JP2019123507A - Brake shoe of brake device - Google Patents

Abstract

To provide a brake shoe of a brake device capable of easily performing the adjustment of brake force while increasing the brake force.SOLUTION: In a brake shoe 6 suspended by a lifting mechanism of a brake device, a recessed part 15 is formed on a top surface of the brake shoe 6, first horizontal parts 16 are formed on both sides in a rail longitudinal direction y of the recessed part 15, and a second horizontal part 17 is formed on a bottom surface of the recessed part 15.SELECTED DRAWING: Figure 3

Description

The present invention relates to a brake shoe of the brake device of the running of the quay cranes and trains, etc. traveling on the rails, details while increasing the braking force, the brake shoe of the brake system the adjustment of the braking force can be easily carried out 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 a disc spring with a hydraulic cylinder at the time of releasing the brake, releases the hydraulic cylinder at the time of braking, and releases the brake shoe installed at the lower end of the disc spring by the restoring force of the disc spring. Press the top surface to stop the crane.

  In the brake device described in Patent Document 1, in order to increase the braking force, both the disc spring and the hydraulic cylinder have to be enlarged, and the manufacturing cost of the brake device is significantly increased. In addition, since the disc spring repeats compression and extension every time the crane travels and stops, deterioration may easily proceed and it may be broken. If the disc spring is broken, the braking force of the braking device is significantly reduced.

  The brake device described in Patent Document 2 pinches the side surface of the rail with two brake shoes, rotates the cam to increase the force pressing the brake shoe against the rail, and stops the crane. In the brake device described in Patent Document 2, in order to increase the braking force, it is necessary to increase the size of the motor to increase the output, so the manufacturing cost of the brake device is significantly increased. Further, even if the motor is enlarged, there is a limit to the force for sandwiching the rail with the brake shoes, and the braking force obtained for the increase of the manufacturing cost of the brake device is small.

JP, 2010-247944, A JP 06-72690 A

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

In order to achieve the above object, a brake shoe of a brake device according to the present invention comprises an expansion and contraction mechanism disposed below a traveling body traveling on a rail and vertically expanding and contracting, and projecting from the expansion and contraction mechanism toward the rail In a brake shoe of a brake device including a pressing portion to be provided, and a brake shoe disposed between the pressing portion and the rail and suspended by an elevating mechanism, a recess portion formed on the upper surface, and the recess It has a first horizontal portion formed on both sides in the rail longitudinal direction of the portion, and a second horizontal portion formed on the bottom surface of the recess .

According to the brake shoe of the present invention, when the pressing portion moves along the recess and the first horizontal portion formed in the brake shoe, the force for pressing the brake shoe is gradually increased and then maintained constant. can do. By providing the recessed portion, 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, it is possible to determine the upper limit value of the force with which the pressing portion presses the brake shoe, so it is necessary to design members constituting the brake device such as the pressing portion and the brake shoe with a higher strength than necessary. There is no Therefore, over-spec can be avoided 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 the brake device can obtain a stable braking force.

  In addition, the maximum value of the stroke amount of the telescopic mechanism can be uniquely determined from the difference in height between the first horizontal part and the second horizontal part and the difference in height between the lower surface of the brake shoe and the upper surface of the rail during standby. 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 and contraction mechanism, it is advantageous for easily adjusting the braking force of the brake device. It is advantageous to stabilize the quality of the brake system.

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 in an 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 in a BB cross section. It is an explanatory view which illustrates a brake device at the time of operation. It is explanatory drawing which illustrates the state which the press 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 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 in a 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 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 a brake system of the present invention will be described based on an embodiment shown in the drawings. In the drawing, the traveling direction (rail longitudinal direction) of the traveling body is indicated by arrow y, the transverse direction crossing the traveling direction y at a right angle is indicated by arrow x, and the vertical direction is indicated by 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 And a brake shoe 6 disposed between the press portion 5 and the rail 2, and an elevating mechanism 7 for raising and lowering 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 space extending along the traveling direction y from the support member 8 and extending downward from the traveling body 3 And a spring member 9. The support member 8 is disposed in a state in which the extending direction is parallel to the vertical direction z. The spring member 9 is disposed in a state of being inclined along the traveling direction y from a state in which the extending direction is parallel to the vertical direction z. The spring member 9 is inclined in the direction in which the upper end approaches the support member 8. In other words, 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 to 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 piled disc springs, and can extend and contract in the axial direction. The configuration of the spring member 9 is not limited to this, as long as it has a configuration such as a coil spring, a hydraulic cylinder, a mechanism combining a hydraulic cylinder and a coil spring, and the like that can expand and contract in the axial direction.

  The pressing unit 5 includes a holder 10 supported by the lower end of the support member 8 and the lower end of the spring member 9 in this embodiment, 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 respectively connected to the lower end of the support member 8 and the lower end of the spring member 9 by pins 12 and 13 whose axial direction is the transverse direction x. The roller 11 is supported by the holder 10 by a rotating shaft 14 whose axial direction is in the transverse direction x, and is configured to be rotatable around the rotating shaft 14. In FIG. 1 and FIG. 2, a part of the roller 11 is shown by a broken line for the sake of explanation.

  The brake shoe 6 is disposed between the pressing portion 5 and the rail 2 and is suspended from the side of the traveling body 3 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 a first horizontal portion 16 formed on both sides in the traveling direction y of the recessed portion 15. A second horizontal portion 17 is formed on the bottom surface which is the central portion in the traveling direction y of the recess 15 and is the lowest.

  The two first horizontal portions 16 and the second horizontal portion 17 are formed in horizontal planes 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 located above the second horizontal portion 17 and at the same height. The first horizontal portion 16 and the second horizontal portion 17 are connected by a flat inclined surface 15 a.

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

  As illustrated in FIG. 1, the elevating mechanisms 7 are respectively disposed at positions on both sides in the transverse direction x of the pressing unit 5. As exemplified in FIG. 4, the lifting mechanism 7 is provided with a string 18 having one end connected to the side opposite to the transverse direction x of the brake shoe 6, and installed on the traveling body 3 to roll up the string 18 or It has a winding upper portion 19 to be lowered or the like, and a guide portion 20 for sandwiching and guiding the string 18 from both sides.

  The string 18 is composed of, for example, a chain. The cord 18 is not limited to a chain, and may be a wire or rope, for example, as long as it has 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 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.

Winding 19 may be comprised of a drum coupled to a drive motor. By rotating the drum by the power of the drive motor, the chain can be wound up and out.

  The guide part 20 can be comprised by a pair of guide sheave. The guide sheave comprises a pin axially oriented in the transverse direction x and a sheave rotatably supported by the pin. The guide portion 20 is fixed to the side of the traveling body 3 and is disposed at a position above the brake shoe 6. The pair of guide sheaves sandwich the string 18 from both sides in the traveling direction y and guide the string 18. The guiding portion 20 is not limited to this configuration, as long as it has a configuration for restraining the string 18 at a predetermined position in the traveling direction y and guiding it in the predetermined direction, for example, a through hole extending in the vertical direction z May be formed of a cylindrical body or the like which allows the string-like material 18 to pass through the through hole.

  The elevating mechanism 7 has an abutting member 21 which maintains the posture of the brake shoe 6 in contact with the upper surface of the brake shoe 6. The contact members 21 are disposed at positions in contact with the first horizontal portions 16 on both sides in the traveling direction y of the brake shoe 6, and have lower surfaces having the same height. Since the first horizontal portions 16 of the brake shoes 6 pulled upward by the string 18 make surface contact with the lower surface of the contact member 21, the posture of the brake shoes 6 becomes horizontal.

  Stops 22 are respectively disposed on both outer sides in the traveling direction y of the brake shoe 6. The stopper 22 is fixed to the side of the traveling body 3 and has a configuration 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 quay crane travels along the rail 2, the brake device 1 is in the standby state. As illustrated in FIG. 2, at the time of standby of the brake device 1, the second horizontal portion 17 of the brake shoe 6 is disposed at a standby position where the second horizontal portion 17 contacts the roller 11 configuring 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 the 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 have 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 is not generated in the expansion and contraction mechanism 4 and the pressing portion 5, it is advantageous for suppressing deterioration due to fatigue or the like. In addition, when disassembling the brake device 1 for maintenance, the spring member 9 which has been contracted does not extend suddenly and push the brake shoe 6 downward, so the safety during maintenance work is improved. Is advantageous.

  When the traveling body 3 such as a wharf crane completes movement to a predetermined position and performs cargo handling work, etc., the brake device 1 is brought into the operating state. As illustrated in FIG. 5, when the brake device 1 is activated, the suspension by the lifting mechanism 7 is released to cause the brake shoe 6 to fall downward. Specifically, the string 18 is fed out by the winding portion 19. By the operation of the lift mechanism 7, the brake shoe 6 is moved to an operating position where the lower surface of the brake shoe 6 and the upper surface of the rail 2 are in contact with each other. At this time, it is desirable that the string 18 be unrolled from the winding portion 19 until it is sufficiently slackened. 5-8, the expansion-contraction mechanism 4 and the press part 5 and the raising / lowering mechanism 7 are shown in the same drawing for description.

When the extension 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, between the roller 11 of the pressing portion 5 and the second horizontal portion 17 of the brake shoe 6, a gap having the same length as the dropped distance of the brake shoe 6 is generated.

At this time, the upper surface of the brake shoe 6 and the circumferential surface of the roller 11 constituting the pressing portion 5 are not in contact with each other, and no force is generated to compress the extension mechanism 4. Does not occur. That is, since the vertical load F _n is not generated on the brake shoe 6, the braking force of the brake device 1 becomes zero as illustrated in FIG.

  When a breakaway occurs in which the traveling body 3 such as a quay crane moves from a predetermined position due to wind, vibration or the like when the brake device 1 is activated, it is mounted on the rail 2 as illustrated in FIG. The brake shoe 6 which has been stopped stays in place, and the pressing portion 5 fixed on the side of the traveling body 3 moves in the traveling direction y.

  In order to prevent tension from being generated in the string 18 when the traveling body 3 escapes and the brake shoe 6 to move in the traveling direction y, the string 18 is drawn out longer from the winding portion 19 and slackened. Alternatively, the string-like member 18 may be appropriately fed out from the winding portion 19 according to the movement of the traveling body 3. For example, in a free state where the drum constituting the winding portion 19 can be rotated with almost no resistance, the string-like material 18 may be automatically fed out according to the tension generated in the string-like material 18.

  When the traveling body 3 escapes, the roller 11 moved in the traveling direction y along with the movement of the traveling body 3 contacts the inclined surface 15 a of the recess 15. Thereafter, the roller 11 moves upward along the recess 15 while rotating. That is, the roller 11 moves in the traveling direction y in accordance with the movement distance of the traveling body 3 and is pushed upward along the upper surface of the recessed portion 15.

  At this time, the expansion and contraction mechanism 4 contracts in accordance with the height at which the roller 11 is pushed up. The support member 8 is formed of a columnar or the like whose length does not change, and the spring member 9 is configured to be extensible and contractible in the axial direction. Therefore, the holder 10 of the pressing portion 5 tilts about the pin 12 connected to the lower end of the support member 8. The tilt of the holder 10 causes the roller 11 to move in the vertical direction z. The spring member 9 constituted by a disc spring or the like shrinks 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 circumferential surface of the roller 11 and the upper surface of the brake shoe 6 with the increase of the vertical load F _n and the frictional force generated between the lower surface of the brake shoe 6 and the upper surface of the rail 2 It will 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 can easily maintain its relative position to the rail 2 . That is, the brake shoe 6 tries to stay on the spot without moving on the rail 2 even when pressed by the force in the traveling direction y by the pressing portion 5.

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

At this time, each member is designed such that the coefficient of friction μ _A between the circumferential surface of the roller 11 and the brake shoe 6 is smaller than the coefficient of friction μ _B between the brake shoe 6 and the rail 2 . By pressing unit 5 is configured to include a roller 15, it can be easily reduced than the frictional coefficient mu _B the friction coefficient mu _A between the pressing portion 5 and the brake shoe 6.

A vertical load F _n having the same magnitude in the vertical direction z is generated 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 circumferential surface of the roller 11 and the brake shoe 6, and this frictional force is the brake shoe It is represented by the product of the vertical load F _n in the up-down direction z generated at 6 mag and the friction coefficient μ _A.

As illustrated in FIG. 9, when the pressing portion 5 is in contact with the inclined surface 15 a of the recessed portion 15, the braking force increases in accordance with the escape distance of the traveling body 3. When the traveling force of the traveling body 3 exceeds this braking force, the roller 11 further moves the inclined surface 15a of the recessed portion 15 upward, and reaches the first horizontal portion 16 soon as illustrated in FIG. 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 the vertical load F _n in the vertical direction z generated on the brake shoe 6 becomes constant. Braking force of the brake device 1, since it is determined by integration of the vertical load F _n and the coefficient of friction mu _A to be the constant value, the braking force as illustrated in FIG. 9 is a constant value F _A.

If towards the escape forces of the running body 3 is larger than the brake force F _A as illustrated in FIG. 8, further traveling body 3 is the brake shoe 6 comes into contact with the stopper 22 without stopping. The brake shoe 6 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 in contact with the stopper 22.

  At this time, the lifting mechanism 7 is configured so as not to inhibit 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 lifting and lowering mechanism 7 can pull out from the winding portion 19 a string 18 having such a length that the brake shoe 6 can move to a position where the brake shoe 6 contacts the stopper 22 when the brake device 1 is actuated. Further, the lifting mechanism 7 can wind the string 18 up to a height such 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 lifting 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 the brake shoe 6 can be moved to a position contacting the stopper 22 when the traveling body 3 travels away. It suffices to have a configuration. The elevating mechanism 7 may be constituted by, for example, a cylinder mechanism such as a hydraulic cylinder that can expand and contract in the vertical direction z, and a swing arm installed at the lower end of the cylinder mechanism and configured to be 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 in contact with each other, the brake shoe 6 moves integrally with the traveling body 3 in the direction of travel of the traveling body 3. That is, the brake shoe 6 is apparently fixed to the side of the traveling body 3. Therefore, when the brake shoe 6 is in contact with the stopper 22 as illustrated in FIG. 9, the braking force of the brake device 1 has a coefficient of friction 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 has a constant value F _B because it is obtained by integration with the vertical load F _n .

Braking force of the brake device 1, the friction coefficient mu _B between the friction coefficient mu _A or the lower surface and the upper surface of the rail 2 of the brake shoe 6 between the circumferential surface and the upper surface of the brake shoe 6 of the roller 11, the brake shoe It can be obtained by integration with the vertical load F _n generated in 6th grade. That is, since the vertical load F _n can be easily increased using the weight of the traveling body 3, the braking force of the braking device 1 can significantly increase the braking force.

By providing the first horizontal portion 16 and the second horizontal portion 17 on the upper surface of the brake shoe 6, the upper limit value of the vertical load F _n can be determined in advance and easily adjusted. As illustrated in FIG. 4, the maximum value of the stroke amount of the expansion and contraction mechanism 4 in the vertical direction z is the difference between the height h1 of the first horizontal portion 16 and the second horizontal portion 17 of the brake shoe 6 in the standby position. The difference h2 in height between the lower surface and the upper surface of the rail 2, that is, the length h1−h2 obtained by subtracting the falling distance of the brake shoe 6 when the brake device 1 is operated. In the present specification, the stroke amount represents the expansion and contraction length of the expansion and contraction mechanism 4 in the vertical direction z.

  For example, if 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 maximum value of the stroke amount in the direction z is 6 mm. That is, by providing the first horizontal portion 16 and the second horizontal portion 17 on the brake shoe 6 and setting the contact position of the roller 11 of the pressing portion 5 and the second horizontal portion 17 as the standby position of the brake shoe 6, The maximum value of the stroke amount of the expansion and contraction mechanism 4 can be uniquely determined.

  Thereby, the braking force of the brake device 1 can be determined regardless of the angle of the inclined surface 15 a of the recess 15 or the like. That is, when processing the recessed portion 15 of the brake shoe 6, the lengths of the first horizontal portion 16 and the second horizontal portion 17 in the traveling direction y vary, or from the first horizontal portion 16 to the second horizontal portion 17 Even if the angle of the inclined surface 15a is uneven, or even if the inclined surface 15a is formed by 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 of a predetermined magnitude. It is advantageous for performing quality control of the brake shoe 6 accurately.

  Further, the difference h2 in height between the lower surface of the brake shoe 6 and the upper surface of the rail 2 can be adjusted by the elevating mechanism 7. The length h2 of the height can be reduced by increasing the feeding length of the string 18 of the lifting 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 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 in the standby position. Specifically, a height adjustment mechanism such as a spacer is disposed between the traveling body 3 and the expansion and contraction mechanism 4 to lower the installation position of the expansion and contraction mechanism 4.

  The height adjustment mechanism may be installed between the brake device 1 and the traveling body 2. That is, the installation positions of the extension mechanism 4 and the lifting mechanism 7 may be simultaneously adjusted by the height adjustment mechanism. According to this configuration, since the entire brake device 1 can be moved in the vertical direction z, the adjustment of the height of the brake shoe 6 and the adjustment of the height of the extension mechanism 4 by the lifting mechanism 7 can be individually performed as described above. There is no need to do it. The braking force of the brake device 1 can be adjusted more easily.

  Since the height difference h2 decreases, the maximum value h1-h2 of the stroke amount of the expansion and contraction mechanism 4 increases, and the braking force of the brake device 1 increases. On the other hand, if the position of the contact member 21 is increased to adjust the height difference h2 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 difference h1 in height between the first horizontal portion 16 and the second horizontal portion 17 of the brake shoe 6. Since the braking force of the braking device 1 can be easily adjusted, quality control of the braking device 1 can be easily performed.

  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 the replacement of the brake shoe 6 and the adjustment by the height adjustment mechanism. It is advantageous to perform quality control of the brake device 1.

By configuring the extension and contraction mechanism 4 with the column member 8 whose length is fixed and the expandable and contractible spring member 9, a part of the vertical load F _n generated in the extension and 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 enlargement of the spring member 9 and suppressing the occurrence of failure or damage.

  Further, by arranging the spring member 9 in a state in which it is inclined in the traveling direction y from a state parallel to the vertical direction z, a large stroke amount of the spring member 9 can be secured. Since it is easy to smoothly raise the braking force of the brake device 1 when the traveling body 3 travels, it is advantageous for avoiding a failure that the brake device 1 breaks down due to an impact.

  If the first horizontal portion 16 is provided on the brake shoe 6 so that the roller 11 rides on the first horizontal portion 16, even if the roller 11 reciprocates in the traveling direction y due to vibration etc. The braking force can be maintained constant. The brake device 1 is advantageous for obtaining a stable braking force.

The roller 11 moves on the upper surface of the brake shoe 6 and exceeds the end thereof when the force of the traveling body 3 for traveling away exceeds the braking force F _A and the traveling of the traveling body 3 can not be stopped due to the arrangement of the stopper 22. And the loss of braking force can be avoided.

When the brake shoe 6 is moved together with the traveling member 3 abuts against the stopper 22 is obtained is large braking force F _B than the braking force F _A generated between the pressing portion 5 and the brake shoe 6. If the order to install the stopper 22, it is possible to determine the intensity of the member or the like constituting the brake apparatus 1 in accordance with the magnitude of the braking force F _B in the appropriate range, these members to overspecification 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 maximum value of the braking force F _B generated between the brake shoe 6 and the rail 2 are the same as the values of the vertical loads Fn, respectively. The coefficient of friction μ _A and the value of μ _B depend on

  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 the departure is not so large or the like, the brake device 1 can be configured without the stopper 22.

If the traveling body 3 does not escape even when the brake device 1 is activated, the vertical load F _n is not generated on the brake shoe 6 or the like. That is, since stress is generated only when the traveling body 3 escapes to the expansion / contraction mechanism 4, the pressing portion 5 and the brake shoe 6, it is advantageous for suppressing deterioration of these members. Similarly, since the stress is generated only when the traveling body 3 travels, the other members constituting the brake device 1 are advantageous for suppressing the deterioration of these members.

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

  Thereafter, when the string 18 is wound up by the winding portion 19 of the lifting mechanism 7, the brake shoe 6 rises toward the standby position and moves in the traveling direction y. Since the cord 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 1 in which direction the brake shoe 6 is. That is, by installing the guide portion 20, the brake shoe 6 can be easily moved to the standby position where the roller 11 of the pressing portion 5 and the second horizontal portion 17 of the brake shoe 6 contact.

  When the first horizontal portion 16 on the upper surface of the brake shoe 6 comes in contact with the lower surface of the contact member 21, the winding of the string 18 by the winding portion 19 is stopped. Since the posture of the brake shoe 6 in a state 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 in parallel with the upper surface of the rail 2. It is advantageous to prevent an accident in which the brake shoe 6 in the standby state is inclined and comes in 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 restoration work of the brake device 1 is completed, the traveling body 3 can travel in any direction.

  A position sensor may be provided to detect the position of the brake shoe 6 with respect to the pressing portion 5 in order to detect the presence or absence of the traveling of the traveling body 3 and the direction thereof when the brake device 1 is restored. This position sensor can be configured, for example, by a laser scanner or the like which measures a distance by irradiating a plurality of laser beams along the rail 2 which is installed on the lower surface or the pressing portion 5 of the traveling body 3 and becomes the opposite surface. The position where the brake shoe 6 is placed on the rail 2 can be specified from the plurality of distance values obtained by the laser scanner. As a result, it is possible to know whether it is necessary to cause the traveling body 3 to travel when releasing the brake, and if necessary, to know the direction in which the traveling body 3 is to travel. it can.

The configuration of the extension and contraction mechanism 4 is not limited to the above 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 unit 5 is not limited to the above embodiment. Any configuration may be employed as long as it can move 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 actuated. Furthermore, the elevation mechanism 7 is not limited to the above 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 and contraction mechanism 4 may be arranged in parallel to the vertical direction z. The support member 8 and the spring member 9 are disposed in parallel to the vertical direction z.

Further, the pressing portion 5 can be configured to include a tilting plate 23 fixed below the extension mechanism 4 and a contact plate 24 protruding downward from the lower surface of the tilting plate 23. The contact plate 24 is formed of a plate-like member whose lower end is processed into a curved surface. Friction coefficient mu _A between the upper surface of the contact plate 24 and the brake shoe 6 is, so that less than the friction coefficient mu _B between the lower and upper surfaces of the rails 2 of the brake shoe 6, the lower end of the contact plate 24 And the upper and lower surfaces of the brake shoe 6 are processed.

For example it is possible to adopt a configuration for reducing the friction coefficient mu _A to the lower portion and the upper surface of the brake shoe 6 of the contact plate 24 by placing a fluorine resin or a nylon resin. Further, when the brake device 1 is operated, 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 performing the processing of roughening the surface of the lower surface of the brake shoe 6, it is also possible to adopt a configuration to increase the friction coefficient mu _B between the upper surface of the rail 2.

  The winding portion 19 of the lifting mechanism 7 is installed on the traveling body 3 in a state in which one end can be raised and lowered, and is constituted by an arm member in which the string-like body 18 is connected to the other end. When the other end of the arm member is raised upward, the brake shoe 6 is pulled upward, and when it is lowered downward, the brake shoe 6 is lowered.

The height adjustment mechanism 25 may be disposed between the brake device 1 and the traveling body 3. The height adjustment mechanism 25 is configured to move 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 mechanism 4 and the lifting mechanism 7 can be moved in the vertical direction z.

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

  The spacer may be formed of, for example, a plurality of plate-like materials 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 plate-like objects. 10 and 11 show a state in which the height adjustment mechanism 25 is configured by a plurality of plate-like spacers.

  The brake shoe 6 is provided with stoppers 22 provided on the upper surface of the first horizontal portion 16 and at both ends in the traveling direction y of the brake shoe 6. The stopper 22 is formed 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 15 a of the recessed portion 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 escapes when the brake device 1 is actuated, the contact plate 24 moves horizontally while rising along the recess 15 on the upper surface of the brake shoe 6, and after moving to the first horizontal portion 16, the stopper 22 Contact In FIG. 10, the contact plate 24 in a state of being 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 and the traveling body 3 further travels in the same direction, the brake shoe 6 is pushed by the contact plate 24 and moves integrally with the traveling body 3.

  By providing the stopper 22 on the side of the brake shoe 6, the configuration of the brake device 1 can be simplified, which is advantageous for reducing the number of parts. Further, by increasing the inclination of the inclined surface 15a of the recess 15, the rate at which the contact plate 24 ascends with respect to the escape distance when the traveling body 3 escapes increases, so the braking force can be rapidly increased. It is advantageous to stop the traveling body 3 from leaving.

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

  The inclined surface 15a of the recessed part 15 can also be comprised by a curved surface so that it may illustrate in FIG. According to this configuration, as illustrated in FIG. 13, the braking force acting on the traveling body 3 can be gradually increased. That is, it is possible to suppress that the braking force is rapidly increased and the impact due to the sudden braking is generated on the traveling body 3. This is advantageous, for example, if the traveling body 3 can be allowed to travel a certain distance, and it is not desirable that an impact be caused to the traveling body 3 at the time of braking.

As illustrated in FIG. 12, the second horizontal portion 17, which is the lowest point of the depressions 15 at the lowest point, may be offset from the center of the brake shoe 6 in the traveling direction y. According to this configuration, it is possible to provide the brake device 1 in which the way of increasing the braking force is different depending on the direction of travel of the traveling body 3.

  Even when the recessed portion 15 is formed into a complicated shape such as a curved surface, the difference h1 in height between the first horizontal portion 16 and the second horizontal portion 17 can be accurately determined. The maximum value of force can be determined uniquely. It is advantageous for suppressing variation in the maximum value of the braking force of each brake device 1 at the time of manufacture of the brake device 1.

  The stopper 22 is not limited to the configuration projecting upward from the brake shoe 6. It suffices to have an abutting surface which is provided so as to protrude from the brake shoe 6 and can abut on the contact plate 24. For example, as illustrated in FIG. 14, stoppers 22 respectively project on both sides in the transverse direction x of the brake shoe 6 and extend downward from both sides in the transverse direction x of the contact plate 24 and abut on the stoppers 22. A possible abutment member 24 a can also be arranged on the contact plate 24.

  According to this configuration, 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 abuts against the stopper 22, so that the contact plate 24 becomes the end of the brake shoe 6 It is possible to avoid the situation where the braking force of the brake device 1 is lost due to overtaking. The contact members 24a disposed on both sides in the transverse direction x of the brake shoe 6 prevent the brake shoe 6 mounted on the rail 2 from moving in the transverse direction x when the brake device 1 is actuated, As 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 constituted by the roller 11 and the like as illustrated in FIG. 2 and the like, the holding member 10 of the roller 11 is provided with the contact members 24a extending downward from both sides in the transverse direction x. Can also be configured. Further, the stopper 22 is not limited to the structure installed on the side of the brake shoe 6, and is constituted by a pair of stoppers 22 and the like protruding toward the rail 2 from the side of the traveling body 3 as illustrated in FIG. It can also be done.

  As illustrated in FIG. 15, a guide portion 26 may be provided to prevent the brake shoe 6 from moving in the lateral direction x of the rail 2. The guide portion 26 is disposed on both sides in the transverse direction x of the holder 10 and extends downward, and a pair of brake shoes installed at the lower end of the post 27 and parallel to the traveling direction y. 6 and a guide plate 28 disposed opposite to each other. The guide plate 28 is disposed with a gap between the guide plate 28 and the brake shoe 6. That is, the brake shoe 6 is placed between the pair of guide plates 28. The support 27 constituting 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 the length of the brake shoes 6 in the transverse direction x in order to suppress the mutual wear due to the constant contact between the brake shoes 6 and the guide plates 28. It is desirable to set slightly longer than

  The installation of the guide portion 26 prevents the brake shoe 6 placed on the rail 2 from moving in the transverse direction x when the brake device 1 is actuated, and the brake shoe 6 is positioned at an appropriate position on the rail 2. You can obtain a stable braking force by restraining.

For example, when the brake device 1 is installed on a wharf crane, the wharf crane may vibrate in the transverse direction x, whereby the pressing unit 5 may move in the transverse direction x. At this time, there is a possibility that the brake shoe 6 is moved in the transverse direction x and is not returned to the original position by being pushed by the pressing portion 5. When the brake shoe 6 is pushed in the transverse direction x by the pressing portion 5 and falls from the rail 2 or the position in the transverse direction x with respect to the rail 2 shifts and the contact area with the rail 2 decreases significantly,
The appropriate braking force can not be obtained.

  When the traveling body 3 is moved in the transverse direction x due to vibration or the like, the lower end portion of the guide plate 28 is the same as that of the rail 2 in order to prevent the guide plate 28 from contacting and damaging the rail 2. It is desirable that the support 27 be installed in a position higher than the upper surface.

In the embodiment illustrated in FIG. 15, the extension and contraction mechanism 4 is configured of two spring members 9 and does not include the support member 8. The extension and contraction mechanism 4 may be configured to move the pressing portion 5 in the vertical direction and to be able to support the vertical load F _n generated in the vertical direction z of the extension and contraction mechanism 4. Therefore, for example, the expansion and 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 any configuration may be employed as long as the brake shoe 6 mounted on the rail 2 is prevented from moving in the transverse direction x when the brake device 1 is actuated. For example, as illustrated in FIG. 16, the roller 11 may be configured by a roller 11 with a flange, and the flange 29 may be used as the guide 26.

  The flange 29 is formed of an annular member protruding in the outer circumferential direction from the circumferential surface of the roller 11 and is disposed at both ends in the transverse direction x of the roller 11. The distance between the pair of flanges 29 is formed to be longer than the length in the transverse direction x of the brake shoe 6. The brake shoe 6 is disposed between the pair of flanges 29 and is restrained from moving in the transverse direction x.

Reference Signs List 1 brake device 2 rail 3 traveling body 4 extension and contraction mechanism 5 pressing portion 6 brake shoe 7 lifting and lowering mechanism 8 support member 9 spring member 10 holder 11 roller 12 pin 13 pin 14 rotation shaft 15 recessed portion 15 a inclined surface 16 first horizontal portion 17 Second horizontal portion 18 String 18a Extension member 19 Winding portion 20 Guide portion 21 Contact member 22 Stopper 23 Tilting plate 24 Contact plate 24a Contact member 25 Height adjustment mechanism 26 Guide portion 27 Column 28 Guide plate 29 Flange

Claims (5)

A telescopic mechanism disposed below the traveling body traveling on the rail and telescopically expanding in the vertical direction, a pressing portion protruding from the telescopic mechanism toward the rail, and a portion between the pressing portion and the rail And a brake shoe having a brake shoe suspended by the lift mechanism,
A brake characterized by having a recess formed on the upper surface, a first horizontal portion formed on both sides in the rail longitudinal direction of the recess, and a second horizontal portion formed on the bottom of the recess. Shoe.   The brake shoe according to claim 1, wherein the first horizontal portion and the second horizontal portion are formed in horizontal planes 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 any one of claims 1 to 3, wherein the second horizontal portion is formed at a position offset 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 fluorine resin or a nylon resin is disposed on the upper surface.

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