JP6699851B2 - Brake shoe of brake device - Google Patents

Description

The present invention relates to a brake shoe for a brake device for traveling bodies such as quayside cranes and trains that travel on rails, and more specifically, a brake shoe for a brake device that can easily adjust the brake force while increasing the brake force. It is about.

  Various brake devices for cranes traveling on rails have been proposed (see, for example, Patent Documents 1 and 2). The brake device described in Patent Document 1 compresses the disc spring with a hydraulic cylinder when releasing the brake, releases the hydraulic cylinder when the brake is activated, and restores the disc spring to the brake shoe installed at the lower end of the disc spring. Press on top to stop the crane.

  In the brake device described in Patent Document 1, both the disc spring and the hydraulic cylinder have to be upsized in order to increase the braking force, resulting in a significant increase in the manufacturing cost of the brake device. In addition, since the disc spring is repeatedly compressed and extended each time the crane travels and stops, deterioration may easily occur and the disc spring may crack. If the disc spring breaks, the braking force of the braking device will be significantly reduced.

  In the brake device described in Patent Document 2, the side surface of the rail is sandwiched by two brake shoes, and the cam is rotated to increase the force for pressing the brake shoe against the rail to stop the crane. In the brake device described in Patent Document 2, in order to increase the braking force, it is necessary to upsize the motor and increase the output, so that the manufacturing cost of the brake device increases significantly. Further, even if the motor is increased in size, there is a limit to the force with which the rail can be sandwiched between the brake shoes, and the braking force obtained is small despite the increase in the manufacturing cost of the brake device.

JP, 2010-247944, A Japanese Patent Laid-Open No. 06-72690

The present invention has been made in view of the above problems, and an object thereof is to provide a brake shoe of a braking device that can easily adjust the braking force while increasing the braking force.

The brake shoe of the brake device of the present invention for achieving the above object is provided with a telescopic mechanism which is disposed below a traveling body traveling on a rail and which vertically expands and contracts, and which projects from the telescopic mechanism toward the rail. In a brake shoe of a brake device including a pressing portion that is provided and a brake shoe that is disposed between the pressing portion and the rail and that is suspended by an elevating mechanism, a recess formed on the upper surface and the recess It is characterized in that it has a first horizontal portion formed on both sides of the rail in the longitudinal direction of the rail and a second horizontal portion formed on the bottom surface of the hollow portion .

According to the brake shoe of the brake device of the present invention, the pressing portion moves along the recessed portion formed in the brake shoe and the first horizontal portion, whereby the force for pressing the brake shoe is gradually increased and then maintained constant. can do. By providing this recess, the brake shoe can be pressed by using the weight of the traveling body, so that the braking force of the brake device can be increased. By providing this horizontal portion, the upper limit value of the force with which the pressing portion presses the brake shoe can be determined, so it is necessary to design the members constituting the braking device such as the pressing portion and the brake shoe with unnecessarily high strength. There is no. Therefore, it is possible to avoid over-spec while significantly improving the braking force of the braking device.

  By moving the pressing portion to the first horizontal portion, the brake shoe can be pressed against the rail with a constant force, so that this brake device can obtain a stable braking force.

  The maximum stroke amount of the telescopic mechanism should be uniquely determined from the height difference between the first and second horizontal parts and the height difference between the bottom surface of the brake shoe and the top surface of the rail during standby. You can Since the maximum value of the vertical load with which the brake shoe is pressed against the rail is determined according to the maximum value of the stroke amount of the expansion/contraction mechanism, it is advantageous to easily adjust the braking force of the brake device. This is advantageous for stabilizing the quality of the braking device.

The brake system during standby is an explanatory diagram illustrating a front view. It is explanatory drawing which illustrates the brake device of FIG. 1 by the AA cross section. It is explanatory drawing which illustrates the brake shoe of the brake device of FIG. It is explanatory drawing which illustrates the brake device of FIG. 1 by a BB cross section. It is explanatory drawing which illustrates the brake device at the time of operation. It is explanatory drawing which illustrates the state which the pressing part contacted with the hollow part. It is explanatory drawing which illustrates the state which the press part contacted the 1st horizontal part. It is explanatory drawing which illustrates the state which the brake shoe contacted with the stopper. It is a graph which illustrates the relationship between the escape distance and the braking force. It is explanatory drawing which illustrates the modification of a brake device. It is explanatory drawing which illustrates the brake device of FIG. 10 by CC cross section. It is explanatory drawing which illustrates the modification of a brake shoe. It is a graph which illustrates the relationship between the escape distance and the braking force in the brake shoe of FIG. It is explanatory drawing which illustrates the modification of a stopper. It is explanatory drawing which illustrates the embodiment which installed the guide part in the brake device. It is explanatory drawing which illustrates the modification of a guide part.

Hereinafter, a brake shoe of the brake device of the present invention will be described based on the embodiment shown in the drawings. In the drawing, the traveling direction of the traveling body (rail longitudinal direction) is indicated by an arrow y, the transverse direction crossing the traveling direction y at a right angle is indicated by an arrow x, and the vertical direction is indicated by an arrow z.

Brake device 1 as illustrated in FIGS. 1 and 2, for example a telescopic mechanism 4 fixed to the lower surface of the traveling body 3 traveling on rails 2 quay cranes and trains, etc., the lower end of the telescopic mechanism 4 The pressing portion 5 is provided so as to project from the rail 2 toward the rail 2, the brake shoe 6 is disposed between the pressing portion 5 and the rail 2, and the elevating mechanism 7 that raises and lowers the brake shoe 6.

In this embodiment, the expansion/contraction mechanism 4 is provided with a support member 8 extending downward from the traveling body 3, and a supporting member 8 extending from the supporting member 8 at a distance along the traveling direction y and extending downward from the traveling body 3. And a spring member 9. The support member 8 is arranged such that its extending direction is parallel to the vertical direction z. The spring member 9 is arranged such that its extending direction is parallel to the vertical direction z and is inclined along the traveling direction y. The upper end of the spring member 9 is inclined in the direction toward the support member 8. That is, the distance between the upper end of the support member 8 and the upper end of the spring member 9 in the traveling direction y is closer than the distance between the lower end of the support member 8 and the lower end of the spring member 9 in the traveling direction y. Is inclined.

  The spring member 9 is composed of a plurality of coned disc springs and is expandable and contractable in the axial direction. The structure of the spring member 9 is not limited to this, and may have a structure that expands and contracts in the axial direction, such as a coil spring, a hydraulic cylinder, or a mechanism that combines a hydraulic cylinder and a coil spring.

  In this embodiment, the pressing portion 5 includes a holder 10 supported by the lower end of the support member 8 and the lower end of the spring member 9, and a roller 11 installed on the holder 10. The holder 10 has a substantially rectangular parallelepiped shape, and both ends in the traveling direction y are connected to the lower end of the support member 8 and the lower end of the spring member 9 by pins 12 and 13 having the transverse direction x as the axial direction. The roller 11 is supported by the holder 10 by a rotary shaft 14 having the transverse direction x as an axial direction, and is configured to be rotatable around the rotary shaft 14. 1 and 2, a part of the roller 11 is shown by a broken line for explanation.

  The brake shoe 6 is arranged between the pressing portion 5 and the rail 2, and is suspended from the traveling body 3 side by the elevating mechanism 7. As illustrated in FIG. 3, the brake shoe 6 has a recessed portion 15 formed in a concave shape on the upper surface and first horizontal portions 16 formed on both sides of the recessed portion 15 in the traveling direction y. A second horizontal portion 17 is formed on the bottom surface, which is the center of the recess 15 in the traveling direction y and is the lowest.

  The two first horizontal portions 16 and the second horizontal portion 17 are formed by horizontal planes that are parallel to each other. The first horizontal portion 16 and the second horizontal portion 17 are parallel to the lower surface of the brake shoe 6. The two first horizontal portions 16 are above the second horizontal portion 17 and are located at the same height. The first horizontal portion 16 and the second horizontal portion 17 are connected by a flat inclined surface 15a.

  When the traveling body 3 on which the brake device 1 is installed is composed of, for example, a quay crane, the length of the brake shoe 6 in the traveling direction y can be set to, for example, about 300 to 1000 mm. The length of the brake shoe 6 in the transverse direction x may be longer than or about the same as the width of the rail 2, and specifically, may be about 150 to 350 mm.

  As illustrated in FIG. 1, the elevating mechanisms 7 are arranged at positions on both sides of the pressing portion 5 in the transverse direction x. As illustrated in FIG. 4, the elevating mechanism 7 includes a string-like object 18 whose one end is connected to a side surface of the brake shoe 6 facing in the transverse direction x, and a string-like object 18 installed on the traveling body 3 to wind up the string-like object 18. It has a winding upper part 19 for winding down and a guide part 20 for sandwiching and guiding the string-like object 18 from both sides.

  The string-like object 18 is composed of, for example, a chain. The string-like object 18 is not limited to a chain, and may be a wire or rope, for example, as long as it has the strength to suspend the brake shoe 6 and can be wound up by the winding portion 19. In the embodiment illustrated in FIG. 1, one end of the string-like material 18 is indirectly connected to the brake shoe 6 via an extension member 18a extending in the transverse direction x. One end of the string 18 connected to the brake shoe 6 may be directly connected to the side surface of the brake shoe 6.

The winding part 19 can be composed of a drum connected to a drive motor. By rotating the drum with the power of the drive motor, the chain can be wound or unwound.

  The guide portion 20 can be composed of a pair of guide sheaves. The guide sheave is composed of a pin whose axial direction is the transverse direction x and a sheave rotatably supported by the pin. The guide portion 20 is fixed to the traveling body 3 side, and is arranged at a position above the brake shoe 6. The pair of guide sheaves has a configuration in which the string-like object 18 is sandwiched from both sides in the traveling direction y and the string-like object 18 is guided. The guide portion 20 is not limited to this configuration, and may have a configuration that restrains the string-like object 18 at a predetermined position in the traveling direction y and guides it in a predetermined direction. For example, a through hole extending in the vertical direction z. It may be configured by a tubular body or the like in which the string-like object 18 is penetrated through the through hole.

  The lifting mechanism 7 has an abutting member 21 that contacts the upper surface of the brake shoe 6 and maintains the posture of the brake shoe 6. The contact member 21 is arranged at a position in contact with each of the first horizontal portions 16 on both sides of the brake shoe 6 in the traveling direction y, and has lower surfaces having the same height. Since the first horizontal portions 16 of the brake shoes 6 pulled up by the string-like object 18 come into surface contact with the lower surface of the contact member 21, the posture of the brake shoes 6 becomes horizontal.

  Stoppers 22 are arranged on both outer sides of the brake shoe 6 in the traveling direction y. The stopper 22 is fixed to the side of the traveling body 3 and has a structure for restraining the brake shoe 6 within a predetermined range in the traveling direction y.

  Next, the operation of the brake device 1 will be described. When the traveling body 3 such as a quayside crane travels along the rails 2, the brake device 1 is put in a standby state. As illustrated in FIG. 2, when the brake device 1 is on standby, the second horizontal portion 17 of the brake shoe 6 is arranged at a standby position where it contacts the roller 11 forming the pressing portion 5. The brake shoe 6 is suspended by the elevating mechanism 7, and the lower surface of the brake shoe 6 is held in a standby position where it does not contact the upper surface of the rail 2.

  At this time, it is desirable that the extension mechanism 4 has a natural length. That is, it is desirable that the spring member 9 has a natural length and does not store elastic energy. In this case, although the brake shoe 6 and the roller 11 are in contact with each other, a stress in the vertical direction z is hardly generated between the two members. Since unnecessary stress does not occur in the expansion mechanism 4 and the pressing portion 5, it is advantageous to suppress deterioration due to fatigue or the like. Further, when the brake device 1 is disassembled for maintenance, the contracted spring member 9 does not suddenly extend and push the brake shoe 6 downward, which improves the safety during maintenance work. Is advantageous.

  When the traveling body 3 such as a quayside crane completes its movement to a predetermined position and performs cargo handling work, the brake device 1 is activated. As illustrated in FIG. 5, when the brake device 1 is operating, the suspension by the elevating mechanism 7 is released to drop the brake shoe 6 downward. Specifically, the string-like material 18 is paid out by the winding portion 19. The operation of the elevating mechanism 7 moves the brake shoe 6 to the operating position where the lower surface of the brake shoe 6 and the upper surface of the rail 2 come into contact with each other. At this time, it is desirable that the string-like object 18 is paid out from the winding part 19 until it is sufficiently loosened. 5 to 8, the expansion/contraction mechanism 4, the pressing portion 5, and the elevating mechanism 7 are shown in the same drawing for the sake of explanation.

If the telescopic mechanism 4 has a natural length during standby, the position of the pressing portion 5 does not change even if the brake shoe 6 is dropped and placed on the rail 2. Therefore, a gap having the same length as the distance that the brake shoe 6 falls is formed between the roller 11 of the pressing portion 5 and the second horizontal portion 17 of the brake shoe 6.

At this time, the upper surface of the brake shoe 6 and the peripheral surface of the roller 11 forming the pressing portion 5 are not in contact with each other, and no force for compressing the expansion mechanism 4 is generated. Does not occur. That is, since the vertical load _Fn is not generated on the brake shoe 6, the braking force of the brake device 1 becomes zero as illustrated in FIG.

  When the traveling device 3 such as a quay crane is moved from a predetermined position due to wind or vibration while the brake device 1 is operating, the traveling device 3 is placed on the rail 2 as illustrated in FIG. The brake shoe 6 staying there remains on the spot, and the pressing portion 5 fixed to the side of the traveling body 3 moves in the traveling direction y.

  In order to prevent the brake shoe 6 from moving in the traveling direction y due to the tension generated in the string-like object 18 when the traveling body 3 departs, the string-like object 18 is preliminarily lengthened from the winding portion 19 and loosened. The string-like object 18 is appropriately unwound from the winding part 19 according to the movement of the traveling body 3. For example, the drum constituting the winding portion 19 may be in a free state in which it can be rotated with almost no resistance, and the string-like object 18 may be automatically paid out in accordance with the tension generated in the string-like object 18.

  When the traveling body 3 runs away, the roller 11 that has moved in the traveling direction y along with the movement of the traveling body 3 comes into contact with the inclined surface 15 a of the recess 15. Then, the roller 11 moves upward along the recess 15 while rotating. That is, the roller 11 moves in the traveling direction y according to the moving distance of the traveling body 3 and is pushed upward along the upper surface of the recess 15.

  At this time, the expansion/contraction mechanism 4 contracts according to the height at which the roller 11 is pushed up. The support member 8 is configured by a columnar member whose length does not change, and the spring member 9 is configured to be expandable/contractible in the axial direction. Therefore, the holder 10 of the pressing portion 5 tilts around the pin 12 connected to the lower end of the support member 8. The tilting of the holder 10 moves the roller 11 in the vertical direction z. The spring member 9 composed of a disc spring or the like contracts in accordance with the height at which the roller 11 is pushed up.

Since the roller 11 pushes the brake shoe 6 downward according to the restoring force of the spring member 9, the vertical load F _n generated on the roller 11, the brake shoe 6, and the rail 2 increases. The frictional force generated between the peripheral surface of the roller 11 and the upper surface of the brake shoe 6 and the frictional force generated between the lower surface of the brake shoe 6 and the upper surface of the rail 2 as the vertical load F _n increases. Increase.

Since the frictional force generated between the lower surface of the brake shoe 6 and the upper surface of the rail 2 increases as the vertical load F _n generated on the brake shoe 6 increases, the brake shoe 6 easily maintains its relative position to the rail 2. .. That is, even if the pressing portion 5 is pressed by the force in the traveling direction y, the brake shoe 6 does not move on the rail 2 and tries to stay there.

  Since the pressing portion 5 installed on the traveling body 3 side with respect to the brake shoe 6 tries to move in the traveling direction y, when the pressing portion 5 moves upward on the inclined surface 15a of the depression 15, the roller 11 is moved. The frictional force generated between the peripheral surface of the and the recess 15 acts on the traveling body 3 as a braking force.

At this time, each member is designed so that the friction coefficient μ _A between the peripheral surface of the roller 11 and the brake shoe 6 is smaller than the friction coefficient μ _B between the brake shoe 6 and the rail 2. .. By configuring the pressing portion 5 to include the roller 15, the friction coefficient μ _A between the pressing portion 5 and the brake shoe 6 can be easily made smaller than the friction coefficient μ _B.

A vertical load F _n of the same magnitude is generated in the vertical direction z on the roller 11, the brake shoe 6, and the rail 2. Therefore, the magnitude of the braking force generated by the brake device 1 with respect to the runaway of the traveling body 3 depends on the magnitude of the frictional force between the peripheral surface of the roller 11 and the brake shoe 6, and this frictional force. It is represented by the product of the vertical load F _n in the up-and-down direction z and the friction coefficient μ _A that occur in 6 and the like.

As illustrated in FIG. 9, when the pressing portion 5 is in contact with the inclined surface 15a of the recess 15, the braking force increases according to the escape distance of the traveling body 3. When the running force of the traveling body 3 exceeds this braking force, the roller 11 further moves upward on the inclined surface 15a of the recess 15 and reaches the first horizontal portion 16 as illustrated in FIG. To do. When the roller 11 reaches the first horizontal portion 16, the spring member 9 of the expansion and contraction mechanism 4 is not further contracted, so that the vertical load F _n in the vertical direction z generated on the brake shoe 6 becomes constant. Since the braking force of the braking device 1 is obtained by integrating the vertical load F _n and the friction coefficient μ _A that have the constant value, the braking force has the constant value F _A as illustrated in FIG. 9.

As illustrated in FIG. 8, when the traveling force of the traveling body 3 is greater than the braking force F _A , the traveling body 3 does not stop traveling and the brake shoes 6 contact the stopper 22. The brake shoe 6 that is in contact with the stopper 22 is pushed in the traveling direction y by the stopper 22 and moves in the traveling direction y together with the traveling body 3 while maintaining the state of being in contact with the stopper 22.

  At this time, the elevating mechanism 7 does not prevent the brake shoe 6 from moving relative to the pressing portion 5 in the traveling direction y and coming into contact with the stopper 22. The elevating mechanism 7 can feed out the string-like material 18 from the winding portion 19 that is long enough to move the brake shoe 6 to a position where the brake shoe 6 contacts the stopper 22 when the brake device 1 is operated. Further, the elevating mechanism 7 can wind up the string-like material 18 by the hoisting portion 19 to such a height that the lower surface of the brake shoe 6 does not contact the rail 2 when the brake shoe 6 is moved to the standby position.

  The configuration of the elevating mechanism 7 is not limited to this configuration, and the brake shoe 6 can be moved between the standby position and the operating position, and when the traveling body 3 escapes, the brake shoe 6 can be moved to a position where it comes into contact with the stopper 22. It only has to have a configuration. The elevating mechanism 7 may be composed of, for example, a cylinder mechanism such as a hydraulic cylinder that expands and contracts in the vertical direction z, and a swing arm that is installed at the lower end of the cylinder mechanism and is tiltable along the traveling direction y. it can. At this time, the brake shoe 6 is installed at the lower end of this swing arm.

When the brake shoe 6 and the stopper 22 come into contact with each other, the brake shoe 6 is in a state of moving integrally with the traveling body 3 in the escape direction of the traveling body 3. That is, the brake shoe 6 is apparently fixed to the traveling body 3 side. Therefore, as illustrated in FIG. 9, when the brake shoe 6 is in contact with the stopper 22, the braking force of the brake device 1 is the friction coefficient μ _B between the lower surface of the brake shoe 6 and the upper surface of the rail 2 and the vertical direction z. The braking force is a constant value F _B because it is obtained by integration with the vertical load F _n .

The braking force of the braking device 1 is determined by the friction coefficient μ _A between the circumferential surface of the roller 11 and the upper surface of the brake shoe 6 or the friction coefficient μ _B between the lower surface of the brake shoe 6 and the upper surface of the rail 2, and the brake shoe. It can be obtained by integrating with the vertical load F _n generated in 6 and the like. In other words, the braking force of the brake device 1 can easily increase the vertical load F _n by utilizing the weight of the traveling body 3, so that the braking force can be significantly increased.

With the configuration in which the first horizontal portion 16 and the second horizontal portion 17 are provided on the upper surface of the brake shoe 6, the upper limit value of the vertical load F _n can be set in advance and easily adjusted. As illustrated in FIG. 4, the maximum value of the stroke amount of the extension/contraction mechanism 4 in the vertical direction z is determined from the height difference h1 between the first horizontal portion 16 and the second horizontal portion 17 of the brake shoe 6 at the standby position. A height difference h2 between the lower surface and the upper surface of the rail 2, that is, a length h1-h2 obtained by subtracting the fall distance of the brake shoe 6 when the brake device 1 is operated. In the present specification, the stroke amount represents the extension/contraction length of the extension/contraction mechanism 4 in the vertical direction z.

  For example, assuming that the height difference h1 between the first horizontal portion 16 and the second horizontal portion 17 is 16 mm, and the height difference h2 between the lower surface of the brake shoe 6 and the upper surface of the rail 2 is 10 mm, the expansion/contraction mechanism 4 moves vertically. The maximum value of the stroke amount in the direction z is 6 mm. That is, by providing the brake shoe 6 with the first horizontal portion 16 and the second horizontal portion 17, and by setting the position where the roller 11 of the pressing portion 5 and the second horizontal portion 17 contact each other as the standby position of the brake shoe 6, The maximum value of the stroke amount of the expansion/contraction mechanism 4 can be uniquely determined.

  As a result, the braking force of the braking device 1 can be determined regardless of the angle of the inclined surface 15a of the recessed portion 15. That is, when the recess 15 of the brake shoe 6 is processed, the lengths of the first horizontal portion 16 and the second horizontal portion 17 in the traveling direction y vary, and the first horizontal portion 16 changes to the second horizontal portion 17. Even if there is variation in the angle of the inclined surface 15a to reach, or even if the inclined surface 15a is formed of a curved surface, if the height difference h1 between the first horizontal portion 16 and the second horizontal portion 17 is accurately set, the brake The braking force of the device 1 can be set to a predetermined value. It is advantageous to accurately control the quality of the brake shoes 6.

  The height difference h2 between the lower surface of the brake shoe 6 and the upper surface of the rail 2 can be adjusted by the lifting mechanism 7. The length difference h2 can be reduced by increasing the feeding length of the string-like object 18 of the elevating mechanism 7 and lowering the position of the contact member 21. That is, the standby position of the brake shoe 6 can be adjusted by the installation position of the contact member 21 and the length of the string-like object 18.

  Along with this, the roller 11 of the pressing portion 5 is lowered to a position where it contacts the second horizontal portion 17 of the brake shoe 6 at the standby position. Specifically, a height adjusting mechanism such as a spacer is arranged between the traveling body 3 and the expansion/contraction mechanism 4 to lower the installation position of the expansion/contraction mechanism 4.

  The height adjusting mechanism may be installed between the brake device 1 and the traveling body 2. That is, the installation position of the expansion mechanism 4 and the elevating mechanism 7 may be simultaneously adjusted by the height adjusting mechanism. With this configuration, the entire brake device 1 can be moved in the vertical direction z, so that the adjustment of the height of the brake shoe 6 by the elevating mechanism 7 and the adjustment of the height of the expansion/contraction mechanism 4 are individually performed as described above. You don't have to do it. The braking force of the braking device 1 can be adjusted more easily.

  Since the height difference h2 becomes smaller, the maximum value h1-h2 of the stroke amount of the expansion/contraction mechanism 4 becomes larger, and the braking force of the brake device 1 increases. On the other hand, if the position of the contact member 21 is raised and the height difference h2 is adjusted to be large, the braking force of the brake device 1 is reduced.

  The braking force of the brake device 1 can also be adjusted by adjusting the height difference h1 between the first horizontal portion 16 and the second horizontal portion 17 of the brake shoe 6. Since it becomes easy to adjust the braking force of the brake device 1, it becomes easy to perform quality control of the brake device 1.

  By exchanging the brake shoes 6 and adjusting the height adjusting mechanism, the braking force of the brake device 1 can be adjusted even after the brake device 1 is installed on the traveling body 3. This is advantageous for quality control of the braking device 1.

By constructing the expansion/contraction mechanism 4 with the column member 8 whose length is fixed and the elastic member 9 capable of expansion/contraction, part of the vertical load F _n generated in the expansion/contraction mechanism 4 is supported by the column member 8. Since the stress generated in the spring member 9 can be suppressed, it is advantageous for suppressing the increase in size of the spring member 9 and suppressing the occurrence of failure or damage.

  In addition, a large stroke amount of the spring member 9 can be ensured by arranging the spring member 9 in a state in which the spring member 9 is parallel to the vertical direction z and inclined in the traveling direction y. Since the braking force of the brake device 1 can be easily increased smoothly when the traveling body 3 escapes, it is advantageous to avoid the problem that the brake device 1 fails due to an impact.

  With the configuration in which the first horizontal portion 16 is provided on the brake shoe 6, if the roller 11 is riding on the first horizontal portion 16, even if the roller 11 reciprocates in the traveling direction y due to vibration or the like, The braking force can be maintained constant. It is advantageous for the braking device 1 to obtain a stable braking force.

With the configuration in which the stopper 22 is installed, when the escape force of the traveling body 3 exceeds the braking force F _A and the escape of the traveling body 3 cannot be stopped, the roller 11 moves on the upper surface of the brake shoe 6 and exceeds the end thereof. It can be avoided that the braking force is lost and the braking force is lost.

When the brake shoe 6 comes into contact with the stopper 22 and moves with the traveling body 3, a braking force F _B larger than the braking force F _A generated between the pressing portion 5 and the brake shoe 6 is obtained. Therefore, when the stopper 22 is installed, it is possible to determine the strength and the like of the members constituting the brake device 1 within an appropriate range according to the magnitude of the braking force F _B , and these members are over-specified. Can be avoided.

Here, the maximum values of the braking force F _A generated between the roller 11 and the brake shoe 6 and the braking force F _B generated between the brake shoe 6 and the rail 2 are the same for the vertical load Fn. Depending on the values of the friction coefficients μ _A and μ _B.

  The stopper 22 is not an essential requirement of the present invention. For example, when the maximum value of the braking force required at the time of departure is not so large, the stopper 22 may not be installed in the brake device 1.

If even during operation of the brake device 1 is traveling body 3 does not escape, no vertical load F _n on the brake shoe 6 and the like. That is, stress is generated in the expansion/contraction mechanism 4, the pressing portion 5, and the brake shoe 6 only when the traveling body 3 escapes, which is advantageous for suppressing deterioration of these members. Similarly, other members constituting the brake device 1 generate stress only when the traveling body 3 escapes, which is advantageous for suppressing deterioration of these members.

When the brake device 1 is restored, the traveling body 3 is caused to travel in the direction opposite to the escape direction, so that the roller 11 is moved above the second horizontal portion 17 of the recess 15. Along with this, the extension mechanism 4 is extended to release the vertical load F _n generated in the vertical direction z of the brake shoe 6 and release the brake.

  After that, when the string-like material 18 is wound up by the hoisting portion 19 of the elevating mechanism 7, the brake shoe 6 ascends toward the standby position and moves in the traveling direction y. Since the string-like object 18 is guided by the guide portion 20, the brake shoe 6 can be moved to the standby position regardless of the direction of the brake device 6 in the brake device 1. That is, by installing the guide portion 20, it becomes easy to move the brake shoe 6 to the standby position where the roller 11 of the pressing portion 5 and the second horizontal portion 17 of the brake shoe 6 come into contact with each other.

  When the first horizontal portion 16 on the upper surface of the brake shoe 6 comes into contact with the lower surface of the contact member 21, the winding of the string-like material 18 by the winding portion 19 is stopped. Since the posture of the brake shoe 6 in a state of being in contact with the lower surface of the contact member 21 is controlled to be horizontal, the lower surface of the brake shoe 6 is parallel to the upper surface of the rail 2. This is advantageous for avoiding an accident in which the brake shoe 6 in the standby state tilts and comes into contact with the rail 2.

  When the brake shoe 6 moves to the standby position, the restoration work of the brake device 1 is completed. After the recovery work of the brake device 1 is completed, the traveling body 3 can travel in any direction.

  A position sensor that detects the position of the brake shoe 6 with respect to the pressing portion 5 may be installed in order to detect whether or not the traveling body 3 has escaped and the direction thereof when the brake device 1 is restored. This position sensor can be configured by, for example, a laser scanner or the like that is installed on the lower surface of the traveling body 3 or on the pressing portion 5 and irradiates a plurality of laser beams along the rail 2 that is an opposing surface to measure the distance. The position where the brake shoe 6 is placed on the rail 2 can be specified from the values of a plurality of distances obtained by this laser scanner. With this, it is possible to know whether or not the traveling body 3 needs to travel when releasing the brake, and if necessary, the direction in which the traveling body 3 travels. it can.

The structure of the expansion/contraction mechanism 4 is not limited to the above-described embodiment. It is sufficient that the pressing portion 5 can be moved in the vertical direction and the vertical load F _n can be supported. Further, the configuration of the pressing portion 5 is not limited to the above-mentioned embodiment. It suffices if the brake shoe 1 can be moved to the first horizontal portion 16 by coming into contact with the recess 15 of the brake shoe 6 when the brake device 1 is operated. Furthermore, the lifting mechanism 7 is not limited to the above-described embodiment. It is sufficient that the brake shoe 6 can be moved to the standby position and the operating position.

  As illustrated in FIGS. 10 and 11, the spring member 9 of the expansion/contraction mechanism 4 may be arranged in a state parallel to the vertical direction z. The support member 8 and the spring member 9 are arranged in parallel with each other in the vertical direction z.

Further, the pressing portion 5 may be configured to include the tilting plate 23 fixed below the expansion mechanism 4 and the contact plate 24 protruding downward from the lower surface of the tilting plate 23. The contact plate 24 is composed of a plate-shaped member whose lower end is processed into a curved surface. The lower end of the contact plate 24 is such that the friction coefficient μ _A between the contact plate 24 and the upper surface of the brake shoe 6 is smaller than the friction coefficient μ _B between the lower surface of the brake shoe 6 and the upper surface of the rail 2. The parts and the upper and lower surfaces of the brake shoe 6 are processed.

For example, a fluororesin or nylon resin may be arranged on the lower end portion of the contact plate 24 or the upper surface of the brake shoe 6 to reduce the friction coefficient μ _A. Further, when the brake device 1 is operated, the lubricating oil or the like may be supplied from the lower end portion of the contact plate 24 toward the upper surface of the brake shoe 6. By making the surface of the lower surface of the brake shoe 6 rough, the friction coefficient μ _B with the upper surface of the rail 2 can be increased.

  The hoisting portion 19 of the elevating mechanism 7 is installed on the traveling body 3 with one end thereof being capable of undulating, and is composed of an arm member having a string-like body 18 connected to the other end. When the other end of this arm member is erected upward, the brake shoe 6 is pulled up, and when it is laid down downward, the brake shoe 6 is lowered.

The height adjusting mechanism 25 may be arranged between the brake device 1 and the traveling body 3. The height adjusting mechanism 25 has a structure that moves in the vertical direction z, and can adjust the installation position of the brake device 1 in the vertical direction z. That is, the positions of the extension/contraction mechanism 4 and the elevating/lowering mechanism 7 can be moved in the vertical direction z.

  The height adjusting mechanism 25 may be composed of a spacer having a fixed length in the vertical direction z. When the brake device 1 is installed on the traveling body 3, the braking force of the brake device 1 can be adjusted by adjusting the vertical length z of the spacer.

  The spacer may be composed of, for example, a plurality of plate-shaped objects stacked in the vertical direction. According to this configuration, even after the brake device 1 is installed on the traveling body 3, the braking force of the brake device 1 can be adjusted by increasing or decreasing the number of the plate-shaped objects. 10 and 11 show a state in which the height adjusting mechanism 25 is composed of a plurality of plate-shaped spacers.

  The brake shoe 6 includes stoppers 22 that are provided on the upper surface of the first horizontal portion 16 and project from both ends of the brake shoe 6 in the traveling direction y. The stopper 22 is composed of a wall-shaped member orthogonal to the traveling direction y. Further, as compared with the embodiment illustrated in FIG. 2, the inclination of the inclined surface 15a of the depression 15 is made larger, and the length of the first horizontal portion 16 in the traveling direction y is formed longer.

  When the traveling body 3 runs away during the operation of the brake device 1, the contact plate 24 moves horizontally along the depression 15 on the upper surface of the brake shoe 6 while moving up to the first horizontal portion 16, and then the stopper 22. To contact. In FIG. 10, the contact plate 24 in contact with the stopper 22 is shown by a broken line for the sake of explanation. After the contact plate 24 contacts the stopper 22, if the traveling body 3 further deviates in the same direction, the brake shoes 6 are pushed by the contact plate 24 and move integrally with the traveling body 3.

  The configuration in which the stopper 22 is installed on the side of the brake shoe 6 can simplify the configuration of the brake device 1 and is advantageous in reducing the number of parts. Further, by increasing the inclination of the inclined surface 15a of the recessed portion 15, when the traveling body 3 escapes, the ratio of the contact plate 24 rising to this escape distance increases, so that the braking force can be rapidly increased. It is advantageous to stop the runaway body 3 from running away.

  The brake shoe 6 provided with the stopper 22 can also be adopted in the embodiment illustrated in FIG. In this case, the stopper 22 installed on the traveling body 3 side is unnecessary. Further, the stopper 22 is installed in a state of being vertical to the first horizontal portion 16 of the brake shoe 6 as illustrated in FIG. 10, but the present invention is not limited to this configuration. The stopper 22 may have a configuration capable of blocking the horizontal movement of the pressing portion 5 (the roller 11 or the contact plate 24). For example, the stopper 22 may be installed on the upper surface of the brake shoe 6 in a state in which the stopper 22 has a steeper inclination than the inclined surface 15a of the recessed portion 15 so that the roller 11 and the like cannot ride on the stopper 22.

  As illustrated in FIG. 12, the inclined surface 15a of the recess 15 may be formed by a curved surface. With this configuration, the braking force acting on the traveling body 3 can be gradually increased as illustrated in FIG. That is, it is possible to prevent the braking force from rapidly increasing and the impact of the sudden braking on the traveling body 3 from occurring. Therefore, for example, it is advantageous when the traveling body 3 can be allowed to travel over a certain distance and it is not desirable that the traveling body 3 is impacted when the brake is applied.

As illustrated in FIG. 12, the second horizontal portion 17, which is the lowest point of the depression 15 that is the lowest, can be located at a position displaced from the center of the brake shoe 6 in the traveling direction y. With this configuration, it is possible to provide the brake device 1 in which the way of increasing the braking force differs depending on the escape direction of the traveling body 3.

  Even when the recess 15 is formed in a complicated shape such as a curved surface, the height difference h1 between the first horizontal portion 16 and the second horizontal portion 17 can be accurately determined, so that the brake of the brake device 1 can be obtained. The maximum value of force can be uniquely determined. It is advantageous to prevent the maximum value of the braking force of each braking device 1 from varying when the braking device 1 is manufactured.

  The stopper 22 is not limited to the configuration in which the stopper 22 projects upward from the brake shoe 6. It suffices that the brake shoe 6 has a contact surface that is provided so as to project and that can contact the contact plate 24. For example, as illustrated in FIG. 14, stoppers 22 are provided on both sides of the brake shoe 6 in the transverse direction x so as to project downward from both sides of the contact plate 24 in the transverse direction x and contact the stoppers 22. The possible contact member 24a may be installed on the contact plate 24.

  According to this structure, when the contact plate 24 moves in the horizontal direction and reaches the vicinity of the end of the brake shoe 6, the contact member 24a contacts the stopper 22, so that the contact plate 24 moves the end of the brake shoe 6 into contact. It is possible to avoid a situation where the braking force of the brake device 1 is lost beyond that. Further, the contact members 24a arranged on both sides of the brake shoe 6 in the transverse direction x prevent the brake shoe 6 placed on the rail 2 from moving in the transverse direction x when the brake device 1 is operated, Since the brake shoe 6 can be restrained at an appropriate position on the rail 2, it is advantageous to obtain a stable braking force.

  When the pressing portion 5 is composed of the roller 11 or the like as illustrated in FIG. 2 and the like, the holding member 10 of the roller 11 is provided with a contact member 24a extending downward from both sides in the transverse direction x. It can also be configured to. Further, the stopper 22 is not limited to the configuration installed on the side of the brake shoe 6, but is constituted by a pair of stoppers 22 and the like that project from the side of the traveling body 3 toward the rail 2 as illustrated in FIG. 2 and the like. You can also

  As illustrated in FIG. 15, it is also possible to adopt a configuration in which the guide portion 26 that prevents the brake shoe 6 from moving in the transverse direction x of the rail 2 is installed. The guide portions 26 are arranged on both sides of the holder 10 in the transverse direction x and extend downward, and a pair of support pillars 27 are provided at the lower ends of the support pillars 27. The brake shoes are parallel to the traveling direction y. 6 and guide plates 28 that are arranged opposite to each other. The guide plate 28 is arranged with a gap between it and the brake shoe 6. That is, the brake shoe 6 is placed between the pair of guide plates 28. The pillar 27 that constitutes the guide portion 26 may be configured such that the upper end thereof is fixed to the traveling body 3.

  The distance between the pair of guide plates 28 in the transverse direction x is determined by the length of the brake shoe 6 in the transverse direction x in order to prevent the brake shoes 6 and the guide plate 28 from wearing each other due to constant contact. It is desirable to set it a little longer than this.

  By installing this guide portion 26, it is possible to prevent the brake shoe 6 placed on the rail 2 from moving in the transverse direction x when the brake device 1 is operated, and to place the brake shoe 6 at an appropriate position on the rail 2. A stable braking force can be obtained by restraining the.

For example, when the brake device 1 is installed on a quay crane, the quay crane may vibrate in the transverse direction x, which may cause the pressing unit 5 to move in the transverse direction x. At this time, there is a possibility that the brake shoe 6 is pushed by the pushing portion 5 and moves in the transverse direction x and does not return to its original position. When the brake shoe 6 is pushed by the pressing portion 5 in the transverse direction x and falls from the rail 2, or when the position of the brake shoe 6 in the transverse direction x is displaced and the contact area with the rail 2 is significantly reduced,
Proper braking force cannot be obtained.

  In order to prevent the guide plate 28 from coming into contact with the rail 2 and being damaged when the traveling body 3 moves in the transverse direction x due to vibration or the like, the lower end portion of the guide plate 28 has a lower end of the rail 2. It is desirable that the support 27 is installed at a position higher than the upper surface.

In the embodiment illustrated in FIG. 15, the expansion/contraction mechanism 4 includes two spring members 9 and does not include the column member 8. The extension/contraction mechanism 4 may be configured to move the pressing portion 5 in the vertical direction, and can support the vertical load F _n generated in the vertical direction z of the extension/contraction mechanism 4. Therefore, for example, the expansion/contraction mechanism 4 may be configured by one spring member 9.

  The configuration of the guide portion 26 is not limited to the above, and may be any configuration that suppresses the movement of the brake shoe 6 placed on the rail 2 in the transverse direction x when the brake device 1 is operated. For example, as illustrated in FIG. 16, the roller 11 may be configured by the roller 11 with a brim and the brim 29 may be used as the guide portion 26.

  The brim 29 is formed of an annular member protruding from the peripheral surface of the roller 11 in the outer peripheral direction, and is arranged at both ends of the roller 11 in the transverse direction x. The distance between the pair of collars 29 is formed longer than the length of the brake shoe 6 in the transverse direction x. The brake shoe 6 is arranged between the pair of collars 29 and is restrained from moving in the transverse direction x.

1 Brake Device 2 Rail 3 Traveling Body 4 Stretching Mechanism 5 Pressing Section 6 Brake Shoe 7 Elevating Mechanism 8 Supporting Member 9 Spring Member 10 Holding Tool 11 Roller 12 Pin 13 Pin 14 Rotating Shaft 15 Recess 15a Slope 16 First Horizontal Section 17 Second horizontal portion 18 String-like object 18a Extension member 19 Winding top 20 Guide portion 21 Contact member 22 Stopper 23 Tilt plate 24 Contact plate 24a Contact member 25 Height adjustment mechanism 26 Guide portion 27 Strut 28 Guide plate 29 Collar

Claims (5)

An expansion/contraction mechanism that is arranged below the traveling body that travels on the rail and expands/contracts in the vertical direction, a pressing portion that projects from the expansion/contraction mechanism toward the rail, and is arranged between the pressing portion and the rail. In a brake shoe of a brake device including a brake shoe suspended by a lifting mechanism,
A brake having a recess formed on the upper surface, a first horizontal portion formed on both sides of the recess in the rail longitudinal direction, and a second horizontal portion formed on the bottom surface of the recess. Shoe.   The brake shoe according to claim 1, wherein the first horizontal portion and the second horizontal portion are configured by horizontal planes that are parallel to each other.   The brake shoe according to claim 1, further comprising an inclined surface formed between the first horizontal portion and the second horizontal portion, wherein the inclined surface is a flat surface or a curved surface.   The brake shoe according to claim 1, wherein the second horizontal portion is formed at a position deviated from the center of the brake shoe in the rail longitudinal direction.   The brake shoe according to any one of claims 1 to 4, which has a configuration in which a fluororesin or a nylon resin is arranged on the upper surface.

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