JP2011121085A - Press machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To further simplify the constitution of a press machine in which the stroke length of a slide is adjustable. <P>SOLUTION: The press machine includes: a crank shaft supported to a frame; a connection member in which one end is connected to the eccentric shaft part of the crank shaft, and which elongates to the outer part in the radial direction of the shaft line of the crank shaft; first and second link members in which each one edge is connected to the other edge of the connection member; a pivot provided in relation to the other edge of the first link member, provided movably to the longitudinal direction of the link member and allowing the oscillation of the first link member; an adjustment mechanism of supporting the pivot to the frame adjustably; a pivot provided at the other edge of the second link member; and a supporting mechanism supporting the pivot to the frame. The first link member is connected to the slide to which a mold is held via a third link member. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a press machine that can adjust the stroke length of a slide that reciprocates by the rotational movement of a crankshaft, and more particularly to a press machine that has a simplified configuration.

  The applicant of the present application has proposed a press that can adjust the stroke length of a slide that can simplify the configuration (see Patent Document 1).

  The main part of the conventional press is shown in FIGS. As shown in FIG. 6, the press machine 100 includes a crankshaft 104 having a main shaft portion 104a that is rotatably supported by an upper frame 102 of a rectangular housing. The upper end portion of the connection member 106 is pivotally attached to the eccentric shaft portion 104 b of the crankshaft 104. As shown in FIG. 7, a pivot 108 is provided at the lower end of the connection member 106, and a slider 110 is provided at both ends of the pivot. A pair of projecting portions 102 a that project from the inner surface of the frame so as to approach each other and whose projecting ends are spaced from each other are provided at opposing portions of the upper frame 102. A guide groove 102b for guiding the pair of sliders 110 in the vertical direction as viewed in FIG. 6 is provided on the opposing surface of each protrusion 102a.

  When the crankshaft 104 is driven and rotated in one direction, the slider 110 provided at the lower end of the connection member 106 reciprocates in the vertical direction by the guide action of the guide groove 102b. As the slider 110 reciprocates, the pivot 108 reciprocates up and down. One end of the first link member 112 is pivotally attached to the pivot 108, and an adjusting mechanism 116 including a connector 114 is provided in association with the other end of the link member 112.

  The connecting tool 114 is connected to the first slider 114a that receives the other end of the link member movably along the longitudinal direction of the first link member 112, and is connected to the slider via a pivot 114b. And a second slider 114c that is movable along the lateral guide portion 102c formed in the above.

  Since the other end of the first link member 112 is slidably received by the first slider 114a and swinging about the pivot 114b is allowed, the upper and lower portions of the pivot 108 of the connection member 106 are With the reciprocating motion in the direction, it swings around the pivot 114b of the adjusting mechanism 116.

  The swing of the first link member 112 includes a connecting link 120 having an upper end pivotally attached to an intermediate portion of the link member via a pivot 118, and a connecting rod connected to the connection link via a pivot 122. 124, the connecting rod is converted into a vertical motion of the slide 126 extending. An upper mold part (not shown) of the mold is attached to the slide 126.

  The adjustment mechanism 116 includes an operation shaft 128 (see FIG. 6) provided with an external gear 128a at one end, and a male screw portion 114d provided on the second slider 114c and extending in the lateral direction. An external gear 130 that is screwed into the male screw portion and is restricted from moving in the axial direction of the male screw portion 114d is screwed into the male screw portion 114d.

  According to the adjusting mechanism 116, the external gear 130 meshing with the external gear 128 a of the operation shaft can be rotated by rotating the operation shaft 128. When the external gear 130 rotates, the first and second sliders 114a and 114c that support the pivot 114b are displaced integrally with the male screw portion 114d in the lateral direction that is the axial direction of the male screw portion.

  FIG. 8A shows an example in which the first link member 112 is maintained in a horizontal posture in a state where the eccentric shaft portion 104b of the crankshaft 104 is positioned immediately below the main shaft portion 104a. In this case, the slide 126 is located at the bottom dead center, and the height position of the bottom dead center does not change regardless of the adjustment position of the pivot 114b.

  On the other hand, FIGS. 8B and 8C show a state in which the eccentric shaft portion 104b of the crankshaft 104 is located immediately above the main shaft portion 104a, and a state in which the slide 126 is at the top dead center position. FIG. 8B shows a state when the connector 114, that is, the pivot 114b is at a position farthest from the pivot 108, and FIG. 8C shows that the pivot 114b is at a position closest to the pivot 108. The state of time is shown.

  As is clear from the comparison between FIG. 8A, FIG. 8B, and FIG. 8C, when the bottom dead center position of the slide shown in FIG. The height S1 of the top dead center position is higher than the height S2 of the top dead center position shown in FIG. The height S (S1, S2) of the top dead center position decreases as the pivot 114b approaches the pivot 108 from the position shown in FIG. 8B toward the position shown in FIG. 8C. Therefore, the stroke length of the slide 126 can be increased or decreased according to the rotation operation of the operation shaft 128 of the adjustment mechanism 116.

JP 2003-80397 A

  However, in the conventional press machine 100, when the crankshaft 104 is driven to rotate, the movement of the pivot 108 is controlled so as to swing the first link member 112 about the pivot 114b. As clearly shown, it is necessary to project a pair of protrusions 102a for the guide groove 102b from the mutually opposing surfaces of the upper frame 102 into the frame. This is disadvantageous in terms of space-saving design of the upper frame 102 and complicates the configuration.

  Further, in the press machine 100 that requires a pair of protrusions 102 a, the crankshaft 104 is related to the motion conversion mechanism such as the connection member 106, the first link member 112, and the connecting link 120 for the stable operation of the slide 126. It is practically impossible to install a plurality of sets of the motion conversion mechanisms at intervals in the axial direction.

  Therefore, Patent Document 1 proposes that motion conversion mechanisms such as the first link member 112 and the connecting link 120 are arranged in parallel in the diameter direction of the crankshaft. According to this proposal, the two motion conversion mechanisms are arranged symmetrically with respect to the central axis of the connection member 106 in a vertical posture. However, according to this, it is only possible to arrange a pair of motion conversion mechanisms in parallel, and it is possible to apply three or more motion conversion mechanisms that can realize more stable operation of the press machine. could not.

Accordingly, an object of the present invention is to further simplify the configuration of a press machine capable of adjusting the slide stroke length.
Moreover, the objective of this invention is providing the press which can employ | adopt the said motion conversion mechanism 3 or more.

  In the press according to the present invention, basically, by providing the second link member that restricts the movement of the pivot that pivotally attaches the lower end portion of the connection member and the first link member to the arcuate movement, The slider and the pair of protrusions that define the guide groove for regulating the movement of the slider become unnecessary. That is, the press according to the present invention is characterized in that the movement locus of the first pivot is defined by an arcuate locus by the second link member.

  Therefore, the press according to the present invention has one end connected to the frame, a crankshaft supported by the frame so as to be rotatable about an axis extending in the first direction, and an eccentric shaft portion of the crankshaft, A connection member extending outward in the radial direction of the axis, and first and second link members, each of which has a first pivot that extends in the first direction as a common pivot, through the pivot. The first and second link members connected to the other end of the connection member and extending in directions away from each other on both sides of the connection member, and the link movable in the longitudinal direction of the first link member A second pivot that is associated with the member and extends in the first direction and has a second pivot that allows the first link member to swing; Is the first one An adjustment mechanism that is supported on the frame so as to be adjustable in a second direction perpendicular to the second direction, a third pivot provided at the other end of the second link member, and extending in the first direction, and the pivot on the frame A support mechanism fixedly supported on the first link member, and one end connected to the first link member via a fourth pivot extending in the first direction at an intermediate position between both ends of the first link member; And a third link member having the other end connected to the slide holding the mold and disposed along a third direction perpendicular to the first and second directions.

  In the press according to the present invention, the other end of the connection member is regulated in an arcuate motion by the second link member connected to the other end via the first pivot. That is, when the crankshaft is driven and rotated in one direction, the first pivot on the other end of the connection member is connected to the frame member via the third pivot. The member provides an arcuate swing trajectory about the third pivot. When the crankshaft is driven and rotated by the restraint of the first pivot along the swing locus, the first link member swings around the second pivot.

  Therefore, by adjusting the position of the second pivot by adjusting the adjusting mechanism, the top dead center position of the slide that reciprocates via the third link member can be adjusted as in the conventional case. .

  In addition, the third pivot is only fixedly supported by the frame by the support mechanism, and it is not necessary to provide opposing protrusions in the frame such as the conventional pair of guide portions. The configuration can be simplified.

  A pair of second link members can be used as the second link member. In this case, the pair of second link members are arranged at an interval in the thickness direction of the link member. Further, the support mechanism for supporting the third pivot of the other end of the pair of second link members may be configured so that the pair of second link members is separated from the inner surface of the frame facing the other end of the pair of second link members. It can comprise by the bearing part formed protruding between the said other ends of this 2nd link member. Each of the protruding ends is pivotally attached to the other end of the pair of second link members via the third pivot.

  The connection member, the first and second link members, and the third link member constitute a set of motion conversion mechanisms, and the plurality of sets of motion conversion mechanisms are spaced apart from each other in the axial direction of the crankshaft. Can be arranged in parallel. In this case, the third link member of each motion conversion mechanism is connected to the slide via the fifth pivot while using the slide as a common slide.

  The connector includes a first slider disposed on the frame movably in the second direction to slidably receive the other end of the first link member, and a second slider on the slider. A second slider coupled via a pivot and movably receiving the first slider in the second direction.

  The adjusting mechanism may include a positioning device that positions the second slider so as to be adjustable in the second direction.

  The positioning device includes a male screw member provided on the second slider, an external gear screwed into the male screw member and restricted in movement in the axial direction of the male screw member, and external teeth of the gear. A rotation operation member that meshes and displaces the male screw member in an axial direction of the male screw member via the external gear.

  According to the present invention, as described above, the first link member connected to the connection member is moved with the rotation of the crankshaft by the movement restricting action of the second link member and the adjusting mechanism. The swinging motion can be adjusted.

  Accordingly, since the pair of protrusions provided with the conventional slider and the guide groove for restricting the movement of the slider can be eliminated, the configuration can be simplified and the three The above motion conversion mechanisms can be arranged in parallel to ensure a more stable vertical movement of the slide.

It is a front view showing a main part of the press machine by breaking a part of the press machine according to the present invention, It is sectional drawing obtained along the II-II line of FIG. FIG. 3 is a cross-sectional view taken along line III-III in FIG. FIG. 4 is a cross-sectional view taken along line IV-IV in FIG. FIG. 5 is a diagram for explaining a change in the stroke length of the slide due to the operation of the adjusting mechanism of the press shown in FIG. 1, and FIG. 5 (a) shows a state when the slide is at the bottom dead center position. b) and FIG. 5C show the change of the top dead center position of the slide at each adjustment position of the adjustment mechanism, It is a drawing showing a main part of the press machine by breaking a part of a conventional press machine, It is sectional drawing obtained along the VII-VII line of FIG. FIG. 8A is a diagram for explaining a change in the stroke length of the slide due to the operation of the adjusting mechanism of the press shown in FIG. 7. FIG. 8A shows a state when the slide is at the bottom dead center position, and FIG. FIG. 8B and FIG. 8C show changes in the top dead center position of the slide at each adjustment position of the adjustment mechanism.

  The press 10 includes a frame 12 as shown in FIG. The frame 12 includes a lower frame 12a in which a lower mold part (not shown) is disposed, and an upper frame 12c supported by the lower frame 12a with a space through a pillar part 12b. In the example shown in the figure, the upper frame 12c is entirely composed of a rectangular casing, and a gear case 14 is provided on one side of the upper frame 12c.

  The crankshaft 18 is arranged along a first direction, for example, a front-rear direction (a direction perpendicular to the paper surface in FIG. 1). As shown in FIG. 2, the crankshaft 18 includes a plurality of main shaft portions 18a and a plurality of eccentric shaft portions 18b provided between the main shaft portions 18a. In the illustrated example, three eccentric shaft portions 18b are provided. 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 part is assembled is attached to the lower ends of three connecting rods 24 (see FIGS. 2 and 3) penetrating the lower end of the upper frame 12c so as to reciprocate in the vertical direction. Each connecting rod 24 is guided by the bearing 26 (see FIGS. 1 and 3) of the upper frame 12c in the above-described reciprocating motion in the vertical direction.
The slide 22 is disposed below the crankshaft 18, and each connecting rod 24 corresponds to the eccentric shaft portion 18 b and is positioned below the eccentric shaft portion in the first direction, that is, the crank. The shafts 18 are arranged at intervals in the axial direction of the shaft 18.

  As shown in FIGS. 2 and 3, the main shaft portion 18 a located at one end of the crankshaft 18 is provided with a flywheel 28 assembled with a drive source (not shown) such as an electric motor. The crankshaft 18 rotates at a constant speed by the rotational driving force received via the flywheel 28. The flywheel 28 incorporates a well-known clutch and brake. In the illustrated example, the rotational motion of the crankshaft 18 is converted into vertical motion by three motion transmission mechanisms, that is, the motion conversion mechanism 30, and transmitted to the slide 22.

  Each motion converting mechanism 30 is shown in its entirety in FIG. 1 and includes a connection member 32, first and second link members 34 and 36, and a third link member 38.

  Each connection member 32 is pivotally connected to the eccentric shaft portion 18b of the crankshaft 18 via a bearing 40 (see FIG. 2) at the upper end, and extends outward in the radial direction of the axis of the crankshaft 18. In FIG. 1, the connection member 30 extends in the vertical direction. Each of the first and second link members 34 and 36 has a first pivot 42 having one axis parallel to the axis of the crankshaft 18 as a common pivot, and the lower end of the connection member 32 via the pivot. It is pivotally attached to. In the illustrated example, as shown in FIG. 4, as the second link member 36, a pair of link members 36 that are spaced apart from each other in the thickness direction are used. Each second link member 36 is located on both ends of the pivot on the pivot 42, and both ends of the first link member 34 and the connection member 32 are located between the pair of link members 36.

  As clearly shown in FIG. 1, the first link member 34 and the pair of second link members 36 respectively extend in directions away from each other on both sides of the connection member 32. A connector 46 having a second pivot 44 is provided at the other end of the first link member 34.

  The connection tool 46 includes a first slider 46a that includes one end including the other end of the first link member 34 and slidably receives one half of the width of the first link member 34, and a pivot 44 on the slider. And a connected second slider 46b. The step between the half and the other half functions as a stopper for the second slider 46b. The second slider 46b is movable in the second direction, that is, in the left-right direction (lateral direction) as viewed in FIG. 1, along the guide portion 48 formed on the upper frame 12c in the vicinity of the gear case 14. The second pivot 44 is disposed along the first direction perpendicular to the second direction. The first slider 46 a coupled to the second slider 46 b via the pivot 44 is rotatable around the pivot 44 within the guide portion 48 and is movable in the longitudinal direction of the first link member 34. It is.

  The other end of the second link member 36 is coupled to a bearing portion 50 formed on the upper frame 12 c at a position facing the guide portion 48 via a third pivot 52. The bearing part 50 supports the third pivot 52 as a support mechanism for the third pivot 52 so that the position of the third pivot 52 cannot be adjusted. Thereby, the pivot 52 is held along the first direction. The third pivot 52 is coupled to the other end of each pair of second link members 36 at both ends protruding from both sides of the support mechanism 50.

  As a result, the movement of the corresponding first pivot 42 provided at the one end of each pair of second link members 36 is an arc whose radius is the distance between the pivots 42 and 52 around the third pivot 52. Regulated by the trajectory.

  As a result, when the crankshaft 18 is driven and rotated, the first pivot 42 reciprocates vertically along the circular arc locus. As the pivot 42 reciprocates, the first link member 34 swings up and down as a whole around the pivot 44.

  As in the prior art, the swing movement of the first link member 34 is the third link connected to the first link member 34 via the fourth pivot 54 between the first pivot 42 and the pivot 44. This is transmitted to the member 38 as a reciprocating motion in the vertical direction. Further, the reciprocating motion of the third link member 38 is transmitted to the slide 22 as a reciprocating motion in the vertical direction via the connecting rod 24 connected to the link member via the fifth pivot 56.

  FIG. 5A shows an example in which the first link member 34 is maintained in a horizontal posture along the second direction with the eccentric shaft portion 18b of the crankshaft 18 positioned immediately below the main shaft portion 18a. Indicates. In this case, the slide 22 is positioned at the bottom dead center, and the height position of the bottom dead center does not change regardless of the position of the connector 46, that is, the guide portion 48 of the pivot 44.

  On the other hand, FIGS. 5B and 5C show a state in which the eccentric shaft portion 18b of the crankshaft 18 is located immediately above the main shaft portion 18a and a state in which the slide 22 is at the top dead center position. FIG. 5B shows a state when the second pivot 44 is at a position farthest from the first pivot 42, and FIG. 5C shows that the second pivot 44 is the first pivot 42. The state when it is in the position closest to is shown.

  With reference to the bottom dead center position of the slide 22 shown in FIG. 5A, the height S1 of the top dead center position shown in FIG. 5B is the height S2 of the top dead center position shown in FIG. taller than. The height S (S1, S2) of the top dead center position decreases as the pivot 44 approaches the pivot 42 from the position shown in FIG. 8B toward the position shown in FIG. 8C. Therefore, as will be described later, the stroke length of the slide 22 can be increased or decreased according to the rotation operation of the operation shaft 64 of the adjustment mechanism 58.

  An adjustment mechanism 58 for adjusting the stroke described above is provided in association with each connector 46. Each adjustment mechanism 58 is screwed into the male screw member 60 and a male screw member 60 disposed so as to protrude outward from the second slider 46b through the gear case 14 so as to extend in the left-right direction as viewed in FIG. And an external gear 62. The external gear 62 is prevented from moving in the axial direction of the male screw member 60 between the upper frame 12 c and the gear case 14. The external gear 62 meshes with a gear 66 formed at one end of a rotation operation shaft 64 serving as a rotation operation member.

  Accordingly, by rotating the rotation operation member 64, the male screw member 60 can be displaced in the axial direction thereof, so that the connector 46 provided with the second pivot 44 is moved along the guide portion 48. Can do. Further, the external thread member 60 and the external gear 62 meshing with the external thread portion act as a positioning device for the connector 46.

  From this, as in the conventional press machine, the position of the second pivot 44 of the connector 46 can be adjusted by rotating the rotation operation member 64, so that the top dead center of the slide 22 can be adjusted. The point position can be adjusted between the height positions shown in FIGS. 5 (b) and 5 (c).

  Instead of the example shown in FIGS. 5a to 5c, the eccentric shaft portion 18b of the crankshaft 18 is in a state of being positioned immediately above the main shaft portion 18a, for example, and the first link member 34 and the second link member 36 are illustrated in FIG. As shown in 5a, the bottom dead center position of the slide 22 can be adjusted by moving the second pivot 44 in the second direction by the operation of the adjusting mechanism 58 in the state of linear alignment.

  According to the press 10, as described above, the third pivot shaft 52 is only fixedly supported on the frame 12 in a non-adjustable manner by the support mechanism 50 that is a bearing portion. Moreover, since it is not necessary to provide the opposing projections (102a, 102a) in the frame 12 as in the conventional pair of guides, the configuration can be simplified. Therefore, the space in the upper frame 12c can be effectively used, and the structure of the press machine 10 is simplified.

  Further, according to the press machine 10, since the three sets of motion conversion mechanisms 30 can be connected to the common slide 22, the reciprocating motion of the slides is further stabilized.

  In the above-described example, the third pivot 52 provided at the other end of the second link member 36 that defines the movement locus of the first pivot as an arcuate locus is fixedly and non-adjustable by the bearing portion 50 by the upper frame. 12c. Instead, for example, in order to be able to adjust the radius of the arcuate trajectory, the attachment position of the third pivot 52 with respect to the second link member 36 is fixed so as to be adjustable in the lateral direction which is the second direction. be able to.

  In the above-described example, no balance weight is provided, but the present invention can be applied to a press machine provided with a balance weight. Further, if necessary, four or more motion conversion mechanisms 30 can be arranged in parallel in the axial direction of the crankshaft 18. However, on the contrary, two sets or one set of motion conversion mechanisms 30 can be applied to the present invention.

  As the adjustment mechanism 58, in place of the above-described example, various other configurations such as an internal gear, a toothed wheel, a sprocket, a timing pulley, and a worm wheel, a worm screw, a small gear, a ratchet, a chain, a timing pulley, a timing belt, and the like The adjusting mechanism 58 can be constituted by elements.

  The present invention is not limited to the above embodiments, and can be variously modified within the scope of the claims.

DESCRIPTION OF SYMBOLS 10 Press machine 12 Frame 18 Crankshaft 18a Main shaft part 18b Eccentric shaft part 22 Slide 30 Motion conversion mechanism 32 Connection member 34 1st link member 36 2nd link member 38 3rd link member 42 1st axis 44 2nd The pivot 46 of the coupling 46a The first slider 46b The second slider 50 The bearing portion (support mechanism)
52 Third Pivot 54 Fourth Pivot 58 Adjustment Mechanism 60 Male Thread Member 62 External Gear 64 Rotation Operation Member (Operation Unit)

Claims (7)

  A frame, a crankshaft supported by the frame so as to be rotatable about an axis extending in a first direction, and a connection member having one end connected to an eccentric shaft portion of the crankshaft and extending radially outward of the axis And one end of each of the first and second link members is connected to the other end of the connection member via the pivot with the first pivot extending in the first direction as a common pivot. The first and second link members respectively extending in directions away from each other on both sides of the connection member, and the first link member movably disposed in the longitudinal direction of the first link member. And a second pivot that extends in a direction and has a second pivot that allows the first link member to oscillate; and a position of the pivot that is perpendicular to the first direction. Adjustable in the second direction An adjustment mechanism that supports the frame, a third pivot that is provided at the other end of the second link member and extends in the first direction, a support mechanism that fixedly supports the pivot on the frame, One end is connected to the first link member via a fourth pivot extending in the first direction at an intermediate position between both ends of the first link member, and the other end is connected to a slide holding the mold. And a third link member disposed along a third direction perpendicular to the first and second directions.   2. The press machine according to claim 1, wherein the second link member restricts the movement of the first pivot to a circular arc movement having a radius from the pivot to the first pivot about the third pivot. .   As the second link member, a pair of second link members are arranged at an interval in the thickness direction of the link member, and the third pivot of the other end of the pair of second link members is used. The support mechanism to support is a bearing portion formed to project between the other ends of the pair of second link members from the inner surface of the frame facing the other ends of the pair of second link members. The press machine according to claim 1, wherein each of the other ends of the pair of second link members is pivotally attached to each of the protruding ends via the third pivot.   The connection member, the first and second link members, and the third link member constitute a set of motion conversion mechanisms, and a plurality of the motion conversion mechanisms are spaced from each other in the axial direction of the crankshaft. The third link member of each of the motion conversion mechanisms is arranged in parallel and is connected to the slide via the fifth pivot with the slide serving as a common slide. Press machine.   The connector includes a first slider disposed on the frame movably in the second direction to slidably receive the other end of the first link member, and a second slider on the slider. The press machine according to claim 1, further comprising a second slider coupled via a pivot and receiving the first slider so as to be movable in the second direction.   The press machine according to claim 5, wherein the adjustment mechanism includes a positioning device that positions the second slider so as to be adjustable in the second direction.   The positioning device includes a male screw portion provided on the second slider, an external gear screwed into the male screw portion and restricted in the axial direction of the male screw material, and an external tooth of the gear. The press machine according to claim 6, further comprising: a rotary operation member that meshes and displaces the male screw portion in an axial direction of the male screw portion via the external gear.

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