JP2007296544A - Flask conveying apparatus - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a flask conveying apparatus which is constituted of a simple mechanism and with which the molding flask or the flask to be carried can smoothly and quickly be carried. <P>SOLUTION: In the flask conveying apparatus in which the flask group is shifted by every pitch interval for the portion of one flask by holding the flask group arranged in a tandem manner between a push-out device and a cushion device, the above push-out device is provided with: a crank-arm; a movement changing device which changes a rotating movement by the crank arm into a straight advancing movement in a conveying direction; and a pushing member which pushes the last end of the flask group by the straight advancing movement in the conveying direction changed by the movement changing device. Further, the cushion device is provided with a cushion member which abuts on the most front part in the flask group at the rear end part, and a braking device which is arranged so as to face the most front part of the cushion member, and gradually generates braking force for stopping the straight advancing movement of the cushion member at the decelerated speed time of the straight advancing movement of the pushing member. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to an apparatus for conveying a casting frame or a mold in a casting line.

  2. Description of the Related Art Conventionally, in a casting line, a plurality of carts are arranged in series and conveyed in order to continuously convey a casting frame and a mold. However, if there is a gap between the carts arranged, the carts collide with each other when transporting the casting frame (mold), and an impact is generated. In order to adversely affect it, it was necessary to transport it with as little impact as possible. Therefore, for example, a device disclosed in Patent Document 1 is known as an apparatus for transporting a group of carts arranged in series without eliminating such a gap between the respective casting frames and giving an impact during transportation. Yes. As shown in FIG. 1 of Patent Document 1, the hydraulic pusher cylinder 1 is provided with a proportional control valve 32 controlled by a controller 31 so as to be capable of high speed, medium speed, and low speed control. 2 is provided with a second electromagnetic valve 34 that can be controlled via the first electromagnetic valve 33 and switches the back pressure in the contraction direction of the rod 12, and decelerates the formwork group 3 during high-speed conveyance by switching the back pressure. It is the conveyance device made into the hydraulic piping. As described above, by adopting a two-pressure control system in which the proportional control valve 32 is used for the control on the hydraulic pusher cylinder 1 side and the electromagnetic solenoid valves 33 and 34 for deceleration are used for the control on the hydraulic cushion cylinder 2 side, It conveys without impact and at high speed.

In addition, what is shown by patent document 2 is known. As shown in FIG. 1 of Patent Document 2, this is installed at one end of the transport rail 1 to push out a plurality of mold transport carts 2 groups, and is installed at the other end of the transport rail 1 and pushed out. Both the cushion cylinders 16 for reducing the moving speed of the two groups of mold transportation carts are of the electric servo type. As described above, the extrusion cylinder 15 and the cushion cylinder 16 are of the electric servo type, so that the cast frame (mold) can be smoothly conveyed without being affected by the temperature change due to the season.
Japanese Patent No. 3680997 (7th page, FIG. 1) Utility registration No. 2559334 (6th page, FIG. 1)

  However, since both the pusher cylinder and the cushion cylinder according to Patent Document 1 are hydraulic, large equipment such as a flow control valve, a hydraulic unit, and hydraulic piping is required. The viscosity of the hydraulic oil used to operate these cylinders decreases when the temperature is high, and increases when the temperature is low, so there is a problem that the feed time by the cylinder changes and the cycle time of the casting frame conveying process varies. there were. In addition, the hydraulic piping used as equipment takes time to maintain oil leakage prevention.

  In addition, the electric servo-type extrusion cylinder and cushion cylinder according to Patent Document 2 can finely set the cylinder operating speed and operating distance, and the cylinder positioning at the start and end points of the transfer work can be performed with high accuracy. it can. However, both the extrusion cylinder and the cushion cylinder were provided with servo motors, requiring special control to synchronize the mutual relations, and the adjustment was troublesome. In addition, precise equipment was required, and the equipment cost was high.

  SUMMARY OF THE INVENTION The present invention has been made in view of the conventional problems, and provides a casting frame conveying apparatus that is configured with a simple mechanism and that can smoothly and quickly convey a conveyed casting frame and mold. Is.

  In order to solve the above-mentioned problem, the structural feature of the invention according to claim 1 is that a group of cast frames arranged in series is sandwiched between an extrusion device and a cushion device, and the group of cast frames is divided into one cast frame. In the cast frame conveying apparatus that moves the pitch interval, the extruding device includes a crank arm, a motion converting device that converts a rotational motion by the crank arm into a linear motion in the conveying direction, and a transport converted by the motion converting device. A push member that pushes a rearmost end of the cast frame group by a linear movement in a direction, and the cushion device includes a cushion member that comes into contact with the foremost end of the cast frame group at a rear end, and the cushion member Braking that is provided opposite to the front end and gradually generates a braking force that stops the rectilinear movement of the cushion member when the push member linearly decelerates. Having a device.

The structural feature of the invention according to claim 2 is that, in claim 1, the braking device is configured such that when a pressure higher than a predetermined level is generated, the oil discharge adjusting means for discharging oil to the outside is fixed by the oil discharge adjusting means. A hydraulic cylinder that generates back pressure and a crank mechanism that converts a rectilinear motion of the cushion member into a rotational motion, wherein the force around the rotation axis of the crank mechanism based on the back pressure of the hydraulic cylinder is used as a rectilinear motion of the cushion member. And a crank mechanism that gradually generates a braking force for stopping the rotational motion by converting the torque into a rotational torque for braking and gradually increasing the rotational torque.

  According to a third aspect of the present invention, the brake device according to the second aspect of the present invention is the pneumatic cylinder according to the second aspect, wherein the brake device returns the cushion member to an initial state before abutting against the cast frame group, and the pneumatic cylinder has an air pressure. A pneumatic pressure-hydraulic converter that converts the air pressure into hydraulic pressure when supplying the hydraulic pressure, and returns the hydraulic cylinder to the initial state by the hydraulic pressure.

  According to a fourth aspect of the present invention, in the first aspect, the brake device includes a brake hydraulic cylinder that works in opposition to the rectilinear movement of the cushion member, and the brake hydraulic cylinder has a hydraulic pressure as the brake force. And a hydraulic control device that gradually generates.

  In the extrusion device according to the first aspect of the present invention, the rotational movement of the crank arm is converted into the straight movement of the push member, and the crank arm swings at the start point and the end point at a substantially horizontal position. When the speed component is small and transported at a low speed, and the crank arm passes the dead center (top dead center or bottom dead center), using the motility that the speed component in the transport direction is large and the transport becomes high speed, Extrude the frame group in the conveying direction.

  In the cushion device, in the process of receiving the linear motion of the steel frame group with a small braking force that does not cause an overload on the extrusion device side at high speed conveyance and decelerating, the braking force is gradually generated, and the steel frame group Since the linear movement is stopped without generating a gap between them, a braking action that smoothly follows the movement of the push member of the extrusion device can be realized.

  By these extruding device and cushioning device, it is possible to realize an ideal conveyance in which low-speed conveyance is started at the start of conveyance, high-speed conveyance in the middle of conveyance, and low-speed conveyance again at the end of conveyance.

  According to the invention according to claim 2, on the one hand, the crank mechanism converts the linear movement of the cushion member into a rotational movement, and on the other hand, converts a constant back pressure based on the hydraulic cylinder into a force around the axis of the crank mechanism, The force around this axis is converted into rotational torque that gradually increases as a braking force by the crank mechanism. Then, the rotational motion based on the rectilinear motion of the cushion member is stopped by the gradually increasing rotational torque. With such a simple mechanism without complicated control, it is possible to follow the feed movement based on the crank arm of the extrusion device and to stop the cast frame group quickly and smoothly.

  According to the invention of claim 3, since the air pressure supplied for the pneumatic cylinder is also converted into the hydraulic pressure, the cushion member can be returned to the initial state only by supplying the pneumatic pressure to the pneumatic cylinder, and the hydraulic cylinder is initialized. It can be returned to the state.

  According to the fourth aspect of the present invention, the braking hydraulic cylinder is controlled by the hydraulic control device, and the braking force can be generated following the feed movement of the frame group based on the crank arm of the extrusion device. The cast frame group can be stopped quickly and smoothly by the apparatus.

  Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a front view showing an outline of a casting frame conveying apparatus in the present embodiment, and FIG. 2 is a front view of an extrusion apparatus.

  The cast frame conveying device 2 includes an extruding device 6 that extrudes the cast frame groups 4 arranged in series in the conveying direction, and a cushion device 8 that stops the movement of the cast frame group 4 extruded by the extruding device 6 in the conveying direction. It consists of. The cast frames of the cast frame group 4 are placed on a transport carriage 7 having wheels that roll. A conveying path 9 is formed between the extrusion device 6 and the cushion device 8 to move the cast frame group 4 in the conveying direction. The starting point side (left side in FIG. 1) and the ending point side (right side in FIG. 1) of the conveying path 9 are formed. Each is provided with a traverser 11 for moving the transport carriage 7 (cast frame) in a direction perpendicular to the transport path 9.

  As shown in FIG. 2, the pushing device 6 is provided with a crank arm 14 on which the rotating shaft 12 is supported on the upper inner wall of the frame 10, and the crank arm 14 is opposite from the substantially horizontal position of the starting point through the bottom dead center. It is configured to rotate on the arc to a substantially horizontal position at the end point on the side. The rotating shaft 12 of the crank arm 14 is connected to a drive device (motor) 16 having an inverter function capable of changing an output frequency via a reduction gear (not shown). A roller 18 having a rotation axis parallel to the rotation shaft 12 is provided at the tip of the crank arm 14, and the roller 18 can freely roll to a pair of roller guides 20 that face the horizontal direction and extend in the vertical direction. Is inserted. The lower part of the roller guide 20 is slidably fitted into a stroke guide 22 extending in the conveying direction, and the stroke guide 22 is fixed to the frame 10 at the front end and the rear end. The roller guide 22 slides in the transport direction with respect to the stroke guide 22 and constitutes a slider crank mechanism that converts the rotational movement of the crank arm 14 into a straight movement in the transport direction. A rear end portion of a cylindrical push member 24 provided in parallel to the stroke guide 22 is assembled to the upper portion of the stroke guide 22 so as not to be relatively movable, and an intermediate portion of the push member 24 is slidably supported on the frame 10. Has been. A cushioning material 26 that abuts against the rearmost end of the cast frame group 4 is attached to the front end of the push member 24.

  As shown in FIG. 4, the cushion device 8 includes a columnar cushion member 28 that comes into contact with the fore end of the cast frame group 4 at the rear end. The cushion member 28 is supported by the frame 30 so as to be slidable in the conveying direction at the intermediate portion, and a cushioning material 32 that contacts the foremost end of the cast frame group 4 is attached to the rear end portion of the cushion member 28. . A cushioning portion 34 extending vertically is provided at the front end portion of the cushion member 28, and a roller of a rocking arm, which will be described later, is in contact with the cushioning portion 34 so as to roll up and down. Below the cushion member 28, a guide member 36 is provided side by side. The guide member 36 extends in the transport direction, and its front end and rear end are fixed to the frame 30. The cushion member 28 is slidably guided by the guide member 36 at the slide portion 29 at the lower front end thereof. A return member 38 protruding upward is provided on the front side of the guide member 36 so as to be slidable in the conveying direction, and a front end portion of a roller of a swing arm to be described later is in contact with the rear surface of the return member 38. . On the lower side surface of the return member 38, a base end of a connecting rod 40 that extends rearward in the transport direction (left side in FIG. 4) is fixed. The connecting rod 40 is slidably fitted in an engaging hole of an engaging portion 42 provided on the slide portion 29 of the cushion member 28, and a stopper 44 for preventing the connecting rod 40 is provided at the tip of the connecting rod 40. ing. When the cushion member 28 moves forward (right side in FIG. 4) by the connecting rod 40, the engaging portion 42 of the cushion member 28 slides on the side surface of the connecting rod 40 without resistance, and the cushion member 28 moves rearward (see FIG. When moving to the left side in FIG. 4, the tip of the connecting rod 44 is locked by the stopper 44 and the return member 38 is interlocked to move backward. In addition, an air cylinder 45 as a pneumatic cylinder is provided in parallel with the cushion member 28, and the air cylinder 45 is moved relative to the rear end portion of the cushion member 28 via the connecting member 41. Linked impossible. A cylinder portion 49 of the air cylinder 45 is fixed to the frame 30.

  The swing arm 46 is formed in a substantially L-shape, and a rotating shaft 48 extending in a direction perpendicular to the conveying direction is provided in the upper portion of the swing arm 46 so as not to be relatively rotatable. The rotary shaft 48 is rotatably supported by the frame 30 so that the swing arm 46 can rotate within a plane including the transport direction. A roller 50 having an axis parallel to the rotation shaft 48 is provided below the swing arm 46, and the roller 50 is configured to be able to contact the front end portion of the cushion member 28 and the rear surface of the return member 38. . A pin portion 43 is provided at the lower end portion of the swing arm 46, and the front end of the piston portion 54 of the hydraulic cylinder 52 is pivotally supported on the pin portion 43. The rear end of the cylinder portion 56 of the hydraulic cylinder 52 is pivotally supported by the support wall 51 on the inner wall of the frame 30. The tip of the piston part of the balancer 60 is connected to the cylinder part 56 via a connecting member 58 protruding downward. The front end of the cylinder portion of the balancer 60 is pivotally supported by the frame 30 so as to be rotatable. The balancer 60 prevents the hydraulic cylinder 52 from rotating due to its own weight. The swing mechanism 46, the roller 50, and the hydraulic cylinder 52 constitute a crank mechanism 62 as a braking device that stops the linear movement of the cushion member 28.

  Next, the hydraulic / pneumatic circuit of the cushion device 8 will be described below. An oil distribution pipe 70 is joined to the front end portion of the cylinder portion 56 of the hydraulic cylinder 52 so as to retract the piston portion 54 when oil is pressurized and flows in, and a relief valve 72 as oil discharge adjusting means is connected to the oil distribution pipe 70. Are connected. A constant back pressure is generated in the hydraulic cylinder 52 by the relief valve 72. The relief valve 72 is provided with a cut valve 74 in parallel, and the relief valve 72 and the cut valve 74 are connected to the hydraulic side of a pneumatic hydraulic tank 78 as a pneumatic-hydraulic converter via the valve 76.

  An air distribution pipe 80 is joined to the front end portion of the air cylinder 45 so that when the air is pressurized and flows in, the piston portion 47 extends, and the air distribution pipe 80 is connected to the electromagnetic valve 84 via the variable throttle 82. . The electromagnetic valve 84 communicates with the pneumatic pump 86 and communicates with the outside air, and a silencer 88 is provided at the exhaust port to the outside air. The air distribution pipe 80 is provided in parallel with an air distribution pipe 90 that communicates with the air pressure side of the pneumatic hydraulic tank 78 via a variable throttle 82. The air distribution pipe 92 is joined to the rear end portion of the cylinder portion 49 of the air cylinder 45 so that the piston portion 47 retracts when air flows in. The air distribution tube 92 is connected to the electromagnetic valve 84 via the variable throttle 82. ing. The solenoid valve 84 is switched between a neutral position where the air distribution pipe 80 and the air distribution pipe 92 communicate with the outside air and an operation position where the air distribution pipe 80 or the air distribution pipe 92 communicates with the pneumatic pump 86.

  Next, the operation of the casting frame conveying apparatus 2 having the above configuration will be described with reference to the drawings.

  First, as shown in FIG. 6, the push member 24 of the extrusion device 6 abuts the rearmost end of the cast frame group 4 arranged in series, and the front end of the cast frame group 4 is the cushion member of the cushion device 8. 28 is in contact, and the cast frame group 4 is sandwiched from the front and rear. At this time, the electromagnetic valve 48 is positioned at the neutral position, and the cut valve 74 is positioned at the closed position.

  Next, the driving device 16 is driven to rotate the crank arm 14 from the rear (leftward in FIG. 6) to the front (rightward in FIG. 6) with respect to the transport direction. As a result, the rotational movement of the crank arm 14 is converted into a straight movement through the roller 18 and the roller guide 20 and transmitted to the push member 24, and the cast frame group 4 is moved forward in the conveying direction by the push member 24 (rightward in FIG. 6). Extruded. By the straight movement of the cast frame group 4, the cushion member 28 of the cushion device 8 is retracted and moved forward.

  Here, the rotational motion of the crank arm 14 of the extrusion device 6 is converted as a linear motion in the transport direction with the following characteristics. First, since the crank arm 14 is in a substantially horizontal position and its vicinity at the beginning of the rotation when the conveyance is started and the velocity component in the conveyance direction is small, the steel frame group 4 is moved (conveyed) at a low speed. Since the crank arm 14 is at or near the bottom dead center and the speed component in the transport direction increases, the cast frame group 4 moves (transports) at a high speed, and the crank arm 14 is substantially horizontal again at the end of the transport. Since the speed component in the transport direction is small at the position and in the vicinity thereof, it is moved (conveyed) at a slow speed.

  On the other hand, in the cushion device 8, the cushion member 28 moves forward (rightward in FIG. 6) in response to the rectilinear movement of the cast frame group 4 from the start of conveyance of the cast frame group 4 to the middle of the conveyance. There is nothing in contact with the front end, and no braking force is generated. As shown in FIG. 7, after the middle part of the transport in which the push member 24 is decelerated, the buffer portion 34 at the front end of the cushion member 24 abuts on the roller 50 of the swing arm 46, and the swing arm 46 is moved. It is converted into a rotating motion that rotates. On the other hand, a hydraulic cylinder 52 is connected to the swing arm 46 at a pin portion 43, and the hydraulic cylinder 52 generates a certain back pressure by a relief valve 72. The back pressure of the hydraulic cylinder 52 is converted into a force around the rotating shaft 48 of the swing arm 46, and a rotational torque as a braking force is generated in the swing arm 46 by the force around the rotating shaft 48. . The rotational movement of the swing arm 46 is braked by this rotational torque.

  First, when the buffer portion 34 of the cushion member 24 contacts the roller 50, the rotation shaft 48 and the pin portion 43 of the swing arm 46 and the support portion 51 of the hydraulic cylinder 52 are configured to be substantially in a straight line. Therefore, the rotational torque as the braking force is almost zero. For this reason, even if the push member 24 abuts on the roller 50, there is almost no impact, and the push member 24 is not overloaded. Further, when the buffer portion 34 pushes the roller 50, the swing arm 46 rotates forward in the conveying direction, and between the straight line connecting the rotary shaft 48 and the pin portion 43 and the straight line connecting the pin portion 43 and the support portion 51. As a result, an angle is generated to generate a rotational torque as a braking force. The rotational torque as the braking force gradually increases as the angle increases.

  Next, at the end of the conveyance, as shown in FIG. 8, the roller 50 is further pushed by the buffer portion 34 and the swing arm 46 rotates, but the rotational torque as a braking force is generated between the rotating shaft 48 and the pin. When the angle between the straight line connecting the portion 43 and the straight line connecting the pin portion 43 and the support portion 51 is 90 degrees, the maximum value is obtained. In the present embodiment, the steel frame is formed at a position where the angle is approximately 90 degrees. The movement of the group 4 in the transport direction is stopped.

  As described above, in the cushion device 8, the push frame 24 is not subjected to an overload by receiving the straight movement of the cast frame group 4 with a small braking force that does not cause an impact in the middle of the transported medium. Then, in the process in which the push member 24 and the frame group 4 are decelerated (during deceleration), the braking force is gradually generated, and the linear movement of the frame group 4 without generating a gap between the frame groups 4. Stop. Therefore, it is possible to realize a braking action that smoothly follows the straight motion of the cast frame group 4 based on the rotational motion of the crank arm 14 of the extrusion device 6 without giving an impact to the transported cast frame group 4 as much as possible. Further, by the extrusion device 6 and the cushion device 8, the ideal steel frame group 4 is configured to perform low-speed conveyance at the start of conveyance of the cast frame group 4, high-speed conveyance in the middle of conveyance, and low-speed conveyance at the end of conveyance. The conveyance can be realized.

  Next, by switching the electromagnetic valve 84 (to the left in FIG. 4), the air from the air pump 86 is supplied to the rear part of the cylinder part 49 of the air cylinder 45, and the piston part 47 is retracted to further move the cushion member 28. It is moved forward (to the right in FIG. 8) and a gap is provided between the foremost end of the cast frame group 4. Then, the traverser 11 is operated to move the transport carriage 7 in a direction perpendicular to the transport direction (not shown).

  Next, the solenoid valve 84 is switched (to the right in FIG. 4), and air is supplied to the front portion of the cylinder portion 49 of the air cylinder 45 via the air distribution pipe 80. By extending the piston portion 47 of the air cylinder 45 in this manner, the cushion member 28 is moved rearward in the conveying direction, and the cushion member 28 is returned to the state before contacting the next cast frame group 4 (initial state). . At this time, the return member 38 is moved backward (leftward in FIGS. 4 and 8) via the connecting rod 40. At this time, since the rear surface of the return member 38 moves while pressing the front end portion of the roller 50, the swing arm 46 rotates backward to return to the initial state before the buffer portion 34 of the cushion member 28 contacts. . At the same time, air is supplied as pressure to the pneumatic hydraulic tank 78 through the air distribution pipe 90, and the pressure is converted into hydraulic pressure and flows into the front end portion of the cylinder portion 56 of the hydraulic cylinder 52, and the piston portion 54 is retracted and shaken. The moving arm 46 is rotated rearward, and oil is caused to flow into the cylinder portion 56 of the hydraulic cylinder 52 to return the hydraulic cylinder 52 to the initial oil storage amount. At this time, the cut valve 74 in the middle of the oil distribution pipe 70 is switched to the open position. Thus, since the air pressure supplied for the air cylinder 45 is also converted into oil pressure, the cushion member 28 can be returned to the initial state only by supplying the air pressure to the air cylinder 45 by the air pressure pump 86. At the same time, the hydraulic cylinder can be returned to the initial state.

  In this embodiment, the cast frame is transported by a transport cart with wheels. However, the present invention is not limited to this. For example, the cast frame may be transported by roller.

  Moreover, although the drive device 16 of the extrusion device 6 is a motor, it is not limited to this. For example, a rotary actuator using pneumatic pressure or hydraulic pressure may be used.

  In the present embodiment, the push arm 6 has the crank arm 14 passing through the bottom dead center in the middle of the transport of the cast frame group 4. However, the present invention is not limited to this. It may be passed through top dead center.

  Next, another embodiment of the cushion device will be described with reference to the drawings. As shown in FIG. 9, the cushion device 102 is provided with a buffer material 106 at the rear end portion of the piston portion 104, and an electromagnetic proportional relief valve 112 and a pneumatic / hydraulic tank 114 controlled by the CPU 110 at the front end portion of the cylinder portion 108. An oil distribution pipe 116 communicating with the pipe is joined. The electromagnetic proportional relief valve 112 is provided with a cut valve 113 in parallel. An air distribution pipe 122 communicating with the pneumatic pump 120 via an electromagnetic valve 118 is joined to the rear end portion of the cylinder portion 108. The piston portion 104 and the cylinder portion 108 constitute a brake hydraulic cylinder, and the electromagnetic proportional relief valve 112 and the CPU 110 constitute a control device.

  According to this cushion device 102, the electromagnetic proportional relief valve 112 is controlled by the CPU 110 so as to gradually increase the back pressure from the cylinder portion 108, so that the frame group 4 can be moved quickly and smoothly by following the movement of the extrusion device. Can be transported. In addition, the movement of the cast frame group 4 can be easily stopped by a simple device instead of such a complicated mechanism. Other operations are the same as those in the previous embodiment, and will be omitted.

The front view which shows the outline | summary of the cast-frame conveying apparatus which concerns on this invention. The front view of an extrusion apparatus. The top view of the extrusion apparatus. The front view of a cushion apparatus. The top view of the cushion apparatus. The figure which shows the action | operation of a cast-frame conveyance apparatus. The figure which shows the action | operation of a cast-frame conveyance apparatus. The figure which shows the action | operation of a cast-frame conveyance apparatus. The front view of the cushion device of other embodiments.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 2 ... Cast-frame conveying apparatus, 4 ... Cast-frame group, 6 ... Extruding apparatus, 8 ... Cushion apparatus, 24 ... Push member, 28 ... Cushion member, 49 ... Pneumatic cylinder (air cylinder), 46 ... Braking device, crank mechanism ( Oscillating arm), 50 ... braking device / crank mechanism (roller), 52 ... braking device (hydraulic cylinder), 62 ... crank mechanism, 72 ... oil discharge adjusting means (relief valve), 78 ... pneumatic hydraulic tank, 102 ... cushion DESCRIPTION OF SYMBOLS 104 ... Brake hydraulic cylinder (piston part), 108 ... Brake hydraulic cylinder (cylinder part), 110 ... Control apparatus (CPU), 112 ... Control apparatus (electromagnetic proportional relief valve).

Claims (4)

In a casting frame conveying apparatus that sandwiches a group of cast frames arranged in series by an extrusion device and a cushion device, and moves the casting frame group by a pitch interval of one casting frame,
The extrusion device includes a crank arm,
A motion conversion device that converts rotational motion by the crank arm into linear motion in the transport direction;
A push member that pushes the rearmost end of the cast frame group by a straight movement in the transport direction converted by the motion conversion device,
The cushion device is a cushion member that comes into contact with a foremost end of the cast frame group at a rear end portion;
A braking device that is provided facing the front end of the cushion member, and that gradually generates a braking force that stops the rectilinear motion of the cushion member during deceleration of the rectilinear motion of the push member;
A casting frame conveying apparatus characterized by comprising: The brake device according to claim 1,
An oil discharge adjusting means for discharging oil to the outside when a pressure exceeding a predetermined level is generated;
A hydraulic cylinder in which a constant back pressure is generated by the oil discharge adjusting means;
A crank mechanism that converts a rectilinear motion of the cushion member into a rotational motion, wherein the force around the rotation axis of the crank mechanism based on the back pressure of the hydraulic cylinder is converted into a rotational torque for braking the rectilinear motion of the cushion member. A crank mechanism for converting and gradually generating a braking force to stop the rotational motion by gradually increasing the rotational torque;
A cast frame conveying apparatus comprising: In Claim 2, the braking device comprises:
A pneumatic cylinder for returning the cushion member to an initial state before coming into contact with the casting frame group;
A pneumatic-hydraulic converter that converts the pneumatic pressure to hydraulic pressure when supplying the pneumatic pressure to the pneumatic cylinder, and returns the hydraulic cylinder to the initial state by the hydraulic pressure;
A cast frame conveying apparatus comprising: The brake device according to claim 1, wherein the braking device includes a braking hydraulic cylinder that works in opposition to a rectilinear movement of the cushion member
A hydraulic control device that gradually generates hydraulic pressure as the braking force in the brake hydraulic cylinder;
A cast frame conveying apparatus comprising:

Images