JP4973727B2 - Press machine - Google Patents

Description

Background of the Invention

  The present invention relates to a press machine.

  In the press machine, the slide is moved up and down, and the workpiece is sandwiched between the upper mold fixed to the lower surface of the slide and the lower mold disposed below the slide to perform the press.

  An example of such a press machine is described in Patent Document 1 below. FIG. 1 shows a press machine of Patent Document 1. As shown in FIG. 1, the driving force of the servo motor 51 is transmitted to the slide 61 via the pinion 53, the main gear 55, the crank shaft 57, and the connecting rod 59. The large diameter portion of the connecting rod 59 is connected to the eccentric portion of the crankshaft 57, and the lower end portion of the connecting rod 59 is connected to the slide 61. Thereby, the rotational movement of the servo motor 51 is converted into the up-and-down movement of the slide 61.

Japanese Patent Laid-Open No. 2004-17089 “Slide Drive Device for Press Machine”

  However, firstly, it is desired to further reduce the size of the entire press machine and improve the degree of freedom of arrangement of power transmission members such as a servo motor and a gear.

  Second, if the servo motor fails, the press operation must be interrupted in order to repair the servo motor or replace the servo motor. In this regard, it is desirable that the press operation can be continued even if the servo motor fails.

Thirdly, Patent Document 1 describes that the main gears driven by two servomotors are engaged with each other, but there is play between the tooth surfaces in the meshing portion of the main gears. During the press operation, the position of the main gear tends to fluctuate by the amount of play.
Therefore, for example, as shown in FIG. 2, the slide 61 frequently tilts during the press operation. This is because the posture of the slide 61 changes due to a change in the relative rotational position of the main gear 55.

Conventionally, as indicated by the arrow a in FIG. 2, the counter balancer always pushes the slide vertically upward to cancel gravity, but the counter balancer does not function to eliminate the inclination of the slide 61. . Therefore, it is desired to prevent such an inclination of the slide 61.

Summary of invention

The present invention has been made to solve the above problems.
That is, a first object of the present invention is to provide a press machine that can be miniaturized and can improve the degree of freedom of arrangement of a drive motor and the like.
A second object of the present invention is to provide a press machine that can continue pressing even when a drive motor fails and can freely change the molding force of the press machine.
A third object of the present invention is to provide a press machine that can prevent the slide from being frequently tilted during operation of the press machine.

  According to the present invention, in order to achieve the third object, a driving motor for performing pressing, a first gear group and a second gear group to which a rotational driving force of the driving motor is transmitted, and the first gear. In a press machine, comprising: a conversion mechanism that converts a gear rotational movement in the group and the second gear group into a reciprocating movement; and a slide that is connected to the conversion mechanism and reciprocates, and presses with a die fixed to the slide The first gear group has a pair of main gears connected by the first connecting portion so that the rotation centers are the same, and the second gear group has the second connection so that the rotation centers are the same. A pair of main gears connected to each other, one main gear of the first gear group meshes with one main gear of the second gear group, and the other main gear of the first gear group is the second gear. Mesh with the other main gear of the group One main gear of the first gear group is shifted by a predetermined angle with respect to the other main gear of the first gear group by the first connecting portion. It is connected to the other main gear, so that the teeth of one main gear of the first gear group come into contact with the teeth of one gear of the second gear group in the rotational direction, and the other main gear of the first gear group There is provided a press machine characterized in that the gear teeth are kept in contact with the other gear teeth of the second gear group in the rotational direction.

Conventionally, when the main gears are engaged with each other, there is play in the rotation direction between the tooth surfaces at the engagement portions of the main gears, so the position of the main gear is not fixed, and the slide frequently tilts during operation of the press machine. End up.
In contrast, in the above configuration, one main gear of the first gear group is shifted by the first connecting portion so that the rotational direction position is shifted by a predetermined angle with respect to the other main gear of the first gear group. By connecting to the other main gear of one group, the teeth of one main gear of the first gear group contact the teeth of one main gear of the second gear group in the rotational direction, and the other gear of the first gear group The state where the teeth of the main gear are in contact with the teeth of the other main gear of the second gear group in the rotational direction is maintained.
Thereby, although there is play between the tooth surfaces at the meshing portion of the main gears, the state where the main gear tooth surfaces are in stable contact with each other can be maintained. Therefore, the rotational direction position of the main gear is always determined. In other words, the rotational position of the main gear does not change by the amount of play. Therefore, it is possible to prevent the slide from being frequently inclined during the operation of the press machine.

  The predetermined angle is larger than 0 degree, and is preferably an angle corresponding to the play amount of the meshing portion of the main gear belonging to the first gear group and the main gear belonging to the second gear group. As a result, the tooth surface of the main gear of the first gear group does not preload the tooth surface of the main gear of the second gear group in the rotational direction. It is possible to avoid the occurrence of torsion in the portion and the second connecting portion.

  According to the present invention, in order to achieve the third object, a drive motor for performing pressing, a first gear group and a second gear group to which the rotational driving force of the drive motor is transmitted, A press that includes a conversion mechanism that converts the gear rotational movement in the first gear group and the second gear group into a reciprocating movement, and a slide that is connected to the conversion mechanism and that reciprocates, and presses with a die fixed to the slide. In the machine, each of the first gear group and the second gear group has a pair of main gears, one main gear of the first gear group meshes with one main gear of the second gear group, and the first gear group The other main gear meshes with the other main gear of the second gear group, and further includes a first meshing gear group and a second meshing gear group, and the first meshing gear group has a center of rotation. The first to be the same The second meshing gear group has a pair of meshing gears coupled by the second meshing gear coupling unit so that the rotation center is the same, and the pair of meshing gears coupled by the coupled gear coupling unit. One meshing gear of the first meshing gear group meshes directly or indirectly with one main gear of the first gear group, and the other meshing gear of the first meshing gear group is the other main gear of the first gear group. One meshing gear of the second meshing gear group meshes directly or indirectly with one main gear of the second gear group, and the other meshing gear group of the second meshing gear group. The meshing gear meshes directly or indirectly with the other main gear of the second gear group, and one meshing gear of the first meshing gear group is connected to the other meshing gear of the first meshing gear group. So that the rotational direction position is shifted by a predetermined angle. It is connected to the other meshing gear of the first meshing gear group by the first meshing gear coupling part, so that the teeth of one main gear of the first gear group become the teeth of one gear of the second gear group. A press that is in contact with the rotation direction and maintains a state in which the teeth of the other main gear of the first gear group contact the teeth of the other gear of the second gear group in the rotation direction. A machine is provided.

In the above-described configuration, the first meshing gear coupling portion causes the first meshing gear coupling portion to shift one meshing gear of the first meshing gear group so that the rotational direction position is shifted by a predetermined angle with respect to the other meshing gear of the first meshing gear group. By connecting to the other meshing gear of one meshing gear group, the teeth of one main gear of the first gear group contact the teeth of one main gear of the second gear group in the rotational direction, and The state in which the teeth of the other main gear contact the teeth of the other main gear of the second gear group in the rotational direction is maintained.
Thereby, although there is play between the tooth surfaces at the meshing portion of the main gears, the state where the main gear tooth surfaces are in stable contact with each other can be maintained. Therefore, the rotational direction position of the main gear is always determined. In other words, the rotational position of the main gear does not change by the amount of play. Therefore, it is possible to prevent the slide from being frequently inclined during the operation of the press machine.

  The predetermined angle is not less than 0 degrees, and is preferably an angle corresponding to the play amount of the meshing portion of the main gear belonging to the first gear group and the main gear belonging to the second gear group. As a result, the tooth surface of the main gear of the first gear group does not preload the tooth surface of the main gear of the second gear group in the rotational direction. Generation of torsion in the gear connecting portion and the second meshing gear connecting portion can be avoided.

According to the present invention described above, firstly, the size can be reduced and the degree of freedom of arrangement of the drive motor and the like can be improved, and second, even when the drive motor fails, the press can be continued and the press The molding force of the machine can be changed freely, and thirdly, it is possible to prevent the slide from tilting frequently during operation of the press machine.

It is a figure which shows the structure of the press machine of patent document 1. FIG. It is a figure which shows the inclination of the slide in the past. It is front sectional drawing of the press machine by 1st Embodiment of this invention. It is a BB line arrow directional view of Drawing 3A. It is front sectional drawing of the press machine by 2nd Embodiment of this invention. It is a BB line arrow directional view of Drawing 4A. It is side surface sectional drawing of the press machine by 3rd Embodiment of this invention. It is a BB arrow directional view of Drawing 5A. It is a figure which shows another structural example of 3rd Embodiment of this invention. It is side surface sectional drawing which shows another structural example of 3rd Embodiment of this invention. It is a BB line arrow directional view of Drawing 7A. It is a perspective view which shows the main gear which mutually meshes | engages. It is a figure for demonstrating the principle of 4th Embodiment. It is a front view which shows the structure of a phase adjustment mechanism. It is an expansion perspective view of the broken-line part in FIG. 10A. It is a figure for demonstrating the twist which generate | occur | produces in a rotating shaft. It is a figure which shows the other structural example 1 by 4th Embodiment. It is a figure which shows the other structural example 2 by 4th Embodiment. It is side surface sectional drawing of the press machine which shows the other structural example 3 by 4th Embodiment. It is a BB arrow directional view of FIG. 14A. It is an aa arrow directional view of FIG. 14B. It is a bb line arrow line view of FIG. 14B. It is crown front sectional drawing of the Example of this invention. It is sectional drawing in the AA of FIG. It is sectional drawing in the BB line of FIG.

  A preferred embodiment of the present invention will be described with reference to the drawings.

[First Embodiment]
3A and 3B show the configuration of the press machine according to the first embodiment of the present invention. 3A is a front sectional view of the press machine, and FIG. 3B is a view taken along the line BB in FIG. 3A.
As shown in FIGS. 3A and 3B, the press machine reciprocates the rotational movement of the drive motor 2 for performing the press, the main gear 3 that rotates by the rotational driving force of the drive motor 2, and the rotation of the main gear 3. A conversion mechanism 5 that converts motion is provided, and a slide 7 that is connected to the conversion mechanism 5 and reciprocates.

  The press machine rotatably supports the rotary shaft 6 coupled to the main gear 3 and incorporates a conversion mechanism 5 into a frame 9, and a driving force of a drive motor 2 provided outside the frame 9 to the main gear 3. A transmission gear 11 for transmission. At least a part of the main gear 3 is positioned outside the frame 9 so that the main gear 3 meshes with the transmission gear 11.

In the example of FIGS. 3A and 3B, the drive motor 2 and the transmission gear 11 fixed to the output shaft of the drive motor 2 are disposed above the frame 9 (for example, the upper surface of the frame 9). 3 protrudes upward from the frame 9. The upper part of the main gear 3 meshes with the transmission gear 11 above the frame 9.
In this configuration, since the entire main gear 3 is not housed in the frame 9, the frame 9 can be reduced in size. In addition, since the drive motor 2 is arranged outside the frame 9 instead of inside the frame 9, the degree of freedom of arrangement of the drive motor 2 and the transmission gear 11 is improved.

  The drive motor 2 is a servo motor, for example, but may be another appropriate motor. The transmission gear 11 is, for example, a pinion fixed to the output shaft of the drive motor 2, but may be a pinion fixed to the output shaft of the speed reducer that transmits the rotational motion of the drive motor 2. The frame 9 may be a crown defined by JIS, but may be another appropriate one. The conversion mechanism 5 is, for example, a four-bar linkage mechanism, but may be another appropriate mechanism.

Further, a configuration in which one main gear 3 is arranged for one rotating shaft 6 may be employed.
In 1st Embodiment, it is good also as a structure which provided the intermediate | middle board part 9a mentioned later.

  Further, the main gear 3 and a part of the conversion mechanism 5 may be integrated or combined. In this case, a part of the conversion mechanism 5 may be an eccentric ring part of an eccentric link mechanism or a four-bar link mechanism, for example. In this case, the main gear 3 may be configured to freely rotate with respect to the rotating shaft 6, and the rotating shaft 6 may be fixed to the frame 9. The rotating shaft 6 that can rotate with respect to the main gear 3 and the rotating shaft 6 that is coupled to the main gear 3 and cannot rotate with respect to the main gear 3 are both shafts that support the main gear 3. Constitute.

[Second Embodiment]
4A and 4B show a configuration example of a press machine according to the second embodiment of the present invention. 4A is a front cross-sectional view of the press machine, and FIG. 4B is a view taken along line BB in FIG. 4A.
In the following, a configuration different from the first embodiment will be described. Other configurations of the second embodiment may be the same as those of the first embodiment.

In the second embodiment, the main gear 3 is disposed outside the frame 9. For example, as shown in FIGS. 4A and 4B, the main gear 3 is disposed outside the frame 9 on both sides of the frame 9.
With this configuration, it is easy to replace the main gear 3 and the maintainability of the main gear 3 is improved. That is, when removing the main gear 3, it is not necessary to remove the rotating shaft 6 supported at both ends by the frame 9 from the frame 9, and it is not necessary to remove the conversion mechanism 5 having a complicated configuration from the frame 9 at the same time. Accordingly, the replacement of the main gear 3 is facilitated, and the maintainability of the main gear 3 is greatly improved.

Preferably, the main gear 3 and the rotating shaft 6 are configured to be separable from each other. Thereby, the exchange of the main gear 3 becomes easier.
In the second embodiment, the intermediate plate portion 9a is provided. However, the intermediate plate portion 9a may be omitted. A detailed description of the intermediate plate portion 9a will be described later with reference to FIG.

[Third Embodiment]
5A and 5B show a configuration example of a press machine according to the third embodiment of the present invention. FIG. 5A is a side cross-sectional view of the press machine, and FIG. 5B is a BB line arrow view of FIG. 5A.
In the following, a configuration different from the second embodiment will be described. Other configurations of the third embodiment may be the same as those of the second embodiment.

In the third embodiment, a plurality of motor attachment portions 12 to which the drive motor 2 can be attached and detached are provided, and the rotational driving force of the drive motor 2 attached to each motor attachment portion 12 can be transmitted to the conversion mechanism 5. ing.
In order to make the drive motor 2 detachable from the press machine, for example, the following configuration can be adopted. A motor mounting member 15 is fixed to the upper surface of the frame 9 of the press machine, and a plurality of motor mounting portions 12 are provided on the motor mounting member 15.
In order to fix the drive motor 2 to the motor mounting portion 12 in a detachable manner, for example, the motor mounting member 15 is provided with a mounting hole 12 in which a female screw is cut as the motor mounting portion 12, while the drive motor 2. A flange portion 17 is formed at one end in the axial direction, and a through hole 18 is provided in the flange portion 17.
Then, the screw 19 is passed through the through hole 18 and fastened to the mounting hole 12. In this way, the drive motor 2 may be detachable from the motor mounting portion 12. In this case, one motor mounting portion 12 may be a plurality of the mounting holes 12, and a plurality of through holes 18 may be formed in each drive motor 2 corresponding to the mounting holes 12.
The configuration of the motor mounting portion 12 described above is an example, and the motor mounting portion can be configured by other appropriate means. For example, the motor mounting portion may have a configuration in which the input shaft of the transmission gear 11 is provided. In this case, the input shaft of the transmission gear 11 and the output shaft of the drive motor 2 may be connectable by a coupling member.

With the above configuration, the number of drive motors 2 attached to the press machine can be changed. Therefore, the press molding force can be changed according to the type of workpiece. For example, four drive motors 2 indicated by broken lines in FIG. 5B can be added to increase the press molding force.
Further, in addition to the number of drive motors 2 for obtaining the required press molding force, one or several extra drive motors 2 can be attached to the motor attachment portion 12. For example, as shown by a broken line in FIG. 5B, four extra drive motors 2 can be added in advance. Thereby, even if one or several drive motors 2 break down, the press can be continued in that state.

FIG. 6 is a diagram showing another configuration example of the third embodiment, and shows a configuration obtained by changing the configuration of FIG. 5B.
In this configuration example, a plurality of drive motors 2a and 2b having different driving capabilities can be attached to and detached from the press machine. For example, a plurality of drive motors having different dimensions and shapes are used, and the dimensions and shapes may be the same.

For example, not only the drive motor 2 having the dimensions shown in FIG. 5B (indicated by 2a in FIG. 6) but also a drive motor 2b larger than the drive motor 2 shown in FIG. For this purpose, for example, the shape and outer diameter of the flange portion 17 of the drive motors 2a and 2b described above can be changed from those of the small drive motor 2a and the large drive motor 2b. While making it the same between the large drive motor 2b, the positions of the plurality of through holes 18 formed in each flange portion 17 are made the same between the small drive motor 2a and the large drive motor 2b. Thereby, either the small drive motor 2a or the large drive motor 2b may be attachable to the same mounting hole 12.

With this configuration, servo motors having different driving capabilities can be attached to the press machine in a replaceable manner. Therefore, the press molding force can be changed according to the type of workpiece.
The drive motor may be replaced together with the transmission gear 11, or the input shaft of the transmission gear 11 is rotatably supported by the frame 9, and the output shaft of the replacement drive motor is coupled to the input shaft. You may make it couple | bond by.

7A and 7B are diagrams showing still another configuration example of the third embodiment. 7A is a side cross-sectional view of the press machine, and FIG. 7B is a view taken along line BB in FIG. 7A.
In this example, a plurality of speed reducers 21 are fixed to the upper surface of the frame 9. For simplicity, only one speed reducer 21 is shown in FIG. 7A. A pinion 11 that meshes with the main gear 3 is fixed to the output shaft of the speed reducer 21. The reduction gear 21 is provided with a plurality of input shafts, and the output shaft of the drive motor 2 is detachably coupled to each of these input shafts.
With this configuration, the number of drive motors 2 coupled to the input shaft of the speed reducer 21 can be changed. For example, a drive motor 2 indicated by a broken line in FIG. 7B can be added. Therefore, the press molding force can be changed according to the type of workpiece.

Moreover, the reduction gear 21 of the same reduction ratio can also be attached or detached to the reduction gear attachment part (not shown) of the same location provided in the flame | frame 9 (for example, frame 9 upper surface). Also in this case, the pinion 11 fixed to the output shaft of the speed reducer 21 attached to the upper surface of the frame 9 meshes with the main gear 3, and the output shaft of the drive motor 2 is coupled to the input shaft of this speed reducer. Good. Also in this case, each speed reducer is provided with a plurality of input shafts, and the output shaft of the drive motor 2 may be detachably coupled to each of these input shafts.
Thereby, even if the speed reducer 21 breaks down, it can be easily replaced. One or a plurality of such reduction gear attachments may be provided. Such a reduction gear mounting portion may be similar to the motor mounting portion 12 described above. That is, for example, the same configuration as the mounting hole 12 and the motor mounting member 15 may be provided on the frame 9 side, and the same configuration as the flange portion 17 and the through hole 18 may be provided on the reduction gear 21 side. However, the present invention is not limited to this, and the speed reducer mounting portion may be provided by other appropriate means.

The reduction gears 21 having different reduction ratios can be detachably attached to reduction gear attachment portions (not shown) at the same location provided on the frame 9 (for example, the upper surface of the frame 9). The different speed reducers 21 may be the same, for example, in any of the dimensions and shapes.
Also in this case, the pinion 11 fixed to the output shaft of the speed reducer 21 attached to the upper surface of the frame 9 meshes with the main gear 3, and the output shaft of the drive motor 2 is coupled to the input shaft of this speed reducer. Good. Also in this case, each speed reducer is provided with a plurality of input shafts, and the output shaft of the drive motor 2 may be detachably coupled to each of these input shafts. Moreover, you may provide one such speed reducer attachment part, and may provide two or more.
Such a reduction gear mounting portion may be similar to the motor mounting portion 12 described above. That is, for example, the same configuration as the mounting hole 12 and the motor mounting member 15 may be provided on the frame 9 side, and the same configuration as the flange portion 17 and the through hole 18 may be provided on the reduction gear 21 side. However, the present invention is not limited to this, and the speed reducer mounting portion may be provided by other appropriate means.

As described above, when the speed reducer 21 having a different size or shape is detachable from the frame 9, the mounting position of the drive motor 2 connected to the speed reducer 21 changes according to the size or shape of the speed reducer 21 attached. Will do.
Although this change in the attachment position can be dealt with by a general method, an example for dealing with the change in the attachment position will be briefly described. An arrow C in FIG. 7B shows an enlarged part.
A plate 51 to be attached to the upper surface of the frame 9 is fixed to the bottom surface of the drive motor 2, a screw hole (not shown) is provided on the upper surface of the frame 9, and one through long hole is provided for each screw hole. 53 is provided on the plate 51. Then, a screw having a screw head 55 of a size that cannot pass through the through long hole 53 is passed through the through long hole 53, this screw is screwed into the screw hole of the frame 9, and the drive motor 2 is attached to the frame 9.
In this case, since the through-hole 53 is long in the left-right direction of FIG. 7B, the drive motor 2 can be fixed so that the position can be adjusted in the left-right direction. On the other hand, the change in the mounting position in the vertical direction can be dealt with such that the plate 51 having a different thickness can be detachably fixed to the bottom surface of the drive motor 2 with a screw or the like.

In the third embodiment, the motor attachment portion 12 and the reduction gear attachment portion may be provided at other locations of the press machine.
In the third embodiment, the intermediate plate portion 9a is provided. However, the intermediate plate portion 9a may be omitted. A detailed description of the intermediate plate portion 9a will be described later with reference to FIG.

[Fourth Embodiment]
A fourth embodiment of the present invention will be described. The press machine by 4th Embodiment may be the same as 2nd Embodiment except the point demonstrated below.
FIG. 8 is a perspective view showing a state where the main gears are engaged with each other as in the configuration of the second embodiment. In this figure, the first gear group is a pair of main gears 3-1 and 3-2 connected by a first connecting portion (rotary shaft 6-1 in the example of the drawing) so that the rotation centers are the same. Have The second gear group has a pair of main gears 3-3 and 3-4 connected by a second connecting portion (in the example of the drawing, a rotating shaft 6-2) so that the rotation centers are the same.
As shown in this figure, one main gear 3-1 of the first gear group meshes with one main gear 3-3 of the second gear group, and the other main gear 3-2 of the first gear group. Meshes with the other main gear 3-4 of the second gear group. In addition, due to the meshing of the main gears, when a plurality of main gears are used, it is possible to prevent left and right misalignments and phase shifts that cause damage to slides and other members.

According to the fourth embodiment, one main gear 3-1 of the first gear group rotates so that its rotational direction position is shifted by a predetermined angle with respect to the other main gear 3-2 of the first gear group. The shaft 6-1 is connected to the other main gear 3-2 of the first gear group. As a result, the teeth of one main gear 3-1 of the first gear group come into contact with the teeth of one main gear 3-3 of the second gear group in the rotational direction, and the other main gear 3 of the first gear group. -2 teeth are kept in contact with the teeth of the other main gear 3-4 of the second gear group in the rotational direction.
Therefore, although there is play in the rotation direction between the tooth surfaces at the meshing portion of the main gears, the state where the main gear tooth surfaces are in stable contact can be maintained even during operation of the press machine.
In the present application, the rotation direction is a concept including not only the rotation direction actually driven by the drive motor 2 but also the direction opposite to the rotation direction.

The principle of the fourth embodiment will be described in detail with reference to FIG.
(1) In FIG. 9, it is assumed that the main gears 3-3 and 3-4 of the second gear group and the rotation shaft 6-2 are fixed in the rotation direction. This fixed position is set as a reference position. At this time, the main gears 3-3 and 3-4 and the rotation shaft 6-2 are coupled so that the phase in the rotation direction does not change. The main gears 3-3 and 3-4 may have the same shape and dimensions, and may be coupled to the rotation shaft 6-2 so that the phases in the rotation direction are the same.
(2) With respect to the main gear 3-4 fixed at the reference position, the main gear 3-2 of the first gear group is rotated in the direction indicated by the arrow a, and the gear teeth are aligned at the position indicated by (A). The main gear 3-2 is fixed with respect to the reference position in a contact state.
At this time, since the main gear 3-2 is fixed to the rotating shaft 6-1, the rotating shaft 6-1 also rotates in the direction indicated by the arrow b and is fixed with respect to the reference position. The main gears 3-1 and 3-2 may have the same shape and dimensions.
(3) Next, the main gear 3-1 of the first gear group is fixed to the rotating shaft 6-1. This fixing is performed by adjusting the rotational phase of the main gear 3-1. Specifically, the main gear 3-1 is rotated in the direction indicated by the arrow c with respect to the rotating shaft 6-1 fixed at the reference position, and the gear teeth come into contact with each other at the position indicated by (B). It will be in the state. In this state, the main gear 3-1 is fixed to the rotating shaft 6-1, so that the main gears 3-1, 3-2, 3-3, 3-4 all have a phase relationship with each other without play in the rotation direction. It becomes a fixed state. In this state, the rotational direction position of the main gear 3-1 is shifted from the main gear 3-2 by a predetermined angle.

In (3) above, the phase in the relative rotational direction of the main gear 3-1 of the first gear group can be adjusted by the phase adjustment mechanism. 10A and 10B show the configuration of the phase adjustment mechanism 27 which is one of various possible configurations of the phase adjustment mechanism, and FIG. 10B is an enlarged perspective view of the broken line portion in FIG. 10A. Note that the directions of arrows a, b, and c in FIGS. 10A and 10B correspond to the directions of arrows a, b, and c in FIG. 9, respectively, and the portions indicated by (B) in FIG. ).
As shown in FIG. 10B, the phase adjustment mechanism 27 includes a wedge 29, a rotating shaft 6-1 having a first notch 31, and a main gear 3-1 having a second notch 33. Is done.

  The wedge 29 has a cross-sectional area perpendicular to the axial direction that gradually increases from one end to the other end. In the example of FIG. 10B, the wedge 29 has a rectangular cross section perpendicular to the axial direction thereof, and the lengths of the sides 29a and 29b gradually increase from one end side to the other end side with an angle of, for example, 1 degree. It has become. This angle may be an angle other than 1 degree.

  The first cutout portion 31 is formed so as to penetrate the rotating shaft 6-1 at a joint portion of the rotating shaft 6-1 with the main gear 3-1. Further, a space formed by the first cutout portion 31 and recessed inward in the radial direction of the rotating shaft 6-1 is open to the main gear 3-1 side. This space extends by a predetermined length in the circumferential direction of the rotating shaft 6-1. The amount of depression in this space, that is, the cross-sectional area of this space parallel to the radial direction of the rotating shaft 6-1 is substantially the same over the circumferential direction of the rotating shaft 6-1.

  The second notch 33 is formed so as to penetrate the main gear 3-1 at a portion where the main gear 3-1 is connected to the rotating shaft 6-1. Further, a space formed by the second cutout portion 33 and recessed toward the outside in the radial direction of the main gear 3-1 is open to the rotating shaft 6-1 side. This space extends by a predetermined length in the circumferential direction of the main gear 3-1. The amount of depression in this space, that is, the sectional area of this space parallel to the radial direction of the main gear 3-1 is substantially the same over the circumferential direction of the main gear 3-1.

  The space formed by the first cutout portion 31 and the space formed by the second cutout portion 33 are caused to partially overlap in the radial direction of the rotating shaft 6-1. The wedge 29 is passed through this overlapping space. When the wedge 29 is pushed in the direction of the arrow d in FIG. 10B, the rotating shaft 6-1 is fixed at the reference position, so that the main gear 3-1 can be rotated in the direction of the arrow c in FIG. 10B. At that time, the rotation amount of the main gear 3-1 is determined by the pushing amount of the wedge 29.

  In this way, the tooth of one main gear 3-1 of the first gear group contacts the tooth of one main gear 3-3 of the second gear group in the rotational direction, and the other main gear of the first gear group. The state in which the teeth of 3-2 are in contact with the teeth of the other main gear 3-4 of the second gear group in the rotational direction can be maintained during the operation of the press machine.

In order to maintain this state, the tooth surfaces of the main gears 3-1 and 3-2 of the first gear group are preloaded in the rotational direction on the tooth surfaces of the main gears 3-3 and 3-4 of the second gear group ( A pressing force may be applied. In this case, as shown in FIG. 9, from the state in which the teeth of one main gear 3-1 of the first gear group simply contact the teeth of one main gear 3-3 of the second gear group in the rotational direction, Pushing the wedge 29 in the direction indicated by the arrow d in FIG. 10B causes elastic deformation in each part of the main gear and the rotating shaft, and the gear tooth surface of the mating member is in each contact part shown in FIGS. 9A and 9B. A preload is applied so that
For example, as shown in FIG. 11, the rotating shaft 6-1 serving as a torsion beam is elastically deformed in a direction to be twisted by pushing the wedge 29, and a deflection angle θ is generated. At this time, the rotating shaft 6-2 is similarly elastically deformed.

  On the other hand, the tooth surfaces of the main gears 3-1 and 3-2 of the first gear group do not apply a preload in the rotational direction to the tooth surfaces of the main gears 3-3 and 3-4 of the second gear group. You may maintain the said state. In this case, the teeth of one main gear 3-1 of the first gear group are simply in contact with the teeth of one main gear 3-3 of the second gear group in the rotational direction. That is, it is possible to avoid the occurrence of torsion in the rotating shafts 6-1 and 6-2.

In other words, the predetermined angle by which the main gear 3-1 is shifted in the rotational direction with respect to the main gear 3-2 can be adjusted by using the phase adjustment mechanism 27.
The predetermined angle is larger than 0 degree, and desirably, the meshing portion of the main gears 3-1 and 3-2 belonging to the first gear group and the main gears 3-3 and 3-4 belonging to the second gear group. An angle corresponding to the amount of play. Thereby, generation | occurrence | production of the twist in rotating shaft 6-1 and 6-2 can be avoided.

As described above, according to the fourth embodiment, the main gear tooth surfaces are in stable contact with each other even during operation of the press machine, although there is play between the tooth surfaces at the meshing portions of the main gears. Can be maintained. Accordingly, the rotational direction positions of these main gears are always determined. That is, the position of the main gear in the rotational direction does not vary by the amount of play. Therefore, frequent tilting of the slide 7 can be prevented during operation of the press machine.
For example, the slide 7 can be prevented from tilting even at the bottom dead center of the slide 7, and as a result, the quality of the press-molded product can be improved.

  In addition, when a plurality of drive motors 2 are used as shown in FIG. 4, as a result of the failure of some of the drive motors 2, the rotational driving force transmitted from the drive motor 2 to the first gear group and the second gear group is different. Even if it becomes, it can maintain the above-mentioned contacted state and can maintain the attitude | position of the slide 7 horizontally.

Next, another configuration example according to the fourth embodiment will be described.
FIGS. 12, 13, 14 </ b> A, and 14 </ b> B show other configuration examples 1 to 3 according to the fourth embodiment, respectively. Hereinafter, when it is not necessary to distinguish between the main gears 3-1, 3-2, 3-3 and 3-4, each main gear is referred to as a main gear 3. Similarly, when it is not necessary to distinguish between the rotating shafts 6-1 and 6-2, each rotating shaft is described as the rotating shaft 6. In addition, the configurations of the configuration examples 1 to 3 are the same as described above, except as described below.

In the configuration example 1 in FIG. 12, an intermediate plate portion 9 a is formed inside the frame 9 as a part of the frame 9. The intermediate plate portion 9a supports the rotary shaft 6 so as to be rotatable. In this configuration, when the preload is applied, a torsional torque is generated on the rotary shaft 6, but the main gear 3 is disposed on both sides of the intermediate plate portion 9a so that the torsional torque is generated. As the range of the rotating shaft 6 is reduced, the rotational movement of the main gear 3 is stabilized.
In addition, since the intermediate plate portion 9a is formed integrally with the frame 9, the rigidity of the entire frame 9 is increased.
Furthermore, by providing the intermediate plate portion 9a, the beam length of the rotating shaft 6 as the bending beam can be shortened, so that the rigidity is increased and the bending due to the molding load or the like is reduced.

  In the configuration example 1, the main gear 3 and a part of the conversion mechanism 5 may be integrated or combined. In this case, a part of the conversion mechanism 5 may be an eccentric ring part of an eccentric link mechanism or a four-bar link mechanism, for example. In this case, the main gear 3 may be configured to freely rotate with respect to the rotating shaft 6, and the rotating shaft 6 may be fixed to the frame 9.

In the configuration example 2 of FIG. 13, a coupling member 35 that couples the main gears is provided. For example, the coupling member 35 extends in parallel with the rotation shaft 6, and both ends thereof are fixed to the opposing side surfaces of the main gear 3. In this configuration, since the main gears 3 are coupled to each other by the coupling member 35, it is possible to prevent the torsional torque from being generated on the rotating shaft 6. In particular, even when the preload is applied, it is possible to prevent or suppress the generation of torsional torque on the rotating shaft 6.
In this configuration example 2, an intermediate plate portion 9a may be provided. In this case, the rotating shaft 6 and the coupling member 35 are configured to penetrate the intermediate plate portion 9a.
The coupling member 35 that couples the main gears 3-1 and 3-2 of the first gear group constitutes the above-described first connecting portion together with or in place of the rotational shaft 6-1. To do. The coupling member 35 that couples the main gears 3-3 and 3-4 of the second gear group constitutes the above-described second connecting portion together with the rotation shaft 6-2 or instead of the rotation shaft 6-2.

  In the configuration example 2, the main gear 3 and a part of the conversion mechanism 5 may be integrated or combined. In this case, a part of the conversion mechanism 5 may be an eccentric ring part of an eccentric link mechanism or a four-bar link mechanism, for example. In this case, the main gear 3 may be configured to freely rotate with respect to the rotating shaft 6, and the rotating shaft 6 may be fixed to the frame 9.

14A and 14B show Configuration Example 3. FIG. 14A is a side sectional view of the press machine, and FIG. 14B is a BB line arrow view of FIG. 14A. In FIG. 14B, the frame 9 and the like are omitted for simplicity.
14A and 14B, the intermediate plate portion 9a is formed as a part of the frame 9 inside the frame 9. Further, each of the rotating shafts 6 described above is divided at the intermediate plate portion 9a into two separate rotating shafts 6a and 6b. In this configuration, the rotating shaft 6a and the rotating shaft 6b are separated at the intermediate plate portion 9a, so that the main gear 3 and the conversion mechanism 5 can be easily replaced and driven by the connecting shafts 14-1 and 14-2. Since the output shafts of the motor 2 are coupled to each other, the main gear 3 can be driven stably.

  Furthermore, in the configuration example 3, a first meshing gear group and a second meshing gear group are provided. The first meshing gear group has a pair of meshing gears 11-1 and 11-2 coupled by a first meshing gear coupling portion (a coupling shaft 14-1 in the example of FIG. 14B) so that the rotation centers are the same. Have In the second meshing gear group, a pair of meshing gears 11-3 and 11-4 coupled by a second meshing gear coupling portion (in the example of FIG. 14B, coupling shaft 14-2) so that the rotation centers are the same. Have

One meshing gear 11-1 of the first meshing gear group meshes with one main gear 3-1 of the first gear group, and the other meshing gear 11-2 of the first meshing gear group is one of the first gear group. It meshes with the other main gear 3-2.
One meshing gear 11-3 of the second meshing gear group meshes with one main gear 3-3 of the second gear group, and the other meshing gear 11-4 of the second meshing gear group is of the second gear group. It meshes with the other main gear 3-4.

  14A and 14B, each meshing gear is a pinion fixed to the output shaft of the drive motor 2, but each meshing gear 11-1, 11-2, 11-3, 11-4 is The rotational driving force of the drive motor 2 may not be transmitted to the main gear 3. In this case, in addition to these meshing gears, another pinion can be provided, and the rotational driving force can be transmitted from the drive motor 2 to the main gear 3 via the pinion.

According to this configuration example 3, one meshing gear 11-1 of the first meshing gear group has a rotational direction position shifted by a predetermined angle with respect to the other meshing gear 11-2 of the first meshing gear group. The connecting shaft 14-1 is connected to the other meshing gear 11-2 of the first meshing gear group.
As a result, the teeth of one main gear 3-1 of the first gear group come into contact with the teeth of one main gear 3-3 of the second gear group in the rotational direction, and the other main gear 3- of the first gear group. The state in which the second tooth contacts the tooth of the other main gear 3-4 of the second gear group in the rotational direction is maintained.

  The principle of the configuration example 3 is the same as the principle described above based on FIG. 9, but will be described in detail based on FIGS. 15A and 15B. 15A is a view taken along line aa in FIG. 14B, and FIG. 15B is a view taken along line bb in FIG. 14B.

(1) It is assumed that the meshing gear 11-2 and the coupling shaft 14-1 of the first meshing gear group are coupled to each other and fixed in the rotational direction. This fixed position is set as a reference position.
(2) With respect to the meshing gear 11-2 fixed at the reference position, the main gear 3-2 of the first gear group is rotated in the direction indicated by the arrow a, and the gear teeth are aligned at the location indicated by (H). The main gear 3-2 is fixed with respect to the reference position in a contact state.
(3) Next, the main gear 3-4 of the second gear group is rotated in the direction indicated by the arrow b with respect to the main gear 3-2 fixed at the reference position, and the gear at the position indicated by (I). The teeth are in contact with each other, and the main gear 3-4 is fixed with respect to the reference position.

(4) After that, the meshing gear 11-4 of the second meshing gear group is rotated in the direction indicated by the arrow c with respect to the main gear 3-4 fixed at the reference position, and the gear at the location indicated by (J). The teeth are brought into contact with each other, and the meshing gear 11-4 is fixed with respect to the reference position.
At this time, since the meshing gear 11-4 is connected and fixed to the coupling shaft 14-2 and the meshing gear 11-3, the coupling shaft 14-2 and the meshing gear 11-3 also rotate in the direction indicated by the arrow c. Fixed with respect to position. The meshing gears 11-3 and 11-4 of the second meshing gear group may have the same shape and dimensions, and are coupled to the coupling shaft 14-2 so that the phases in the rotational direction are the same. Good.
(5) Next, the main gear 3-3 of the second gear group is rotated in the direction indicated by the arrow d with respect to the meshing gear 11-3 fixed at the reference position, and the gear is indicated at the position indicated by (K). The teeth are in contact with each other, and the main gear 3-3 is fixed with respect to the reference position.
(6) After that, the main gear 3-1 of the first gear group is rotated in the direction indicated by the arrow e with respect to the main 3-3 fixed at the reference position, and the gear teeth are located at the location indicated by (L). And the main gear 3-1 is fixed with respect to the reference position.

(7) Finally, the meshing gear 11-1 of the first meshing gear group is fixed to the connecting shaft 14-1. This fixing is performed by adjusting the rotational phase of the meshing gear 11-1. Specifically, the meshing gear 11-1 is rotated in the direction indicated by the arrow f with respect to the connecting shaft 14-1 fixed at the reference position, and the gear teeth are in contact with each other at the position indicated by (M). And
In this state, by fixing the meshing gear 11-1 to the connecting shaft 14-1, the main gears 3-1, 3-2, 3-3, 3-4 all have a phase relationship with each other without play in the rotation direction. It becomes a fixed state. In this state, the rotational direction phase of the meshing gear 11-1 is shifted from the meshing gear 11-2 by a predetermined angle.

  The meshing gears 11-1, 11-2, 11-3, 11-4 may have the same shape and dimensions, and the main gears 3-1, 3-2, 3-3, 3-4 May have the same shape and dimensions.

  In (7) above, the phase in the relative rotational direction of the meshing gear 11-1 of the first meshing gear group can be adjusted by the same phase adjustment mechanism as the phase adjustment mechanism 27 described above.

In this way, the tooth of one main gear 3-1 of the first gear group contacts the tooth of one main gear 3-3 of the second gear group in the rotational direction, and the other main gear of the first gear group. The state in which the teeth of 3-2 are in contact with the teeth of the other main gear 3-4 of the second gear group in the rotational direction can be maintained during the operation of the press machine.
In order to maintain this state, the tooth surfaces of the main gears 3-1 and 3-2 of the first gear group are in a rotational direction with respect to the tooth surfaces of the main gears 3-3 and 3-4 of the second gear group. A preload (pressing force) may be applied or may not be applied.
In other words, the predetermined angle by which the meshing gear 11-1 is shifted in the rotational direction with respect to the meshing gear 11-2 can be adjusted by using the phase adjusting mechanism.

  The predetermined angle is not less than 0 degrees, and is preferably an angle corresponding to the play amount of the meshing portion of the main gear 3 belonging to the first gear group and the main gear 3 belonging to the second gear group. The play amount includes the play amount of the meshing portion between each meshing gear 11 and the main gear 3. Thereby, in the meshing part of the main gears 3 and the meshing part of the meshing gear 11 and the main gear 3, the contact between the tooth surfaces can be maintained without applying a preload between the tooth surfaces. -1, 14-2 can be avoided.

  In addition, one meshing gear 11-1 of the first meshing gear group meshes with one main gear 3-1 of the first gear group indirectly not through the other gear, but the first meshing gear group. The other meshing gear 11-2 may mesh with the other main gear 3-2 of the first gear group indirectly through another gear instead of directly. Similarly, one meshing gear 11-3 of the second meshing gear group meshes with one main gear 3-3 of the second gear group indirectly not through the other gear, but the second meshing gear group. The other meshing gear 11-4 may mesh with the other main gear 3-4 of the second gear group indirectly through other gears instead of directly. In this case as well, the occurrence of torsion in the connecting shafts 14-1 and 14-2 can be avoided by making other configurations similar to the above.

  In the configuration example 3, the main gear 3 and a part of the conversion mechanism 5 may be integrated or combined (in this case, a part of the conversion mechanism 5 is, for example, an eccentric link mechanism or a four-bar link mechanism). It may be an eccentric ring part). In this case, the main gear 3 may be configured to freely rotate with respect to the rotating shaft 6, and the rotating shaft 6 may be fixed to the frame 9.

16-18 is a figure which shows the Example of this invention. 16 is a front cross-sectional view of the crown, FIG. 17 is a cross-sectional view taken along line AA in FIG. 16, and FIG. 18 is a cross-sectional view taken along line BB in FIG.
Hereinafter, only the crown drive portion related to the present invention will be described. In the following description, the line feed direction is “front / rear”, the line orthogonal direction is “left / right”, and the vertical direction is “up / down”.

1 Conversion mechanism (4-bar linkage mechanism 40)
As the conversion mechanism, a four-bar linkage mechanism 40 is employed. The four-bar link mechanism 40 includes an eccentric disc 40a, a swing plate 40b, a restriction link 40c, and a drive link 40d. Such a four-bar linkage mechanism 40 is disclosed in, for example, Japanese Patent Application No. 2006-293555. With this configuration, it is possible to exhibit a high pressurization capacity in the entire drawing region and to suppress the molding speed.
Further, in this example, each press has four sets of link mechanisms (in this case, a four-bar link mechanism 40) arranged symmetrically on the left and right and front and rear.
As a result, the four sets of link mechanisms 40 support the slide at two or more points in each of the front and rear and left and right directions, so that the stability of the slide when the forming load is eccentric is improved.
Further, the four sets of link mechanisms 40 operate symmetrically with respect to the front and rear and left and right directions.
This prevents the generation of an asymmetrical inertial force and minimizes the rolling of the press machine.

2 Main gear 42
The main gear 42 is disposed at the center position of the press with respect to the front-rear direction. Each press has a total of two main gears 42, one symmetrically left and right.
Each main gear 42 is integrated with the eccentric disc 40a.
In addition, there are two eccentric discs 40a, one on each of the front and rear sides per main gear.
With this configuration, four sets of link mechanisms 40 can be driven by a small number of main gears 42 such as a total of two per press, leading to cost reduction.

3 Rotating shaft (Main pin 44)
For the two main gears 42 on the left and right, two main pins 44 for supporting the same are provided on the left and right.
Both ends of the main pin 44 are supported and horizontally supported by a main web 41a provided on the front and rear outside of the crown 41.
One of the front and rear end portions of the main pin 44 is coupled to the main web 41a and cannot rotate.

4 Transmission gear (pinion 46)
The pinion 46 is provided so as to mesh with the main gear 42 partially taken out above the crown 41.
Moreover, two places are rotatably supported by the cap 43 attached to the crown upper part. The cap 43 is a frame installed on the crown upper part, and has a function of supporting the pinion 46 and a cover of the crown upper part.
The pinion 46 also functions as a speed reduction mechanism by meshing with the main gear 42 having a large number of teeth.
With this configuration, the driving force transmitted from the motor 45 can be effectively decelerated and transmitted to the main gear 42.

5 Motor mounting part (pinion shaft end 49 taken out of cap and bracket 48 for motor installation)
The pinion 46 has a shaft end 49 protruding outside the cap 43.
The shaft end 49 can be coupled to the motor shaft by a coupling 47, and functions as a motor mounting portion.
A bracket 48 for motor installation is attached to the crown 41, which serves as a mounting location for a drive motor disposed at a position far away from the crown outward in the front-rear direction.

  The present invention is not limited to the above-described embodiment, and can be modified without departing from the scope of the present invention.

Claims (2)

Drive motor for performing pressing, first gear group and second gear group to which the rotational driving force of the drive motor is transmitted, and gear rotational motion in the first gear group and second gear group are converted into reciprocating motion In a press machine that includes a conversion mechanism that performs a reciprocating motion that is coupled to the conversion mechanism, and performs a press using a die fixed to the slide.
The first gear group has a pair of main gears connected by the first connecting part so that the rotation center is the same, and the second gear group has the second connecting part so that the rotation center is the same. A pair of main gears connected by
One main gear of the first gear group meshes with one main gear of the second gear group, and the other main gear of the first gear group meshes with the other main gear of the second gear group. ,
One main gear of the first gear group is moved to the other main gear of the first group by the first connecting portion so that the rotational direction position is shifted by a predetermined angle with respect to the other main gear of the first gear group. As a result, the teeth of one main gear of the first gear group contact the teeth of one gear of the second gear group in the rotational direction, and the teeth of the other main gear of the first gear group A press machine characterized by maintaining a state in which the teeth of the other gear of the two gear group are in contact with each other in the rotational direction. Drive motor for performing pressing, first gear group and second gear group to which the rotational driving force of the drive motor is transmitted, and gear rotational motion in the first gear group and second gear group are converted into reciprocating motion In a press machine that includes a conversion mechanism that performs a reciprocating motion that is coupled to the conversion mechanism, and performs a press using a die fixed to the slide.
Each of the first gear group and the second gear group has a pair of main gears. One main gear of the first gear group meshes with one main gear of the second gear group, and the other of the first gear group. The main gear is adapted to mesh with the other main gear of the second gear group,
Furthermore, a first meshing gear group and a second meshing gear group are provided,
The first meshing gear group has a pair of meshing gears connected by the first meshing gear coupling portion so that the rotation centers are the same, and the second meshing gear group is the first meshing gear so that the rotation centers are the same. A pair of meshing gears connected by two meshing gear coupling parts;
One meshing gear of the first meshing gear group meshes directly or indirectly with one main gear of the first gear group, and the other meshing gear of the first meshing gear group is the other main gear of the first gear group. Meshing directly or indirectly with
One meshing gear of the second meshing gear group meshes directly or indirectly with one main gear of the second gear group, and the other meshing gear of the second meshing gear group is the other main gear of the second gear group. Meshing directly or indirectly with
One meshing gear of the first meshing gear group is moved by the first meshing gear coupling portion so that the rotational direction position is shifted by a predetermined angle with respect to the other meshing gear of the first meshing gear group. In this way, the teeth of one main gear of the first gear group come into contact with the teeth of one gear of the second gear group in the rotational direction, and the other gear of the first gear group A press machine characterized by maintaining a state in which the teeth of the main gear contact the teeth of the other gear of the second gear group in the rotational direction.

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