JP2016088638A - Rail clamp device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rail clamp device that can realize large holding force by converting force by running-away of a moving structure into force for pressure-contacting a rail.SOLUTION: A pair of swing arms 11 and 11 which open and close in forward and backward travelling directions are pivoted to a travelling truck 3 that travels on a rail R, the swing arms 11 and 11 are elastically energized in a closed direction with a coil spring 8, and a pair of left and right wedge-shaped brake shoes 7 and 7 which can be freely press-contacted with side faces Rb and Rb of a head part of the rail R are held in lower end parts 11b of the swing arms 11, so that the wedge-shaped brake shoes 7 and 7 are inserted in a space between the rail R and the travelling truck 3 by elastically energizing force of the coil spring 8 to be brought into a preparatory clamp state. Further when the travelling truck 3 starts to run away, the wedge-shaped brake shoes 7 and 7 at a front side in a direction of the running-away are inserted deeply into the space between the rail R and the travelling truck 3 to be switched into a full clamp state for preventing running-away, so that force by which the shoes are press-contacted with the side faces Rb and Rb of the head part of the rail R is increased.SELECTED DRAWING: Figure 5

Description

  The present invention relates to a rail clamp device.

  Conventionally, there has been a rail clamp device that is attached to a moving structure such as a cargo handling machine that travels on a rail and grips the rail by the elastic biasing force of a coil spring (see Patent Document 1).

Japanese Patent No. 517128

  However, since the rail clamp device described in Patent Document 1 has a structure in which the brake shoe attached to the lower end of the clamp lever is pressed against (in pressure contact with) the rail head by the elastic biasing force of the coil spring, the moving structure In order to obtain a holding force that can withstand the escape force of an object, a very large impact force is required, and the coil spring is increased in size and cost. Moreover, when clamping the location where the width | variety of the head of a rail is narrower than a reference value, since the deflection amount of the coil spring became small, there existed a fault that holding force fell. Also, when the clamp is released, the distance between the rail and the brake shoe cannot be made sufficiently large, so if the rail is bent or locally bulged, the rail and the brake shoe may come into contact with each other during traveling. .

  Then, an object of this invention is to provide the rail clamp apparatus which converts the escape force of a moving structure into the force which press-contacts a rail, and obtains big holding force.

  In the rail clamp device according to the present invention, a pair of swing arms that open and close in the front-rear direction of travel is pivotally connected to a traveling carriage that travels on a rail, and the swing arms are elastically biased in a closing direction by a coil spring. In addition, a pair of left and right wedge-shaped brake shoes that are press-contactable to the side surface of the head of the rail is held at the lower end of each swing arm, and the wedge-shaped brake shoe is attached to the rail by the elastic biasing force of the coil spring. When the traveling carriage is about to escape, the wedge-shaped brake shoe on the front side in the escape direction is wedge-shaped in the clearance between the rail and the traveling carriage. It is inserted deeply into the main body, is switched to the full-fledged clamp state for preventing escape, and is configured to increase the force of pressing against the side surface of the head of the rail.

The wedge-type brake shoe is elastically biased in a direction away from each other by an elastic member.
The coil spring is housed in a hydraulic cylinder for opening the swing arm against the elastic urging force.
The traveling carriage has a guide roller that rolls in contact with the outer surface of the wedge-shaped brake shoe.
Further, the swing arm is provided with a contact member that can come into contact with the stopper of the traveling carriage, and in the full-scale clamped state, the hydraulic cylinder is operated, so that one arm on the rear side in the escape direction is provided. Swings first, the abutting member of one of the arms comes into contact with the stopper and the swinging is restricted, and the power of the hydraulic cylinder is used to swing the other arm on the front side in the escape direction. The wedge-shaped brake shoe inserted deeply in a wedge shape into the gap is configured to be pulled out.

  According to the rail clamp device of the present invention, when the traveling carriage tries to escape, the force with which the wedge brake shoe presses the rail increases, and a large holding force can be obtained. A small force for the pre-clamped state is sufficient as the spring biasing force of the coil spring. As described above, since the spring biasing force of the coil spring can be small, the coil spring can be reduced in size, and the housing case of the coil spring and the member for transmitting the spring biasing force can be reduced in size and weight can be reduced. Cost can be kept low. Even when the part where the width of the head of the rail is narrower than the reference value is clamped, the wedge-type brake shoe is only inserted deeply, and the holding force is not lowered, so it is possible to reliably prevent the runaway. Even when the rail is bent or locally swollen, the rail and the brake shoe do not come into contact with each other during traveling, and the vehicle can travel smoothly.

It is the perspective view which looked at the rail clamp apparatus of this invention from diagonally upward. It is the perspective view which looked at the rail clamp device of the present invention from the slanting bottom. It is the perspective view which removed and showed the bracket of the rail clamp apparatus of this invention. It is the top view which showed the rail clamp apparatus of this invention. It is the partial cross section side view which showed the rail clamp apparatus of this invention. It is a simplified sectional side view showing a preliminary clamp state. It is a simplified sectional front view which shows a preliminary clamp state. It is a simplified cross-sectional top view which shows a real clamp state. It is a simplified cross section side view which shows a clamp open state. It is a simplified cross-sectional top view which shows a clamp open state.

Hereinafter, the present invention will be described in detail with reference to the drawings illustrating embodiments.
The rail clamp device of the present invention is a runaway for preventing a moving structure such as a cargo handling machine moving along the rail from running away (moving in the running direction) due to a strong external force or a strong wind while stopping. Prevention device. The cargo handling machine is, for example, a container crane that is used in a harbor to load and unload containers. Another moving structure is a dome-type open / close roof that moves along a rail. A rail clamp device is connected to a large moving structure such as a container crane or an open / close roof, and the rail clamp device grips (clamps) the rail to prevent runaway during stoppage. It is configured to be movable.
As shown in FIGS. 1 and 2, the rail clamp device of the present invention includes a bracket 2 attached to a moving structure (not shown), and an internal unit 1 accommodated inside the bracket 2.

  The bracket 2 is formed in a rectangular shape in a plan view (see FIG. 4), and when the moving structure is about to escape, the abutting piece portions 20, 20, 20 that contact the internal unit 1 (the traveling carriage 3) and transmit the escape force. 20 and 20 are formed in a protruding shape on the inside. The bracket 2 is open at the top and bottom, surrounds a traveling carriage 3 to be described later in a loose fit, and surrounds the lower part of the internal unit 1 and accommodates it inside. The bracket 2 and the internal unit 1 are not connected and fixed, and the internal unit 1 (travel carriage 3) can move within the bracket 2 by a small dimension. When the moving structure moves along the rail, the movement is transmitted through the contact piece 20 and the bracket 2 pulls (or pushes) the internal unit 1.

As shown in FIGS. 2 to 5, the internal unit 1 includes a traveling carriage 3 having traveling rollers 5 and 5 that roll on the upper surface Ra of the head of the rail R, and a pair of front and rear rockers pivoted on the traveling carriage 3. The hydraulic cylinder 4 disposed between the movable arms 11 and 11 and the swinging arms 11 and 11 and pivotally attached to the traveling carriage 3; A compression coil spring 8 for energizing and energizing.
Left and right connecting rods 17, 17 are fixed to the lower end portion 11 b of each swing arm 11, and mounting members 6, 6 are held by the connecting rods 17, 17 so as to be able to approach and be separated from each other. . A pair of left and right wedge-shaped brake shoes 7, 7 that are press-contactable to the head side surfaces Rb, Rb of the rail R are attached to the mounting members 6, 6. The wedge-type brake shoes 7 and 7 have inclined surfaces 21 and 21 on the outside, and are formed so that the thickness gradually decreases toward the tip. In addition, the wedge-type brake shoes 7 and 7 have friction surfaces 22 and 22 that press against the head side surfaces Rb and Rb of the rail R and brake the traveling carriage 3 with frictional force. The friction surfaces 22 and 22 are formed with a plurality of vertical grooves for improving the friction coefficient, or are formed with irregularities. The wedge-type brake shoes 7 and 7 are attached (fixed) by bolts inserted through the mounting members 6 and 6, and can be easily replaced when worn or damaged. Between the mounting members 6 and 6 to which the wedge brake shoes 7 and 7 are attached, the resilient members 12 and 12 wound around the connecting rods 17 and 17 are disposed. The elastic members 12 and 12 are elastically biased in directions away from each other.

The swing arm 11 has a pair of left and right flat plate members 18, 18 which are arranged in parallel to each other so as to sandwich the front end portion and the rear end portion of the traveling carriage 3, The fulcrum pins 23 are integrally connected and fixed. That is, the pair of front and rear swing arms 11, 11 can be opened and closed (swinged) in the front-rear direction of the travel cart 3 around the fulcrum pins 23, 23. Note that the fulcrum pins 23 and 23 are disposed at intermediate positions in the vertical direction of the swing arms 11 and 11, and in FIG. 9, the length dimension La from the fulcrum pin 23 to the upper end portion 11a of the swing arm 11 is The relationship between the fulcrum pin 23 and the length Lb from the lower end portion 11b of the swing arm 11 is set to satisfy La <Lb. The upper ends 11a and 11a of the swing arms 11 and 11 are connected to the rod 14 of the hydraulic cylinder 4 via link members 19 and 19, and the swing arm is driven by the spring force (elastic urging force) of the coil spring 8. 11 and 11 are elastically biased so as to swing in the closing direction.
The hydraulic cylinder 4 is supplied with a working fluid from a hydraulic supply device (not shown) and opens the swing arms 11 and 11 against the spring force (elastic urging force) of the coil spring 8 (in the opening direction). It is configured to swing. When the hydraulic cylinder 4 is not operated, the swinging arms 11 and 11 are always elastically biased in the closing direction by the coil spring 8.
In the present invention, the “open direction” refers to the direction in which the lower end portions 11b, 11b of the swing arms 11, 11 are separated from each other, and the “close direction” refers to the lower ends of the swing arms 11, 11. It is assumed that the parts 11b and 11b approach each other.

  The traveling carriage 3 has vertical contact walls 9 and 9 that hang down with a gap on both sides of the rail R. That is, a gap having a predetermined width is formed between the abutting walls 9 and 9 of the traveling carriage 3 and the head side surfaces Rb and Rb of the rail R. The width of the gap is a wedge-shaped brake shoe 7. , 7 is set to be larger than the distal end side minimum width dimension and smaller than the proximal end side maximum width dimension. By swinging the swing arms 11, 11 in the closing direction by the spring force of the coil spring 8, the wedge-type brake shoes 7, 7 are inserted into the gap between the rail R and the abutting walls 9, 9, While the inclined surfaces 21 and 21 are brought into contact with the contact walls 9 and 9, the distance between the wedge brake shoes 7 and 7 is reduced (closer to each other), and the inner friction surfaces 22 and 22 are moved to the head of the rail R. It abuts on the side surfaces Rb and Rb. The traveling carriage 3 has guide rollers 13 and 13 on the inner side of the abutting walls 9 and 9, which roll while contacting the outer inclined surfaces 21 and 21 when the wedge-type brake shoes 7 and 7 are inserted. doing. The inclined surfaces 21 and 21 of the wedge-type brake shoes 7 and 7 and the surfaces of the guide rollers 13 and 13 are subjected to a surface treatment for reducing the friction coefficient and improving the surface hardness. Yes. With this configuration, the efficiency of converting the escape force into the pressure contact force is further improved. Moreover, since the traveling cart 3 has the traveling rollers 5 and 5 with left and right hooks that roll on the upper surface Ra of the head of the rail R, the traveling cart 3 follows the rail R even if the rail R is bent. It travels and can move in the left-right direction and the up-down direction in the bracket 2.

  Further, the swinging arms 11 and 11 are provided with contact members 15 and 15 at an intermediate position in the vertical direction. When the swinging arms 3 and 11 swing in the opening direction by a certain amount, Stoppers 16 and 16 projectingly come into contact with the contact members 15 and 15 to restrict swinging.

A method (action) of using the above-described rail clamp device of the present invention will be described.
As shown in FIGS. 6 and 7, the elastic urging force of the coil spring 8 pulls the rod 14 of the hydraulic cylinder 4 and swings the swing arms 11 and 11 in the closing direction. As the swing arms 11 and 11 swing in the closing direction, the wedge-type brake shoes 7 and 7 are inserted into the gap between the rail R and the traveling carriage 3 (the contact wall portions 9 and 9). The wedge-type brake shoes 7 and 7 have outer inclined surfaces 21 and 21 that are pressed against the abutting wall portions 9 and 9 (guide rollers 13 and 13) and approach each other, and head side surfaces Rb and Rb of the rail R Is lightly gripped with a small pressure contact force F ₀ , F ₀ , and a preliminary clamped state is established.

Next, as shown in FIG. 8, when a runaway force is applied to the bracket 2 (connected to the moving structure), the runaway force is transmitted from the contact piece portions 20, 20 of the bracket 2 to the running carriage 3. When the traveling carriage 3 tries to escape (pressed by the bracket 2), the wedge-shaped brake shoes 7, 7 on the front side in the escape direction are deeply wedged in the gap between the rail R and the abutting walls 9, 9. Plugged in. In other words, when a runaway force in the longitudinal direction of the running is applied to the traveling carriage 3, a great force is applied to the wedge brake shoes 7 and 7 by the runaway force, and the wedge brake shoes 7 and 7 are strongly pressed against the rail R. Switch to the full clamp state to prevent runaway. In the fully clamped state, the wedge-type brake shoes 7 and 7 are strongly pressed against the guide rollers 13 and 13 of the abutting wall portions 9 and 9, and the wedge side action of the brake shoes 7 and 7 causes the head side surfaces Rb and Rb of the rail R to face. Is strongly tightened with a large pressure contact force F ₁ , F ₁ . If the escape force applied to the traveling carriage 3 increases under the full clamp condition, the magnitudes of the pressure contact forces F ₁ and F ₁ also increase in proportion to this.

  When the pre-clamp state is switched to the full-clamp state, the hydraulic cylinder 4 is slightly tilted from the vertical state (see FIG. 6) to the front side in the escape direction, and the link member 19 moves the upper end portion 11a of the swing arm 11. The wedge-shaped brake shoes 7 and 7 at the lower end portion 11 b are inserted deeply into the gap between the rail R and the contact wall portions 9 and 9. In other words, the traveling carriage 3 slightly moves forward in the escape direction due to the escape force, but since the hydraulic cylinder 4 is pivotally attached to the traveling carriage 3, the wedge brake shoes 7, 7 are connected to the rail R The structure is such that the wedge action of the brake shoes 7 and 7 can be increased without stopping in the longitudinal direction (front-rear direction).

  Next, as shown in FIGS. 9 and 10, hydraulic pressure is supplied to the hydraulic cylinder 4 to operate, and the swing arms 11 and 11 are opened in the opening direction against the spring force (elastic urging force) of the coil spring 8. Rocks. By swinging the swing arms 11, 11 in the opening direction, the wedge-type brake shoes 7, 7 are pulled out from the gap between the rail R and the contact wall portions 9, 9. Since the contact portion between the traveling carriage 3 and the wedge brake shoes 7 and 7 is almost free from friction due to rolling with the guide rollers 13 and 13, the wedge brake shoes 7 and 7 are pulled out with a small force.

  In the full clamp state, the wedge brake shoes 7, 7 on the front side in the escape direction are inserted deeply into the gap between the rail R and the abutting walls 9, 9, so that the front wedge brake A strong force is required to pull out the shoes 7,7. For this reason, when the hydraulic cylinder 4 is operated, the wedge-shaped brake shoes 7 and 7 on the rear side in the escape direction are removed first, and only one arm 11 (on the rear side) swings first. When the fixed amount swings, the contact member 15 comes into contact with the stopper 16 of the traveling carriage 3 (not shown), and the swing of the rear arm 11 is restricted. It doesn't move. Since one arm 11 is locked, the power of the hydraulic cylinder 4 is used only for swinging the other arm 11 on the front side in the escape direction, and the wedge brake is inserted deeply into the gap. The shoes 7, 7 can be pulled out.

As shown in FIG. 10, the wedge-type brake shoes 7, 7 are elastically urged in a direction away from each other by the elastic members 12, 12, so that the rail R and the contact wall portions 9, 9 are separated from each other. When pulled out from the gap, a sufficient clearance (gap) C can be automatically secured by separating from the head side surfaces Rb, Rb of the rail R.
9, the relationship between the length dimension La from the upper end portion 11a of the swing arm 11 to the fulcrum pin 23 and the length dimension Lb from the lower end portion 11b of the swing arm 11 to the fulcrum pin 23 is as follows. Since La <Lb, the stroke in the opening / closing direction of the lower end portion 11b of the swing arm 11 can be increased. In other words, even when the portion where the width of the head of the rail R is narrower than the reference value is clamped, the wedge-shaped brake shoes 7 and 7 are inserted deeply and pressed against the head side surfaces Rb and Rb of the rail R. Can do. Further, when the clamp is released, the clearance (gap) C between the wedge-type brake shoes 7 and 7 can be secured sufficiently wide. Specifically, when the clamp is opened, the width of the clearance C between the head side surfaces Rb and Rb of the rail R and the wedge-shaped brake shoes 7 and 7 is set to 20 mm. Compared with the clearance of 5 mm on one side, it is clear that there is a margin in the clearance C of the wedge-type brake shoes 7, 7. Therefore, even when the rail R is bent or locally swollen, it can be said that the probability that the rail R and the wedge brake shoes 7 and 7 are in contact with each other during traveling is low.

  In the present invention, the design can be changed. For example, the guide rollers 13 and 13 may be omitted, and the wedge-shaped brake shoes 7 and 7 are inserted in the gap between the rail R and the contact wall portions 9 and 9. The wedge-shaped brake shoes 7 and 7 may be slidably contacted with the inner surfaces of the contact walls 9 and 9 of the traveling carriage 3.

  As described above, in the rail clamp device according to the present invention, the pair of swinging arms 11 and 11 that open and close in the traveling front-rear direction are pivotally connected to the traveling carriage 3 that travels on the rail R. And a pair of right and left wedge-shaped brake shoes 7, 7 that can be pressed against the head side surfaces Rb, Rb of the rail R at the lower end portion 11 b of each swing arm 11. The wedge-type brake shoes 7 and 7 are inserted into the gap between the rail R and the traveling carriage 3 due to the elastic urging force of the coil spring 8 and are in a pre-clamp state, and when the traveling carriage 3 tries to escape, The front wedge wedge shoes 7 and 7 are inserted into the gap between the rail R and the traveling carriage 3 in a wedge shape and switched to a full clamp state for preventing runaway, and are pressed against the head side surfaces Rb and Rb of the rail R. Since that force is arranged to increase, when the traveling carriage 3 is to escape, can wedge brake shoes 7, 7 a force for pressing the rail R is increased, obtaining a large holding force. The spring urging force of the coil spring 8 can be small, the coil spring 8 can be miniaturized, and the cost can be kept low. Even when clamping the portion where the width of the head of the rail R is narrower than the reference value, the wedge-type brake shoes 7 and 7 are only inserted deeply, and the holding force does not decrease, so it is possible to reliably prevent escape. . Even when the rail R is bent or locally swollen, the rail R and the wedge-shaped brake shoes 7 and 7 do not come into contact with each other during traveling, and the vehicle can travel smoothly.

  Further, since the wedge-type brake shoes 7 and 7 are elastically biased in a direction away from each other by the elastic member 12, the clearance C (interval) between the rail R and the wedge-type brake shoes 7 and 7 is released when the clamp is released. Can be secured sufficiently large.

  Further, since the coil spring 8 is housed inside the hydraulic cylinder 4 for opening the swing arms 11 and 11 against the elastic biasing force, the overall height can be suppressed and the entire apparatus can be made compact. .

  In addition, the traveling carriage 3 has guide rollers 13 and 13 that roll in contact with the outer surfaces (inclined surfaces 21 and 21) of the wedge-type brake shoes 7 and 7, so that the escape force is efficiently used as a holding force. Can convert well. If surface treatment is performed on the inclined surfaces 21 and 21 and the guide rollers 13 and 13 of the wedge brake shoes 7 and 7, the conversion efficiency can be further improved.

  In addition, the swinging arms 11 and 11 are provided with contact members 15 and 15 that can come into contact with the stoppers 16 and 16 of the traveling carriage 3, and the hydraulic cylinder 4 is operated in a full-clamped state, so One arm 11 on the rear side in the direction swings first, the contact member 15 of one arm 11 abuts against the stopper 16 and the swing is restricted, and the other arm 11 on the front side in the escape direction swings. Since the power of the hydraulic cylinder 4 is used and the wedge-shaped brake shoes 7, 7 deeply inserted in a wedge shape are pulled out into the gap, the wedge-shaped brake shoes 7 on the front side in the escape direction are inserted deeply. , 7 requires a strong force, but since the power of the hydraulic cylinder 4 can be used to swing the arm 11 on the front side in the escape direction, the wedge-type brake shoes 7, 7 inserted deeply are pulled out. Can Can, it is possible to reliably release the clamp.

DESCRIPTION OF SYMBOLS 3 Traveling trolley 4 Hydraulic cylinder 7 Wedge-type brake shoe 8 Coil spring 11 Swing arm 11b Lower end part 12 Elastic member 13 Guide roller 15 Contact member 16 Stopper R Rail Rb Head side surface

Claims (5)

A pair of swing arms (11) and (11) that open and close in the front-rear direction of travel are pivotally connected to a traveling carriage (3) that travels on the rail (R), and the swing arms (11) and (11) are coil springs. (8) A pair of left and right arms that are elastically biased in the closing direction and can be press-contacted to the head side surfaces (Rb) and (Rb) of the rail (R) at the lower end (11b) of each swing arm (11). Hold the wedge-shaped brake shoe (7) (7)
Due to the elastic urging force of the coil spring (8), the wedge-shaped brake shoes (7) (7) are inserted into the gap between the rail (R) and the traveling carriage (3) to be in a preliminary clamp state, When the traveling carriage (3) tries to escape, the wedge brake shoes (7) (7) on the front side in the escape direction are wedged in the gap between the rail (R) and the traveling carriage (3). A rail clamping device characterized in that it is inserted deeply and switched to a full-fledged clamping state for preventing runaway, and the force that presses against the head side surface (Rb) (Rb) of the rail (R) is increased. .   The rail clamp device according to claim 1, wherein the wedge-shaped brake shoes (7) (7) are elastically biased in a direction away from each other by an elastic member (12).   The said coil spring (8) is accommodated in the inside of the hydraulic cylinder (4) for opening the said rocking | swiveling arm (11) (11) against the said elastic urging | biasing force. The rail clamp device described.   The said traveling cart (3) has the guide roller (13) (13) which abuts on the outer surface of the said wedge type brake shoes (7) (7), and rolls. Rail clamp device. The swing arms (11) (11) are provided with contact members (15) (15) that can come into contact with the stoppers (16) (16) of the traveling carriage (3),
When the hydraulic cylinder (4) is operated in the full clamp state, one arm (11) on the rear side in the escape direction swings first, and the contact member ( 15) abuts against the stopper (16) and the swinging is restricted, and the power of the hydraulic cylinder (4) is used for swinging the other arm (11) on the front side in the runaway direction. The rail clamp device according to claim 3 or 4 constituted so that said wedge type brake shoes (7) (7) deeply inserted in the shape of a wedge may be pulled out.

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