JP2588476B2 - Fluid shelves - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a method for intermittently moving a load carried into a carry-in port in a horizontal direction toward a carry-out port and continuously storing the load from the carry-in port to the carry-out port. It is about a possible fluid shelf.

[0002]

2. Description of the Related Art Conventionally, in a fluidized shelf widely used in various parts warehouses, distribution warehouses, production factories, etc., loads are successively carried in from a carry-in entrance, and are sequentially carried out from a carry-out exit in accordance with the carrying order.

In order to perform such an operation, in a conventional general fluidized shelf, a large number of rollers or wheels are freely rotatable along the longitudinal direction of the rail on a rail that is gently inclined downward from the carry-in port to the carry-out port. Pivoted to
The self-propelling force P = Wsin α in the longitudinal direction of the inclined rail due to the weight (W) of the load placed on the roller of the inclined rail inclined at an angle α with respect to the horizontal plane is the frictional force F = μWc of the load.
The inclination angle α of the inclined rail is set so as to slightly exceed os α (μ; the coefficient of rolling friction of the load of the inclined rail against the roller), and the load is caused to travel by the self-propelling force P.

However, since the rolling friction coefficient μ of the load on the roller of the inclined rail varies not only with the material of the bottom surface of the load, but also greatly depending on the state of the unevenness of the bottom surface of the load, the rolling friction coefficient μ is large. As a result of setting the inclination angle α of the inclined rail to a slightly large value so that the load can move on its own, the self-propelled speed increases in the state of a load with a small rolling friction coefficient, especially when the inclined rail is long and transported. If there is no load between the mouth and the exit, the load carried into the entrance of the inclined rail accelerates while traveling on the inclined rail,
When a self-propelled load abuts a stationary load on the carry-out side or a stopper at the carry-out port, an undesirably large impact force may be generated on the load. In an attempt to eliminate these shortcomings,
In the past, there was a roller that applied braking force to a roller in the middle of the self-propelled path from the carry-in entrance to the carry-out exit.However, it was difficult to adjust this braking force, and the adverse effects caused by fluctuations in the rolling friction coefficient were sufficiently reduced. Could not be ruled out.

In order to eliminate such a defect, the present applicant has disclosed Japanese Patent Publication No. 2-50004 (JP-A-62-249).
No. 803) was invented. In this fluidized shelf, a pair of left and right long fixed rails parallel to each other are set so as to be inclined slightly downward to the carry-out port so that the load cannot move from the carry-in port to the carry-out port by itself. A moving rail shorter than the fixed rail is set inside each pair of fixed rails so as to be able to reciprocate back and forth through a roller, and a wheel for transferring the load protruding upward from the fixed rail above the moving rail. And a reciprocating drive device that pivots the moving rail back and forth along the fixed rail at a constant stroke.

In the fluidizing shelf described in Japanese Patent Publication No. 2-50004, the reciprocating drive device reciprocates the moving rail which is slightly inclined so that the load on the moving rail is not directed toward the carry-out port and can not move on its own. When the moving rail moves forward,
The load moves forward with the moving rail while the rotation of the wheel for transferring the load is prevented by the force of the self-propelling force in the forward direction, and when the moving rail retreats, the forward self-propelling force and the load in the direction opposite to the movement of the moving rail are reversed. The inertia force of the load overcomes the rolling friction force of the load,
The load transfer wheel rotates, the load is held at its forward position, and the load is transferred from the carry-in port to the carry-out port by one-way intermittent rotation of the load transfer wheel.
When there are various load materials and the rolling friction force of the load fluctuates widely, if the rolling friction force is large depending on the material of the load compared to the self-propelling force of the load due to the inclination of the fixed rail, In addition to the forward and backward movement of the moving rail, the load may reciprocate in unison with the moving rail, and the load may not be able to be discharged toward the discharge port. As a result, dead space was generated that was not directly involved in storage of the load, and storage efficiency was low.

[0007] In order to overcome such difficulties, the present applicant has disclosed Japanese Patent Application Laid-Open No. 2-300012 (Japanese Patent Publication No. 7-33).
163). According to the present invention, a pair of left and right guide rails and a movable rail are disposed in a horizontal direction, and an upper portion of the pair of guide rails is arranged substantially upward in the transport direction in a locking frame arranged at the center in the width direction. 45 °
A large number of inclined locking plates are pivotally supported at intervals of a fraction B of the dimension A in the transport direction of the load.

When the lower portion of the locking plate abuts on the locking frame,
5 ° In the inclined state, the upper part of the locking plate falls forward to allow the load to move forward when passing the load in the transport direction at the front of the moving rail, but the load passes through the upper part of the locking plate. Then, it returns to the 45 ° inclined state again and faces the back of the load, and the upper portion of the locking plate abuts against the back of the load to be retreated along with the retreating stroke of the moving rail, thereby preventing the retreat of the load. The load is conveyed by such a step.

[0009]

However, the locking plate of the invention (Japanese Patent Application Laid-Open No. 2-300012) allows both forward and backward movement of the load when the upper portion thereof is in contact with the bottom surface of the load and falls down. In this state, the load is prevented from retreating by abutting the back of the load, and in most cases, there is a gap between the back of the load when it has finished moving forward and the upright stop plate immediately after that. Therefore, during the retreating stroke of the moving rail, the load retreats together with the moving rail by a distance corresponding to the gap, and stops only after colliding with the locking plate.

As a result, if the gap between the locking plates is large, each time the moving rail retreats, a collision with the locking plate exerts an impact force on the load, which may adversely affect the load. The stepping distance of the load is shorter than the rail stroke,
The transport efficiency decreases. If the gap between the locking plates is reduced in order to prevent such a large impact force and a decrease in the transport efficiency, the number of locking plates is greatly increased, the number of assembling steps is also increased, and the cost is increased. Is inevitable.

[0011] In addition, when the load is closely moved forward and backward and collectively steps forward, only the locking plate abutting on the rear surface of the rearmost load is provided.
There is a concern that the inertia force of the load of the entire group acts in a concentrated manner and the locking plate is damaged. Further, until the rear end of the load delivered to the carry-in port passes over the locking plate closest to the carry-in port, the retreat of the load due to the retreat of the moving rail is not prevented, and the transport of the incoming load is delayed. There is.

Further, in order to reduce the contact load on the back surface of the load locked by the locking plate, the width of the locking plate is increased, and the width of the locking frame pivotally supporting the locking plate is also increased. As a result, the locking frame cannot be removed and the locking plate cannot be pivotally supported on one side of the fixed rail, and a locking frame is separately required at the center in the width direction of the pair of left and right fixed rails. Had to be arranged. Therefore, when the position of the center of gravity of the load is unevenly distributed to one of the right and left, a turning moment is generated in the load, and there is a concern that the direction of the load may change to the left or right.

[0013]

SUMMARY OF THE INVENTION The present invention relates to an improvement of a flow end which solves such a problem.
At least one pair of left and right long fixed rails, which are installed parallel to each other at predetermined intervals on the left and right and are directed in the front-rear horizontal direction, and one pair of left and right supported by the fixed rails so as to be able to reciprocate back and forth. And a plurality of load transfer rotating wheels protruding upward from the fixed rail at predetermined intervals in the longitudinal direction of the moving rail and rotatably supported on the upper part of the moving rail. The pair of left and right moving rails are integrally connected to each other with a connecting rod, and reciprocating drive means for reciprocating the connecting rod back and forth is provided. Due to the lower eccentric weight of the piece, a plurality of load-return preventing portions are pivotally supported in a vertical upright posture over the longitudinal direction of the fixed rail, and the top of the load-return preventing portion is carried out from the vertical upright position. Can tilt toward
Reverse tilt preventing means is provided which can abut against the load reverse-feed preventing piece so that it cannot tilt in the reverse direction from the vertical standing posture, and the top of the load reverse-feed preventive piece has a concave-convex curved shape protruding upward. The height of the top surface of the load transfer rotating wheel is set to be lower than the height of the top end of the load-return preventing section in the upright posture, and the top end of the load-return preventing section is located at the carry-out port. It is characterized in that it is locked to the bottom surface of the load on the load transfer rotary wheel in a state inclined toward the load.

Since the present invention is constructed as described above, when the load is loaded from the carry-in port onto the rotating wheel for transferring the load of the moving rail and loaded, and the reciprocating drive means is operated, the moving rail is moved. Reciprocates with respect to the fixed rail, and when the moving rail moves toward the carry-out port,
The load on the moving rail receives a weak frictional force with the top of the load back-feed prevention part due to the eccentric moment of the inclined load back-feed prevention part, but the load is moved by the movement of the load toward the carry-out port. The top portion of the reverse feed prevention portion tilts toward the carry-out port to eliminate the frictional force, and the load on the moving rail slides on the top portion of the load reverse feed prevention portion and is carried along with the moving rail as it is. It can move toward the outlet by the stroke of the reciprocating drive means.

When the moving rail moves back toward the carry-in entrance, the load on the moving rail is lifted by the eccentric moment of the inclined load reverse-feed preventing piece to the top of the load reverse-feed preventing piece. In addition to the frictional force described above, a stronger frictional force is applied by the frictional force caused by the load-return-preventing piece trying to stand in the vertical direction, and a large stopping force acts on the load on the moving rail, Only the moving rail is returned to the entrance, and the load on the moving rail remains stopped. In addition, in the present invention, if the top of the load-return preventing piece is in contact with the bottom surface of the load, the stopping force of the load-return-preventing piece is always applied to the load. Works, and the load is fixed.Therefore, a large load is not applied to the individual load reverse-prevention pieces and it is hard to break, and there is no play in the movement of the load against the reciprocation of the moving rail, and the transport efficiency is improved. Is high,
No impact occurs. In addition, even if the stopping force is further increased and the load reverse-prevention piece is raised vertically and tries to fall down toward the carry-in port, the fall-down is prevented by the reverse tilt preventing means, and the moving rail is prevented. The upper load is prevented from being sent back to the entrance.

As described above, by the operation of the reciprocating drive means, when the moving rail moves forward by one stroke to the carry-out port, the load on the moving rail advances, and when the moving rail moves backward to the carry-in port, Since the load on the moving rail is stopped, the load intermittently moves along the longitudinal direction of the moving rail from the entrance to the exit.

Therefore, according to the present invention, the load can be held firmly and stopped when the moving rail moves backward, so that the load can be moved efficiently and reliably with the minimum number of reciprocations in the reciprocating drive means.

Further, since the fixed rail is erected horizontally,
There is no drop between the carry-in port and the carry-out port, and the number of loads stored is large relative to the volume occupied by the entire flow shelf, and the storage volume efficiency is high.

Further, according to the present invention, the load reverse-prevention members located immediately below the load are respectively engaged with the load above the load and the reverse feed toward the carry-in port is prevented. The back-feed preventing force applied to the back-feed prevention member is reduced, and the back-feed prevention member is less likely to be damaged.

Further, according to the present invention, since the load-return preventing piece always tends to stand up due to its eccentric weight at the bottom, the load-return preventing piece does not need any return means, and can be tilted. Can be automatically returned to the standing state, the structure is significantly simplified, and a large cost reduction is possible.

Further, by configuring the present invention as described in the second aspect, when the moving rail is moved backward, the top portion of the load reversing prevention portion is securely frictionally pressed against the load on the moving rail. In this way, it is possible to prevent the load from being sent backward and to carry out the load more reliably.

According to the third aspect of the present invention, when the bottom surface of the load is relatively easily deformed, the sharpness of the load reverse-preventing piece can be reduced when the moving rail moves backward. The top portion is made to bite into the bottom surface of the load on the moving rail, so that the reverse transfer of the load can be reliably prevented, and the load can be transported more reliably.

Further, by configuring the present invention as described in claim 4 or 5, the moving rail can be reciprocated lightly on the fixed rail, and the size of the reciprocating drive means can be reduced. Can be planned.

Still further, according to the present invention, at least one pair of right and left reverse feed preventing portions is always locked regardless of the position on the moving rail. Thus, the load stopping force acting on the back-feed preventing portion can be reduced, and the durability of the back-feed preventing portion can be improved.

According to the seventh aspect of the present invention, it is possible to prevent the impact force at the time of carrying in from being directly applied to the back-feed preventing portion, thereby preventing the back-feed preventing portion. Can reliably be prevented from being damaged.

Further, according to the present invention, the back-feed preventing pieces on the entrance side, which are apt to receive a large load stopping force at the time of starting the load transfer, are densely arranged to prevent the back-feed. It is possible to disperse the load stopping force applied to the piece and avoid damage to the back-feed preventing piece.

Further, according to the present invention, the load conveyed to the carry-out port can be stably supported by the auxiliary rotating wheel independently of the reciprocating motion of the moving rail. Can be carried out smoothly.

According to the present invention, the load on the transfer rail can be immediately advanced by one stroke when the transfer of the load is started, so that the time required for the load transfer can be reduced. As a result, it is possible to improve the shipping efficiency, and at the time of unloading, reduce the mutual pressure contact between the load at the unloading port and the load located on the loading side, thereby facilitating the unloading of the load at the unloading port.

Further, according to the present invention, the moving rail is slowly moved from the carry-in port to the carry-out port, and is pivotally mounted on the moving rail to support the load. The load can be transferred to the unloading side together with the moving rail while preventing the rotating wheel for transferring the load from rotating, and the moving rail is rapidly moved from the carry-out port to the carry-in port, and pivoted to the moving rail. The load transfer rotating wheel that is being worn can be idled, and the load on the moving rail can be stopped irrespective of the movement of the moving rail, and as a result,
The load on the load-return preventing piece is reduced, the load is prevented from being returned, and the load can be surely moved forward. The load can be conveyed to the unloading side.

[0030]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention shown in FIGS. 1 to 10 will be described below.

In the fluidizing shelf 1, a large number of columns 2 are erected in rows in the front-rear direction (left-right direction in FIG. 1) and left-right direction (right-left direction in FIG. 2). Are connected to each other by a transverse beam 3 directed in the direction, and are reinforced by a brace 4 and the like, between adjacent left and right pillars 2 and 2 and upper and lower lateral beams 3 and 3 (above the uppermost lateral beam 3, ), A shelf booth 5 is formed. As shown in FIG. 1, each shelf booth 5 extends from the carry-in port 8 (right side in FIG. 1) to the carry-out port 9 in the front-rear direction (the left-right direction in FIG. 1).
(Left side in FIG. 1), and such a shelf booth 5
However, as shown in FIG. 2, a large number are arranged vertically and horizontally.

In each of the shelf booths 5, a pair of left and right rail devices 6 are respectively connected from the entrance 8 to the exit 9 by connecting the lower lateral beam 3 back and forth, and a stopper 10 is provided at the exit 9. The load 7 carried into the shelf booth 5 from the inlet 8 of the fluidized shelf 1 is stepped toward the outlet 9 and stopped by the stopper 10 as described later. Has become.

Further, the rail device 6 comprises a pair of left and right fixed rails 11 and a pair of left and right moving rails 16. The fixed rails 11 are separated to the left and right and the arrangement center line is set as a symmetry axis. As shown in FIG. 5, the upper portions of the fixed rail pieces 12 and 13 are formed in a lateral channel shape, and the lower portions thereof are formed as shown in FIG. It is bent downward at a right angle, and its lower end is bent outward at a right angle.
The fixed rail pieces 12, 13 have a fixed width on the left and right sides and are horizontally parallel to each other by bolts 14 which are screwed into the lateral beams 3 through the support portions 12a, 13a. It is integrally fixed to the transverse beam 3 in a direction.

Further, the moving rail 16 is formed by bending the upward channel-like side portions 16a, 16b outward at a right angle,
The end 16c of the outer portion 16b is bent obliquely upward and outward, and a central portion 16d of the moving rail 16 is provided with a large number of holes 17 in the longitudinal direction of the moving rail 16, and the end 16c is While serving as a guide plate, dust and the like that has fallen onto the fixed rail 11 and the moving rail 16 from above are discharged downward through the holes 17 and the openings 15.

As shown in FIG. 8, the moving rail 16 is set shorter than the fixed rail 11 by a stroke L of an air cylinder 33, as shown in FIG. 8, and as shown in FIG. The lower part of both sides 16a, 16b of
An axis oriented laterally with a predetermined interval along its longitudinal direction
18 is penetrated, and a rolling wheel 20 is provided at both ends of the shaft 18 via bearings 19.
Are provided rotatably, and the rolling wheels 20 are fixed rails 11.
Rolling on the tread portions 12b, 13b of the fixed rail pieces 12, 13, so that the moving rail 16 can move lightly in the fixed rail 11 reciprocally along its longitudinal direction.

As shown in FIG. 5, shafts 21, which extend in the horizontal direction at regular intervals in the longitudinal direction of the moving rail 16, penetrate through the upper portions of both sides 16 a and 16 b of the moving rail 16. A sleeve 22 is fitted around the outer periphery of the shaft 21, and
The load-transporting rotating wheels 24 project from the side portions 16a, 16b of the moving rail 16 upward through the ball bearings 23, and are rotatably fitted in a staggered manner in plan view. I have.

Further, as shown in FIG. 6, the upper portions of a pair of left and right mounting plates 26 are integrally attached to a substantially central portion of the left and right moving rails 16 in the longitudinal direction, as shown in FIG. The lower part of the plate 26 is the opening of the fixed rail 11
15, a gusset plate 27 is integrally fixed to the lower part of the pair of mounting plates 26 by bolts and nuts 28, and a connecting rod 29 oriented in the width direction of the flow shelf 1 is provided below the gusset plate 27.
Mounting plate 30 is integrally mounted by bolts and nuts 31.

Further, as shown in FIG. 4, the horizontal beam 3 located at the center of the left and right rail devices 6 in the left-right width direction and the horizontal beam 3 located on the side of the carry-out exit 9 therefrom include:
A cylinder support member 32 is installed in parallel with the rail device 6,
A double-acting air cylinder 33 serving as a reciprocating drive means is installed on the cylinder support member 32 in parallel with the rail device 6, and the tip of a piston rod 34 of the air cylinder 33 is connected to the connection rod 29 via a connection member 35. When the piston rod 34 expands and contracts by the stroke L (set to 1/4 of the longitudinal dimension of the load 7 or slightly larger), the connecting rod 29, that is, the moving rail 16 is correspondingly moved. You can go back and forth.

When the moving rail 16 reciprocates between the carry-in port 8 and the carry-out port 9, the load 7 on the rolling wheel 20 of the moving rail 16 is advanced together with the moving rail 16 when the moving rail 16 advances. Further, a load reversing prevention piece 36 for stopping the load 7 when the moving rail 16 is retracted is densely provided near the carry-in port 8 via the pivot 40 as shown in FIGS. 3, 5 and 9. The support frame 41 is pivotally attached to the support frame 41 at predetermined intervals so as to be sparse near the carry-out port 9, and the support frame 41 is moved from the place located near the carry-out port 9 by the front and rear dimensions of the load 7 from the carry-in port 8. 9 are integrally attached to the inner surface of the inner fixed rail portion 12 of the fixed rail 11.

Further, as shown in FIG. 9, the sharp tip 37 of the top end of the load-return preventing member 36 protrudes upward from the opening 42 of the support frame 41, and the lower portion 39 of the weight 39 of the load-return preventive member 36. Due to the eccentric weight, the load-return preventing piece 36 always stands upright in the vertical direction, and the loading side edge 38 of the load-return preventing piece 36 comes into contact with the loading edge 43 in the opening 42 of the support frame 41, and the load reverses. The sharp end 37 of the top end of the feeding preventing piece 36 is moved from the vertical state to the outlet 9.
(A counter-clockwise direction), but a reverse-direction tilt preventing means capable of contacting the load reverse-preventing piece 36 so as not to tilt from the vertical state to the carry-in port 8 (clockwise). The height of the top surface of the load transfer rotating wheel is set to be lower than the height of the top of the load-return preventing piece in the standing posture, and With the top end inclined toward the discharge port, it is locked to the bottom surface of the load on the load transfer rotating wheel. Even if the bottom surface of the load 7 undulates, Even if the sharp end 37 of the top end of the reverse feed preventing portion 36 abuts in a nearly vertical state, the tilting of the load reverse preventive portion 36 toward the carry-in port 8 causes the load reverse feed preventive portion 36 to be loaded on the loading side. The contact between the side portion 38 and the carry-in edge 43 ensures the prevention.

Thus, the air pressure control circuit of the air cylinder 33
44 is configured as shown in FIG. That is, in the air pressure control circuit 44, one end of a supply pipe 46 is connected to an air pump or an air pressure source 45 including an air pump and an air tank, and a filter 47 and a pressure reducing valve 48 are interposed in the supply pipe 46. The other end of the port 46 is connected to a port 51 of a 5-port 2-position solenoid-operated switching valve 49, and a port 54 of the 5-port 2-position solenoid-operated switching valve 49 is connected to a discharge-side cylinder chamber 57 of the air cylinder 33 through a supply / exhaust pipe 55. 5 ports 2
The port 53 of the position electromagnetic switching valve 49 is connected to a carry-in side cylinder chamber 58 of the air cylinder 33 via a supply / exhaust pipe 56, and the supply / exhaust pipes 55, 56 are provided with flow control valves 59, 60 with check valves, respectively. Is equipped.

The control computer 61 for controlling the operation of the 5-port 2-position electromagnetic switching valve 49 and the loading / unloading indicating lamps 62 and 63 provided at the loading / unloading port 8 and the loading / unloading port 9 includes a start button 64, Loading load detector 65, loading load detector 66
And a call button 67.

In the control computer 61, when the start button 64 is turned on, the load 7 is carried into the carry-in port 8 and the carry-in load detector 65 is operated in the carry-in operation.
Operates, the 5-port 2-position solenoid-operated directional control valve 49 is operated intermittently four times by a control signal from the control computer 61 after a lapse of a predetermined time of, for example, 3 seconds, and the loads 7 in the shelf booth 5 are loaded all at once. The transfer rail 16 is conveyed toward the carry-out port 9 by the size of the transfer direction 7, and after one cycle, the moving rail 16 is stopped near the carry-in port 8.

Further, when the load 7 is discharged from the discharge port 9 and the discharge side load detector 66 detects that the load 7 does not exist in the discharge port 9, the control is performed after a predetermined time elapses as described above. The control signal from the computer 61 causes the 5-port 2-position solenoid-operated directional control valve 49 to operate intermittently four times, and the loads 7 in the shelf booth 5 to be conveyed all at once to the carry-out port 9 by the size of the loads 7 in the conveying direction. It has become so.

When the call button 67 is further pressed, the load 7
The 5-port 2-position solenoid-operated directional control valve 49 is operated intermittently by the control signal from the control computer 61 until the unloading-side load detector 66 detects that the. The 5-port 2-position electromagnetic switching valve 49 is automatically stopped by the detection signal of 66.

Since the embodiment shown in FIGS. 1 to 10 is configured as described above, when the start button 64 is turned on, the loading-side load detector 65 determines whether or not the load 7 exists at the loading port 8. If the load 7 is detected at the entrance 8, the control computer 61 sends an ON signal to the 5-port 2-position electromagnetic switching valve 49, and the 5-port 2-position electromagnetic switching valve 49 is turned on, thereby turning on 5 in FIG. The port 2 position electromagnetic switching valve 49 is switched upward, the port 51 and the port 54 are connected, and compressed air is supplied to the discharge side cylinder chamber 57.

Since the throttle flow path of the flow control valve 60 with a check valve is restricted, the atmosphere from the carry-in side cylinder chamber 58 to the atmosphere via the supply / exhaust pipe 56, the flow control valve 60 with a check valve, and the ports 53 and 50. The flow rate of the air discharged inside is restricted, the piston rod 34 extends gently toward the carry-out port 9 and a small acceleration acts on the moving rail 16. The wheel 24 does not idle and stops as it is, and the load 7 is transported to the carry-out port 9 together with the moving rail 16 by one stroke of the air cylinder 33.

The time required for the air cylinder 33 to expand and contract by one stroke toward the carry-out port 9 is set to a very short time (pneumatic pressure, time during which variation in the throttle opening of the flow control valve 60 with a check valve can be tolerated). When it is determined by the control computer 61 that the added time has elapsed, the 5-port 2-position electromagnetic switching valve 49 is turned off, and the 5-port 2-position electromagnetic switching valve 49 is switched to the state shown in FIG. Since the throttle in the throttle passage of the flow control valve 59 with a check valve is slight, the air in the discharge side cylinder chamber 57 is supplied to the supply / exhaust pipe 55 and the flow control valve 5 with a check valve.
9, is rapidly discharged into the atmosphere through ports 54 and 52, and the piston rod 34 is suddenly shortened toward the carry-in port 8, and the moving rail
Since a large acceleration acts on the load 16 and the load reverse prevention piece 36 acts, even if the moving rail 16 moves toward the entrance 8, the load 7 is stopped at that position and the piston rod 34 is shortened to the limit. When the carry-in end of the moving rail 16 reaches the carry-in port 8, the control computer 61 again controls the 5-port 2-position electromagnetic switching valve.
49 is turned on.

When the above operation is repeated four times and one cycle is completed, the stroke L of the air cylinder 33 is set to about 1/4 of the dimension of the load 7 in the conveying direction. Can be advanced toward the carry-out port 9 by the size of the load 7 in the carrying direction. The number of repetitions of one cycle may be increased to five or more as necessary.

As described above, when the load 7 is present at the carry-in port 8, the air cylinder 33 operates under the control of the control computer 61, and the load 7 in the shelf booth 5 is transported while moving forward by the dimension in the transport direction. Next, use a forklift or the like to
And the load 7 can be sequentially loaded into the shelf booth 5.

While the air cylinder 33 is operating, the carry-out possible indicator light 63 is not turned on. However, when the operation of the air cylinder 33 is stopped, the carry-out possible indicator light 63 is turned on and the load 7 is discharged from the carry-out port 9. Unloading is possible.

Further, when the call button 67 is pressed in a state where the load 7 is not present in the outlet 9, the air cylinder 33 is repeatedly operated under the control of the control computer 61, and the load 7 is transported to the outlet 9. By the detection signal of the side load detector 66,
The air cylinder 33 is stopped.

Further, in a state where the moving rail 16 is gently moving toward the carry-out port 9 which is the carry-out end direction X, the sharp tip 37 of the top end of the load-return preventing piece 36 is shown by a broken line in FIG. The pallet of the load 7 falls slightly from the posture toward the exit 9
The bottom surface of 68 can be moved integrally with the moving rail 16 toward the outlet 9 without being restrained by the sharp end 37 of the top end of the load reverse-preventing piece 36.

When the moving rail 16 is rapidly moving toward the carry-in port 8, which is the carry-in end direction Y, the top end sharp portion 37 of the load-return preventing piece 36 is kept in the state shown by the broken line, Of the pallet 68, and the load 7 is stopped as it is by the stopping force, and as a result, the load 7 is reliably advanced.

Further, since the moving rail 16 moves slowly in the unloading end direction X so as not to exert a large inertial force on the load 7, the load transfer rotary wheel 24 idles clockwise (see FIG. 7). ) Can be prevented.

Further, the top end sharp portion is added to the load
37, the moving rail 16 is moved in the loading end direction Y.
When moving, the top-end sharp portion 37 bites into the bottom surface of the pallet 68 of the load 7, the load 7 is integrated and fixed with the fixed rail 11 and the support frame 41, and only the moving rail 16 moves in the loading end direction Y. Can be moved.

The arrangement interval of the load reversing prevention piece 36 is
Is set to a size smaller than the front-rear dimension, i.e., the dimension in the transport direction, so that the load reverse-feed preventing piece 36 engages with the load 7 at any position of the moving rail 16 and reverses the load 7. Transmission is reliably prevented.

Further, as shown in FIG.
In the range corresponding to the size of the load 7 in the transport direction, the load reverse rotation preventing piece 36 is not arranged, so that when loading the forklift load 7 (not shown) Even if a large drop impact force is applied to the load 24, the impact force does not act on the load-return preventing piece 36, and the load-return preventing piece 36 is prevented from being damaged.

Further, as shown in FIG. 3, the arrangement intervals of the load-return preventing pieces 36 located closer to the carry-in port 8 are set more densely than the positions closer to the carry-out port 9. The load 7 near the carry-in port 8 where reverse feeding is likely to occur is reliably prevented from being reversed by the load reverse-preventing piece 36, and the load on the load reverse-feed preventing piece 36 near the carry-in port 8 is large. Reduced in width.

The moving rail 16 returns to the carry-in port 8 after one cycle, and stops at that position, so that the load 7 located at the carry-out port 9 is more strongly carried out by the load 7 near the carry-in port 8. Prevented from being pushed in the direction X,
The load 7 located at the carry-out port 9 can be easily carried out without being restricted by the load 7 closer to the carry-in port 8.

In the embodiment shown in FIGS. 1 to 10, the rolling wheel 20 for reciprocating the moving rail 16 lightly with respect to the fixed rail 11 is pivotally supported by the moving rail 16. May be pivotally supported on the fixed rail pieces 12 and 13 of the fixed rail 11.

In the embodiment shown in FIGS. 1 to 10,
A support frame 41 having a channel-like cross section is fixed to the inner surface of the fixed rail portion 12 from a position approaching the carry-out port 9 from the carry-in port 8 by a dimension in the carrying direction of the load 7 to the carry-out port 9, as shown in FIG. Such support frame pieces 70 may be arranged at predetermined intervals, and the load reverse prevention piece 36 may be pivotally supported between the support frame piece 70 and the fixed rail piece 12 via the pivot 40.

As shown in FIG. 12, instead of the load-return preventing piece 36 having the sharp tip 37, the load-return preventing piece is
Instead of forming the top end of the convex portion 71 on the concave-convex arc surface 72 and making the top end sharp portion 37 bite into the pallet 68 of the load 7, the concave-convex circular surface 72 may exert a large frictional force on the pallet 68.

Further, as shown in FIG. 13 and FIG.

The load-return preventing piece 73 includes a metal main body 74 having a top end portion 75 and a lightening portion 76 at an upper portion, a pivot hole 77 and a weight portion 78 thereunder, and a main body 74. Top end of the 75
A rubber curved contact portion 79 protruding upward and curved so as to be removably fitted to the bottom of the pallet 68 of the load 7 when the top of the rubber curved contact portion 79 contacts the bottom surface of the pallet 68 of the load 7. The curved contact portion 79 is deformed so that a large frictional force acts on the pallet 68.

Instead of using metal as the main body 74 of the load-return preventing piece 73, a synthetic resin may be used, and a metal weight may be embedded in the lower part of the main body 74.

In this embodiment, since no local sharp force acts on the pallet 68 of the load 7, the pallet 68 is hardly damaged.

Also, the back-up preventing piece 73 is replaced with the one shown in FIGS.
As shown in the figure, a rubber curved contact portion 79 may be baked on the top end portion 75 of the lightening portion 76 to be completely integrated.

As further shown in FIGS. 17 and 18,
An auxiliary rotating wheel 69 is rotatably mounted on the inside of the support frame 41 at the same height as the load transferring rotating wheel 24 from the carry-out port 9 over a range longer than the stroke L of the air cylinder 33.

Further, an intermediate rail 80 is disposed at the center of the pair of fixed rails 11 in the width direction from the carry-in port 8 to the carry-out port 9 in parallel with the fixed rail 11, and is supported over the entire length of the intermediate rail 80. The support rollers 81 may be pivotally mounted at equal intervals so that the top surface of the roller 81 is slightly lower than the top surface of the load transfer rotating wheel 24. With such a configuration, the load 7 is large and large. When the center of the pallet 68 in the width direction is deformed downward, a part of the weight of the load 7 is supported by the intermediate rail 80 and the support roller 81, and the pallet 68 is appropriately adapted to the fixed rail 11, the moving rail 16 and the load transfer rotating wheel 24. A large load can be applied.

Further, the support frame is located near the carry-out port 9.
In 41, the auxiliary rotating wheel 69 is pivotally supported at the same height as the load transferring rotary wheel 24 within a range wider than the stroke L of the moving rail 16, so that the load 7 is transported by the auxiliary rotating wheel 69 at the carry-out port 9. It is supported stably irrespective of the reciprocation of the moving rail 16.

[Brief description of the drawings]

FIG. 1 is a side view illustrating an embodiment of a fluidizing shelf according to the present invention.

FIG. 2 is a front view of a fluidized shelf viewed from a carry-out port.

FIG. 3 is a plan view of FIG. 1;

FIG. 4 is an enlarged plan view of a main part of FIG. 3;

FIG. 5 is a transverse sectional view cut along the line VV of FIG. 3;

FIG. 6 is a transverse sectional view taken along the line VI-VI of FIG. 4;

FIG. 7 is a view taken along line VII-VII of FIG. 6;

FIG. 8 is an enlarged side view of a main part of FIG. 1;

9 is a view as viewed in the direction of arrows XX in FIG.

FIG. 10 is a control diagram of a fluidized shelf.

FIG. 11 is a perspective view of a main part of another embodiment in which a pivot portion of a connecting member is changed.

FIG. 12 is a side view of another support frame piece.

FIG. 13 is a side view of still another concave-convex arc surface.

FIG. 14 is an exploded perspective view of the concavo-convex arc surface shown in FIG.

FIG. 15 is a side view of another load-return preventing piece;

FIG. 16 is a longitudinal sectional view cut along the line XVI-XVI of FIG. 15;

FIG. 17 is a plan view of another embodiment of the fluidized shelf.

18 is a view taken in the direction of arrows XVIII-XVIII in FIG. 17;

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Flow shelf, 2 ... Column, 3 ... Side beam, 4 ... Brace, 5
... shelf booth, 6 ... rail device, 7 ... load, 8 ... carry-in, 9 ...
Loading port, 10 ... Stopper, 11 ... Fixed rail, 12, 13 ... Fixed rail part, 14 ... Bolt, 15 ... Opening, 16 ... Movable rail,
17 ... Hole, 18 ... Shaft, 19 ... Bearing, 20 ... Rolling wheel, 21 ... Shaft, 22 ...
Sleeve, 23: Ball bearing, 24: Rotating wheel for load transfer, 25: Bolt nut, 26: Mounting plate, 27: Gusset plate, 28: Bolt nut, 29: Connecting rod, 30: Mounting plate, 31: Bolt nut, 32 ... Cylinder support member, 33 ... Air cylinder, 34 ...
Piston rod, 35… Connecting member, 36… Load reverse prevention piece, 37…
Sharp end of top end, 38: loading side edge, 39: lower part of weight, 40: pivot, 41: support frame, 42: opening, 43: loading edge, 44: air pressure control circuit, 45: air pressure source, 46 ... supply Tube, 47… filter,
48 ... pressure reducing valve, 49 ... 5 port 2 position solenoid switching valve, 50, 51,
52, 53, 54 ... ports, 55, 56 ... supply and exhaust pipes, 57 ... carry-out side cylinder chamber, 58 ... carry-in side cylinder chamber, 59, 60 ... flow control valve with check valve, 61 ... control computer, 62 ... carry-in Allowable indicator light, 63: Unloadable indicator light, 64: Start button, 65: Load-side load detector, 66: Load-side load detector, 67: Call button,
68… Pallet, 69… Auxiliary rotating wheel, 70… Support frame piece, 71… Load reverse prevention piece, 72… Concave and convex arc surface, 73… Load reverse feed piece,
74 ... body, 75 ... top end, 76 ... lightening, 77 ... pivot hole, 78
… Weight part, 79… rubber curved contact part, 80… middle rail, 81
... support rollers.

Claims (11)

(57) [Claims] At least one pair of long fixed rails extending in the front-rear horizontal direction parallel to each other at predetermined intervals on the left and right sides, and supported by the fixed rails so as to be able to reciprocate back and forth. A pair of left and right moving rails, and a plurality of load transfer members that protrude upward from the fixed rails at a predetermined interval in the longitudinal direction of the moving rails and are rotatably supported on the upper part of the moving rails. A rotating wheel, and the pair of left and right moving rails are integrally connected to each other with a connecting rod, and reciprocating driving means for reciprocating the connecting rod back and forth is provided; at least one side of the fixed rail, a plurality of load reverse feed preventing piece by the lower eccentric weight Nigyakuoku prevention piece is, the fixed Les
Over the longitudinal direction of the tool, the top of the load-return preventing piece can tilt from the vertical- standing posture toward the carry-out port, but cannot tilt in the reverse direction from the vertical- standing posture. Reverse tilting prevention that can abut the load reverse feed prevention piece
Means are provided such that the top of the back-up prevention piece is directed upward.
Is formed have protruding uneven curved shape, the height of the top surface of the load-conveying rotary ring is set slightly lower than the top end of the load backhaul preventing piece of the vertical upright position,該荷reverse A flow shelf, wherein a top end of a transport prevention piece is locked to a bottom surface of a load on the load transfer rotating wheel in a state where the top end is inclined toward a carry-out port. 2. A top portion of the back-up preventing piece is rich in elasticity.
2. The fluidizing shelf according to claim 1, wherein the fluidizing shelf is made of a flexible material. 3. The front and rear sides are parallel to each other at a predetermined interval on the left and right.
At least one pair of right and left
Long fixed rail and reciprocable to move back and forth on the fixed rail
A pair of left and right moving rails supported by
Above the fixed rail at a predetermined interval in the longitudinal direction
And is rotatably supported on the upper part of the moving rail.
A plurality of rotating wheels for transferring the load,
The moving rails are integrally connected to each other by connecting rods, and
Reciprocating means for reciprocating the connecting rod back and forth is provided,
On at least one side of the fixed rail, the lower part of the back
Due to the eccentric weight, a plurality of load-return preventing pieces are
The robot is pivotally supported in a vertical standing posture over the length of the
The top of the feed prevention piece is tilted from the vertical
Can move, but cannot tilt in the opposite direction from the vertical standing position
A reverse tilt preventing hand that can abut against the load reverse feed prevention piece
A step is provided, and the top of the back-up prevention piece is rigid.
And the height of the top surface of the load transfer rotary wheel is
It is lower than the height of the top end of the load-return preventing piece in the upright posture.
Is set, and the top end of the back-up preventing piece is
Locks to the bottom of the load on the load transfer wheel in an inclined state
A fluidized shelf characterized by being made . 4. A multiple rollable rolling element on the tread surface of the fixed rail.
Several rolling wheels are fixed along the longitudinal direction of the moving rail.
Being rotatably supported by the moving rail at an interval
The fluidized shelf according to any one of claims 1 to 3, characterized in that: 5. The fixed rail according to claim 5 , wherein a plurality of rolling wheels are provided on the fixed rail.
Can be freely rotated on the fixed rail at a predetermined interval in the hand direction
And the moving rail is supported by the rolling wheels.
4. The apparatus according to claim 1, wherein the apparatus can be moved from the apparatus.
Fluid shelf according to any of the above . 6. The fluidizing shelf according to claim 1, wherein an interval between the back-feed preventing portions is set to be smaller than a dimension of the load in the front-rear direction. 7. The fluidizing shelf according to claim 3, wherein the back-feed preventing piece is not located within a range corresponding to the front-rear dimension of the load from the carry-in end of the fluidizing shelf. Arrangement interval wherein said positioned at inlet port toward the reverse feed preventing unit pieces, claims 1 to 3 any or claims, characterized in that it is densely set than other positions
6. The fluidized shelf according to 6 . 9. The stroke of the reciprocating drive means when the auxiliary rotating wheel faces from the carry-out port to the carry-in port while the top surface of the auxiliary rotating wheel is located at substantially the same height as the top surface of the load transfer rotating wheel. 4. The fluidized shelves according to claim 1 , wherein a plurality of fluidized shelves are arranged within a range corresponding to the above . Wherein said returning rest position of the moving rail, characterized in that set in the entrance side claims 1 to
Item 4. A fluidized shelf according to Item 3 . 11. A moving speed of moving from the entrance of the moving rail to the unloading opening is claimed, characterized in that set slower than the moving speed of moving from the carry-out port to the inlet port
The fluidized shelf according to any one of claims 1 to 3 .