JP5008077B2 - Loader / Unloader for press machine - Google Patents

Description

  The present invention relates to a loader / unloader for a press apparatus for carrying a molding material into a press apparatus for laminating a molded article such as a laminated article or carrying out a molded article laminated and molded by the press apparatus.

  Such a loader / unloader is disclosed in Patent Document 1, for example. Patent Document 1 is a loader / unloader for a multistage press apparatus for feeding a feed plate loaded with a material to be pressed to a hot plate of a multistage press apparatus or a press position on the press plate, in the width direction of the feed plate. A plurality of pairs of support arms that are parallel to each other for supporting the both end portions of the multi-stage press and mounting the feed plate are provided vertically corresponding to the arrangement interval of the hot plate or the press plate of the multistage press device. A feed plate supporting device, at least a floating position for raising the feed plate mounted on the support arm by a predetermined distance from each corresponding hot plate or press plate of the multi-stage press device, and each corresponding hot plate or Elevating means for raising and lowering the feed plate support device between a release position for placing on the press plate and separating from the support arm, and a feed plate mounted on the support arm for the multi-stage press The feed plate between a forward position that is positioned at the press position between the hot plate or the press plate and a retracted position that positions the feed plate at a retracted position that is out of the space between the hot plate or the press plates of the multistage press device. Advancing / retreating means for moving the support device back and forth in the extending direction of the support arm, a floating position detecting means for detecting that the feed plate support device has reached the floating position, and the feed plate support device at the separation position Detachment position detection means for detecting that it has reached, forward position detection means for detecting that the feed plate support device has reached the forward position, and detection that the feed plate support device has reached the reverse position Based on the detection results of the reverse position detection means, the floating position detection means, the separation position detection means, the forward position detection means, and the reverse position detection means, the elevation means and the advance / retreat means The feed plate mounted on the support arm of the feed plate support device is floated from the hot plate or press plate to the corresponding press position of the hot plate or press plate of the multistage press device. While feeding and placing, the feed plate placed at the press position of the hot plate or press plate was mounted on the support arm of the feed plate support device and floated from the hot plate or press plate The present invention relates to a loader / unloader for a multistage press apparatus including drive control means for taking out from the multistage press apparatus in a state. And the raising / lowering means in patent document 1 drives a ball screw screwed to the ball screw nut fixed to the arm with an electric motor, and raises / lowers the arm.

  However, according to the loader / unloader described in Patent Document 1, since a ball screw or the like is used as the lifting means, the cost is increased and a problem may occur at a high load. Also, since the arm has a cantilever structure, when the weight of the material to be pressed is relatively heavy or the shape of the material to be pressed is relatively large, the tip of the arm bends and hangs down, and it is safe for a narrow gap between the hot plates. In such a case, the arm cannot be entered or the tip of the arm comes into contact with the surface of the hot plate during transportation, causing damage to the hot plate.

Japanese Patent Publication No.7-115240

  The present invention has been made to solve the above-described problems, and provides a loader / unloader configured to withstand a high load and to compensate for the influence of the arm even if it bends. With the goal.

  The present invention is a loader / unloader for a press device that carries a molding material into a press device and unloads a molded product molded from the molding material by the press device, the outer frame being erected, and the outer frame A first shaft that is horizontally supported at the inner lower portion, a second shaft that is horizontally supported at the inner upper portion of the outer frame, and one or both of the first shaft and the second shaft are rotationally driven. Driving means, two inner frames swingably attached to the first shaft and the second shaft via an eccentric cam, and a plurality of arms fixed horizontally to respective opposing surfaces of the inner frame The present invention relates to a loader / unloader for a press device.

  According to the loader / unloader for a press device of the present invention, it is possible to withstand a high load, and even if the arm is bent, the influence can be compensated.

  Embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a front view showing a loader / unloader of the present invention. FIG. 2 is a cross-sectional view taken along the line H-H in FIG. 3 is a cross-sectional view taken along the arrow showing the arm ascending in FIG. 4 is an enlarged partial cross-sectional view of a portion J in FIG. 1 which is a connecting portion between the eccentric cam of the first shaft and the inner frame. FIG. 5 is an explanatory diagram showing a state of the eccentric portion of the second shaft when the arm is lowered and when the arm is raised.

  The press device 19 shown in FIGS. 2 and 3 is a pressure clamping device (not shown) in which a plurality of heat plates 13 arranged at equal intervals between the movable platen 14 and a fixed plate (not shown) are connected to the lower surface of the movable platen 14. Then, the molding material 12 on the carrier plate 11 placed between the hot plates 13 is heated and compressed by stacking and molding the molding material 12 into a molded product. Is.

  The loader / unloader 20 includes a base 10 fixed to an upper surface of a gantry (not shown) that moves in the loading / unloading direction of the molding material 12 or a molded product, and a gate-shaped outer frame 2 that is erected and fixed to the base 10. A first shaft 5 that is horizontally supported at the lower portion of the inner facing surface of the outer frame 2, a second shaft 6 that is horizontally supported at the upper portion of the inner facing surface of the outer frame 2, and a first shaft 5 And a drive means 7 comprising a brake motor and a speed reducer fixed on the base 10, and a first shaft 5 and a second shaft 6 which are swingably attached via eccentric cams 8 and 9. The inner frame 3 and a plurality of U-shaped vertical cross-sectional shapes that are fixed in a cantilevered manner and horizontally engaged with the carrier plate 11 corresponding to the gaps between the hot plates 13 on the opposing surfaces of the inner frame 3. It consists of an arm 4.

  The loader / unloader 20 carries the molding material 12 between the open hot plates 13 of the press device 19 in a state where the arm 4 engaged with the carrier plate 11 on which the molding material 12 is placed is lifted, and the arm 4 is loaded. After lowering and disposing the carrier plate 11 on the upper surface of the hot plate 13, the arm 4 is separated from the carrier plate 11, and the molding material 12 is laminated between the closed hot plates 13 to form a molded product. The plate 13 is opened to allow the arm 4 to enter the lower surface of the engaging portion of the carrier plate 11, and the arm 4 is raised and engaged with the carrier plate 11 to carry out the molded product together with the carrier plate 11.

  As shown in FIG. 4, the first shaft 5 is horizontally supported by a pillow block 18 at the lower part of the opposing surface of the outer frame 2, and is not movable in the axial direction and can be rotated smoothly. An eccentric cam 8 is fixed to both ends of the first shaft 5 in the vicinity of the surface facing the outer frame 2 by a key 25 so as not to rotate. The eccentric cam 8 includes a through hole 23 into which the first shaft 5 is inserted, and an eccentric portion 21 having an axis at a position displaced by an eccentric amount A from the axis of the through hole 23. A bearing 15 is fitted into the eccentric portion 21, and an outer ring of the bearing 15 is fitted into a lower one of the two through holes 24 drilled at both ends of the inner frame 3. Both surfaces of the inner frame 3 and the outer ring of the bearing 15 are sandwiched between mounting plates 16 and 17, and the inner frame 3 is a surface parallel to the facing surface of the outer frame 2 based on the rotation of the first shaft 5. The single shaft 5 is swingable so as not to move in the axial direction.

  Although the illustration is omitted because it is the same as FIG. 4, the second shaft 6 is pivotally supported horizontally by a pillow block 18 on the upper surface of the outer frame 2 so that it cannot move in the axial direction and can rotate smoothly. ing. An eccentric cam 9 is fixed to both ends of the second shaft 6 in the vicinity of the surface facing the outer frame 2 by a key 25 so as not to rotate. The eccentric cam 9 includes a through hole 23 into which the second shaft 6 is inserted, and an eccentric portion 22 having an axis at a position displaced by an eccentric amount B from the axis of the through hole 23. A bearing 15 is inserted into the eccentric portion 22, and an outer ring of the bearing 15 is inserted into the upper one of the two through holes 24 drilled at both ends of the inner frame 3. The both surfaces of the inner frame 3 and the outer ring of the bearing 15 are sandwiched between mounting plates 16 and 17. Therefore, the eccentric cam 9 is driven based on the swing of the inner frame 3, and the inner frame 3 swings in a direction parallel to the opposing surface of the outer frame 2 so that it cannot move in the axial direction of the second shaft 6. It is possible.

The first shaft 5 and the second shaft 6 are provided on the opposing surfaces of the outer frame 2 so as to be pivotally supported at the lower portion and the upper portion with an inter-axis distance D therebetween. On the other hand, the shaft centers of the through holes 24 and 24 of the inner frame 3, that is, the shaft centers of the eccentric parts 21 and 22 are provided at both ends of the inner frame 3 with an inter-axis distance C therebetween. The inter-axis distance C is set to be larger than the inter-axis distance D by the difference E of the inter-axis distance. Therefore, as shown in FIGS. 2 and 5, when the direction of the eccentric amount A of the first shaft 5 is vertically downward and the inner frame 3, that is, the arm 4 is at the lowest position, the second shaft 6 is eccentric. The direction of the amount B is a right angle rotation of the rotation angle F in the direction opposite to the protruding direction of the arm 4 from the vertical line position. At this time, the axis of the second shaft 6 is separated from the axis of the eccentric portion 22 by a distance X in the horizontal direction. The distance X is a value obtained by subtracting the difference E of the inter-axis distance from the eccentric amount A, and the distance separated in the vertical direction between the axis of the second shaft 6 and the axis of the eccentric portion 22; Thus, the square root of {B ² − (AE) ² } is obtained. In addition, in order to position the axial center of the eccentric part 21 and the eccentric part 22 on the same perpendicular line and to make the inner frame 3 vertical and the arm 4 horizontal when the arm 4 is lowered, the outer frame of the second shaft 6 The horizontal support position to 2 is separated from the support position of the first shaft 5 to the outer frame 2 by a distance X in the direction opposite to the protruding direction of the arm 4.

From this state, in FIG. 2, when the first shaft 5 is driven 180 degrees clockwise or counterclockwise by the driving means 7, the eccentric portion 21 is also eccentrically rotated right or left, and based on the eccentricity A, The inner frame 3 moves upward twice as much as the eccentric amount A while swinging. Since the eccentric portion 22 of the second shaft 6 is provided so that the phase is different in the right rotation direction by the rotation angle F from the eccentric portion 21 of the first shaft 5, it is rotated to the right by following the swinging inner frame 3. To do. As shown in FIGS. 3 and 5, the eccentric portion 22 of the second shaft 6 has a distance that is vertically separated from the axis of the second shaft 6 and the axis of the eccentric portion 22 as the eccentric amount A. Turn right until the difference E between the shaft distances is added. At this time, the arm 4 is in the ascending state, and the direction of the eccentric amount B of the second shaft 6 is inclined by the rotation angle G in the protruding direction of the arm 4 to the vertical line. At this time, the axis of the second shaft 6 is separated from the axis of the eccentric portion 22 by a distance Y in the horizontal direction. The distance Y is a value obtained by adding the difference E between the shaft distances to the distance A between the axis of the second shaft 6 and the axis of the eccentric portion 22 in the vertical direction. From the above, the square root of {B ² − (A + E) ² } is obtained.

  The distance Z in which the axis of the eccentric portion 22 of the second shaft 6 moves horizontally when the arm 4 is raised is the distance X minus the distance Y. When the arm 4 is raised, the axis of the eccentric portion 22 of the inner frame 3 is displaced by a distance Z in the direction opposite to the direction in which the arm 4 protrudes from the inner frame 3, and the eccentric portion 21 of the first shaft 5. Since the distance of the horizontal movement of the axial center of the arm 4 is zero, the tip of the arm 4 rises according to the inter-axis distance C and the length of the arm 4. Thus, in order for the distance Z to be generated, the second axis needs to be driven as shown in FIG. 5, and at that time, the eccentric amount B of the second shaft 6 becomes the eccentric amount A of the first axis. There is a relationship of greater than the value obtained by adding the difference E between the axes (B> A + E).

  For example, as an example, when A: 15 mm, B: 17 mm, C: 1516.5 mm, D: 1515 mm, E: 1.5 mm, X: 10.2 mm, Y: 4 mm, Z: 6.2 mm Since the inclination angle of the inner frame 3 when the arm 4 is raised is 0.23 degrees, if the length of the arm 4 is 1300 mm, the tip of the arm 4 is raised by 5.3 mm. Thus, even if the tip of the arm 4 is bent due to the load of the carrier plate 11 or the molding material 12, the tip of the arm 4 is raised by the mechanism of the present invention to compensate for the droop. Not only can the arm 4 enter the narrow gap between the plates 13 safely, but also prevents the tips of the arms 4 and the carrier plate 11 from coming into contact with the surface of the hot plate 13 during transportation to damage the hot plate. .

  The present invention is not limited to the embodiments described above, and various modifications can be added and implemented without departing from the spirit of the invention. For example, in the present embodiment, the first shaft provided at the lower portion of the outer frame is described as the drive shaft, but the second shaft provided at the upper portion of the outer frame may be configured as the drive shaft. In this case, the rotation angle (F) at the eccentric portion of the lower first shaft, which is the driven shaft, is the protruding direction of the arm from the vertical line position, contrary to the case of the above embodiment where the first shaft is the drive shaft. The rotation direction of the eccentric part is counterclockwise. In the above embodiment, the second shaft is a driven shaft. However, other driving means may be provided on the second shaft, or the first shaft may be interlocked with a chain or the like. In this case, the inter-axis distance C and the inter-axis distance D may be the same value.

It is a front view which shows the loader / unloader of this invention. It is the HH arrow sectional drawing of FIG. 1 which shows the time of the descent | fall of an arm. It is arrow sectional drawing which shows the time of the raise of the arm in FIG. It is an expanded partial sectional view of the J section in Drawing 1 which is a connection part of the eccentric cam of the 1st axis, and an inner frame. It is explanatory drawing which shows the state at the time of the arm lowering in the eccentric part of a 2nd axis | shaft, and an arm rising.

Explanation of symbols

2 Outer frame 3 Inner frame 4 Arm 5 First shaft 6 Second shaft 7 Driving means 8, 9 Eccentric cam 10 Base 11 Carrier plate 12 Molding material 13 Hot plate 14 Movable platen 15 Bearing 16, 17 Mounting plate 18 Pillow block 19 Press device 20 Loader / Unloader 21, 22 Eccentric part 23, 24 Through hole 25 Key A Eccentric amount of eccentric part of first axis B Eccentric quantity of eccentric part of second axis C Eccentric part of first axis and second axis Distance between axes with eccentric part D Distance between axes of first and second axes E Difference in distance between axes (CD)
F Rotational angle when the arm descends in the direction of eccentricity B G Rotational angle when the arm rises in the direction of eccentricity B Direction X Horizontal distance between the axis of the second axis and the axis of the eccentric part when the arm descends Y Y Horizontal distance between the axis of the second axis and the axis of the eccentric part Z Horizontal distance that the axis of the eccentric part of the second axis moves when the arm rises

Claims (3)

A loader / unloader for a press device that carries a molding material into a press device and carries out a molded product formed from the molding material by the press device,
An upright outer frame, a first shaft that is horizontally supported at an inner lower portion of the outer frame, a second shaft that is horizontally supported at an inner upper portion of the outer frame, the first shaft and the Drive means for rotationally driving either one or both of the second shafts, two inner frames pivotably attached to the first shaft and the second shaft via an eccentric cam, and each of the inner frames A loader / unloader for a press apparatus, comprising a plurality of arms fixed horizontally to the opposite surface of the press apparatus.   The inter-axis distance C between the axis of the eccentric portion of the eccentric cam fixed to the first shaft and the axis of the eccentric portion of the eccentric cam fixed to the second shaft is the first axis and the first axis. The loader / unloader for a press apparatus according to claim 1, wherein the loader / unloader for a press apparatus is set so that the difference E between the shaft distances is greater than the distance D between the two shafts.   The eccentric amount B of the eccentric portion of the shaft on which the driving means for the first shaft or the second shaft is not provided is the eccentric portion of the shaft on which the driving means for the first shaft or the second shaft is provided. The loader / unloader for a press apparatus according to claim 2, wherein the loader / unloader is set to be larger than a value obtained by adding the difference E of the inter-axis distance to the eccentric amount A.

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