Method and device for controlling rail brakes for track-traveling machines

Abstract

To provide a rail brake control method and device for a track travel type machine that are able to restrict a difference in braking distance to a minimum regardless of a position of a hanging load and are able to reduce a load on a body frame.SOLUTION: A rail brake control device for a track travel type machine includes: a load detector 800 that measures a vertical load (w1 on a land side and w2 on a sea side) acting on a support leg 210; and a control unit 900 by which, based on the vertical load (w1 on the land side, w2 on the sea side) measured by the load detector 800, a control signal (901 on the land side, 902 on the sea side) that increases / decreases a fluid pressure introduced into a fluid pressure cylinder 420 from a fluid pressure unit 430 is output to the fluid pressure unit 430.SELECTED DRAWING: Figure 2

Description

[Technical field]

[0001] The present invention relates to a method and device for controlling a rail brake of a track-traveling machine. [Background technology]

[0002] Generally, as shown in FIG. 10, a gantry crane 100 as a track-traveling machine deployed on traveling rails Rx on a quay Q of a port H has a traveling gear 300 and a rail brake 400 attached to a lower frame 220 extending parallel to the traveling rails Rx so as to connect the lower ends of the support legs 210 of the main frame 200.

[0003] The traveling device 300 has traveling wheels 310 that can roll freely along traveling rails Rx, and is adapted to be rotationally driven by a motor (not shown).

[0004] The rail brake 400 performs braking by pressing a brake pad 410 against the traveling rail Rx.

[0005] The support legs 210 are erected on the land side and the sea side, two on each side, for a total of four, and the upper parts of the land-side and sea-side support legs 210 are connected by a connecting frame 230 extending in a direction intersecting with the traveling rail Rx.

[0006] A girder 500 extending horizontally from the land side to the sea side is provided on the upper part of the main frame 200, and a boom 600 extending on an extension line of the girder 500 is attached to the tip of the girder 500.

[0007] A traverse rail Ry is laid on the girder 500 and the boom 600, and a trolley 700 for lifting and lowering a load C (container) travels traversely along the traverse rail Ry.

[0008] Incidentally, for example, Patent Document 1 shows the general state of the art related to the gantry cranes. [Prior art documents] [Patent documents]

[0009] [Patent Document 1] JP 2019-199220 A Summary of the Invention [Problem to be solved by the invention]

[0010] However, since the conventional rail brake 400 is designed to press the brake pad 410 against the traveling rail Rx with a constant force, for example, if the brake is applied during traveling with the load C located at the tip side (sea side) of the girder 500 or boom 600, the inertial force of the sea side support leg 210 becomes larger than the inertial force of the land side support leg 210, and the braking distance of the sea side traveling gear 300 becomes longer than the braking distance of the land side traveling gear 300.

[0011] Conversely, if the brakes are applied while traveling with the load C located at the base end (land side) of the girder 500 or the boom 600, the inertial force of the land-side support leg 210 will be greater than the inertial force of the sea-side support leg 210, and the braking distance of the land-side running gear 300 will be longer than the braking distance of the sea-side running gear 300.

[0012] In this way, if the inertial force acting on the support leg 210 is not uniform depending on the position of the load C, resulting in a difference in braking distance, the connecting frame 230 connecting the sea side and land side support legs 210 may twist, causing a large load to be placed on the main frame 200, and improvement was desired.

[0013] The present invention has been made in consideration of the above-mentioned problems in the conventional technology, and aims to provide a rail brake control method and device for a track-running machine which is able to minimize the difference in braking distance regardless of the position of the suspended load and reduce the load on the main body frame. [Means for solving the problem]

[0014] The present invention provides a rail brake control method for a track-traveling machine comprising a main frame having support legs that can travel freely along traveling rails extending in parallel and in which a vertical load changes depending on the position of a suspended load, a fluid pressure cylinder that can press and release brake pads against the traveling rails, and a fluid pressure unit that introduces and discharges a working fluid to and from the fluid pressure cylinder, a load detection step of measuring a vertical load acting on the support leg; a braking force adjusting step of increasing or decreasing the fluid pressure introduced from the fluid pressure unit to the fluid pressure cylinder based on the vertical load measured in the load detecting step; This relates to a rail brake control method for a track-traveling machine that performs

[0015] The present invention also provides a rail brake control method for a track-traveling machine, comprising a main frame having support legs that are movable along parallel traveling rails and whose vertical load changes depending on the position of a suspended load, a fluid pressure cylinder that can press and release brake pads against the traveling rails, and a fluid pressure unit that introduces and discharges working fluid to and from the fluid pressure cylinder, A weight detection process for measuring the weight of the suspended load; A position detection step of measuring a distance from a reference point of the suspended load; a load calculation step of determining a vertical load acting on the support leg based on the weight of the suspended load measured in the weight detection step and the distance of the suspended load from a reference point measured in the position detection step; a braking force adjusting step of increasing or decreasing the fluid pressure introduced from the fluid pressure unit to the fluid pressure cylinder based on the vertical load calculated in the load calculating step; This relates to a rail brake control method for a track-traveling machine that performs

[0016] On the other hand, the present invention provides a rail brake control device for a track-traveling machine, comprising a main frame having support legs that can travel freely along parallel traveling rails and in which a vertical load changes depending on the position of a suspended load, a fluid pressure cylinder that can press and release brake pads against the traveling rails, and a fluid pressure unit that introduces and discharges a working fluid to and from the fluid pressure cylinder, A load detector that measures a vertical load acting on the support leg; a controller that outputs a control signal to the fluid pressure unit to increase or decrease the fluid pressure introduced from the fluid pressure unit to the fluid pressure cylinder based on the vertical load measured by the load detector; This relates to a rail brake control device for a track-traveling machine equipped with a rail brake.

[0017] The present invention also provides a rail brake control device for a track-traveling machine, comprising a main frame having support legs that are movable along parallel traveling rails and whose vertical load changes depending on the position of a suspended load, a fluid pressure cylinder that can press and release brake pads against the traveling rails, and a fluid pressure unit that introduces and discharges operating fluid to and from the fluid pressure cylinder, A weight detector that measures the weight of the suspended load; A position detector that measures the distance of the suspended load from a reference point; a controller that determines a vertical load acting on the support leg based on the weight of the suspended load measured by the weight detector and the distance of the suspended load from a reference point measured by the position detector, and outputs a control signal to the fluid pressure unit to increase or decrease the fluid pressure introduced from the fluid pressure unit to the fluid pressure cylinder based on the vertical load; This relates to a rail brake control device for a track-traveling machine equipped with a rail brake. Effect of the Invention

[0018] According to the rail brake control method and device for a track-traveling machine of the present invention, it is possible to minimize the difference in braking distance regardless of the position of the suspended load, and it is possible to achieve the excellent effect of reducing the load on the main body frame. [Brief description of the drawings]

[0019] [Figure 1] 1 is a front view of a main portion showing a first embodiment of a rail brake control method and device for a track-traveling machine according to the present invention. FIG. [Diagram 2] 1 is a schematic diagram showing a first embodiment of a rail brake control method and device for a track-traveling machine according to the present invention; FIG. [Diagram 3]1 is a flowchart showing a first embodiment of a rail brake control method and device for a track-traveling machine according to the present invention. [Figure 4] FIG. 2 is an overall side view showing a second embodiment of the rail brake control method and device for a track-traveling machine of the present invention. [Diagram 5] FIG. 2 is a schematic diagram showing a second embodiment of a rail brake control method and device for a track-traveling machine according to the present invention. [Figure 6] FIG. 11 is a diagram showing an example of a weight detector in a second embodiment of the rail brake control method and device for a track-traveling machine of the present invention. [Figure 7] FIG. 11 is a diagram showing another example of a weight detector in the second embodiment of the rail brake control method and device for a track-traveling machine of the present invention. [Figure 8] 5 is a flowchart showing a second embodiment of a rail brake control method and device for a track-traveling machine according to the present invention. [Figure 9] FIG. 1 is a perspective view showing an example of a jib crane to which the rail brake control method and device for a track-traveling machine of the present invention can be applied. [Figure 10] FIG. 1 is a perspective view showing an example of a gantry crane as a typical track-traveling machine. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0020] Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings.

[0021] 1 to 3 show a first embodiment of a rail brake control method and device for a track-traveling machine according to the present invention, and in the figures, parts given the same reference numerals as those in FIG. 10 represent the same things.

[0022] As shown in FIG. 1, a traveling device 300 and a rail brake 400 are provided on the bottom side of a lower frame 220 that extends along the traveling rail Rx so as to connect the support legs 210 of the main body frame 200 of the gantry crane 100.

[0023] The traveling device 300 includes an upper equalizer beam 320, an intermediate equalizer beam 330, and a lower equalizer beam 340. The upper equalizer beam 320 is supported at its middle portion by rocker pins 350 extending in a horizontal direction perpendicular to the traveling direction on the bottom surface side of the lower frame 220 so as to be able to swing. The intermediate equalizer beam 330 is supported at its middle portion by rocker pins 360 extending in a horizontal direction perpendicular to the traveling direction on both ends of the upper equalizer beam 320 in the traveling direction so as to be able to swing. The lower equalizer beam 340 is supported at its middle portion by rocker pins 370 extending in a horizontal direction perpendicular to the running direction at both ends of the intermediate equalizer beam 330 in the running direction so as to be freely swingable, and running wheels 310 are arranged at both ends of the lower equalizer beam 340 in the running direction so as to be freely rollable along the running rails Rx.

[0024] The rail brake 400 is attached to a brake bracket 450 held by a tension rod 440 on the bottom side of the lower frame 220, and is equipped with a fluid pressure cylinder 420 and a fluid pressure unit 430 on each of the land side and the sea side, as shown in Fig. 2. In the first embodiment, two rail brakes 400 are provided, one on each of the land side and the sea side, but depending on the size of the gantry crane 100, four rail brakes may be provided, two on each of the land side and the sea side.

[0025] The fluid pressure cylinder 420 includes a fluid pressure cylinder body 421, a fluid pressure piston 422, and a fluid pressure piston rod 423. The fluid pressure cylinder body 421 is suspended from the lower part of the brake bracket 450 via a support pin 470 extending in a horizontal direction perpendicular to the traveling rail Rx, and is attached facing downward by being inserted into an outer case 460 provided at the lower part of the brake bracket 450. The fluid pressure piston 422 is slidably fitted into the inside of the fluid pressure cylinder body 421, and divides the inside of the fluid pressure cylinder body 421 into a cap side chamber 424 and a rod side chamber 425. The fluid pressure piston rod 423 extends downward from the fluid pressure piston 422 through the rod side chamber 425, and a brake pad 410 is connected to the lower end of the fluid pressure piston rod 423 so as to be capable of being pressed against and separated from the traveling rail Rx in a direction perpendicular to the traveling rail Rx. A compression spring S2 serving as an elastic member S extending in the vertical direction is loaded inside the fluid pressure cylinder body 421 of the fluid pressure cylinder 420 (rod side chamber 425) so as to bias the fluid pressure piston rod 423 in a retracting direction.

[0026] The fluid pressure unit 430 introduces working fluid into the fluid pressure cylinder 420 via a supply and discharge line 431, thereby extending the fluid pressure cylinder 420 and pressing the brake pad 410 against the traveling rail Rx, while discharging working fluid from the fluid pressure cylinder 420 via the supply and discharge line 431, thereby contracting the fluid pressure cylinder 420 with the biasing force of the compression spring S2, thereby pulling the brake pad 410 away from the traveling rail Rx.

[0027] The first embodiment is characterized in that it includes a load detector 800 and a controller 900, as shown in FIG.

[0028] The load detector 800 is a detector that measures the vertical load (w1 on the land side, w2 on the sea side) acting on the support legs 210, and can be configured, for example, by incorporating a pin-type load cell as any one of the rocker pins 350, 360, or 370 (see FIG. 1). In the gantry crane 100, the vertical load acting on the two support legs 210 on the land side is the same (w1), and the vertical load acting on the two support legs 210 on the sea side is the same (w2), so that it is sufficient to provide two load detectors 800 in total, one on the land side and one on the sea side.

[0029] The controller 900 outputs a control signal (901 for the land side, 902 for the sea side) to the fluid pressure unit 430 to increase or decrease the fluid pressure introduced from the fluid pressure unit 430 to the fluid pressure cylinder 420 based on the vertical load (w1 for the land side, w2 for the sea side) measured by the load detector 800.

[0030] On the other hand, in the case of the first embodiment, the rail brake control method includes a load detection process and a braking force adjustment process, as shown in FIG.

[0031] The load detection step is a step of measuring a vertical load acting on the support leg 210 (w1 on the land side, w2 on the sea side).

[0032] The braking force adjusting step is a step of increasing or decreasing the fluid pressure introduced from the fluid pressure unit 430 to the fluid pressure cylinder 420 based on the vertical load (w1 on the land side, w2 on the sea side) measured in the load detecting step.

[0033] Next, the operation of the first embodiment will be described.

[0034] When the rail brake 400 is activated to stop the gantry crane 100 from a traveling state, the vertical load acting on the support leg 210 (w1 on the land side, w2 on the sea side) is measured by the load detector 800 (see the load detection process in Figure 3).

[0035] The vertical load (w1 on the land side, w2 on the sea side) measured by the load detector 800 is input to a controller 900, which outputs a control signal (901 on the land side, 902 on the sea side) to the hydraulic unit 430.

[0036] The fluid pressure introduced from the fluid pressure unit 430 to the fluid pressure cylinder 420 is increased or decreased by a control signal (901 for the land side, 902 for the sea side) based on the vertical load (w1 for the land side, w2 for the sea side) measured by the load detector 800, and the pressing force of the brake pad 410 against the traveling rail Rx is increased as the vertical load increases (see the braking force adjustment process in Figure 3).

[0037] As a result, for example, when the brakes are applied during travel with the load C located at the tip side (sea side) of the girder 500 or the boom 600, the inertial force of the sea-side support leg 210 becomes larger than the inertial force of the land-side support leg 210. However, in the first embodiment, instead of pressing the brake pad 410 against the travel rail Rx with a constant force as in the conventional rail brake 400, the braking force of the sea-side rail brake 400 is adjusted to be larger than the braking force of the land-side rail brake 400, so that it is possible to prevent the braking distance of the sea-side traveling device 300 from becoming longer than the braking distance of the land-side traveling device 300.

[0038] Conversely, if the brakes are applied during travel with the load C located on the base end side (land side) of the girder 500 or the boom 600, the inertial force of the land-side support leg 210 becomes greater than the inertial force of the sea-side support leg 210. However, in the first embodiment, the braking force of the land-side rail brake 400 is adjusted to be greater than the braking force of the sea-side rail brake 400, so that it is possible to prevent the braking distance of the land-side traveling device 300 from becoming longer than the braking distance of the sea-side traveling device 300.

[0039] In this way, even if the inertial force acting on the support leg 210 is different depending on the position of the load C, there will be no difference in the braking distance, and it is possible to prevent the connecting frame 230 connecting the sea side and land side support legs 210 from twisting and causing a large load on the main frame 200.

[0040] In this way, the difference in braking distance can be minimized regardless of the position of the suspended load C, and the load on the main body frame 200 can be reduced.

[0041] 4 to 8 show a second embodiment of the rail brake control method and device for a track-traveling machine according to the present invention, and in the drawings, parts that are given the same reference numerals as in FIGS. 1 to 3 represent the same things.

[0042] The basic configuration is similar to that of the first embodiment shown in Figures 1 to 3, but the second embodiment is characterized in that it is equipped with a weight detector 810, a position detector 820, and a controller 900, as shown in Figure 5.

[0043] The weight detector 810 is a detector for measuring the weight W of the load C, and can be constructed, for example, by incorporating a pin-type load cell as a support shaft 720 of a sheave 710 as shown in Fig. 6. Incidentally, a wire rope 740 for hoisting and lowering a spreader 730 for the load C from a trolley 700 is wound around the sheave 710. The weight detector 810 can also be constructed by incorporating a tension-type load cell into the end of the wire rope 740 as shown in Fig. 7.

[0044] The position detector 820 is a detector that measures the distance L from the reference point O of the load C, and may be, for example, a detector that detects the rotation of a drive motor (not shown) that moves the trolley 700 laterally along the lateral rail Ry (see Figure 10) to determine the distance L.

[0045] The controller 900 determines the vertical load (w1 for the land side, w2 for the sea side) acting on the support leg 210 based on the weight W of the load C measured by the weight detector 810 and the distance L of the load C from the reference point O measured by the position detector 820, and outputs a control signal (901 for the land side, 902 for the sea side) to the fluid pressure unit 430 to increase or decrease the fluid pressure introduced from the fluid pressure unit 430 to the fluid pressure cylinder 420 based on the vertical load (w1 for the land side, w2 for the sea side).

[0046] Here, the load acting on the land-side support leg 210 due to the weight of the gantry crane 100 is w1a, the load acting on the land-side support leg 210 due to the suspended load C is w1b, and the span between the land-side and sea-side support legs 210 is l. If the moment with respect to the reference point O is positive (+) in the clockwise direction in FIG. 4 and negative (-) in the counterclockwise direction, then from the balance, w1b l=-W L w1b=-W L / l The vertical load w1 on the land side is w1=w1a+w1b =w1a-W·L / l It is more demanding.

[0047] In addition, if the load acting on the sea-side support leg 210 due to the weight of the gantry crane 100 is w2a, and the load acting on the sea-side support leg 210 due to the suspended load C is w2b, w2b=W-w1b =W+W L / l =(1+L / l) W The vertical load w2 on the sea side is w2=w2a+w2b =w2a+(1+L / l)·W It is more demanding.

[0048] On the other hand, in the case of the second embodiment, as shown in FIG. 8, the rail brake control method includes a weight detection process, a position detection process, a load calculation process, and a braking force adjustment process.

[0049] The weight detection process is a process of measuring the weight W of the suspended load C.

[0050] The position detection step is a step of measuring a distance L from a reference point O of the load C.

[0051] The load calculation process is a process of calculating the vertical load (w1 on the land side, w2 on the sea side) acting on the support leg 210 based on the weight W of the load C measured in the weight detection process and the distance L of the load C from the reference point O measured in the position detection process.

[0052] The braking force adjustment step is a step of increasing or decreasing the fluid pressure introduced from the fluid pressure unit 430 to the fluid pressure cylinder 420 based on the vertical load (w1 on the land side, w2 on the sea side) calculated in the load calculation step.

[0053] Next, the operation of the second embodiment will be described.

[0054] When the rail brake 400 is activated to stop the gantry crane 100 from a traveling state, the weight W of the load C is measured by the weight detector 810 (see the weight detection process in Figure 8), and the distance L of the load C from the reference point O is measured by the position detector 820 (see the position detection process in Figure 8).

[0055] The weight W of the load C measured by the weight detector 810 and the distance L of the load C from the reference point O measured by the position detector 820 are input to the controller 900, and the vertical load acting on the support leg 210 (w1 on the land side and w2 on the sea side) is calculated by the controller 900. w1=w1a-W L / l w2=w2a+(1+L / l)·W (See the load calculation process in FIG. 8).

[0056] Based on the vertical load (w1 for the land side, w2 for the sea side) determined in the controller 900, a control signal (901 for the land side, 902 for the sea side) is output from the controller 900 to the hydraulic unit 430.

[0057] The fluid pressure introduced from the fluid pressure unit 430 to the fluid pressure cylinder 420 is increased or decreased by a control signal (901 for the land side, 902 for the sea side) based on the vertical load (w1 for the land side, w2 for the sea side) calculated by the controller 900, and the pressing force of the brake pad 410 against the traveling rail Rx is increased as the vertical load increases (see the braking force adjustment process in Figure 8).

[0058] As a result, for example, when the brakes are applied during traveling with the load C located at the tip side (sea side) of the girder 500 or the boom 600, the inertial force of the sea-side support leg 210 becomes larger than the inertial force of the land-side support leg 210, as in the first embodiment. However, also in the second embodiment, instead of pressing the brake pad 410 against the traveling rail Rx with a constant force as in the conventional rail brake 400, the braking force by the sea-side rail brake 400 is adjusted to be larger than the braking force by the land-side rail brake 400, so that it is possible to prevent the braking distance of the sea-side traveling device 300 from becoming longer than the braking distance of the land-side traveling device 300.

[0059] Conversely, if the brakes are applied during travel with the load C located on the base end side (land side) of the girder 500 or the boom 600, the inertial force of the land-side support leg 210 becomes greater than the inertial force of the sea-side support leg 210, as in the first embodiment. However, also in the second embodiment, the braking force of the land-side rail brake 400 is adjusted to be greater than the braking force of the sea-side rail brake 400, so that it is possible to prevent the braking distance of the land-side traveling device 300 from becoming longer than the braking distance of the sea-side traveling device 300.

[0060] In this way, even if the inertial force acting on the support leg 210 is different depending on the position of the load C, there is no difference in the braking distance in the second embodiment, and it is possible to prevent the connecting frame 230 connecting the sea side and land side support legs 210 from twisting and causing a large load to be generated on the main frame 200.

[0061] Thus, similarly to the first embodiment, in the second embodiment as well, the difference in braking distance can be minimized regardless of the position of the suspended load C, and the load on the main frame 200 can be reduced.

[0062] Incidentally, while the first and second embodiments both apply the present invention to a gantry crane 100, it is also possible to apply the present invention to a jib crane 110 having a main body frame 200 with support legs 210, as shown in Figure 9.

[0063] In this case, since the vertical load acting on each support leg 210 changes depending on the rotation direction of the jib 111, a total of four load detectors 800 shown in FIG. 2 may be provided.

[0064] Incidentally, the rail brake control method and device for a track-running 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 spirit and scope of the present invention. [Explanation of symbols]

[0065] 100 Gantry Crane (track-running machine) 110 Jib crane (track-running machine) 111 Jib 200 Body Frame 210 Support legs 220 Lower Frame 230 Connecting Frame 300 Running gear 310 Running Wheel 320 Upper equalizer beam 330 Intermediate Equalizer Beam 340 Lower Equalizer Beam 350 Rocker pin 360 Rocker Pin 370 Rocker pin 400 Rail Brake 410 Brake pads 420 Fluid Pressure Cylinder 421 Fluid pressure cylinder body 422 Fluid Pressure Piston 423 Fluid pressure piston rod 424 Cap Concubine 425 Rod's Concubine 430 Fluid Pressure Unit 431 Supply and Discharge Line 440 Tension Rod 450 brake bracket 460 Outer Case 470 Support pin 500 Guarda 600 Boom 700 trolley 710 Sheaves 720 Support shaft 730 Spreader 740 Wire Rope 800 Load Detector 810 Weight detector 820 Position detector 900 Controller C Hanging load H port L distance O reference point Q Wharf Rx Running rail Ry Traverse rail S Elastic member S2 Compression Spring W weight w1 Vertical load w2 vertical load

Claims

1. A rail brake control method for a track-traveling machine comprising: a main frame having support legs that are movable along traveling rails extending in parallel and in which a vertical load changes depending on a position of a suspended load; a fluid pressure cylinder that can press and release brake pads against the traveling rails; and a fluid pressure unit that introduces and discharges a working fluid to and from the fluid pressure cylinder, a load detection step of measuring a vertical load acting on the support leg; a braking force adjusting step of increasing or decreasing the fluid pressure introduced from the fluid pressure unit to the fluid pressure cylinder based on the vertical load measured in the load detecting step; A rail brake control method for a track-traveling machine.

2. A rail brake control method for a track-traveling machine comprising: a main frame having support legs that are movable along traveling rails extending in parallel and in which a vertical load changes depending on a position of a suspended load; a fluid pressure cylinder that can press and release brake pads against the traveling rails; and a fluid pressure unit that introduces and discharges a working fluid to and from the fluid pressure cylinder, A weight detection process for measuring the weight of the suspended load; A position detection step of measuring a distance from a reference point of the suspended load; a load calculation step of determining a vertical load acting on the support leg based on the weight of the suspended load measured in the weight detection step and the distance of the suspended load from a reference point measured in the position detection step; a braking force adjusting step of increasing or decreasing the fluid pressure introduced from the fluid pressure unit to the fluid pressure cylinder based on the vertical load calculated in the load calculating step; A rail brake control method for a track-traveling machine.

3. A rail brake control device for a track-traveling machine, comprising: a main frame having support legs that are movable along traveling rails extending in parallel and in which a vertical load changes depending on a position of a suspended load; a fluid pressure cylinder that is capable of pressing and releasing a brake pad against the traveling rails; and a fluid pressure unit that introduces and discharges a working fluid to and from the fluid pressure cylinder, A load detector that measures a vertical load acting on the support leg; a controller that outputs a control signal to the fluid pressure unit to increase or decrease the fluid pressure introduced from the fluid pressure unit to the fluid pressure cylinder based on the vertical load measured by the load detector; A rail brake control device for a track-running machine equipped with the rail brake control device.

4. A rail brake control device for a track-traveling machine, comprising: a main frame having support legs that are movable along traveling rails extending in parallel and in which a vertical load changes depending on a position of a suspended load; a fluid pressure cylinder that is capable of pressing and releasing a brake pad against the traveling rails; and a fluid pressure unit that introduces and discharges a working fluid to and from the fluid pressure cylinder, A weight detector that measures the weight of the suspended load; A position detector that measures the distance of the suspended load from a reference point; a controller that determines a vertical load acting on the support leg based on the weight of the suspended load measured by the weight detector and the distance of the suspended load from a reference point measured by the position detector, and outputs a control signal to the fluid pressure unit to increase or decrease the fluid pressure introduced from the fluid pressure unit to the fluid pressure cylinder based on the vertical load; A rail brake control device for a track-running machine equipped with the rail brake control device.

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