JP5781796B2 - Press machine - Google Patents

Description

  The present invention relates to a press machine having a motion conversion mechanism that converts rotational movement of a crankshaft into vertical movement of a slide, and more particularly to a press machine that can reduce the lateral component force acting on the slide and can be made compact.

  In a press machine, a slide to which a mold is attached generally converts the rotational movement of a crankshaft into vertical movement by a movement conversion mechanism. As one of the motion conversion mechanisms, there is a press using a rocking link disposed in a substantially horizontal direction substantially perpendicular to a crankshaft (see, for example, Patent Document 1).

  Referring to FIG. 4 showing this conventional press machine, the swing link 1 is swingable about a swing support shaft 4 supported by a frame 2 and arranged in parallel with the crankshaft 3. The swing link 1 is formed with a guide groove 5 extending in the longitudinal direction thereof. A slider 6 is slidably received in the guide groove 5 along the guide groove. The slider 6 receives the crankpin 3a of the crankshaft 3. Further, the lower portion of the swing link 1 is connected to the slide 8 via the connection link 7.

  Therefore, when the crankshaft 3 is rotated by the operation of the driving device 9, the slider 6 that receives the crankpin 3a is slid along the guide groove 5, and the swing link 1 swings. The swing of the swing link 1 causes the slide 8 to which a mold (not shown) is attached to move up and down via the connecting link 7. Since the slider 6 for transmitting the eccentric motion of the crank pin 3a to the swing link 1 slides in the guide groove 5 in the lateral direction as the crank shaft 3 rotates, the crank pin 3a Therefore, it is possible to prevent the lateral movement component force due to the eccentric movement of the second movement from acting strongly on the connecting link 7 and the slide 8. As a result, durability and press accuracy are improved.

JP-A-11-226788

However, the conventional press machine has the disadvantage that the swing link 1 is disposed at right angles to the crankshaft 3 across the frame 2, which leads to an increase in the size of the frame 2 and the press machine. It was.

  Accordingly, an object of the present invention is to provide a press machine that can improve durability and press accuracy and can be made compact.

The press according to the present invention includes a connection member that rotatably receives an eccentric shaft portion of a crankshaft rotatably supported by a frame, and the connection member via a first pivot disposed in parallel to the crankshaft. And a swing member supported by the frame via a second pivot that is parallel to the first pivot, a slide that is guided so as to be movable in the vertical direction, and holds the mold, and the connection A guide groove formed in the member and extending laterally at right angles to the first pivot, and the vertical movement in the direction perpendicular to the lateral direction is constrained within the guide groove and slidable in the extending direction of the guide groove The slide is connected to the slider via a third pivot arranged parallel to the first pivot.

In the press according to the present invention, the connection member that rotatably receives the eccentric shaft portion of the crankshaft swings along with the rotation of the crankshaft so that the connection member has the first pivot. The movement is restricted by the rocking member connected to the frame and supported by the frame via the second pivot , and the movement is received in the guide groove provided in the connection member. The slide is connected via a slider.

Therefore, the movement along the guide groove of the slider accompanying the rotation of the crankshaft can prevent a lateral component force accompanying the rotation of the crankshaft from acting on the slide, and the slide It is possible to prevent a decrease in durability and a decrease in press accuracy due to a lateral component force acting on the sheet. Further, the connection member and the swing member are connected via the first pivot, and both members are rigidly aligned in a straight line across the frame like the conventional swing link 1. Therefore, the frame can be made compact and the press machine can be made compact.

  The guide groove may be formed to extend laterally along a straight line. Alternatively, the guide groove may be formed to extend in the lateral direction along an arcuate curve that opens upward. By forming this arcuate curve along the arcuate locus drawn by the virtual third pin position on the connection member as the connection member swings, the vertical movement stroke of the slide is slightly reduced. Compared to the guide groove along the straight line, the lateral component force acting on the slide can be further reduced.

The slider has a substantially central position between both end portions in the extending direction of the guide groove when an imaginary straight line connecting the central axis of the crankshaft main axis portion and the eccentric shaft portion passes through the central axis line of the third pivot axis. Set to be located at. This prevents the formation of the guide groove having an unnecessary length that causes a decrease in mechanical strength of the connection member where the guide groove is formed, and reduces the mechanical strength of the coupling portion of the connection member. Can be prevented.

  The second pivot is disposed at a position deviating from an imaginary line that connects the first pivot and the center of the main shaft, thereby allowing the connection member to swing appropriately.

  When a virtual straight line connecting the central axis of the crankshaft and the central axis of the eccentric shaft passes through the central axis of the third pivot, the central axis of the first pivot, the central axis of the eccentric shaft, and the first axis An imaginary straight line connecting the central axes of the three pivots connects the side connecting the central axis of the first pivot and the central axis of the eccentric shaft part with the central axis of the eccentric shaft part and the central axis of the third pivot axis. The first and third pivots can be arranged to draw a right triangle that forms a right angle with the side.

  The press machine may further include a positioning mechanism for adjustably positioning the second pivot on the frame.

  The positioning mechanism is provided with a male screw portion at one end, and is supported by the frame so as to be displaceable in the linear direction, and is screwed into the male screw portion with a shaft member that supports the second pivot. A positioning mechanism including a female screw member rotatably supported by the frame and a driving device that rotates the female screw member to displace the shaft member in the axial direction can be employed.

  As the drive device, a drive device including a worm meshing with external teeth formed on the female screw member and a drive source for rotating the worm can be used.

According to the present invention, as described above, the lateral component force accompanying the rotation of the crankshaft acts on the slide by the movement of the slider along the guide groove accompanying the rotation of the crankshaft. Therefore, it is possible to prevent a decrease in durability and a decrease in press accuracy. Further, since it is not necessary to arrange the connection member and the swinging member rigidly in a straight line across the frame, it is possible to reduce the size of the frame that covers them, and hence the press machine. It becomes possible.

Is a front view showing a part of the press according to the present invention, It is a side view which shows the principal part of the press machine shown in FIG. It is an adjusted figure, It is sectional drawing obtained along the III-III line of Fig.2 (a), It is a side view which fractures | ruptures and shows a part of conventional press machine.

  The press 10 according to the present invention includes a frame 12 as shown in FIG. The frame 12 includes a lower frame 12a in which a lower die (not shown) is arranged, and an upper frame 12c supported by the lower frame 12a at an interval via a pillar portion 12b. In the illustrated example, the upper frame 12c is a crown portion formed of a rectangular housing as a whole, and the upper portion of the crown portion 12c is shown in FIGS. 2 (a), 2 (b), and 3. As shown, a housing 16 for the positioning mechanism 14 is provided.

  Referring to FIG. 1 again, the crankshaft 18 is disposed in the horizontal direction in the crown portion 12c. The crankshaft 18 has a pair of main shaft portions 18a and an eccentric shaft portion 18b provided between the main shaft portions 18a. The crankshaft 18 is supported by the upper frame 12c by the bearing 20 so as to be rotatable around the axis of the main shaft, that is, around the axis of the crankshaft 18, at each main shaft 18a.

  The slide 22 to which the upper mold of the mold is assembled is integrally attached to the lower end of the connecting rod 24 that penetrates the lower end of the upper frame 12c in the vertical direction. The connecting rod 24 is guided by the bearing 26 of the upper frame 12c to reciprocate in the vertical direction along the axial direction of the connecting rod.

  As shown in FIG. 1, a flywheel 28 that receives a driving force of a main electric motor M <b> 1 such as an electric motor is provided on one main shaft portion 18 a located at one end of the crankshaft 18. The crankshaft 18 rotates at a stable speed by the rotational driving force received through the flywheel 28. Although not shown, the flywheel 28 incorporates a well-known clutch and brake. The rotational movement of the crankshaft 18 is converted into a vertical movement by the link mechanism 30 which is a movement conversion mechanism and transmitted to the slide 22.

  As clearly shown in FIGS. 2A and 2B, the link mechanism 30 includes a connection member 32 rotatably connected to the eccentric shaft portion 18b of the crankshaft 18, and a parallel to the main shaft portion 18a. And a swing member 36 connected to the connection member 32 via a first pivot 34. In the illustrated example, as shown in FIG. 3, a pair of swinging members 36 parallel to each other is used, and the pair of swinging members is a second pivot shaft parallel to the main shaft portion 18a, as will be described later. 38, and is supported by the upper frame 12 c via the driving device 40 of the positioning mechanism 14.

  As clearly shown in FIGS. 2 (a) and 2 (b), the connection member 32 has a rectangular main body portion 32a formed with a guide groove 44 for slidably receiving the slider 42 in the lower portion. And an arm part 32b projecting to one side of the main body part, and the eccentric shaft part 18b is rotatably received in a circular opening 32c formed in the upper part of the main body part 32a.

  In the example shown in FIG. 1, a bifurcated portion that branches downward is formed in the lower portion of the main body portion 32a of the connection member 32, and a pair of guide grooves 44 correspond to each other in the bifurcated portion. Is formed. In the illustrated example, the pair of guide grooves 44, as shown in FIG. 2, when the virtual straight line L1 connecting the central axis O1 of the main shaft portion 18a and the central axis O2 of the eccentric shaft portion 18b is held vertically, It is formed in a lateral direction along a straight line extending perpendicular to the virtual straight line L1.

  In each guide groove 44, the slider 42 is arranged so as to be slidable in the extending direction of the guide groove 44 and to restrain movement in a direction perpendicular to the sliding direction. The upper part of the connecting rod 24 is inserted between the pair of sliders 42, and the upper part of the connecting rod 24 is connected to the pair of sliders 42 via the third pivot 46 parallel to the main shaft portion 18 a on both sides thereof. It is supported by.

  Further, the lower portion of the swing member 36 is pivotally attached to the distal end portion of the arm portion 32 b of the connection member 32 via the first pivot 34. As shown in FIG. 2, when the virtual straight line L1 passes through the central axis O3 of the third pivot 46, the virtual straight line L2 passing through the central axis O2 and the central axis O4 of the first pivot 34 forms a right angle, and the center The central axes O2, O3, and O4 are arranged so that a virtual straight line connecting the axes O2, O3, and O4 forms a right triangle.

  The second pivot shaft 38 that supports the upper end portion of the swing member 36 on the upper frame 12c is disposed at a position deviated to one side from an imaginary straight line L2 connecting the central axis lines O2 and O4. In the example shown in FIG. 2A, the second pivot 38 supports the swinging member 36 on the upper frame 12c via the positioning mechanism 14 so as to be swingable above the virtual straight line L2.

  That is, in the illustrated example, as shown in FIGS. 2A and 2B, the positioning mechanism 14 has a male screw groove 48a at one end, and the other end can protrude from the housing 16 into the crown portion 12c. The shaft member 48 arranged, a worm wheel 50 that is screwed into the male screw groove 48a of the shaft member, and a worm 52 are provided.

  The housing 16 is formed with a guide hole 56 that is formed in alignment with the opening 54 of the crown portion 12c that receives the shaft member 48 in a projectable manner. The shaft member 48 has a male screw portion (48a) provided with a male screw groove 48a so as to be movable in the axial direction of the shaft member, and is received in the guide hole 56. The upper end portion of the swing member 36 is supported.

  An enlarged diameter portion 56 a is formed in the housing 16 in association with the guide hole 56. The worm wheel 50 is rotatably held by the enlarged diameter portion 56a. The worm wheel 50 has an inner thread groove 50a that is screwed into the male thread portion 48a of the shaft member 48, and has outer teeth 50b. The worm wheel 50 is prevented from moving in the axial direction of the shaft member 48 by the shoulder of the enlarged diameter portion 56a. A worm 52 that is rotatably supported in the housing 16 meshes with the external teeth 50 b of the worm wheel 50.

  The worm 52 can be rotated by a drive source such as an adjustment servo electric motor (not shown). Therefore, by actuating the servo electric motor, the worm 52 is rotated, and the worm wheel 50 meshing with the worm is rotated at a fixed position, so that the shaft member 48 screwed into the worm wheel 50 is connected to the shaft member. Can be displaced in the axial direction. Therefore, the worm 52 that meshes with the external teeth 50 b of the worm wheel 50 that is a female screw member and the servo electric motor that is the drive source for rotating the worm constitute the drive device 40 of the positioning mechanism 14.

When the crankshaft 18 is driven and rotated around the main shaft portion 18a by driving the main electric motor M1, the eccentric shaft portion 18b moves eccentrically around the main shaft portion 18a. Along with the eccentric movement of the eccentric shaft portion 18b, the connection member 32 eccentrically moves around the eccentric shaft portion 18b with the swing of the pair of swing members 36 having the second pivot 38 as the swing center. 2A, the central axis O1 of the main shaft portion 18a, the central axis O2 of the eccentric shaft portion 18b, and the central axis O3 of the third pivot 46 are positioned on a vertical virtual straight line L1. And a bottom dead center position in a posture where the central axis O1 is positioned on the central axis O2, and a top dead center position (not shown) where the central axis O1 is positioned below the central axis O2 on the virtual straight line L1. The slide 22 moves up and down.

  FIG. 2A shows a state in which the shaft member 48 is in the retracted position at the back of the guide hole 56 by the rotation operation of the worm 52. In FIG. 2A, the virtual straight line L3 passing through the central axis O4 of the first pivot 34 and the central axis O5 of the second pivot 38 is parallel to the virtual straight line L1 passing through the central axes O1, O2, and O. FIG. 2B shows a state in which the worm 52 is in the projecting position that projects most from the guide hole 56 by the reverse rotation operation of the worm 52. In FIG. 2 (b), the virtual straight line L3 passing through the central axes O4 and O5 breaks the parallel relationship with the virtual straight line L1 passing through the central axes O1, O2, and O.

  In the retracted position of the shaft member 48 shown in FIG. 2A, the slide 22 is in the above-described bottom dead center position. For example, in the state where the slide 22 is at the bottom dead center position, the worm 52 is rotated by driving the servo electric motor of the driving device, and thereby the height position of the second pivot 38 is moved downward. As a result, as shown in FIG. 2B, the swinging member 36 swings slightly counterclockwise around the second pivot 38, and the eccentric shaft portion 18b is swung as the swinging member 36 swings. Oscillates slightly counterclockwise around. As a result, the bottom dead center position of the slide 22 is lowered by S from the position shown in FIG.

  As is clear from this, regardless of whether or not the slide 22 is at the bottom dead center position, the bottom dead center position of the slide 22 can be adjusted by operating the driving device of the positioning mechanism 14. .

  The shaft member 48 of the positioning mechanism 14 is disposed above the arm portion 32b so as to be positioned in the vertical direction. Alternatively, the shaft member 48 can be disposed below the arm portion 32b. In addition, the shaft member 48 can be inclined and disposed above or below the arm portion 32b, and the housing 16 is replaced with the illustrated top portion of the upper frame 12c, as shown in phantom lines in FIG. It can be provided on the side of the upper frame 12c.

  In the press 10 according to the present invention, as described above, the slide 22 swings between the top dead center and the bottom dead center by the swing of the connection member 32 accompanying the rotation of the crankshaft 18. As the connection member 32 swings, a lateral component force acts on the third pivot 46 that connects the slide 22 to the slider 42, and a part of this lateral component force is a slider. Since 42 is movably received along the guide groove 44, the slider 42 is absorbed by sliding along the guide groove 44.

  Therefore, since this lateral component force can prevent the slide 22 supporting the mold from being subjected to unnecessary posture change and twist, the durability component and the press accuracy are reduced by this lateral component force. It is possible to prevent the press machine 10 from being improved in durability and press accuracy.

Further, since the swing member 36 and the connection member 32 do not cross the frame 12 as a single member unlike the conventional swing link 1 , the swing member 36 and the connection member 32 are angled. It can be accommodated in the upper frame 12c in a compact manner. Therefore, the size of the press machine 10 is not increased without increasing the size of the frame 12.

  As described above, as shown in FIG. 2A, when the straight line L1 passes through the central axis O3 of the third pivot 46, the slider 42 is configured to be positioned at the center of the guide groove 44. . Instead, when the straight line L1 passes through the central axis O3 of the third pivot 46, the guide groove 44 is arranged so that the slider 42 is offset from the center of the guide groove 44 toward one end of the guide groove 44. Can be formed. However, in order to prevent unnecessary extension of the guide groove and thereby prevent a decrease in unnecessary mechanical strength of the connecting portion between the connection member 32 and the slider 42, as shown in FIG. It is preferable that the slider 42 be positioned at the center of the guide groove 44 when the straight line L1 passes through the central axis O3 of the third pivot 46.

  In the above description, the guide groove 44 is a straight guide groove. However, instead of this, as shown in FIG. 2 (a) or (b), an arc shape that opens the guide groove upward is shown. It can be formed to extend laterally along a curve. By forming this arcuate curve along an arcuate locus drawn by the virtual third pin position O3 on the connection member as the connection member 32 swings, the vertical movement stroke of the slide 22 is slightly reduced. However, it is possible to substantially eliminate the lateral component force acting on the third pivot 46 compared to the guide groove 44 along the straight line, that is, acting on the slide 22.

  Further, in the above-described example, the example in which the positioning mechanism 14 is provided has been described. However, the positioning mechanism 14 can be omitted so that the adjustment of the bottom dead center position is not required. In this case, the second pivot 38 of the swing member 36 is fixedly supported by the upper frame 12c.

  The present invention is not limited to the above-described embodiments. For example, the arrangement of each pivot can be variously changed within the scope of the claims.

DESCRIPTION OF SYMBOLS 10 Press machine 12 Frame 14 Positioning mechanism 18 Crankshaft 18a Main shaft part 18b Eccentric shaft part 22 Slide 32 Connection member 34 First pivot 36 Swing member 38 Second pivot 40 Drive device 42 Slider 44 Guide groove 46 Third Axis of 48 Shaft member 50 Worm wheel (Female thread member)
50b External teeth 52 Worm (Male thread member)

Claims (8)

A frame, a crankshaft having a main shaft portion rotatably supported by the frame, an eccentric shaft portion eccentric to the main shaft portion, a connection member rotatably receiving the eccentric shaft portion, and a parallel arrangement with the crankshaft A swing member coupled to the connection member via a first pivot and supported by the frame via a second pivot parallel to the first pivot, and guided to be movable in the vertical direction. , A slide for holding the mold, a guide groove formed in the connection member and extending laterally at right angles to the first pivot axis, and restraining vertical movement in the lateral direction and right angle in the guide groove And a slide that is slidable in the direction of extension of the guide groove, the slide being coupled to the slider via a third pivot disposed parallel to the first pivot , In addition, the slider When a virtual straight line connecting the center axis of the main shaft portion and the eccentric shaft portion of the rank shaft passing through the central axis of the third pivot is located substantially at the center position between the both ends in the extending direction of the guide groove, press.   The press machine according to claim 1, wherein the guide groove extends in a lateral direction along a straight line.   The press machine according to claim 1, wherein the guide groove extends in a lateral direction along an arcuate curve that opens upward.   2. The press according to claim 1, wherein the second pivot is disposed at a position away from an imaginary line connecting the first pivot and the center of the main shaft.   When a virtual straight line connecting the central axis of the crankshaft and the central axis of the eccentric shaft passes through the central axis of the third pivot, the central axis of the first pivot, the central axis of the eccentric shaft, and the first axis An imaginary straight line connecting the central axes of the three pivots connects the side connecting the central axis of the first pivot and the central axis of the eccentric shaft part with the central axis of the eccentric shaft part and the central axis of the third pivot axis. The press according to claim 1, which draws a right triangle that forms a right angle with a side.   The press machine according to claim 1, further comprising a positioning mechanism for adjustably positioning the second pivot on the frame. The positioning mechanism is a shaft member which is provided with a male screw portion at one end and is supported by the frame so as to be displaceable in a linear direction, and is screwed into the male screw portion with a shaft member which supports the second pivot. The press machine according to claim 6 , comprising: a female screw member rotatably supported by a frame; and a driving device that rotates the female screw member to displace the shaft member in the axial direction. The press machine according to claim 7 , wherein the driving device includes a worm meshing with external teeth formed on the female screw member, and a driving source for rotating the worm.

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