JP5943973B2 - Slide drive device for press machine and press machine using the same - Google Patents

Description

  The present invention relates to a slide drive device for a press machine and a press machine using the same. More specifically, the present invention relates to a slide drive device of a press machine provided with a booster mechanism and a press machine using the same.

  Normally, in a press machine that uses a crankshaft and a connecting rod to drive a slide, due to the inclination of the connecting rod, the slide has a component force in a direction (thrust direction) perpendicular to the direction of movement (pressing direction). Works. When the component force increases, the product accuracy and the mold life tend to be adversely affected.

  Patent Document 1 discloses a technique for reducing the thrust component in the thrust direction based on such background. In the drive device of the press machine shown in Patent Document 1, a motion conversion mechanism (connection member) 24 connected to a crankshaft 14 (refer to FIGS. 1 and 2 of Patent Document 1 for reference numerals) is connected to a slide 18. The rod 20 is driven. The connecting rod (plunger) 20 is guided by the bearing (plunger guide) 22 of the upper frame 12c to reciprocate in the vertical direction along the axial direction. Therefore, a thrust component in the thrust direction does not act on the slide 18.

  Furthermore, in the slide drive device of the Narcle press of Patent Document 2, the lower link 3 connected to the slide 2 is driven by the vertical swing of the lateral link 4 (refer to Patent Document 2 for reference numerals). The inclination by the swing of the lower link 3 is set to be very small. Thereby, a load can be applied from a position higher than the bottom dead center, and the thrust force generated in the slide 2 is reduced.

Patent Document 3 discloses a two-point or four-point pressure rod type drive device that is connected to a plurality of eccentric shafts that are symmetrical about the center line. Eccentric shaft f across the center line
(See FIG. 3 of Patent Document 3 for the reference numerals) rotate in opposite directions (opposite rotation). For this reason, the inclination of the left and right pressure rods g is symmetric with respect to the center line. Accordingly, the thrust forces acting on the slide e due to the inclination of the left and right pressure rods cancel each other, reducing the thrust force.

JP2011-189351A JP-A-11-277296 JP 58-110198 A

In the drive device of Patent Document 1, the height of the connecting rod 20 is added to the height of the motion conversion mechanism (connection member) 24, so that the press height is increased. If the connection member 24 is shortened in order to keep the press height low, the swing angle of the connection member 24 is increased, and the efficiency of converting the torque of the crankshaft 14 into the applied pressure of the slide 18 is lowered.
Furthermore, in the mechanism of Patent Document 2, in addition to the height of the lower link 3, a driving device for swinging the horizontal link 4 up and down must be provided on the upper portion of the ring 4. For this reason, press height becomes high. Moreover, the mechanism is complicated.
Patent Document 3 is a multi-point press in which an eccentric shaft rotates oppositely, and cannot be applied to a one-point press.

  Accordingly, an object of the present invention is to provide a slide drive device and a press machine for a press machine that are compact and reduce the thrust force of the slide during processing.

(1) A slide drive device for a press machine according to the present invention includes a slide of a press machine that moves up and down by rotation of a drive shaft, and the slide is rotatable about a first axis that is orthogonal to the direction of movement of the slide. A disk-shaped member to be pivoted, and one end of which is pivotally supported by the disk-shaped member so as to be rotatable around a second axis parallel to the first axis, and the other end is the drive A connecting rod that is rotatably connected to a shaft, one end of which is pivotally supported by the disk-like member around a third axis parallel to the first axis, and the other end is pressed A lever that is pivotally coupled to the frame of the machine, wherein the second and third axes are at substantially the same distance from the first axis, with the third axis as a fulcrum, A booster mechanism is formed with the axis of 2 as the power point and the first axis as the action point. Inclination with respect to the slide in the direction of movement of the micro lever is substantially symmetrical with respect to the direction of movement of the slide in the vicinity of the bottom dead center of the slide, it is characterized.

(2) In the slide drive device of such a press machine, the disk-shaped member is divided into two plates arranged in parallel so as to face each other, and between these plates, It is preferable that a second shaft member having the second axis and a third shaft member having the third axis are provided.

(3) It is preferable that the slide is provided with a case for pivotally supporting the disk-shaped member.

(4) A press machine of the present invention is characterized by including the above-described slide drive device.

(1) In the slide drive device of the press machine of the present invention, a connecting rod and a lever are rotatably provided on a disk-shaped member, and the second and third axes are at substantially the same distance from the first axis. Yes, a booster mechanism is formed with the third axis as a fulcrum, the second axis as a power point, and the first axis as an action point. In addition, the inclination of the lever and connecting rod with respect to the moving direction of the slide is made substantially symmetrical with respect to the moving direction of the slide in the vicinity of the bottom dead center of the slide. Accordingly, the thrust force transmitted from the lever and the connecting rod to the disk-shaped member is offset as the internal stress of the disk-shaped member, and the thrust force generated in the slide can be reduced.
And since the connecting rod and lever are arranged almost opposite to each other and the lower part of each is connected to the slide via a disk-like member, space is saved in the height direction, and the press height can be suppressed. it can.

(2) In the slide drive device of such a press machine, the disk-shaped member is divided into two plate bodies arranged in parallel so as to face each other, and between the plate bodies, When the second shaft member having the second shaft center and the third shaft member having the third shaft center are provided, the second shaft member and the third shaft member are supported at both ends. The rotation of the shaped member is stable and lightweight.

(3) Further, when the slide is provided with a case for pivotally supporting the disk-shaped member, the rotation of the disk-shaped member is further stabilized with a simple structure.

(4) Since the press machine of the present invention includes a booster mechanism in which the connecting rod and the lever are connected to the slide via disc-shaped members, respectively, a high pressure is generated from a high position on the bottom dead center, The thrust load can be offset while being a one-point press, space is saved in the height direction, and the press height can be reduced.

1a is a partial cross-sectional front view of a slide drive device for a press machine according to the present invention, and FIG. 1b is a cross-sectional view taken along the line II of FIG. FIG. 2 is a side view of the press machine of the present invention. FIG. 3A is a partial sectional right side view of the slide drive device, and FIG. 3B is a partial sectional left side view. 4 is an exploded perspective view, partly cut away, showing the case of FIG. FIG. 5 is a schematic process diagram showing how the connecting rod and lever slide of FIG. 1 are driven. FIG. 6 is a schematic process diagram showing how to drive the connecting rod and lever slide of 90 ° to 180 ° in FIG. 5 in increments of 10 °. FIG. 7 is a schematic mechanism diagram showing transmission of force of the slide drive device of the present invention. FIG. 8 is a schematic mechanism diagram showing transmission of force of a slide drive device of a normal crank mechanism using a crankshaft and a connecting rod. FIG. 9 is a graph showing the thrust ratios of the example and the comparative example with respect to the stroke ratio. FIG. 10 is a graph showing the ratio of the thrust ratio of the example to the stroke ratio and the ratio of the thrust ratio of the comparative example.

[Outline of press machine]
First, an example of the press machine of the present invention will be described with reference to FIG. The press machine 11 includes a slide drive device (hereinafter simply referred to as a slide drive device) of the press machine of the present invention. In the figure, the mold is shown open. The press machine 11 shown in FIG. 2 includes a so-called integrated straight side type frame 12. Examples of the frame 12 include a ring frame in which a bed 13, side walls 14 rising from the left and right sides of the bed 13, and an upper portion 15 provided at the upper ends of the side walls 14 are integrally formed. A bolster 17 is provided on the upper surface of the bed 13.
In addition to the straight side type frame, a C-shaped side frame may be used as the side frame.

  The upper portion 15 is provided with a motor 18 for driving the press. A pulley 18 a is attached to the drive shaft of the motor 18. Further, a bearing (reference numeral 12b in FIG. 1b) is provided on the upper portion 15, and a drive shaft 19 having an eccentric portion 19a is rotatably supported by the bearing. When the drive shaft 19 including the eccentric portion 19a rotates, the connecting rod 4 of the slide drive device 1 connected to the eccentric portion 19a is driven up and down.

  The slide drive device 1 of the present invention is connected to the drive shaft 19 and the frame 12. An upper die 20 a is attached to the lower surface of the slide 2 of the slide drive device 1, and a lower die 20 b is attached to the upper surface of the bolster 17. Further, the slide 2 is provided with a guide portion 2c (see FIG. 4). The guide portion 2c is guided in the up-and-down direction by a slide guide 12a (see FIG. 3) provided on the frame 12. The slide guide 12 a supports the thrust force applied to the slide 2.

A flywheel 21 is provided at one end of the drive shaft 19, and a belt 21a is hung between the flywheel 21 and the pulley 18a. The flywheel 21 is provided with a clutch / brake 21b inside thereof, which turns the drive shaft 19 on and off.
In the drawing, a crankshaft having an eccentric pin is shown as the drive shaft 19, but an eccentric shaft having an eccentric portion or a main gear integrally having an eccentric sheave may be used.

[Slide drive]
Next, the slide drive device will be described with reference to FIG. A slide drive device 1 shown in the figure includes a slide 2. A disk-like member 3 is supported on the slide 2 so as to be rotatable around a first axis 3a perpendicular to the vertical movement direction of the slide 2 (direction perpendicular to the paper surface). This disk-shaped member 3 acts as a large-diameter support shaft, supports the weight of the slide 2, and supports the processing reaction force during processing.

The lower part of the connecting rod 4 is rotatably connected to the disk-shaped member 3. That is, the lower part 4b of the connecting rod 4 is pivotally supported by the disk-shaped member 3 by the second shaft member 7 so as to rotate around the second axis 4a parallel to the first axis. ing. An upper portion 4c of the connecting rod 4 is rotatably connected to an eccentric portion 19a of the drive shaft 19.

  Further, the lower part of the lever 5 is rotatably connected to the disk-shaped member 3. That is, the lower part 5b of the lever 5 is supported by the disk-shaped member 3 by the third shaft member 8 so as to rotate around the third axis 5a parallel to the first axis 3a. A portion 5 c above the lever 5 is rotatably supported by a pin member 16 provided on a stationary member such as the frame 12. Therefore, the slide 2 is suspended by a four-point link mechanism including the disk-shaped member 3, the connecting rod 4, and the lever 5, and its position is determined together with the slide guide 12a.

  In the disk-shaped member 3, a booster mechanism 6 is formed with the third axis 5a as a fulcrum, the second axis 4a as a power point, and the first axis 3a as an action point ( (See FIG. 7). The distances from the action point (3a) to the force point (4a) and the fulcrum (5a) are the same. Furthermore, the force point 4a and the fulcrum 5a are arranged at positions symmetrical with respect to the action point 3a.

  The inclinations of the longitudinal axes of the connecting rod 4 and the lever 5 with respect to the movement direction of the slide 2 are made almost symmetrical with respect to the movement direction of the slide 2 near the bottom dead center of the slide 2 ( (See S3 in FIG. 5).

  As shown in FIG. 3, the disk-shaped member 3 is divided into two circular plates 3b and 3b arranged in parallel so as to face each other. Between the plates 3b and 3b, there is a columnar second shaft member 7 having the second axis 4a and a columnar third shaft member 8 having the third axis 5a. Is provided. The both ends of the second shaft member 7 and the third shaft member 8 are supported by the plate bodies 3b and 3b.

  Next, an example of the case 9 will be described. As shown in FIG. 4, a case 9 that pivotally supports the disk-shaped member 3 is provided above the slide 2. The case 9 is provided on the main body side of the slide 2 and is divided into a lower portion 9a that slides on the lower surface side of the plate body 3b and an upper portion 9b that slides on the upper surface side of the plate body 3b. The lower part 9a and the upper part 9b are integrated by a fastener such as a bolt. The lower part 9a is cup-shaped and can contain lubricating oil.

A step portion 9 c is formed in the middle of the inner peripheral surface of the lower portion 9 a of the case 9. From the inner end of the stepped portion 9c, an enormous portion 9d having a semicircular inner surface that slides with the peripheral surface of the plate body 3b is provided. Further, a vertical wall 9e is erected from the vicinity of the outer end of the step 9c.
On the other hand, the upper part 9b has an arch part 9f having a semicircular sliding surface that slides with the upper peripheral surface of the disk-shaped member 3. Near both ends of the upper portion 9b, there are provided fixing portions 9g that fit into the stepped portion 9c and the hanging wall 9e. A through hole (not shown) for a fastening member is formed in the fixing portion 9g, and is fastened to the lower step portion 9c to be integrated.
By being integrated in this way, the inner surface of the half circumference of the arch portion 9f and the inner surface of the half circumference of the enormous portion 9d are continuous and slidably surround the circumferential surface of the plate body 3a.

  Next, how the slide drive device 1 operates will be described with reference to FIG. In the state S1, the slide 2 is at the top dead center, and the phase of the drive shaft 19 at this time is 0 °. That is, the connecting rod 4 has moved upward as a whole from the state S4 described later. Then, the disk-shaped member 3 moves around the first axis 3a of the connecting rod 4 upward and the third axis 5a of the lever 5 relatively downward. In order to make this happen, the case 9 is rotated counterclockwise in the figure.

Next, in the state S2, the drive shaft 19 rotates counterclockwise and its phase is 90 °. The upper end of the connecting rod 4 moves in the lower left direction so that the connecting rod 4 and the lever 5 are substantially parallel, and the second axis 4a moves in the clockwise direction.
Further, the slide 2 is suspended by a connecting rod 4 and a lever 5 in a state where it is not processed. That is, the weight of the slide 2 and the upper mold is such that the upper portion 9b of the slide 2 is supported on the upper surface of the disc body 3b, and the disc-like member 3 rotates in the clockwise direction in the figure within the case-like member 9. ing.

  In the state S3, the drive shaft 19 further rotates counterclockwise and its phase is 180 °. That is, the second axis 4a further moves downward from the state S2, the disk-like member 3 moves down in the case 9 while rotating clockwise in the figure, and the slide 2 comes to the bottom dead center. In this embodiment, the first axis 3a is lowered by an amount that is approximately ½ of the amount by which the second axis 4a is lowered. At this time, the angle ζ between the axis 4 d extending in the longitudinal direction of the connecting rod 4 and the axis O parallel to the movement direction of the slide 2 is the movement direction of the slide 5 and the axis 5 d extending in the longitudinal direction of the lever 5. The angle κ is approximately the same as the angle κ with the axis O parallel to the axis.

Next, in the state S4, the phase of the drive shaft 19 is 270 °. That is, the second axis 4a moves upward from the state S3, the disk-shaped member 3 rises while rotating counterclockwise in the case 9, and the first disk-shaped member 3 is moved upward. The axis 3a is further raised, and the slide 2 is raised. Finally, when the phase of the drive shaft 19 is 360 °, the slide 2 returns to the top dead center (state S1).
As described above, when the drive shaft 19 rotates once, the disk-shaped member 3 reciprocates around the third axis 5a.

[Example]
FIG. 6 shows an embodiment of the slide drive device 1.
FIG. 6 shows the operation of the slide drive device 1 according to the first embodiment whose phase is 90 ° to 180 ° in increments of 10 °. State R1 (S2) shows a state when the phase is 90 °, and from there, states R2, R3, R4, R5, R6, R7, R8, R9 in increments of 10 °, and a state where the phase is 180 ° R10 is reached. The numbers described above the connecting rod 4 and the lever 5 in the figure are the angles formed with the direction of motion of the slide 2 (axis O in FIG. 5), and correspond to ζ and κ in FIG. 5, respectively.
When attention is paid to the angles ζ and κ in the state R9 (phase 170 °) and the state R10 (phase 180 °), ζ = κ between 170 ° and 180 °. That is, immediately before the bottom dead center arrives, the angles of the connecting rod 4 and the lever 5 with respect to the axis O become the same, and the component force in the thrust direction is offset. This is because the processing is performed from a position slightly above the bottom dead center and before reaching the bottom dead center, so that they are offset.

FIG. 7 is a schematic diagram illustrating the flow of force of the apparatus of the example. This figure shows the state of the apparatus of the first embodiment in the vicinity of the state R8 (phase 160 °) in FIG. Reference numeral 19b in the drawing indicates the axis of the drive shaft 19, and reference numeral 19c indicates the axis of the eccentric portion 19a. Symbol F in the figure is a force applied in the vertical direction from the lever 5 and the connecting rod 4 to the disk-shaped member 3 in the press working state, and its magnitude is about 4000 kN. This corresponds to a press load. The circle of the one-dot chain line in the upper right of the figure is the locus of the axis 19c of the eccentric part. The radius of the circle, that is, the amount of eccentricity is 200 mm. The slide stroke is 199.5 mm.
FL1 in the figure is a force transmitted from the lever 5 to the disk-shaped member 3. FL1H is the horizontal direction component. Frank is the tangential force of the crank. FL 3 is a force transmitted from the connecting rod 4 to the disk-shaped member 3. FL3H is the horizontal direction component. Further, the auxiliary line composed of the symbols A, B, C, and D is a horizontal line and is orthogonal to the axis O. The symbols β, ν, η, λ, γ, ζ, and θ indicate the angles of the portions to which the symbols are attached. In this figure, the angle ζ is 5.129 ° and κ is 7.816 °.
The difference between FL3H and FL1H is represented by ½ (tan κ−tan ζ) × F. This difference is the thrust force received by the disk-shaped member 3.
Here, a value obtained by dividing the thrust force by the press load F is defined as a thrust ratio. More specifically, the thrust ratio is the ratio of the thrust force (horizontal component force) generated on the slide due to the inclination of the connecting rod during press working and the press load. That is, thrust ratio = thrust force (horizontal component force) / press load. In FIG. 7, 1/2 (tan κ−tan ζ) is the thrust ratio.

[Comparative example]
FIG. 8 is a schematic diagram showing force transmission in a slide mechanism (comparative example) of a press machine used for comparison. In addition, about the part which shows the same mechanism as FIG. 7, the same code | symbol is attached | subjected and the description is abbreviate | omitted.
In this device, the upper end of the connecting rod 4 is attached to the eccentric part of the crankshaft, and the slide 2 is attached to the lower end of the connecting rod 4. The eccentric amount of the mechanism 22 of this comparative example is 100 mm, and its slide stroke is 200.0 mm.
Fcon. Is a force transmitted in the axial direction to the connecting rod 4 and is represented by a crank tangential force / sin δ. F is a load applied to the slide. Further, Fx is the thrust force of F.
Symbols α, β, γ, and δ indicate the angles of the portions to which those symbols are attached. Further, symbols Y1, Y2, and x indicate the lengths of the designated portions. Note that the calculated values of those portions in this driving state are attached in the vicinity of these codes. The unit is “mm” or “°”.

[Verification of Examples and Comparative Examples]
FIG. 9 is a diagram showing the thrust ratio with respect to the stroke ratio. The horizontal axis indicates the stroke ratio (%), and the vertical axis indicates the thrust ratio (−). The stroke ratio is the ratio of the distance from the bottom dead center of the slide to the distance from the top dead center to the bottom dead center of the slide. That is, stroke ratio = (distance from bottom dead center of slide / total stroke of slide) × 100.
The solid line in the figure shows an example, and the broken line shows a comparative example. As shown in the figure, in the lower half region of the slide stroke where the press working is performed, the thrust ratio of the example is smaller than the thrust ratio of the comparative example.

FIG. 10 is a graph showing the ratio of the thrust ratio of the example to the thrust ratio of the comparative example with respect to the stroke ratio.
The horizontal axis of the graph is the stroke ratio (%). The vertical axis of the graph represents the ratio (−) of the thrust ratio of the apparatus of Example 1 (see FIG. 7) to the thrust ratio in the mechanism 22 (see FIG. 8) of the comparative example. When the slide 2 is lowered until its height from the bottom dead center reaches about 5% of the stroke, the thrust ratio of the example starts to decrease greatly compared to the comparative example. In particular, it decreases rapidly as it approaches the bottom dead center. From this, the effect of the slide drive device of the present invention can be understood.

The disk-shaped member 3 includes two plate bodies 3b and 3b, but may be a single columnar shaft having the same diameter as the plate body. Further, the number of plate bodies may be one. In that case, it is preferable to make the plate body somewhat thick. At this time, the second shaft member 7 and the third shaft member 8 are cantilevered.
Further, the second shaft member 7 may be fixed to the connecting rod 4 side, or may be fixed to the disk-shaped member 3 side. The third shaft member 8 may also be fixed to the lever 5 side, or may be fixed to the disk-shaped member 3 side.
Furthermore, the lever ratio of the booster mechanism is preferably 0.5, but it may be larger or smaller.
Furthermore, one slide 2 may be driven using two slide drive devices 1.
Furthermore, the upper end of the lever 5 may be pivotally supported on the disk-shaped member 3 and the lower end may be pivotally supported on the frame 12 below the disk-shaped member 3.

DESCRIPTION OF SYMBOLS 1 Slide drive device 2 Slide 2a Lower part 2b Upper part 2c Guide part 3 Disk-shaped member 3a 1st axial center 3b Plate body 4 Connecting rod 4a 2nd axial center 4b Lower part 4c (Connecting rod) Upper part 4d (Connecting rod) Connecting rod axis 5 Lever 5a Third axis 5b (Lever) lower part 5c (Lever) upper part 5d (Lever) axis 6 Boosting mechanism 7 Second shaft member 8 Third shaft member 9 Case 9a (Case of the case) ) Lower part 9b (Case) upper part 9c Step part 9d Enlarged part 9e Hanging wall 9f Arch part 9g Fixed part 11 Press machine 12 Frame 12a Slide guide 12b Bearing 13 Bed 14 Side wall 15 Upper part 16 Pin member 17 Bolster 18 Motor 18a Pulley 19 Drive shaft 19a Eccentric part 19b Axis center 19c (of the drive shaft) Axis center 20a (of the eccentric part) Upper mold 20b Lower mold 21 Fly hoist Le 21a belt 21b clutch and brake 22 Comparative Example mechanism

Claims (4)

A slide of the press machine that moves up and down by the rotation of the drive shaft;
A disk-like member pivotally supported around the first axis perpendicular to the direction of movement of the slide on the slide;
A connecting rod having one end pivotally supported by the disk-like member around a second axis parallel to the first axis and the other end pivotally connected to the drive shaft; ,
A lever whose one end is pivotally supported by the disk-like member around a third axis parallel to the first axis and whose other end is pivotally connected to the frame of the press machine And
The second and third axes are at substantially the same distance from the first axis, the third axis is a fulcrum, the second axis is a power point, and the first axis is an action point. A boost mechanism is formed,
A slide drive device of a press machine, wherein the inclination of the connecting rod and the lever with respect to the movement direction of the slide is substantially symmetric with respect to the movement direction of the slide near the bottom dead center of the slide. The disk-shaped member is divided into two plates arranged in parallel so as to face each other,
The slide drive device for a press machine according to claim 1, wherein a second shaft member having the second axis and a third shaft member having the third axis are provided between the plates. .   The slide drive device for a press machine according to claim 1, wherein a case for pivotally supporting the disk-shaped member is provided on the slide.   The press machine provided with the slide drive device in any one of Claims 1, 2, or 3.

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