized. As shown in FIGS. 6 and 7, a plurality (two) of the pressure cylinders 13 are arranged so as to correspond to the positions directly below the plate material 9cp of the lower equalizer beam 9c (lower equalizer beam), and therefore the reaction force thereof. The base plate 11 does not bend. As a result, it is possible to prevent the axis of the fluid pressure cylinder 13 from being displaced from the vertical direction, the load is not applied to the fluid pressure cylinder 13, and there is a concern that the fluid pressure cylinder 13 operates smoothly and causes malfunction. Is gone.

Further, although the pressing frame 52 is inevitably bent, the upper surface side of the pressing frame 52 is formed of a tensile rigid member 52A such as carbon fiber reinforced plastic, and the lower surface side is formed of a compressive rigid member 52B such as steel material or ceramics. Since it is formed, the deformation of the pressing frame 52 is minimized. In addition to this, in the second embodiment, even if the pressing frame 52 is slightly bent, the curved concave surface 52a of the pressing frame 52 is in close contact with the curved convex surface 53a of the transmission frame 53, and the pressing frame 52 Since the load is transmitted from the fluid pressure cylinder 13 to the brake pad 12 while the deformation is absorbed, the influence of the bending of the pressing frame 52 is not transmitted to the brake pad 12, and the one-sided contact of the brake pad 12 with respect to the rail 4 occurs. There is no worry that it will occur.

Further, when the pressing frame 52 is deformed, as shown in FIG. 9, the convex spherical surfaces 61 and 62 of the absorption mechanism 60 formed on the end surface of the cylinder body 13a of the fluid pressure cylinder 13 and the end surface of the piston 13b press the pressing frame 52. It slides on the concave spherical surfaces 63 and 64 formed on the frame 52 and the fixed frame 51. Therefore, tilting of the axis of the fluid pressure cylinder 13 is allowed by the absorption mechanism 60, and it is possible to avoid applying a load to the fluid pressure cylinder 13.

As a result, in the second embodiment as well as in the first embodiment, it is possible to meet the demand for providing a braking device at the lower part of the traveling device 8 in the track traveling type machine such as the container crane 1 in recent years. By bringing the load input point of the fluid pressure cylinder 13 and the position where the braking force is generated close to each other, it is possible to reduce the generation of the moment with respect to the fluid pressure cylinder 13 and to obtain a structure advantageous in terms of strength.

In this way, in the second embodiment, while suppressing the deformation of the pressing frame 52 itself, it is possible to eliminate the influence of the deformation on the brake pad 12, and the generation of a moment on the fluid pressure cylinder 13 is reduced to improve the strength. It can be an advantageous structure, and the operation can be further facilitated.

It should be noted that the braking device for the track-traveling machine of the present invention is not limited to the above-described embodiment, and it is needless to say that various modifications can be made without departing from the gist of the present invention.

1 Container crane (track traveling machine)
2 Port 3 Quay 4 Rail 4a Traveling wheel rolling surface 5 Crane body 6 Support 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 10a Rocker pin 10b Rocker pin 10c Rocker pin 11 Base plate 12 Brake pad 13 Fluid pressure cylinder 13a Cylinder body 13b Piston 13c Cylinder chamber 14 Fluid pressure unit 15 Tank 16 Pumping line 17 Supply / discharge line 19 Return line 20 Motor 21 Pump 22 Reverse Stop valve 23 Solvent valve 23A Brake operation position 23B Brake release position 24 Accumulator 26 Accumulator 26 Relief line 27 Relief valve 28H High pressure switch 28L Low pressure switch 28V Shut-off valve 29 Drain line 30 Manual on-off valve 40 Braking mechanism 50 Frame 51 Fixed Frame 52 Pressing frame 52A Tensile rigid member 52B Compressive rigid member 52a Curved concave surface 53 Transmission frame 53a Curved convex surface 53b Hole 54 Reamer pin 54a Head 54b Tip thread 60 Absorption mechanism 61 Convex spherical surface 62 Convex spherical surface 63 Concave spherical surface 64 Concave spherical surface 70 Brake release mechanism 71 Connecting rod 72 Compression spring

Claims (5)

An upper equalizer beam and both ends of the upper equalizer beam in the traveling direction are arranged swingably by supporting the intermediate portion by a rocker pin extending in the horizontal direction perpendicular to the traveling direction at the lower part of the support leg traveling on the rail. The unit has at least one equalizer device consisting of a pair of lower equalizer beams in which the intermediate portion is supported by a rocker pin extending in the horizontal direction perpendicular to the traveling direction and is swingably arranged, and the lowermost equalizer device. A braking device for a track-traveling machine equipped with a traveling device in which traveling wheels that can roll along a rail are arranged at both ends of the lower equalizer beam in the traveling direction.
The lower equalizer beam in the lowermost equalizer device is configured by arranging a plurality of plate members at required intervals in the width direction of the rail.
A fixed frame provided on the lower surface of the lower equalizer beam and a plurality of fluid pressure cylinders arranged on the lower surface side of the fixed frame so as to correspond to a position directly under the plate material of the lower equalizer beam can be freely moved up and down. It is provided with a provided pressing frame and a transmission frame suspended from the lower surface side of the pressing frame and having a brake pad attached to the lower surface.
The pressing frame is formed of a tensile rigid member on the upper surface side and a compressive rigid member on the lower surface side , the tensile rigid member is a carbon fiber reinforced plastic, and the compressive rigid member is a steel material or a ceramic . Braking device. The trajectory according to claim 1 , wherein a curved concave surface is formed on the lower surface of the pressing frame, and a curved convex surface to which the curved concave surface is in close contact is formed on the upper surface of the transmission frame when the pressing frame is deformed by applying a load from the fluid pressure cylinder. Braking device for traveling machines. An absorption mechanism that allows the axis of the fluid pressure cylinder to tilt when the pressing frame is deformed and absorbs the load on the fluid pressure cylinder.
A braking release mechanism interposed between the fixed frame and the pressing frame and urging the pressing frame in a direction in which the brake pad separates from the rail.
The second aspect of claim 2 is provided with a fluid pressure unit that can freely supply and discharge the working fluid to the cylinder chamber of the fluid pressure cylinder and that extends the fluid pressure cylinder against the urging force of the braking release mechanism when the working fluid is supplied. Braking device for track-traveling machines. The absorption mechanism is
A convex spherical surface formed on the end face of the cylinder body of the fluid pressure cylinder and the end face of the piston,
The braking device for a track-traveling machine according to claim 3 , further comprising a fixed frame and a concave spherical surface formed on the pressing frame so that the convex spherical surface is slidably engaged. The braking release mechanism is
A connecting rod that connects the pressing frame to the fixed frame so that it can move close to and away from each other.
The braking device for a track-traveling machine according to claim 3 or 4 , further comprising a compression spring that is elastically fitted to the connecting rod and urges the pressing frame toward the fixed frame.

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