JP5583798B2 - Reciprocating slider crank press device - Google Patents

Description

  In the present invention, a heated molding material is sandwiched between a molding fixed mold and a molding movable mold and press molded, and then the molding material is pressed and held by the molding fixed mold and molding movable mold. The present invention relates to a reciprocating slider crank press apparatus that performs shape freezing to be cooled while being in a state.

Conventionally, when a molding material made of steel or thermoplastic resin is press-molded into a predetermined molding shape, in order to improve the moldability of the molding material while reducing the pressing force necessary for this press molding, the molding material is used. In some cases, the material is pre-heated and then press-molded (this process is also referred to as “hot pressing” in this specification). Here, after hot-pressing the molding material at a predetermined press pressure, the molding material is cooled while being kept in a pressurized state at a press pressure larger than the press pressure of the hot press (in this specification, this process is performed). (Also referred to as “shape freezing”).
Patent Document 1 describes a hydraulic press apparatus that uses a hydraulic cylinder to perform hot pressing and shape freezing.

Japanese Patent No. 4551144

By the way, in the conventional hydraulic press apparatus used for performing hot press and shape freezing, both a pressing force for performing hot pressing and a pressing force for performing shape freezing are generated by a hydraulic cylinder. For this reason, in the conventional hydraulic press apparatus, it is necessary to supply and discharge a relatively large amount of pressure oil to and from the hydraulic cylinder in both the hot press and the shape freezing process. There is a problem that the energy consumption of the hydraulic press device increases due to the discharge.
The present invention was devised as a solution to the above-described problem, and this shape is generated by generating a pressing force by a hydraulic cylinder different from a pressing force source for performing hot pressing to freeze the shape. This eliminates the need to supply and discharge a large amount of pressure oil to and from the hydraulic cylinder during freezing, thereby reducing the energy consumption of the press device in the shape freezing.

In the present invention, after a heated molding material is press-molded with a pair of a molding fixed mold and a molding movable mold, a press pressure larger than the press pressure in this press molding is applied to the molding fixed mold and the molding movable. It is a reciprocating slider crank press device that performs shape freezing to cool a molding material while realizing a pressure holding state that is a state applied to the molding material by a set of dies. This reciprocating slider crank press device is a reciprocating slider crank that realizes press molding of a molding material by driving the slider in which a molding movable die is set against a molding fixed mold in which the molding material is set. mechanism and, mounted between the molding movable die and the slider, and a hydraulic cylinder for adjusting the press pressure for molding material by pressure oil filled inside, this slider the slider in order to perform the above-described shape fixability A servomechanism that stops at a position where it is not pushed out for a predetermined time; and a hydraulic control device that supplies and discharges the pressure oil so as to keep the molding material in the pressure holding state while the slider is stopped. It has. Here, the extrusion position where the movable mold is positioned when the slider is no longer pushed out is formed more than the press molding completion position where the movable mold is positioned when the press molding is completed. It is set at a position close to the fixed mold. Further, the reciprocating slider crank mechanism, after realizing the press molding of the molding material, pushes the molding movable mold from the press molding completion position toward the extrusion position, thereby causing the pressure oil in the hydraulic cylinder to be predetermined. The pressure is increased to the hydraulic pressure value, and the molding material is brought into the pressure holding state. Further, the hydraulic control device determines the hydraulic pressure of the pressure oil in the hydraulic cylinder boosted by the reciprocating slider crank mechanism, and supplies or discharges the pressure oil depending on whether the hydraulic pressure is insufficient or excessive with respect to the predetermined hydraulic pressure value. By performing the above, the molding material is configured to be in the above-described pressure holding state.
According to the present invention, the slider driven by the reciprocating slider crank mechanism in press molding is stopped by the servo mechanism, and the hydraulic control device supplies and discharges the pressure oil to and from the hydraulic cylinder attached to the slider. The shape can be frozen by holding the molding material under pressure. Here, the hydraulic cylinder adjusts the pressing pressure on the molding material, and can pressurize and compress the internal pressure oil by being sandwiched between the molding movable mold and the slider. . For this reason, the said hydraulic cylinder can be formed smaller than the hydraulic cylinder which implement | achieves press molding, and can reduce supply amount and discharge | emission amount of pressure oil. This eliminates the need to supply and discharge a relatively large amount of pressure oil to the hydraulic cylinder when the shape of the molding material is frozen, and can reduce the energy consumed in the shape freezing compared to the conventional hydraulic press device. It becomes.

It is a longitudinal section showing the principal part of the reciprocating slider crank press device concerning one embodiment of the present invention. It is the elements on larger scale of FIG. It is a conceptual diagram showing the hydraulic control apparatus in the reciprocating slider crank press apparatus of FIG. It is a motion curve showing the vertical movement of the shaping | molding movable metal mold | die of FIG. It is the elements on larger scale of FIG.

Below, the structure of the reciprocating slider crank press apparatus 10 concerning one Embodiment of this invention is demonstrated using FIG. 1 thru | or FIG. In the following, regarding the incidental configuration in the present invention, such as a specific mold structure for realizing the drawing process on the fixed mold and the movable mold, and a cooling water circulation system used for freezing the shape, etc. The illustration and detailed description thereof will be omitted.
As shown in FIG. 1, the reciprocating slider crank press apparatus 10 uses a steel sheet heated in advance to a predetermined heating temperature (for example, 1000 [° C.]) as a molding material 90 and presses the molding material 90 to the reciprocating slider crank mechanism 13. This is a reciprocating slider crank press device that manufactures a molded product (not shown) that has been subjected to drawing by hot pressing with pressure and then freezing the shape. Here, the molding material 90 is set on the molding fixed mold 11 attached to the frame main body 10A of the reciprocating slider crank press device 10 via the bolster 11A.

The reciprocating slider crank mechanism 13 is configured to vertically move a slider 13D attached to the crank 13A via a connecting rod 13B and a connecting pin 13C by the rotation of the crank 13A that is pivotally supported by the frame body 10A. . Here, the slider 13D is moved up and down along a predetermined path along the slider guide 13F by being guided by a slider guide 13F fixed to the frame body 10A.
The reciprocating slider crank mechanism 13 is provided with a servo mechanism 14 that can control the vertical movement of the slider 13D by controlling the rotation of the crank 13A of the reciprocating slider crank mechanism 13. The servo mechanism 14 detects the rotational position of the crank 13A by a rotary position detector 14C attached to the crank 13A of the reciprocating slider crank mechanism 13, processes the detection result by the control computer 14D, and controls the control computer 14D. Thus, the servo motor 14A for rotating the crank 13A is controlled. A gear speed reducer 14B that allows the rotational speed of the servo motor 14A to be reduced and transmitted to the crank 13A is attached between the crank 13A and the servo motor 14A.

The movable mold 12 is set on the slider 13D of the reciprocating slider crank mechanism 13 via a hydraulic piston mechanism 20 having a hydraulic cylinder 22. The molding movable mold 12 is driven so as to be pressed from above with respect to the molding fixed mold 11 on which the molding material 90 is set by the vertical movement of the slider 13D, thereby realizing a hot press of the molding material 90. It is configured to let you.
The molding movable mold 12 is integrated with a slide member 12A guided by a slide guide 10B formed on the frame main body 10A. Thereby, in the hot press of the molding material 90, the position shift of the molding movable mold 12 with respect to the molding fixed mold 11 can be suppressed.

The hydraulic piston mechanism 20 is attached to the slider 13D by screwing a male screw portion 23A formed on the mounting rod 23 into a female screw portion 13E formed on the slider 13D. The hydraulic piston mechanism 20 includes a worm shaft 20B attached so as not to rotate with respect to the frame body 10A, and a worm gear 20A integrally attached to the attachment rod 23 and meshed with the worm shaft 20B. Yes.
Then, the hydraulic piston mechanism 20 rotates the worm shaft 20B with a predetermined handle (not shown), and transmits this rotation as the rotation of the worm gear 20A and the mounting rod 23, whereby the male screw portion 23A of the mounting rod 23 is transmitted. The screwing depth of the slider 13D with respect to the female screw portion 13E can be adjusted. As a result, the vertical position of the movable mold 12 relative to the slider 13D can be easily adjusted.

As shown in FIG. 2, a hydraulic piston 21 formed in a plate shape is fitted into the hydraulic cylinder 22 of the hydraulic piston mechanism 20 without a gap, so that a hydraulic chamber 22 </ b> A is formed inside. The hydraulic chamber 22A is filled with the pressure oil 80 through the pressure oil port port 22B provided in the lower portion thereof. The hydraulic piston 21 is provided with a plurality of (for example, three) piston rings 21 </ b> A that suppress the leakage of the pressure oil 80 from between the hydraulic piston 21 and the hydraulic cylinder 22.
Then, the hydraulic cylinder 22 has its hydraulic chamber 22A sandwiched between the molding movable mold 12 and the mounting rod 23 and slightly compressed (see the phantom line in FIG. 2), thereby boosting the pressure oil 80 inside. Be able to.

Here, the mounting rod 23 of the hydraulic piston mechanism 20 generates a force that compresses and contracts the hydraulic chamber 22A by pressing the hydraulic piston 21 with the surface of the pressing portion 23B without being fixed to the hydraulic piston 21. It is like that. By not fixing the mounting rod 23 to the hydraulic piston 21, the rotation of the mounting rod 23 when adjusting the screwing depth of the mounting rod 23 with respect to the slider 13 </ b> D becomes difficult to be transmitted to the hydraulic piston 21 and the hydraulic cylinder 22.
Note that the pressing portion 23 </ b> B of the mounting rod 23 is formed to have a larger diameter than other portions of the mounting rod 23. The pressing portion 23B is covered with a cover member 24 fastened to the hydraulic cylinder 22 by a plurality of mounting bolts 24A. As shown by a solid line in FIG. 2, the cover member 24 functions as a pressing member that presses the pressing portion 23 </ b> B so that the mounting rod 23 and the hydraulic piston 21 do not come off the hydraulic cylinder 22.

As shown in FIG. 3, a hydraulic control device 30 that supplies and discharges the pressure oil 80 to and from the hydraulic chamber 22 </ b> A of the hydraulic cylinder 22 is connected to the pressure oil port port 22 </ b> B of the hydraulic cylinder 22. The hydraulic control device 30 includes a control valve 31 for releasing the pressure oil 80 filled in the hydraulic chamber 22A of the hydraulic cylinder 22 to the oil discharge port 30B, and a pressure oil for supplying the pressure oil 80 to the hydraulic chamber 22A. A supply means 32 and a conduit 30C that connects the pressure oil supply means 32 and the control valve 31 to the hydraulic chamber 22A are provided.
The pressure oil supply means 32 can adjust the discharge pressure when supplying the pressure oil 80 in a stepless manner in accordance with a command from the pressure oil supply control circuit 32A connected to the pressure oil supply means 32. It is configured. Note that a swash plate type axial piston pump K3VG63-13FRS-1EH4 manufactured by Kawasaki Heavy Industries, Ltd. is used for the pressure oil supply means 32 of the present embodiment.

The control valve 31 has an electromagnetic actuator attached to a spring safety valve. This spring safety valve is temporarily opened when a hydraulic pressure exceeding a predetermined value (hereinafter also referred to as “first hydraulic pressure value”) is applied through the pipe line 30C, and the hydraulic oil in the hydraulic chamber 22A and the pipe line 30C. 80 is allowed to escape to the oil discharge port 30B, and the hydraulic pressure in the hydraulic chamber 22A and the pipe line 30C is set to be equal to or lower than the first hydraulic pressure value. The electromagnetic actuator is configured to be operated by a control valve control circuit 31A connected to the control valve 31 so that the spring safety valve can be forcibly opened. When the operation of the electromagnetic actuator is stopped, the spring safety valve is automatically closed by the elastic force of the built-in spring.
A check valve 30A for preventing the pressure oil 80 from flowing back from the hydraulic chamber 22A to the pressure oil supply means 32 is provided in the pipe line 30C. In the pipe line 30C, a pressure sensor 31B that measures the hydraulic pressure in the pipe line 30C and outputs it to the control valve control circuit 31A is connected between the check valve 30A and the hydraulic chamber 22A.

The control valve control circuit 31A includes a hydraulic cylinder while the hydraulic pressure output from the pressure sensor 31B (hereinafter also referred to as “output hydraulic pressure”) exceeds a predetermined threshold (hereinafter also referred to as “second hydraulic pressure value”). 22, it is determined that the hydraulic pressure in the hydraulic chamber 22 </ b> A (hereinafter also referred to as “hydraulic chamber hydraulic pressure”) is excessive, and the electromagnetic actuator of the control valve 31 is operated to forcibly open the control valve 31. It has become. Thereby, the hydraulic pressure in the hydraulic chamber 22A and the pipe line 30C can be made equal to or lower than the second hydraulic pressure value.
The second hydraulic pressure value is stored as data in a storage medium (not shown) attached to the control valve control circuit 31A. This data can be rewritten by the control computer 14D of the servo mechanism 14 (see FIG. 1). Thereby, the control computer 14D can change the upper limit of the hydraulic pressure in the hydraulic chamber 22A and the pipe line 30C within the range equal to or less than the first hydraulic pressure value described above in accordance with the output of the rotary position detector 14C.

Further, the control valve control circuit 31A has insufficient hydraulic chamber hydraulic pressure of the hydraulic cylinder 22 while the output hydraulic pressure is below a predetermined value (hereinafter also referred to as “third hydraulic pressure value”) that is lower than the second hydraulic pressure value. It judges that it has carried out, and outputs a command signal and the above-mentioned output oil pressure to pressure oil supply control circuit 32A. Upon receiving the output of the control valve control circuit 31A, the pressure oil supply control circuit 32A has a discharge pressure slightly higher than the output oil pressure (eg, 1.1 [times] to 1.2 [times] the output oil pressure. ] Is driven to supply the pressure oil 80 to the pipe line 30C and the hydraulic chamber 22A. Thereby, the hydraulic pressure in the hydraulic chamber 22A and the pipe line 30C can be made equal to or higher than the third hydraulic pressure value.
Here, the third hydraulic pressure value is stored as data different from the second hydraulic pressure value in a storage medium (not shown) attached to the control valve control circuit 31A. This data can be rewritten by the control computer 14D of the servo mechanism 14 (see FIG. 1). As a result, the control computer 14D can prevent the discharge pressure of the pressure oil supply means 32 determined by the third hydraulic pressure value from exceeding the second hydraulic pressure value.

The operation of the reciprocating slider crank press apparatus 10 when performing hot pressing and shape freezing of the molding material 90 will be described mainly with reference to FIGS. 4 and 5. In the following description, detailed explanations of operations incidental to the present invention such as setting of the molding material 90 are omitted.
When the molding material 90 is set on the molding fixed mold 11, as shown in FIG. 4, the molding movable mold 12 is brought into a retracted position H 1 that cannot be pulled any further by the crank 13 A of the reciprocating slider crank mechanism 13. Has been stopped.

The hydraulic chamber 22A of the hydraulic cylinder 22 and the pipe line 30C of the hydraulic control device 30 are filled with the pressure oil 80 with a predetermined hydraulic pressure (hereinafter also referred to as “initial hydraulic pressure”). Thereby, the hydraulic chamber 22A of the hydraulic cylinder 22 is in an extended state as shown by a solid line in FIG.
Here, the magnitude of the initial hydraulic pressure and the second hydraulic pressure value and the third hydraulic pressure value stored in the storage medium attached to the control valve control circuit 31A described above are “the hydraulic cylinder 22 necessary for freezing the shape”. It is set in advance so that the relationship of “pressing pressure” = “second hydraulic value”> “initial hydraulic pressure” ≧ “third hydraulic value”> “pressing pressure of the hydraulic cylinder 22 necessary for hot pressing” is established. Yes. The magnitude of the initial hydraulic pressure is stored as data in a storage medium (not shown) of the control computer 14D.

When the molding material 90 is set on the molding fixed mold 11, the servo mechanism 14 pushes down the crank 13A of the reciprocating slider crank mechanism 13 by the servo motor 14A, and further pushes down the slider 13D depending on the crank 13A. Rotate towards the bottom dead center where you can't. As the crank 13A rotates, the reciprocating slider crank mechanism 13 drives the slider 13D and the movable mold 12 to be pressed against the lower fixed mold 11.
Then, the reciprocating slider crank mechanism 13 performs a press drawing process by hot pressing on the molding material 90 sandwiched between the molding movable mold 12 and the molding fixed mold 11. This press drawing process corresponds to “press molding” in the present invention. The press drawing process is performed while the movable mold 12 is pushed down to the press forming completion position H2 shown in FIGS.

Incidentally, as shown in FIGS. 4 and 5, the crank 13A of the reciprocating slider crank mechanism 13 is still at the bottom dead center position described above immediately after the molding movable mold 12 is pushed down to the press molding completion position H2. Not reached. Further, the crank 13A continues to rotate toward the bottom dead center position even after the press drawing process is completed, and further presses the molding movable mold 12 from the press molding completion position H2, and the phantom line in FIG. It tries to move to the extrusion position H4 with a motion curve as shown.
At this time, the molding movable mold 12 is brought into contact with the molding material 90 and the molding fixed mold 11, and the downward movement is regulated by the molding material 90 and the molding fixed mold 11. For this reason, the actual motion curve of the molding movable mold 12 has a shape as shown by a solid line in FIG. 5, and the actual extrusion position H3 of the molding movable mold 12 is higher than the above-described virtual extrusion position H4. Located in.

The displacement between the push-out position H3 and the push-out position H4 (hereinafter also referred to as “ΔH”) is caused by the hydraulic chamber 22A of the hydraulic cylinder 22, the force by which the crank 13A pushes down the slider 13D, and the molding material 90 against this force. It is absorbed by being compressed by the same length as ΔH by the reaction force of the molding fixed mold 11 (see the phantom line in FIG. 2). As a result, the hydraulic cylinder 22 raises the pressure oil 80 in the hydraulic chamber 22A to the above-described second hydraulic pressure value, and the press pressure applied to the molding material 90 is the press pressure necessary for freezing the shape of the molding material 90. (Hereinafter, also referred to as “shape freezing pressure”).
It should be noted that the relationship between ΔH and the amount of increase in the press pressure is a known parameter such as the shape of the hydraulic chamber 22A and the conduit 30C of the hydraulic cylinder 22 and the volume elastic coefficient, thermal expansion coefficient, and temperature of the pressure oil 80. Is determined by Accordingly, by appropriately specifying the shape of each component of the reciprocating slider crank press device 10 and the type of the molding material 90 and the pressure oil 80, the molding movable when the molding movable mold 12 is pushed down to the extrusion position H3. It is possible to set the pressing pressure of the mold 12 to be equal to the shape freezing pressure.

When the rotational position of the crank 13A input from the rotary position detector 14C reaches the bottom dead center position described above, the control computer 14D of the servo mechanism 14 pushes the molding movable mold 12 down to the extrusion position H3. The crank 13A is stopped at the bottom dead center position, and the slider 13D is stopped. At the same time, the control computer 14D operates a cooling water circulation system (not shown) of the reciprocating slider crank press device 10.
As a result, the molding material 90 is sandwiched between the molding movable mold 12 pushed down to the extrusion position H3 and the molding fixed mold 11, and is held in a pressurized state with the above-described shape freezing pressure. The shape is frozen by being cooled by the cooling water circulation system. The time required for freezing the shape varies depending on the type of the molding material 90, but is, for example, several [seconds] to 10 [seconds], and is stored as data in advance in a storage medium (not shown) of the control computer 14D. .

Here, the control computer 14D sets the third hydraulic pressure value stored in the storage medium attached to the control valve control circuit 31A to be slightly smaller than the second hydraulic pressure value when the shape freezing of the molding material 90 starts. The value is rewritten to a small value (for example, the value of the output oil pressure when the discharge pressure of the pressure oil supply means 32 determined by the output oil pressure of the pressure sensor 31B is equal to the second oil pressure value).
Thereby, the hydraulic control device 30 supplies and discharges the pressure oil 80 so that the molding material 90 is pressurized and held at the shape freezing pressure described above. The supply and discharge of the pressure oil 80 is continued until the control computer 14D determines that the shape freezing of the molding material 90 has been completed.

The supply and discharge of the pressure oil 80 will be described more specifically. For example, when the hydraulic chamber hydraulic pressure of the hydraulic cylinder 22 is insufficient due to leakage of the pressure oil 80, the press pressure applied to the molding material 90 becomes lower than the shape freezing pressure. In this case, the control valve control circuit 31A determines that the hydraulic chamber hydraulic pressure is insufficient by using the third hydraulic pressure value as a threshold value, and the hydraulic oil supply means 32 of the hydraulic control device 30 supplies the hydraulic oil 80 to the hydraulic cylinder 22. Done. Then, by supplying the pressure oil 80, the hydraulic chamber hydraulic pressure is increased, and the molding material 90 is brought into a pressure holding state at the shape freezing pressure.
Further, when the thickness of the molding material 90 is thicker than expected and the hydraulic chamber 22A of the hydraulic cylinder 22 is compressed more than expected, the hydraulic chamber hydraulic pressure of the hydraulic cylinder 22 becomes excessive, and the molding material 90 The press pressure applied to is higher than the shape freezing pressure. In this case, the control valve control circuit 31 </ b> A determines that the hydraulic chamber hydraulic pressure is excessive, using the second hydraulic pressure value as a threshold value, and pressure oil 80 by the control valve 31 of the hydraulic control device 30 with respect to the hydraulic cylinder 22. Is discharged. Then, by discharging the pressure oil 80, the hydraulic chamber hydraulic pressure is decreased, and the molding material 90 is brought into a pressure holding state at the shape freezing pressure.

According to the operation of the reciprocating slider crank press device 10 described above, the slider 13D driven by the reciprocating slider crank mechanism 13 is stopped by the control computer 14D of the servo mechanism 14 in the press drawing process described above. Then, the hydraulic pressure control device 30 supplies and discharges the pressure oil 80 to and from the hydraulic cylinder 22 attached to the slider 13D, so that the molding material 90 is kept in a pressurized state and the shape is frozen.
Here, the hydraulic cylinder 22 is for adjusting the pressing pressure on the molding material 90, and can be further pressurized by the internal pressure oil 80 by being compressed between the molding movable mold 12 and the slider 13D. It can be done. For this reason, the hydraulic cylinder 22 can be made smaller than the conventional hydraulic cylinder for realizing press molding, and the supply amount and discharge amount of the pressure oil 80 can be reduced. As a result, it is not necessary to supply and discharge a relatively large amount of pressure oil 80 to the hydraulic cylinder 22 when the shape of the molding material 90 is frozen, and energy consumption in the shape freezing is less than that of the conventional hydraulic press device. It becomes possible.

The control computer 14D determines the timing at which the shape freezing of the molding material 90 is completed from the data on the time required for the shape freezing stored in the storage device (not shown) and the elapsed time from the start of the shape freezing to the current time. to decide. Then, the control computer 14D drives the servo motor 14A in accordance with the above timing and restarts the rotation of the crank 13A of the reciprocating slider crank mechanism 13 (see FIG. 4). Thereby, the shaping | molding movable metal mold | die 12 is pulled up toward the drawing position H1 shown in FIG.
The rotation of the crank 13A is restarted from the state where the crank 13A is positioned at the above-described bottom dead center position, and the crank 13A reaches the top dead center position where the slider 13D cannot be lifted any further by the crank 13A. Can continue. Here, when the operation of stopping the crank 13A at the bottom dead center position and restarting the rotation of the crank 13A from this bottom dead center position is adopted, the slider 13D, the hydraulic piston mechanism 20 and the molding are instantly restarted. There is no need to move the movable mold 12 up and down. For this reason, the driving force of the servo motor 14A required when restarting the rotation of the crank 13A is reduced, and the servo motor 14A can be downsized.

Further, the control computer 14D sets the second hydraulic pressure value stored in the storage medium attached to the control valve control circuit 31A to the initial value stored in the storage medium of the control computer 14D in accordance with the restart of the rotation of the crank 13A. Rewrite to the same value as hydraulic pressure. At the same time, the control computer 14D sets the third hydraulic pressure value stored in the storage medium attached to the control valve control circuit 31A to a value slightly smaller than the initial hydraulic pressure (for example, the pressure determined by the output hydraulic pressure of the pressure sensor 31B). The value of the output hydraulic pressure when the discharge pressure of the oil supply means 32 is equal to the initial hydraulic pressure is rewritten.
Then, as the second hydraulic pressure value and the third hydraulic pressure value are rewritten, the hydraulic control device 30 causes the control valve 31 to discharge the pressure oil 80 from the hydraulic chamber 22A of the hydraulic cylinder 22. For this reason, the press pressure applied to the molding material 90 by the hydraulic piston mechanism 20 is unloaded almost simultaneously with the resumption of the rotation of the crank 13A. Thereby, immediately after resuming the rotation of the crank 13A, the influence of the reaction of the press pressure that the reciprocating slider crank mechanism 13 receives from the hydraulic piston mechanism 20 is reduced.

As shown in FIG. 4, when the rotational position of the crank 13A input from the rotary position detector 14C reaches the above-described top dead center position, the control computer 14D stops the crank 13A at this top dead center position. Thus, the slider 13D, the movable mold 12 and the hydraulic piston mechanism 20 are stopped. At this time, the molding material 90 set on the molding die 11 has already been completed as a molded product (not shown) that has been subjected to press drawing and shape freezing by hot pressing. For this reason, in the reciprocating slider crank press device 10, when the crank 13A is stopped at the top dead center position, the molded product is taken out, and the next molding material 90 is hot-pressed and frozen in shape. Preparations are made.
In the series of operations of the reciprocating slider crank press device 10 described above, the hydraulic pressure in the hydraulic chamber 22A and the conduit 30C of the hydraulic cylinder 22 does not exceed the first hydraulic pressure value that opens the spring safety valve of the control valve 31 described above. To be controlled. For this reason, while the series of operations are normally performed, the control valve 31 is opened and closed only by the control of the control valve control circuit 31A. The spring safety valve of the control valve 31 has an abnormally high pressure where the hydraulic pressure of the hydraulic oil 80 in the hydraulic chamber 22A and the pipe line 30C exceeds the first hydraulic pressure value due to some failure in the reciprocating slider crank press device 10. When it becomes, it functions as a safety valve for releasing the pressure oil 80 to the oil discharge port 30B.

The present invention is not limited to the appearance and configuration described in the above-described embodiment, and various modifications, additions, and deletions can be made without changing the gist of the present invention. For example, the following various forms can be implemented.
(1) The molding material on which hot pressing and shape freezing are performed is not limited to a steel plate, and can be changed to any molding material on which hot pressing and shape freezing steps are performed, such as a thermoplastic resin.
(2) Specific setting conditions in hot pressing and shape freezing are not limited to those described above. That is, for example, when performing hot pressing and shape freezing using a thermoplastic resin as a molding material, the time for shape freezing is increased to about 30 [seconds], and specific setting conditions for hot pressing or shape freezing are appropriately changed. be able to.

DESCRIPTION OF SYMBOLS 10 Reciprocating slider crank press apparatus 10A Frame main body 10B Slide guide 11 Molding fixed metal mold 11A Bolster 12 Molding movable metal mold 12A Slide part 13 Reciprocating slider crank mechanism 13A Crank 13B Connecting rod 13C Connecting pin 13D Slider 13E Female thread part 13F Slider guide 14 Servo mechanism 14A Servo motor 14B Gear speed reducer 14C Rotary position detector 14D Control computer 20 Hydraulic piston mechanism 20A Worm gear 20B Worm shaft 21 Hydraulic piston 21A Piston ring 22 Hydraulic cylinder 22A Hydraulic chamber 22B Pressure oil port 23 Mounting rod 23A Male Screw part 23B Press part 24 Cover member 24A Mounting bolt 30 Hydraulic control device 30A Check valve 30B Oil discharge port 30C Pipe line 31 Control valve 31A Valve control circuit 31B pressure sensor 32 the pressure oil supply means 32A pressurized oil supply control circuit 80 pressurized oil 90 molding material H1 retracted position H2 press molding completion position H3 extrusion position H4 extrusion position

Claims (1)

After the heated molding material is sandwiched between a pair of a fixed mold and a movable mold, press pressure greater than the press pressure in the press molding is applied to the fixed mold and the movable mold. A reciprocating slider crank press device that performs shape freezing to cool the molding material while realizing a pressure holding state that is a state of being applied to the molding material by a set,
A reciprocating slider crank mechanism that realizes the press molding of the molding material by driving the slider in which the molding movable mold is set against the molding fixed mold in which the molding material is set;
A hydraulic cylinder that is attached between the movable mold and the slider, and adjusts a pressing pressure on the molding material by pressure oil filled therein;
A servomechanism for stopping the slider for a predetermined period of time at a position where the slider is not pushed out further to perform the shape freezing;
A hydraulic control device for supplying and discharging the pressure oil so as to bring the molding material into the pressurized holding state while the slider is stopped;
Equipped with a,
The extrusion position where the movable mold is positioned when the slider is no longer extruded is more than the press completion position where the movable mold is positioned when the press molding is completed. It is set near the fixed mold,
The reciprocating slider crank mechanism, after realizing the press molding of the molding material, pushes the molding movable mold from the press molding completion position toward the extrusion position, thereby causing the pressure oil in the hydraulic cylinder to flow. Increase the pressure to a predetermined hydraulic pressure value to achieve the pressurization holding state of the molding material,
The hydraulic pressure control device determines a hydraulic pressure of the pressure oil in the hydraulic cylinder boosted by the reciprocating slider crank mechanism, and supplies the pressure oil according to whether the hydraulic pressure is insufficient or excessive with respect to the predetermined hydraulic pressure value. It is configured to bring the molding material into the pressurized holding state by performing discharge .
Reciprocating slider crank press device.

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