JP2019077563A - Braking device for travel crane - Google Patents

Abstract

To provide a braking device for a travel crane capable of easily allowing a maintenance/inspection work, realizing stable operation, free from environmental contamination, hardly influenced by an environmental temperature.SOLUTION: There is provided a braking device for a travel crane comprising: a brake friction member 5 which performs brake action by performing pressure-contact with/separating from a rail R; a male screw rod 28 which is rotated by an electric motor M; a lifting member 26 which moves vertically and reciprocatingly, screwed to the outside of the male screw rod 28 in an externally-fitted manner; a pair of right and left arm members 6, 6 having the brake friction member 5 provided at its lower end portion; and a spring member 29 which energizes the lifting member 26 always upward; wherein a screwing portion 70 of the lifting member 26 and the male screw rod 28 are configured with a ball screw 71 or a screw which does not satisfy a self-sustaining condition of a screw, wherein the lifting member 26 moves upward with the male screw rod 28 rotated by an urging force of the spring member 29 in a stopped state of the electric motor M, and wherein the lower end portion of the pair of right and left arm members 6, 6 is closed to bring the brake friction member 5 to come in pressure contact with a head side surface 9 of the rail.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a braking system for a traveling crane.

  Conventionally, in order to prevent a traveling crane traveling along a rail laid on the quay of a harbor from escaping due to wind gusts, earthquakes, etc., a traveling crane for extending a hydraulic cylinder and pressing a braking friction member against the rail There has been a braking device (see, for example, Patent Document 1).

Unexamined-Japanese-Patent No. 2003-238069

  However, in the hydraulic cylinder, there is a possibility that the hydraulic oil may flow out and contaminate the harbor due to the service life of the hydraulic piping and the seal, the contact accident and the like. Also, there is a problem that hydraulic oil expands and contracts depending on the ambient temperature, and the operation is not stable, and there are many parts such as hydraulic pump, hydraulic tank, hydraulic piping equipment, etc., requiring a lot of time and effort for maintenance and inspection. In addition to this, there is also a problem that the entire apparatus becomes large.

  Therefore, according to the present invention, there is no risk of environmental pollution, stable operation can be realized with little adverse effect of ambient temperature (environmental temperature), and a traveling crane that can easily perform maintenance and inspection work It is an object of the present invention to provide a braking system for

The braking system for a traveling crane according to the present invention is a braking system attached to a traveling crane that moves along a rail, comprising: a braking friction member that performs a pressing action against the rail and performs a braking operation; A vertical male screw that rotates, an elevating member that is engaged with the male screw in an externally fitted shape and reciprocated up and down, a pair of left and right arm members with the braking friction member attached to the lower end, A spring member for constantly urging the lift member upward, and the screwing portion of the lift member and the male screw rod is constituted by a ball screw or a screw which does not satisfy the self-supporting condition of the screw In the electric stop state of the electric motor, the elevating member is moved upward while rotating the male screw rod by the resilient biasing force from the spring member, and the lower ends of the pair of left and right arm members are closed. And the above braking Friction member is that configured to be press rail head side surfaces.
Further, a pair of left and right pressing rollers are pivotally attached to the elevating member, and the arm member is provided at the upper end portion with an inclined surface which inclines inward leftward and rightward, and the elevating member moves upward Then, the pressing roller slides on the inclined surface and spreads the upper end portions of the pair of left and right arm members to close the lower end portions of the pair of left and right arm members, and the braking friction member makes the rail head It is configured to be in pressure contact with the side surface of the part.

  Further, in a braking system attached to a traveling crane which moves along a rail, a braking / friction member which performs a braking action by pressing on and separating from the rail and a vertical male screw which is rotated by an electric motor A pair of left and right pressing rollers are pivotally mounted, and an elevating member is engaged with the male screw rod so as to be reciprocated up and down, and the braking friction member is attached to the lower end portion and upward to the upper end portion And a pair of left and right arm members provided with inclined surfaces which are inclined toward the left and right inwards, and the screwing portion of the elevating member and the male screw is constituted by a screw satisfying the self-supporting condition of the screw The electric motor is driven to move the elevating member upward while rotating the male screw rod, and the pressing roller is in sliding contact with the inclined surface to push and spread the upper end portions of the pair of left and right arm members. Arm of The lower end portion of the elevating member is closed so that the braking friction member is brought into pressure contact with the side surface of the rail head, and further, with the electric motor stopped, the self-locking of the screwing portion Vertical movement is blocked, and the open / close state of the lower end portions of the pair of left and right arm members is held as it is.

  Further, in a braking system attached to a traveling crane which moves along a rail, a braking / friction member which performs a braking action by pressing on and separating from the rail and a vertical male screw which is rotated by an electric motor A raising and lowering member screwing up and down reciprocatingly engaged with the male screw rod, a pair of left and right arm members having the braking friction member attached to a lower end portion, a vertical reciprocating movement of the raising and lowering member and the left and right A left and right interlocking link member for interlocking the opening and closing operation of the lower end of the pair of arm members; one end of the left and right interlocking link member and the other end of the other interlocking link member And coaxially pivoting to the elevating member, and further pivotally attaching the other end of one of the left and right interlocking link members to the upper end of one of the left and right arm members; The other end The left and right interlocking link members are arranged in a V-shape in a front view by being pivotally attached to the upper end of the other right arm member, the electric motor is driven to rotate the male screw rod while moving up and down The member is moved upward, one end of the pair of left and right interlocking link members is lifted, and the other end is moved left and right outward, and the upper end of the pair of left and right arm members is opened leftward and rightward, The lower ends of the pair of left and right arm members are closed so that the braking friction member is in pressure contact with the side surface of the rail head, and the self-locking of the screwing portion is stopped when the electric motor is stopped. Thus, the vertical movement of the elevating member is blocked, and the open / close state of the lower end portion of the pair of left and right arm members is maintained as it is.

  According to the braking system of the traveling crane of the present invention, there is no need for hydraulic units such as hydraulic pumps and hydraulic tanks, so that the structure can be simplified and downsizing of the apparatus can be realized, and parts maintenance and inspection can be performed quickly. And it becomes easy to do. There is no risk of hydraulic fluid flowing out of the device, and there is no risk of environmental pollution. Stable operation can be realized without being adversely affected by environmental temperature (air temperature). It can reduce consumable parts and reduce maintenance costs.

It is the schematic of a traveling crane. It is a schematic side view of a braking system of a traveling crane of the present invention. It is a principal part section front view showing a 1st embodiment of the present invention. It is a principal part cross-sectional front view which shows 2nd Embodiment. It is a principal part cross-sectional front view which shows 3rd Embodiment. It is a principal part cross-sectional front view which shows 4th Embodiment. It is a principal part cross-sectional front view which shows 5th Embodiment. FIG. 7 is a simplified cross-sectional side view showing another embodiment. It is a simplified cross section side view showing the modification of other embodiments. (A) is an enlarged sectional front view of a non-braking state, (B) is an enlarged sectional front view of a preliminary braking state, (C) is an enlarged sectional front view of the main braking state FIG. It is an enlarged sectional plan view explaining a step-wise braking action, (A) is an enlarged sectional plan view of a non-braking state, (B) is an enlarged sectional plan view of a preliminary braking state, (C) is a main braking It is an enlarged sectional top view of a state. It is a principal part enlarged section front view showing a rail head side correction tool. It is a perspective view which shows the modification of an arm member, a damping | braking friction member, and a wedge type interlocking connection mechanism. FIG. 14 is an enlarged front view of the main part of FIG. 13, (A) is an enlarged cross-sectional front view of a non-braking state, (B) is an enlarged cross-sectional front view of a preliminary braking state, and (C) is a main braking state It is an enlarged section front view. It is an enlarged sectional plan view explaining a step-wise braking action, (A) is an enlarged sectional plan view of a non-braking state, (B) is an enlarged sectional plan view of a preliminary braking state, (C) is a main braking It is an enlarged sectional top view of a state.

Hereinafter, the present invention will be described in detail based on the drawings showing the embodiments.
The braking system of the traveling crane according to the present invention comprises, for example, as shown in FIG. 1, traveling devices 42, 42 for traveling along rails R, R at the lower end of the support legs of a portal crane body 41. It is attached to a provided traveling crane (gantry crane) 40 to prevent the traveling crane 40 from escaping due to gusts or earthquakes. The traveling crane 40 may be new or existing.

As shown in FIG. 2, the braking device Z of the traveling crane according to the present invention includes a bracket 44 attached to a lower frame 41 a extending horizontally so as to connect the support legs of the crane main body 41, and A braking unit (internal unit) 45 to be accommodated is provided. The bracket 44 is formed in a rectangular shape in plan view, and surrounds the braking unit 45 in a loose fitting manner.
As shown in FIGS. 3 to 7, the braking unit 45 is mounted on a traveling carriage 33 having traveling rollers 32 (pairs of front and rear) rolling on the rail R.
Since the bracket 44 and the braking unit 45 are not connected and fixed, the braking unit 45 mounted on the traveling carriage 33 can travel following the ups and downs of the rail R. When the traveling crane 40 travels along the rail R, the bracket 44 is configured to push or pull the braking unit 45.

  The braking unit 45 includes a braking friction member 5 that performs a braking action by pressing on and separating from the rail R, a pair of left and right arm members 6 and 6 to which the braking friction member 5 is attached at the lower end, and an electric motor M A rotating vertical male screw rod 28 and an elevating member 26 screwed on the male screw rod 28 in an externally fitted shape and reciprocatingly moving up and down are provided, and the elevating member 26 and the braking friction member 5 are interlocked .

The lower end portions of the pair of left and right arm members 6 and 6 are pivotally mounted on the left and right sides of the base portion (member) 27 mounted (attached) to the traveling carriage 33 by pivot shafts 23 and 23, respectively. The lower end is provided so as to be openable and closable in the left and right direction. Then, when the male screw rod 28 is rotated by the electric motor (electric motor) M, the elevating member 26 is provided so as to reciprocate up and down without rotating.
The lower end portions of the pair of left and right arm members 6, 6 are operated to open and close along with the up and down reciprocation of the raising and lowering member 26, so that the braking friction member 5 is brought into pressure contact with and separated from the rail head side surface 9. .

First, a first embodiment shown in FIG. 3 will be described.
In the first embodiment, the braking unit 45 is provided with a coil spring type spring member 29 which is disposed upright on the base portion 27 so as to always bias the lifting member 26 upward. The spring member 29 and the male screw rod 28 are disposed coaxially (at the same position in the left-right direction and at the same position in the front-rear direction).

A pair of left and right pressing rollers (pressing members) 25, 25 is pivotally attached to the elevating member 26. At the upper end portions of the pair of left and right arm members 6, 6, wedge members 13, 13 having inclined surfaces (taper surfaces) 13a, 13a which are inclined to the left and right inwards (adjacent to each other) are fixed. The pressing rollers 25 and 25 slide in contact with the inclined surfaces 13a and 13a of the wedge members 13 and 13 as the lifting member 26 moves upward, and press the wedge members 13 and 13 outward in the left-right direction. .
The pair of left and right arm members 6, 6 is resiliently urged in the direction in which the upper end portions of the pair of left and right arm members 6, 6 approach each other so that the wedge member 13 always contacts the pressing roller 25. A tension spring 14 is attached.

  The screwing portion 70 of the male screw rod 28 and the female screw portion 26 d of the elevating member 26 is configured by the ball screw 71. The ball screw 71 is capable of idle rotation in which the male screw rod 28 receives no rotational force or braking force (braking force) from the electric motor M, and the elevating member 26 can move in the axial direction of its own weight or other members' weight or external force When the force in the axial direction is received, the elevating member 26 is configured to be vertically movable while rotating the male screw 28. In other words, the ball screw 71 is a screw in which the self-locking function does not work.

In the state shown in FIG. 3, the electric motor M is driven to rotate the male screw rod 28 in a predetermined direction (forward rotation) to resist the resilient biasing force of the spring member 29 (while shortening the spring member 29) The raising and lowering members 26 are lowered, and the upper end portions of the arm members 6 and 6 are made to approach each other by the resilient biasing force of the tension spring 14, and the braking friction members 5 of the lower end portions of the pair of left and right arm members 6 and 6 5 (brake shoes 12, 12) are in a non-braking state in which the rail head side surfaces 9, 9 are separated.
In this non-braking state, the male screw rod 28 is incapable of rotating by the braking force from the electric motor M, and the vertical position of the elevating member 26 is maintained (vertical movement is blocked).

Then, although not shown, in order to set the braking state, the braking force from the electric motor M is released, or the electric supply to the electric motor M is stopped (an electric stopping state to the electric motor M is set) .
Then, the male screw rod 28 is allowed to idle (rotate) freely, and the elevating member 26 receiving the resilient biasing force upward from the spring member 29 moves upward while rotating the male screw rod 28, and the pressing roller 25 , 25 press the inclined surfaces 13a, 13a of the wedge members 13, 13 to push and spread the upper end portions of the arm members 6, 6 (against the resilient biasing force of the tension spring 14). The lower end portion of 6 is closed, and the braking friction members 5 and 5 are pressed against the rail head side surfaces 9 and 9 to hold the rail head in a braking state (also referred to as a main braking state described later) Yes).

By this configuration, when the electric power supply to the electric motor M is stopped due to a typhoon, an earthquake or the like in the non-braking state, the screwing portion 70 does not self lock, and the spring member 29 is resiliently attached. The braking state can be automatically made by the force, and the runaway of the traveling crane 40 can be prevented.
Further, even when the electric motor M is stopped in the braking state, since the upward elastic biasing force from the spring member 29 continues to be received, the braking state is maintained as it is.
In order to set the braking state, the electric motor M is driven to rotate the male screw 28 (reverse rotation) to raise the lifting member 26 and close the lower end portions of the pair of left and right arm members 6, 6 It is also possible.

Furthermore, control processing (calculation) units such as a CPU and a sequencer, storage units such as a RAM, a ROM, and a flash memory, rotation angle detection means such as an encoder for detecting the rotation angle position of the male screw 28, The rotational angle control means is provided with a braking completion confirmation means for determining whether or not the dynamic friction member 5 is in a braking state in which the dynamic friction member 5 is in pressure contact with the rail head side face 9.
The control processing unit is provided to be able to receive rotational control of the electric motor M and read (measurement) signals from each sensor. The braking completion confirmation means is a sensor capable of confirming the presence or absence or position of one or more of the members such as the male screw rod 28, the braking friction member 5, the raising and lowering member 26, the arm member 6, the spring member 29 and the like. Etc.

The rotational angle control means encoders the rotational angle position of the male screw rod 28 in the braking state in which the lower ends of the pair of left and right arm members 6, 6 are closed and the braking friction member 5 is in pressure contact with the rail head side surface 9 It is configured to be read by the angle detecting means, and to store the read rotational angle position as the reference position (to be stored in the storage unit).
That is, the rotational angle position of the male screw 28 is reset (restored) as the reference position each time the braking state is achieved.
Then, the rotation angle control means operates the electric motor M while detecting the rotation angle position by the rotation angle detection means so as to rotate only the predetermined rotation angle from the stored rotation angle position (reference position) of the male screw 28 Control (rotation).
Therefore, when the braking state (pressure contact completion state) is changed to the non-braking state (separation completion state), a constant gap (gap size) is formed between the braking friction member 5 and the rail head side surface 9.
For example, when the rotational speed of the electric motor M is controlled (set) so as to rotate the male screw 28 by 90 degrees from the stored reference position when operating (switching) from the braking state to the non-braking state, the braking friction The member 5 will always be spaced from the rail head side 9 with a gap dimension of 2 mm.

  By controlling in this manner, even if the rail R and the braking friction member 5 are corroded or worn away over time, it is necessary to make an adjustment to increase the opening / closing movement amount of the pair of left and right arm members 6, 6. Can be eliminated, and work such as adjustment and parts replacement can be reduced. Also. The amount of opening and closing movement of the arm members 6, 6 does not increase year after year, and it is possible to prevent the operation time when switching from the non-braking state to the braking state to be delayed (the operation time is stabilized over a long period of time).

Next, a second embodiment shown in FIG. 4 will be described.
In the second embodiment, the screw 70 of the male screw 28 and the lifting member 26 is a screw (slip) in which the slope of the male screw (convex) and the slope of the female screw (concave) are in sliding contact with each other. It is a screw 72 which is composed of a rotating screw and does not satisfy the self-supporting condition of the screw. In other words, it is the screw 72 in which the lead angle (of the screw) is set larger than the friction angle (of the screw surface). Furthermore, in the same way as the embodiment of FIG. 3, the screwing portion 70 is constituted by the screw 72 which does not work (does not exert) the self-locking function (action). That is, when the elevation member 26 receives an axial force while the male screw rod 28 can idle, the elevating member 26 can move up and down while rotating the male screw rod 28. The shape of the screw thread (tooth) is free of triangular screw, square screw, trapezoidal screw, round (bulb) screw, pipe screw, serrated screw, and so on. Other configurations and effects are the same as those of the above-described embodiment.

Next, a third embodiment shown in FIG. 5 will be described.
In the third embodiment, the braking unit 45 is provided on the elevating member 26 so as to be externally fitted, and has a sliding member 53 capable of reciprocating up and down, and a spring member 29 for always biasing the sliding member 53 upward. Is equipped. In addition, between the elevating member 26 and the slide member 53, a sliding portion (low friction portion) 59 for sliding such as a lubricating layer coated with a self-lubricating sliding bearing material or a lubricating material is provided.

The elevating member 26 and the pair of left and right arm members 6, 6 are connected to move the elevating member 26 up and down and open and close the lower end of the pair of left and right arm members 6, 6 (pressure contact of the braking friction member 5) · A pair of left and right first link members 51, 51 for interlocking the approaching operation) is provided.
Further, the slide member 53 and the pair of left and right arm members 6 and 6 are connected, and the pair of left and right for interlocking the vertical movement of the slide member 53 and the opening / closing operation of the lower end portion The second link members 52, 52 are provided.
The toggle mechanism 50 is configured by the pair of left and right first link members 51 and 51 and the pair of left and right second link members 52 and 52.
The interlocking connection mechanism by the first and second link members 51 and 52 may be called a toggle type, and the interlocking connection mechanism by the wedge member 13 and the pressing roller 25 in FIGS. 3 and 4 may be called a wedge type.

A pair of left and right first link members 51, 51 are arranged in an inverted V shape in a front view, and a pair of left and right second link members 52, 52 are arranged in an inclined manner upward in the left, right, outside view The member 26 and the slide member 53 are interlockingly connected to the arm member 6. More specifically, one end (left and right inner end) of the left and right first link member 51 and one end (left and right inner end) of the other left and right first link member 51 are coaxial with the elevating member 26. It is pivotally attached. One end (right and left inner end) of the left and right second link members 52 is pivotally attached to one of the left and right portions of the slide member 53. One end of the other left and right second link members 52 is pivotally attached to the other left and right portions of the slide member 53.
Then, the other end (right and left outer end) of the left and right first link member 51 and the other end (right and left outer end) of the left and right one second link member 52 It coaxially pivots to the upper end of the. The other end of the other left and right first link member 51 and the other end of the other left and right second link member 52 are coaxially pivoted on the upper end of the other left and right arm member 6.

  Although the screwing portion 70 is configured by the ball screw 71 in the illustrated example, it may be configured by the screw 72 which does not satisfy the self-supporting condition of the screw as in the embodiment of FIG. 4. In other words, it may be constituted by screws 71 and 72 which do not work the self-locking function (action).

In the lifting member 26, the upper portion of the screwing portion 70 (the upper end portion of the male screw 28 and the upper opening of the female screw portion 26d of the lifting member 26) is surrounded from the upper side A cap 80 is provided to prevent the entry of foreign matter such as insects.
Further, foreign matter is prevented from entering the screwing portion 70 from the lower portion of the screwing portion 70 (the lower portion of the male screw rod 28 and the lower opening of the female screw portion 26d of the lifting member 26) of the slide member 53. The cover portion 81 is provided.

  In the state shown in FIG. 5, the electric motor M is driven to rotate the male screw lever 28 in a predetermined direction, and the elevating member 26 is moved upward to raise one end of the pair of left and right first link members 51. At the same time, the other end is pulled inward to the left and right to make the upper ends of the pair of left and right arm members 6, 6 close to each other, and the braking friction members 5, 5 at the lower end of the arm members 6, 6 It is a non-braking state separated from the side surfaces 9 and 9. The male screw rod 28 is in a non-rotatable state by the braking force from the electric motor M, and the elevating member 26 is held at the upper and lower positions.

  Further, the upper resilient biasing force of the spring member 29 is transmitted to the second link member 52 via the slide member 53 to lift one end of the second link member 52, and the second link member 52. The other end (arm) of the first link member 51 by the drive of the electric motor M (lifting of the raising and lowering member 26) than the force to move the other end (upper end of the arm member 6) to the left and right outward The force to move the upper end portion of the member 6 inward in the left and right direction sets the spring member 29 and the electric motor M and the toggle mechanism 50 so as to win.

  Then, although not shown, in order to set the braking state, the braking force from the electric motor M is released, or the electric supply to the electric motor M is stopped (an electric stopping state to the electric motor M is set) . Then, the male screw rod 28 can freely rotate (idle), and the elevating member 26 can move up and down without self-locking of the screwing portion 70. That is, the first link member 51 is swingable, and hardly exerts a force to move the upper end portion of the arm member 6 in the left and right direction.

  And while the raising / lowering member 26 becomes vertically movable as mentioned above, the slide member 53 moves upward by the resilient biasing force upward from the spring member 29, and raises one end of the second link member 52. At the same time, the other end of the second link member 52 is moved laterally outward. The upper ends of the pair of left and right arm members 6, 6 move outward in the left and right direction, and the lower ends of the pair of left and right arm members 6, 6 are closed to be in a braking state.

  Similar to the embodiment of FIGS. 3 and 4, even when the electric stopping state occurs in the non-braking state, the screwing portion 70 does not self lock and the braking state is automatically performed by the resilient biasing force of the spring member 29. It is possible to prevent the traveling crane 40 from leaving. In addition, even when the electric stop state is brought about in the braking state, since the elastic biasing force from the spring member 29 continues to be received, the braking state is maintained as it is. Other configurations and effects are similar to those of the embodiment of FIGS. 3 and 4.

Next, a fourth embodiment shown in FIG. 6 will be described.
In the fourth embodiment, the screwing portion 70 is configured by a screw (slidingly rotating screw) in which the slope of the male screw (convex portion) and the slope of the female screw (recess) are in sliding contact with each other. The screw 73 is configured to satisfy the self-supporting condition.
In this screw 73, the male screw rod 28 is in an idle state where it can not rotate or receives braking force (braking force) from the electric motor M, and the weight of the member such as the lifting member 26 rests on the male screw rod 28. Even in this case, the male screw rod 28 is configured not to rotate (do not loosen). That is, it is a screw in which the self-locking function works. For example, it is composed of a screw having a lead angle smaller than the friction angle 8.5 ° (friction coefficient 0.15) of the screw surface. The shape of the threads is free as in the embodiment of FIG. 4, but trapezoidal threads are preferred.

  The interlocking connection mechanism between the elevating member 26 and the arm member 6 is a wedge type including the pressing roller 25 and the wedge member 13 as in the embodiment of FIGS. 3 and 4. In addition, a tension spring 14 is provided.

  In the state shown in FIG. 6, the electric motor M is driven to rotate the male screw lever 28 in a predetermined direction (forward rotation), and the elevating member 26 is lowered. , 6 are brought close to each other, and the braking friction members 5, 5 at the lower ends of the arm members 6, 6 are separated from the rail head side faces 9, 9 in a non-braking state.

Then, although not shown, in order to set the braking state, the electric motor M is driven (reverse rotation) to reversely rotate the male screw rod 28 to raise the lifting member 26, and the pressure rollers 25, 25 are wedged. By pressing the members 13, 13, the upper end portions of the arm members 6, 6 are pushed apart (against the resilient biasing force of the tension spring 14), and the lower ends of the arm members 6, 6 are closed. Put in the braking state.
Therefore, the spring member 29 and the tension spring 14 described in the embodiment of FIGS. 3 to 4 are unnecessary.

  Further, when the braking friction member 5 is brought into pressure contact with the rail R, the control processing unit does not show the load detection means (not shown) (a current measuring device for reading the current value applied to the electric motor M, or the electric motor M and the male screw rod 28) The load is detected and measured by a spring-type thrust detection mechanism) provided between them, and the electric motor M is stopped when a predetermined load is applied. This load detection means is also a braking completion confirmation means.

Then, in the braking state, the electric stopping state is brought about, and the male screw rod 28 can idle and the reaction force from the rail R can be elevating member 26 (pressing roller 25) via the arm member 6 (the wedge member 13). Is self-locking, the vertical movement of the lifting member 26 is blocked, and the lower ends of the pair of left and right arm members 6, 6 are kept closed. .
In addition, even if the traveling crane 40 is traveling (in the non-braking state), even if the electric stop state occurs, the self-locking function keeps the open state, does not start braking, and does not perform rapid deceleration ( It is possible to prevent a large load from acting on the arm member 6, the pivot shaft 23 and the like, and to prevent a large load (damage) from being applied to the traveling crane 40.
That is, even if the pair of left and right arm members 6, 6 is in a state in which the electricity to the electric motor M is stopped, the open / close state before the electric stop is maintained as it is. Further, since the lead angle is smaller than the friction angle, the torque of the electric motor M can be suppressed, which can contribute to downsizing of the electric motor M and energy saving.

Next, a fifth embodiment shown in FIG. 7 will be described.
In the fifth embodiment, the braking unit 45 (in the same manner as the embodiment of FIG. 6) includes the screwing portion 70 of the male screw rod 28 and the elevating member 26 with the screw 73 satisfying the self-supporting condition of the screw. . That is, it is a screw in which a self-locking function (action) works. In addition, the lifting and lowering member 26 is provided with a cap 80 and a cover 81.

  The elevating member 26 and the pair of left and right arm members 6, 6 are connected to each other to vertically move the elevating member 26 and open and close the lower end portions of the pair of left and right arm members 6, 6 (pressure contact of the braking friction member 5 A pair of left and right interlocking link members 55, 55 for interlocking the approaching movement) is provided. That is, the interlocking connection mechanism of the elevating member 26 and the pair of left and right arm members 6, 6 is a link type.

The left and right interlocking link members 55 are disposed in a V-shape in a front view. More specifically, one end (right and left inner end) of the left and right interlocking link member 55 and one end (right and left inner end) of the other left and right interlocking link member 55 are coaxially formed on the elevating member 26 Pivotally attached to
Then, the other end (right and left outer end) of one of the left and right interlocking link members 55 is pivotally attached to the upper end of one of the left and right arm members 6, and the other end of the other left and right interlocking link member 55 is Is pivotally attached to the upper end of the arm member 6 of FIG.

  In the state shown in FIG. 7, the electric motor M is driven to rotate the male screw lever 28 in a predetermined direction (forward rotation), and the elevating member 26 is lowered to move one end of the left and right interlocking link members 55 While lowering and pulling the other end (right and left outer ends) to the left and right inwards, the upper ends of the pair of left and right arm members 6, 6 are made to approach each other, and the braking friction of the lower ends of the arm members 6, 6 The members 5 and 5 are in the non-braking state separated from the rail head side faces 9 and 9.

  Then, although not shown, in order to set the braking state, the electric motor M is driven to reversely rotate the male screw lever 28 to move the elevating member 26 upward and raise one end of the interlocking link member 55 And move the other end outwards. The upper ends of the pair of left and right arm members 6, 6 open outward in the left and right direction and the lower end of the arm member 6 is closed to bring the braking friction members 5, 5 into pressure contact with the rail head sides 9, 9 It becomes a state.

  By this configuration, even when the electric motor M is stopped in the pair of left and right arm members 6, 6, as in the embodiment of FIG. It can hold. Also, the spring member 29 is unnecessary. Other configurations and effects are the same as those of the above-described embodiment.

  Although not shown, in the reference example of the embodiment of FIG. 7, the lower end portions of the pair of left and right arm members 6, 6 are opened when the elevating member 26 ascends (non-braking state), and the elevating member 26 The pair of left and right interlocking link members 55 are disposed in an inverted V-shape in a front view so that the pair of left and right arm members 6, 6 is closed (braking) when lowered.

Next, another embodiment shown in FIG. 8 will be described.
In another embodiment, two braking units 45 (the first braking unit 45A and the second braking unit 45B) are arranged in series on one traveling carriage 33.
The first braking unit 45A, like the braking unit 45 described with reference to FIGS. 3 to 5, has a screwing portion 70 (first screwing portion 70A) that does not have a self-locking function. Ball screw 71 or a screw 72 which does not satisfy the self-supporting condition of the screw, and the screwing portion 70 does not self-lock when the electric motor M (the first electric motor MA) is electrically stopped. The lower end portions of the pair of left and right arm members (first arm members) 6, 6 (not shown in FIG. 8) are closed due to the resilient biasing force of the member 29 upward, and the braking state is established. It is configured as follows.

  The second braking unit 45B may be any of the braking units 45 described with reference to FIGS. 6 and 7, and the screwing portion 70 (second screwing portion 70B) may be a screw that operates as a self-locking function. (The screw satisfying the self-supporting condition of the screw) 73, the screwing portion 70 self-locks when the electric motor M (the second electric motor MB) is stopped electrically (not shown in FIG. 8). The open / close state of the lower end portion of the pair of left and right arm members (second arm members) 6, 6 is configured to be held as it is.

  Further, the second braking unit 45B is configured to perform the braking operation (closing operation) later than the braking operation (closing operation) of the first braking unit 45A. That is, the first braking unit 45A is used for a sliding brake in which the braking friction member 5 brakes while sliding on the rail R (sometimes referred to as for deceleration and stopping), and the second braking unit 45B is a traveling crane 40 After the stop, it is used for holding the stop to operate (sometimes called for anti-shake, clamper or clamp).

  When the traveling crane 40 is electrically stopped while traveling, it is braked by the first braking unit 45A, and the traveling crane 40 can be prevented from traveling away. In the second braking unit 45B, the lower ends of the pair of left and right arm members 6, 6 are not closed due to the self-locking of the screwing portion 70, unnecessary braking force is not exerted, and a large load is applied to the traveling crane 40 Damage) can be prevented.

  Then, when the traveling crane 40 is stopped, the braking is held by the first braking unit 45A and the second unit 45B. Then, during the stop, the braking state is continued (maintained) even if the electric stop state is reached. In particular, the second braking unit 45B does not move the lifting member 26 (the second lifting member 26B) up and down even when receiving the reaction force from the rail R, and stops (clamps) with a strong predetermined pressure.

Further, since the first electric motor MA and the second electric motor MB can be electrically controlled, respectively, the left and right pair of first arm members 6, 6 and the left and right pair of second arm members The lower end portions 6 and 6 can easily set the timing of opening and closing.
In addition, the first and second braking units 45A and 45B slide in the installation space of the conventional hydraulic braking device because hydraulic units such as a hydraulic tank and a pump are unnecessary (because they are electrically driven). It is possible to install both the first brake unit 45A of the type and the second brake unit 45B of the clamp (par) type.

Further, in the embodiment of FIGS. 3 to 8, the electric motor M and the male screw 28 are coaxially arranged, but as in the modification shown in FIG. The electric motor M may be disposed at the position where the male screw rod 28 and the electric motor M are interlocked and coupled via a reduction gear or the like.
In this way, even if a large electric motor M is used, the upper end position of the male screw 28 does not become high, and the height of the entire device can be kept low. Further, the electric motor M can be disposed outside the spring member 29, and a large (high output) electric motor M can be used, and the spring member 29 can be miniaturized.

Next, as shown in FIG. 10, the braking friction member 5 attached to the lower end portion (arm end portion) of the arm member 6 operates with a delay from the first-stage braking portion 1 and the first-stage braking portion 1 The second stage braking unit 2 is provided.
The first-stage braking portion 1 and the second-stage braking portion 2 have pressing surfaces 10 and 20 on the inner surface side facing the rail head side surface 9.
The first-stage braking unit 1 is provided via a resilient member 8 resiliently urged in a direction approaching the rail head side surface 9, and in the non-braking state shown in FIG. 10A, the first-stage braking unit A pressure contact surface 10 is provided so as to project in a direction closer to the rail head side surface 9 than the pressure contact surface 20 of the second stage braking portion 2. The resilient member 8 is preferably a disc spring.

The pressure contact surface 10 of the first-stage braking unit 1 is formed by the brake pad 11 and performs sliding type brake control.
The brake pad 11 is a resin-based material, and is, for example, a resin-based composite material obtained by adding a metal-based material such as silicon (silicon carbide) or aluminum oxide to organic fibers and baking it with a synthetic resin. In addition, it is also preferable to add inorganic materials, such as glass fiber.

The pressure contact surface 20 of the second stage braking portion 2 is harder than the rail head side surface 9. As shown in FIG. 10C, in the main braking state (braking state) in which the pressure contact surface 20 of the second-stage braking portion 2 is in pressure contact with the rail head side surface 9, the pressure contact surface 20 is high in surface pressure on the rail head side surface 9. It is formed in the shape of a concavo-convex surface so as to be in pressure contact with each other (see FIG. 11C). As described above, the pressure contact surface 20 of the second-stage braking unit 2 performs main braking (of a clamp type).
The second-stage braking portion 2 is made of, for example, ceramic or carburized / quenched steel material, and a large number of narrow convex portions having a trapezoidal or triangular cross-sectional shape are formed on the pressing surface 20 to form an uneven surface (jagged shape) , And preferably configured to bite into the rail head side surface 9. A grid-like groove may be formed in the pressure contact surface 20.

As shown in FIGS. 10 (B) and 11 (B) from the non-braking state shown in FIGS. 10 (A) and 11 (A), the pressure contact surface 20 of the second stage braking portion 2 The pressure contact surface 10 of the first-stage braking unit 1 is pressed against the rail head side surface 9 and braked prior to pressure contact with the rail. The first stage damping unit 1 is resiliently urging by the elastic member 8, the rail head side surfaces 9,9 a relatively with small contact pressure F _1, F ₁ to nipping (pinching). This state is referred to as a preliminary braking state.

Next, as shown in FIGS. 10C and 11C from the preliminary braking state, the pressure contact surface 20 of the second stage braking portion 2 is in pressure contact with the rail head side surface 9 to clamp the rail head And brake. The second stage braking portion 2 strongly clamps (holds) the rail head side surfaces 9 and 9 with relatively large pressure contact forces F ₂ and F _2, and the large number of narrow convex portions of the pressure contact surface 20 Then, it switches to the main braking state (braking state) for preventing the escape.
That is, from the non-braking state in FIGS. 10A and 11A to the first-stage braking state (also referred to as a preliminary braking state) in FIGS. 10B and 11B, and the first-stage braking Switching from the state (preliminary braking state) to the main braking state (for preventing runaway) in FIGS. 10 (C) and 11 (C) is gradually switched to increase the braking force (stepwise).

  In the braking unit 45 according to the embodiment of FIGS. 3 to 5, the first stage braking unit 1 is firstly operated even when an abnormal situation such as a power failure or a failure occurs while the traveling crane 40 is traveling. The pressure contact surface 10 of the second slide makes sliding contact with the side surface 9 of the rail head to perform deceleration braking of the traveling crane 40, and thereafter, the pressure contact surface 20 of the second stage braking portion 2 makes pressure contact with the side surface 9 of the rail head And clamp the rail head. That is, damage to the traveling crane 40 (destruction or partial deformation of the crane main body 41) due to rapid deceleration and stop can be reduced. The first stage braking unit 1 and the second stage braking unit 2 hold the rail head side surfaces 9 and 9 to perform braking, so that the braking force can be applied regardless of the state of the rail R, that is, the situation of ups and downs There is. In addition, if the rotation angle of the male screw lever 28 of the braking unit 45 (drive of the electric motor M) is controlled, it is also possible to maintain the preliminary braking state, and the pressure contact surface 10 of the first stage braking portion 1 has a rail head After the traveling crane 40 is completely stopped by sliding (sliding) on the side surface 9, the pressure contact surface 20 of the second stage braking unit 2 is brought into pressure contact with the rail head side surface 9, and the main braking state (braking state) It is also preferable to switch to.

The braking system of the traveling crane according to the present invention can apply a braking force with the above-described configuration and operation, but if the rail head side surface 9 is not flat, the braking force of the first and second braking portions 1 and 2 is There is a possibility that the frictional force with the press contact surfaces 10 and 20 can not be secured. Usually, as the aged deterioration of the rail R, the upper surface of the rail is crushed, and a plastic deformation ridge X may be locally generated on the side surface 9 of the rail head (see FIG. 12A). When the pressure contact surface 10 of the first-stage braking portion 1 is pressed against the plastic deformation protrusion X, the pressure contact surface 10 (the brake pad 11) and the plastic deformation protrusion X contact locally (sliding contact) And there is a possibility that the friction characteristic can not be secured.
Therefore, as shown in FIG. 11 and FIG. 12, the rail head side surface correction tool 3, 3 is provided to delete the plastic deformation ridge X locally generated on the rail head side surface 9 as the crane travels. ing.

The rail head side surface correction tool 3 has a correction surface portion 30 for removing a plastic deformation protrusion X formed by a grindstone or a cutting blade or the like, and one end face of a support base for supporting the grindstone or the cutting blade or the like. And a flat guide surface portion 31 to be formed. The correction surface 30 and the flat guide surface 31 are formed in the same plane. The flat guide surface portion 31 is preferably formed of a ceramic, a hardened steel material or the like which is excellent in wear resistance.
The rail head side surface correction tool 3 is provided to always contact the rail head side surface 9. As shown in FIG. 12A, in the state where the plastic deformation protrusion X is formed on the rail head side surface 9, only the correction surface portion 30 is in sliding contact with the plastic deformation protrusion X, and the rail head side surface 9 Scrape the bulged plastic deformation ridge X from it. After scraping the plastic deformation projection X, as shown in FIG. 12 (B), the flat guide surface 31 is in sliding contact with the lower side of the rail head side surface 9, and the correction surface 30 is more than necessary. The side surface 9 (the portion where the plastic deformation protrusion X was present) is not scraped, and the entire rail head side surface 9 is configured to be corrected and maintained in a flat surface shape.

Next, modifications of the arm member 6, the braking friction member 5 and the wedge type interlocking connection mechanism will be described.
As shown in FIG. 13, the sliding friction member 1 can be braked even when the traveling crane 40 is moving, and the second braking member 1 is a sliding type, and the second clamping type intended for holding when stopped. The step brake unit 2 is divided into separate units. The arm member 6 is divided into a first differential arm 21 to which the first-stage braking portion 1 is attached and a second differential arm 22 to which the second-stage braking portion 2 is attached. And The first stage braking unit 1 and the second stage braking unit 2 can be mechanically sequenced.
Each arm member 6 is formed of one first differential arm 21 and two second differential arms 22, 22. The first differential arm 21 and the second differential arms 22 and 22 are pivotally mounted on the same axis by a pivot shaft 23, and the first differential arm 21 is disposed at an axially intermediate portion, A pair of front and rear second differential arms 22, 22 are disposed on both sides (both sides) in the axial direction of the 1 differential arm 21.
A first step braking portion 1 to which a resin-based brake pad 11 is attached is attached to the lower end portion of the first differential arm 21, and stop holding is performed at the lower end portions of the pair of front and rear second differential arms 22 and 22. Second-stage brakes 2 and 2 for (clamp) are attached.

In FIG. 13, although not shown, the braking unit 45 is a raising and lowering member in which the male screw 28 and the male screw 28 are screwed in the same manner as described with reference to FIGS. 3, 4 and 6. It has 26 and. As the configuration for moving the lifting member 26 to be in the braking state, as described with reference to FIGS. 3 and 4, the configuration using the screws 71 and 72 and the spring member 29 in which the self-locking function does not work is electric. It is preferable because the braking operation is performed in the stopped state. Note that, as described with reference to FIG. 6, a configuration may be made such that the motor 73 is operated by the screw 73 in which the self-locking function works.
The interlocking connection mechanism between the elevating member 26 and the braking / friction member 5 is a wedge type, and the wedge member 13 corresponds to the first wedge member 18 corresponding to the first differential arm 21 and the second differential arm 22. It is divided into a corresponding second wedge member 19 to be separately configured. The pressure roller (pressing member) 25 is provided in an eccentric type having the front end roller portion 16 corresponding to the first wedge member 18 and the rear end roller portion 17 corresponding to the second wedge member 19.
In FIG. 13, the first wedge member 18 having the first inclined surface (tapered surface) 18 a is fixed to the upper end portion of the first differential arm 21, and the second upper end portion of the second differential arm 22 is The second wedge members 19, 19 having the inclined surfaces (taper surfaces) 19a, 19a are fixed. The lifting member 26 is provided with a pair of left and right eccentric type pressing rollers (pressing members) 25, 25. The eccentric type pressing roller 25 is provided at the front end roller portion 16 for pressing the first inclined surface 18 a provided at the upper end portion of the first differential arm 21 and at the upper end portions of the second differential arms 22 and 22. The back contact roller portions 17 and 17 for pressing the second inclined surfaces 19 a and 19 a are provided, and the axial center of the front contact roller portion 16 is slightly above the shaft center of the back contact roller portions 17 and 17. It is disposed so as to be offset by offsetting.

As shown in FIG. 14A, the first inclined surface 18 a of the first wedge member 18 provided at the upper end of the first differential arm 21 and the upper end of the second differential arm 22 in the non-braking state. The second inclined surfaces 19a of the provided second wedge members 19 are disposed on the same plane.
As shown in FIG. 14 (A) to FIG. 14 (B), when the front end roller portion 16 and the rear end roller portion 17 (eccentric type pressing roller 25) ascend, the front end roller portion 16 becomes the first wedge member 18 By pressing the first inclined surface 18a, only the first differential arm 21 operates first.
Next, as shown in FIG. 14 (A) to FIG. 14 (B), the front end roller portion 16 and the rear end roller portion 17 are further raised, and the rear end roller portion 17 becomes the second of the second wedge member 19. The second differential arm 22 operates with a delay by pressing the inclined surface 19a. At this time, the front end roller portion 16 is in sliding contact with the flank 18b of the first wedge member 18 so as not to further spread the first differential arm 21.

From the non-braking state shown in FIG. 15A, as shown in FIG. 15B, the pressure contact surface 20 of the second stage braking portion 2 (provided at the lower end portion of the second differential arm 22) ahead pressed against the side surface 9, (first provided at the lower end of the differential arm 21) first stage damping unit 1 of the press-contact surface 10, with the pressing force F _1, F ₁ to the rail head side surfaces 9 pressure And brake. The pressure contact surface 10 of the first-stage braking portion 1 formed by the resin-based brake pad 11 is in sliding contact (sliding) with the rail head side surfaces 9 and 9 to perform deceleration braking. This state is called a first-stage braking state or a preliminary braking state.

Next, from the preliminary braking state (first-stage braking state), as shown in FIG. 15C, the pressure contact surfaces 20, 20 of the second-stage braking portions 2, 2 press against the rail head side surfaces 9, 9. Clamp the rail head. The pressure contact surface 20 of the second stage braking portion 2 is harder than the rail head side surface 9 and is formed in a concavo-convex surface (jagged shape) in which a large number of narrow convex portions having trapezoidal or triangular cross sections are formed. The head sides 9, 9 are strongly pressed (held) with a large pressing force F ₂ , F ₂ , and the pressing surface 20 is pressed against the rail head side 9 with a high surface pressure, and a large number of narrow projections of the pressing surface 20 The part is made to bite into the rail head side surface 9 to switch to the main braking state for escape prevention.
That is, switching from the non-braking state in FIG. 15A to the preliminary braking state in FIG. 15B and from the preliminary braking state to the main braking state (braking state) in FIG. The braking force is increased (in steps). In the main braking state, the first-stage braking unit 1 and the second-stage braking units 2 and 2 strongly clamp (hold) the rail head side surfaces 9 and 9 by the resultant force of the pressing forces F ₁ and F _2. , To clamp.

As shown in FIG. 13, a buffer (damper) member 24 may be provided for delaying the operation of the second differential arm 22 constituting the second-stage braking portion 2 with respect to the first differential arm 21.
The buffer member 24 couples the pair of left and right second differential arms 22. The buffer member 24 can be reworded as a damping member (mechanism). By installing the buffer member 24, even when the power is lost due to a power failure or failure, the time difference between the movements of the first differential arm 21 and the second differential arms 22 and 22 can be increased, so that Damage to the crane body 41 can be further reduced.

In FIG. 13, buffer members 24 are attached to each of the pair of front and rear second differential arms 22. It is also preferable to give a difference to the damper characteristics of the two buffer members 24. By differentiating the damper characteristics of the buffer members 24, it becomes possible not only to apply the braking force in two steps, but also to add three or four steps of braking force.
In addition, braking can be performed in stages by the plurality of differential arms 21 and 22, so that the structural configuration flexibility is wide and easy to use (it can meet the needs of various traveling cranes 40 and customers).

  Further, in the non-braking state of FIG. 14A, the inclination of the first inclined surface 18a is set to be larger than that of the second inclined surface 19a, and the first inclined surface 18a comes into contact with the first contact roller portion 16 first. The movement of the first differential arm 21 and the second differential arm 22 may have a time difference.

  In this manner, the traveling is attached to the traveling crane 40 moving along the rails R, R, and the braking friction member 5 provided at the lower end (arm end) of the arm member 6 is pressed against the rail head side 9 and gripped A braking device for a crane, wherein the braking friction member 5 includes a first-stage braking unit 1 and a second-stage braking unit 2 that operates with a delay from the first-stage braking unit 1, so that the first-stage braking unit The braking by the braking unit 1 and the second stage braking unit 2 can be performed in stages, and destruction or partial deformation of the crane main body 41 can be prevented and damage can be reduced without applying an impulsive braking force. . The first stage braking portion 1 and the second stage braking portion 2 are in pressure contact with the rail head side surface 9, so that the braking force can be reliably exerted regardless of the state of the rail R, that is, the state of ups and downs. It can be installed in a small space at low cost. The braking by the first stage braking unit 1 and the second stage braking unit 2 can mechanically give a time difference without transmitting the sequence control signal from the crane body side.

  Further, the first-stage braking portion 1 is provided via a resilient member 8, and the pressing surface 10 of the first-stage braking portion 1 is closer to the pressing portion 20 of the second-stage braking portion 2. Since it is provided protruding toward the side surface 9, it can be manufactured at low cost, and the performance of the sliding brake device and the rail clamp device can be added in the space of one conventional rail clamp device. it can. Since the first and second braking units 1 and 2 have a fixed mechanical order by a mechanical mechanism, no special control signal exchange is required, and even in the event of a failure such as a power failure or failure, control is performed in stages. It is possible to provide a braking device that can operate power and is easy to maintain.

  Further, since the pressure contact surface 10 of the first-stage braking portion 1 is formed of the resin-based brake pad 11, the brake pad 11 (pressure contact surface 10) is brought into sliding contact with the rail head side surface 9 to slide. A type of braking force can be applied.

  Further, the pressure contact surface 20 of the second stage braking portion 2 is harder than the rail head side surface 9 and is formed in an uneven surface shape so as to be in pressure contact with the rail head side surface 9 with high surface pressure. Therefore, the pressure contact surface 20 can be made to bite into the side surface 9 of the rail head to generate a strong second stage braking force, and the escape can be reliably prevented.

  Further, since the rail head side surface correction tools 3 and 3 are provided for removing the plastic deformation protrusion X locally generated on the rail head side surface 9 as the crane travels, the rail head side surface 9 Can be corrected and maintained in the form of a flat surface, and the pressure contact surface 10 (brake pad 11) of the first-stage braking portion 1 can be prevented from locally contacting the plastic deformation projection X, ensuring suitable friction characteristics it can.

  In addition, since the first differential arm 21 having the first-stage braking portion 1 and the second differential arm 22 having the second-stage braking portion 2 are configured independently of each other, The differential arm 21 and the second differential arms 22 and 22 can be operated independently with a time difference to apply a braking force stepwise. The performance of the sliding brake device and the rail clamp device can be added in the space of one conventional rail clamp device. By separately configuring the first differential arm 21 and the second differential arm 22, the respective arms 21 and 22 can be lightened, and the manufacturing cost can be reduced as well as the ease of handling such as assembly.

  In addition, since the buffer member 24 for delaying the operation of the second differential arm 22 is provided, even when the power is lost due to a power failure or a failure, the second differential arm 21 can not be used for the second differential arm 21. The operation of the differential arm 22 can be delayed, and the braking forces of the first stage braking unit 1 and the second stage braking units 2 and 2 can be applied stepwise, and damage to the traveling crane 40 can be reduced.

  The present invention can be changed in design, and the braking friction member 5 is not limited to one divided into the first-stage braking portion 1 and the second-stage braking portion 2, and one braking portion (frictional portion) is provided. It may be In addition, the braking friction member 5 may be configured to be in contact with the upper surface of the head of the rail R for braking. The cap 80 and the cover 81 may be provided in the embodiments of FIGS. 3, 4, 6, 8 and 9. In FIG. 3 to FIG. 8, the male screw rod 28 is illustrated integrally with the output shaft of the electric motor M (a part of the output shaft), but between the male screw rod 28 and the output shaft of the electric motor M A reduction mechanism (machine), a coupling, a clutch, a thrust detection mechanism, etc. may be provided. The raising and lowering member 26 is not limited to interlocking connection with the upper portion of the arm member 6 as shown in the figure, but is interlocked with the middle portion of the arm member 6 (portion above the pivot shaft 23 in the arm member 6). You may also configure. Further, as shown in FIGS. 8 and 9, when a plurality of braking units 45 are provided, the configuration of the modification described with reference to FIGS. 13 and 14 may be applied to all the braking units 45, It may be applied to one or more braking units 45. The rotation angle detection means (encoder) may be provided to detect the rotation angle position of the male screw 28 and may not be provided to directly measure the male screw 28. For example, it is provided to detect the rotation angle (rotational speed) of the output shaft of the electric motor M, the gear of the reduction gear, the driven shaft (gear shaft) or the like, and the control processing unit Convert (compute) to

  Further, in a braking system attached to the traveling crane 40 moving along the rail R, a braking friction member 5 which performs a braking action by pressing on and separating from the rail R, and a vertical shape rotated by the electric motor M The male screw rod 28 and the elevating member 26 screwed up and down on the male screw rod 28 so as to be vertically reciprocated, and the elevating member 26 and the braking friction member 5 are interlocked, There is no need for a hydraulic unit such as a hydraulic pump or a hydraulic tank, the structure can be simplified, the apparatus can be miniaturized, and parts can be maintained and inspected quickly and easily. There is no risk of hydraulic fluid flowing out of the device, and there is no risk of environmental pollution. Stable operation can be realized without being adversely affected by environmental temperature (air temperature). It can reduce consumable parts and reduce maintenance costs.

  Further, the braking friction member 5 includes a pair of left and right arm members 6, 6 attached to the lower end portion, and the lower end portion of the pair of left and right arm members 6, 6 Since the braking friction member 5 is brought into pressure contact with and separated from the rail head side surface 9 by opening and closing, braking can be performed with a strong holding force while realizing downsizing of the entire device.

  The screwing portion 70 of the elevating member 26 and the male screw rod 28 is formed of a ball screw 71 or a screw 72 which does not satisfy the self-supporting condition of the screw, and the elevating member 26 is always upward. The elevating member 26 is moved upward while rotating the male screw lever 28 by the resilient biasing force from the spring member 29 in a state where the electric motor M is stopped electrically. Since the lower ends of the pair of left and right arm members 6, 6 are closed and the braking friction member 5 is brought into pressure contact with the side surface 9 of the rail head, a typhoon When the electricity supply to the electric motor M is stopped due to an earthquake etc., the springing force of the spring member 29 can automatically make the braking state, and the runaway of the traveling crane 40 due to the earthquake or gust can be surely prevented, and the safety Is high. Further, even in the braking state, even when the electric motor M is in the electric stop state, since the resilient biasing force upward from the spring member 29 is continuously received, the braking state can be maintained as it is. Energy saving can be realized without the need for electrical energy to maintain the closing operation.

  Further, the screwing portion 70 of the elevating member 26 and the male screw rod 28 is constituted of a ball screw 71 or a screw 72 not satisfying the self-supporting condition of the screw, and further, the elevating member 26 and the left and right A pair of left and right first link members 51, 51 for interlockingly connecting the pair of arm members 6, 6, a vertically movable reciprocable slide member 53 externally fitted to the elevating member 26, and the pair of left and right A pair of left and right second link members 52, 52 interlockingly connecting the arm members 6, 6 together constitute a toggle mechanism 50, and provided with a spring member 29 for constantly biasing the slide member 53 upward. While the screwing portion 70 is not self-locking while the electric motor M is electrically stopped, the elevating member 26 can move up and down, and the sliding force of the spring member 29 causes the sliding member 53 to move. Is moved upward, through the second link members 52, 52. The lower ends of the pair of left and right arm members 6, 6 are closed so that the braking friction member 5 is in pressure contact with the side surface 9 of the rail head. When the supply of electricity to the electric motor M is stopped, the braking force can be automatically applied by the spring force of the spring member 29, so that the traveling crane 40 can be reliably prevented from traveling by an earthquake or a gust, and the safety is high. Further, even in the braking state, even when the electric motor M is in the electric stop state, since the resilient biasing force upward from the spring member 29 is continuously received, the braking state can be maintained as it is. There is no need for electrical energy to maintain the closing operation, and energy efficiency is good (energy saving can be realized). The braking friction member 5 can be pressed against the rail head side surface 9 with a strong holding force. Compared with the wedge-type interlocking connection mechanism, there is an advantage that the wear of the sliding contact portion (contact portion) is small and the durability is excellent. That is, there is a possibility that the sliding contact (contact) state may change due to wear, or the friction resistance of the sliding contact portion may change due to the roughness of the sliding contact surface due to wear, and the force of pressing the braking friction member 5 against the rail R is stable. There is no problem that it loses (that is, the braking force is stabilized). Further, compared with the wedge-type interlocking connection mechanism, the sliding portion is the inner peripheral surface of the link pivot hole and the outer peripheral surface of the link pin, and is not open to the outside, thereby reducing maintenance time such as cleaning. . That is, a predetermined braking force (holding force of the arm member 6) can be stably obtained over a long period of time.

Further, the screwing portion 70 of the elevating member 26 and the male screw rod 28 is constituted by a screw 73 which satisfies the self-supporting condition of the screw, and self-locking of the screwing portion 70 in an electric stop state to the electric motor M. The vertical movement of the elevating member 26 is blocked by the movement of the traveling crane 40 so that the open / close state of the lower end of the pair of left and right arm members 6, 6 is maintained as it is. ), Even if the electric stop state is achieved, there is no rapid deceleration (no sudden braking),
It is also possible to prevent the braking device Z itself and the traveling crane 40 from being loaded. The torque of the electric motor M can be suppressed, which can contribute to downsizing of the electric motor M and energy saving. Since the spring member 29 for opening operation is unnecessary, the number of parts can be reduced and the manufacturing can be easily (inexpensive). It can be stopped (clamped) with a predetermined pressing force without being affected by the reaction force from the rail R.

  Further, the lower end portions of the pair of left and right arm members 6, 6 are closed and the braking friction member 5 is in pressure contact with the side surface 9 of the rail head based on the rotational angle position of the male screw 28 in the braking state Since the rotation angle control means is provided to rotate by a predetermined rotation angle so as to form a fixed gap between the rail head side surface 9 and the braking friction member 5, the rail R and the braking friction member 5 Even if it corrodes or wears over time, it is not necessary to adjust so as to increase the opening / closing movement amount of the pair of left and right arm members 6, 6, and work such as adjustment or part replacement can be reduced. Also. The amount of opening and closing movement of the arm members 6, 6 does not increase year by year, and it is possible to prevent the operating time when switching from the non-braking state to the braking state to be delayed, and the operating time is stabilized over a long period of time. It is possible to cope with the wear and deformation (slimness and expansion) of the head of the rail R easily and quickly.

  As described above, the braking system of the traveling crane according to the present invention is a braking system attached to the traveling crane 40 moving along the rail R, and performs the braking action by pressing on and separating from the rail R. A braking friction member 5, a vertical male screw 28 which is rotated by an electric motor M, an elevating member 26 which is screwed on the male screw 28 in an externally fitted shape and reciprocates up and down, and the braking friction member 5 A pair of left and right arm members 6, 6 attached to the lower end portion, and a spring member 29 for constantly urging the lifting member 26 upward, and the screwing between the lifting member 26 and the male screw rod 28 The portion 70 is constituted by a ball screw 71 or by a screw 72 which does not satisfy the self-supporting condition of the screw, and in the electric stop state of the electric motor M, the raising and lowering by the resilient biasing force from the spring member 29 The member 26 moves upward while rotating the male screw rod 28, The lower ends of the pair of left and right arm members 6, 6 are closed so that the braking friction member 5 is in pressure contact with the rail head side surface 9, so a hydraulic unit such as a hydraulic pump or hydraulic tank is necessary. As a result, the structure can be simplified, the apparatus can be miniaturized, and parts can be maintained and inspected quickly and easily. There is no risk of hydraulic fluid flowing out of the device, and there is no risk of environmental pollution. Stable operation can be realized without being adversely affected by environmental temperature (air temperature). It can reduce consumable parts and reduce maintenance costs. When the power supply to the electric motor M is stopped due to a typhoon or an earthquake or the like in a non-braking state, it can be automatically braked by the resilient biasing force of the spring member 29. It is possible to reliably prevent the escape and has high safety. Further, even in the braking state, even when the electric motor M is in the electric stop state, since the resilient biasing force upward from the spring member 29 is continuously received, the braking state can be maintained as it is. Energy saving can be realized without the need for electrical energy to maintain the closing operation.

  Further, a pair of left and right pressing rollers 25, 25 are pivotally attached to the elevating member 26, and the arm member 6 is provided at the upper end portion with an inclined surface 13a which is inclined inward rightward and leftward. When the elevating member 26 moves upward, the pressing roller 25 slides on the inclined surface 13a to push and spread the upper end portions of the pair of left and right arm members 6, 6, and the lower ends of the pair of left and right arm members 6, 6 Since the braking friction member 5 is brought into pressure contact with the rail head side surface 9 by closing the unit, the braking can be performed with a strong holding force while realizing the downsizing of the entire device.

  Further, in a braking system attached to the traveling crane 40 moving along the rail R, a braking friction member 5 which performs a braking action by pressing on and separating from the rail R, and a vertical shape rotated by the electric motor M Male and female screw rods 28, a pair of left and right pressing rollers 25 and 25 pivotally mounted on the male and female screw rods 28 and 25 and vertically moving the upper and lower reciprocating members 26; A pair of left and right arm members 6, 6 provided at the lower end portion and provided with inclined surfaces 13a inclined upward and downward to the left and right at the upper end portion; the elevating member 26 and the male screw rod 28 The screwing portion 70 is constituted by a screw 73 that satisfies the self-supporting condition of the screw, and drives the electric motor M to rotate the male screw rod 28 while moving the elevating member 26 upward, and the pressing roller 25 The left and right arm members are in sliding contact with the inclined surface 13a. , 6 are pushed out, and the lower ends of the pair of left and right arm members 6, 6 are closed so that the braking friction member 5 is in pressure contact with the rail head side surface 9, When the electric motor M is stopped electrically, the vertical movement of the elevating member 26 is blocked by the self-locking of the screwing portion 70, and the open / closed state of the lower end of the pair of left and right arm members 6, 6 is maintained as it is With this configuration, there is no need for a hydraulic unit such as a hydraulic pump or hydraulic tank, and the structure can be simplified, the apparatus can be miniaturized, and parts maintenance and inspection can be performed quickly and easily. It becomes possible. There is no risk of hydraulic fluid flowing out of the device, and there is no risk of environmental pollution. Stable operation can be realized without being adversely affected by environmental temperature (air temperature). It can reduce consumable parts and reduce maintenance costs. The braking can be performed with a strong holding force while realizing the downsizing of the entire device. Even when the traveling crane 40 is traveling (in the non-braking state), even if the electric stopping state is achieved, the rapid deceleration is not performed (the sudden braking is not applied), and the braking device Z itself and the traveling crane 40 are loaded. Can also be prevented. The torque of the electric motor M can be suppressed, which can contribute to downsizing of the electric motor M and energy saving. Since the spring member 29 for opening operation is unnecessary, the number of parts can be reduced and the manufacturing can be easily (inexpensive). It can be stopped (clamped) with a predetermined pressing force without being affected by the reaction force from the rail R.

  Further, in a braking system attached to the traveling crane 40 moving along the rail R, a braking friction member 5 which performs a braking action by pressing on and separating from the rail R, and a vertical shape rotated by the electric motor M Male screw rod 28, a lifting member 26 screwed up and down on the male screw rod 28 so as to reciprocate up and down, and a pair of left and right arm members 6, 6 to which the braking friction member 5 is attached at the lower end. And a pair of left and right interlocking link members 55, 55 for interlocking the vertical reciprocation movement of the elevating member 26 and the opening / closing operation of the lower end portions of the pair of left and right arm members 6, 6, One end of the link member 55 and one end of the other left and right interlocking link member 55 are coaxially pivoted to the elevating member 26, and the other end of the left and right interlocking link member 55 is It is pivotally attached to the upper end of one of the left and right arm members 6 The other end of the other left and right interlocking link member 55 is pivotally attached to the upper end of the other left and right arm member 6, and the pair of left and right interlocking link members 55 are disposed in a V-shape in a front view The electric motor M is driven to move the elevating member 26 upward while rotating the male screw rod 28 to raise one end of the left and right interlocking link members 55, 55 and to move the other end left and right. The upper ends of the pair of left and right arm members 6, 6 are opened outward to the left and right, and the lower ends of the pair of left and right arm members 6, 6 are closed to move the braking friction member 5 The self-locking of the screwing portion 70 prevents the vertical movement of the elevating member 26 when the electric motor M is stopped electrically, and the pair of left and right The open / close state of the lower end of the arm members 6, 6 is held as it is With this configuration, there is no need for a hydraulic unit such as a hydraulic pump or hydraulic tank, and the structure can be simplified, the apparatus can be miniaturized, and parts maintenance and inspection can be performed quickly and easily. It becomes possible. There is no risk of hydraulic fluid flowing out of the device, and there is no risk of environmental pollution. Stable operation can be realized without being adversely affected by environmental temperature (air temperature). It can reduce consumable parts and reduce maintenance costs. The braking can be performed with a strong holding force while realizing the downsizing of the entire device. Even when the traveling crane 40 is traveling (in the non-braking state), even if the electric stopping state is achieved, the rapid deceleration is not performed (the sudden braking is not applied), and the braking device Z itself and the traveling crane 40 are loaded. Can also be prevented. The torque of the electric motor M can be suppressed, which can contribute to downsizing of the electric motor M and energy saving. Since the spring member 29 for opening operation is unnecessary, the number of parts can be reduced and the manufacturing can be easily (inexpensive). It can be stopped (clamped) with a predetermined pressing force without being affected by the reaction force from the rail R.

5 Braking friction member 6 Arm member 9 Rail head side
13a inclined surface
25 pressure roller
26 Lifting member
28 Male thread screw
29 Spring member
40 traveling crane
55 Interlocking link member
70 Screwing part
71 ball screw
Screws that do not meet the self-supporting requirements of 72 screws
73 screw M electric motor R rail meeting the freestanding condition of screw

Claims (4)

In a braking system attached to a traveling crane (40) moving along a rail (R),
A braking / frictional member (5) for pressing and separating from the rail (R) to perform a braking function, a vertical male screw rod (28) rotated by an electric motor (M), and the male screw rod (28) And the pair of left and right arm members (6) and (6) with the braking friction member (5) attached at the lower end, and the lifting and lowering member (26). And a spring member (29) for always urging the member (26) upward.
The screwing portion (70) of the elevating member (26) and the male screw rod (28) is constituted by a ball screw (71) or a screw (72) which does not satisfy the self-supporting condition of the screw;
In an electric stop state to the electric motor (M), the elevating member (26) moves upward while rotating the male screw rod (28) by the resilient biasing force from the spring member (29), and the left and right The braking of the traveling crane is characterized in that the lower ends of the pair of arm members (6) and (6) are closed and the braking friction member (5) is brought into pressure contact with the rail head side surface (9). apparatus. A pair of left and right pressure rollers (25), (25) are pivotally attached to the elevating member (26),
The arm member (6) is provided at its upper end with an inclined surface (13a) which inclines upward and downward to the left and right.
When the elevating member (26) moves upward, the pressing roller (25) comes in sliding contact with the inclined surface (13a) and pushes the upper end portions of the pair of left and right arm members (6) and (6) apart. The traveling crane according to claim 1, wherein the braking friction member (5) is brought into pressure contact with the rail head side surface (9) by closing the lower end portions of the pair of left and right arm members (6, 6). Braking system. In a braking system attached to a traveling crane (40) moving along a rail (R),
A braking / frictional member (5) for pressing and separating from the rail (R) to perform a braking function, a vertical male screw rod (28) rotated by an electric motor (M), and a pair of left and right pressing rollers ( 25) A lifting member (26) which is pivotally attached to the male screw rod (28) and is reciprocated upward and downward while the (25) is pivotally attached and the braking friction member (5) is attached to the lower end portion And a pair of left and right arm members (6, 6) provided with inclined surfaces (13a) which are inclined at the upper end in the left and right direction at the upper end thereof,
The screwing portion (70) of the elevating member (26) and the male screw rod (28) is constituted by a screw (73) satisfying a self-standing condition of the screw,
The electric motor (M) is driven to move the lifting member (26) upward while rotating the male screw rod (28), and the pressing roller (25) is in sliding contact with the inclined surface (13a) to cause the above-mentioned movement. The upper ends of the pair of left and right arm members (6) and (6) are pushed apart and the lower ends of the pair of left and right arm members (6) and (6) are closed to operate the braking friction member (5) Configured to be in pressure contact with the part side surface (9),
Further, in the state where the electric motor (M) is electrically stopped, the vertical movement of the elevating member (26) is blocked by the self-locking of the screwing portion (70), and the pair of left and right arm members (6) (6) A braking system for a traveling crane, characterized in that the open / close state of the lower end portion of the) is held as it is. In a braking system attached to a traveling crane (40) moving along a rail (R),
A braking / frictional member (5) for pressing and separating from the rail (R) to perform a braking function, a vertical male screw rod (28) rotated by an electric motor (M), and the male screw rod (28) And the pair of left and right arm members (6) and (6) to which the braking friction member (5) is attached at the lower end, and the raising and lowering A pair of left and right interlocking link members (55) (55) for interlocking the up and down reciprocation of the member (26) and the opening / closing operation of the lower end portions of the pair of left and right arm members (6) (6);
One end of the left and right interlocking link member (55) and the other end of the other left and right interlocking link member (55) are coaxially pivoted to the elevating member (26), and further, The other end of the interlocking link member (55) is pivotally attached to the upper end of one of the left and right arm members (6), and the other end of the other interlocking link member (55) is the other of the left and right Pivoting to the upper end of the arm member (6), the pair of left and right interlocking link members (55) (55) are arranged in a V-shape in a front view,
The electric motor (M) is driven to move the elevating member (26) upward while rotating the male screw rod (28) to raise one end of the pair of left and right interlocking link members (55), (55) While moving the other end left and right outward, the upper end of the pair of left and right arm members (6) and (6) opens outward to the left and right, and the pair of left and right arm members (6) and (6) The lower end portion is closed so as to press the braking friction member (5) against the rail head side surface (9);
Further, in the state where the electric motor (M) is electrically stopped, the vertical movement of the elevating member (26) is blocked by the self-locking of the screwing portion (70), and the pair of left and right arm members (6) (6) A braking system for a traveling crane, characterized in that the open / close state of the lower end portion of the) is held as it is.

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