JPH0785839B2 - Slide drive device of press machine - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a drive device for moving a slide of a press machine up and down, and can be used for a device in which a slide motion is a quick return motion.

[0002]

[Background Art] In a press machine, the speed of the slide in the processing area during the descending stroke is slowed down, and the speed of the slide that has reached a certain height from the bottom dead center is increased, which results in high precision machining and high efficiency. There is a press machine that can achieve production and the mechanism for making the slide motion into the quick return motion in this way is a slider mechanism type (Actual opening 57-76997 etc.) and an eccentric link mechanism type (special feature). (Kaisho 62-275599 etc.). 4 and 5 are schematic diagrams showing a slider mechanism type, and FIGS. 6 and 7 are schematic diagrams showing an eccentric link mechanism type.

In FIGS. 4 and 5, a main gear 52 meshes with a pinion 51 which is rotated by power transmitted from a motor which is a drive source, and a lever 53 axially opposed to the main gear 52 is a shaft of a crankshaft 54. The connecting rod 55 is fixed to the end and is attached to the eccentric portion 54A of the crankshaft 54.
The slide 56 is connected via. A guide groove 53A extending in the radial direction is formed in the lever 53, and a slider 58 at the tip of a rotary shaft 57 provided in the main gear 52 is slidably engaged with the guide groove 53A. O ₇ (the axis of the crankshaft 54) centers of rotation O ₆ and the lever 53 of the main gear 52 is eccentric e ₃ minutes.

When the main gear 52 is rotated by the pinion 51, the lever 53 and the crankshaft 5 are moved through the slider 58.
4 rotates, which causes the slide 56 to move up and down. In FIG. 5, when the lever 53 rotates from the position indicated by the solid line 180 degrees about O ₇ to the position indicated by the dotted line 53 ′, the main gear 52 rotates θ ₃ about O ₆ and the lever 53 moves further. When it has rotated 180 degrees and returned to the position indicated by the solid line, the main gear 52 is rotating by θ ₄ . O ₇
Is decentered from O ₆ , θ ₃ is smaller than 180 degrees and θ ₄ is larger than 180 degrees. Since the main gear 52 is rotating at a constant speed, when the position of the slide 56 is set to the bottom dead center when the lever 53 is at the position indicated by the solid line, the slide 56 is positioned below the time from the top dead center to the bottom dead center. The time from the dead point to the top dead point is shortened, and the slide motion becomes a fast-return motion.

In FIGS. 6 and 7 showing the eccentric link mechanism type, a main gear 62 meshes with a pinion 61 which is rotated by power transmitted from a motor which is a drive source, and the main gear 62 is rotated by a pair of left and right bearings 63. It is supported freely. A crankshaft 64 is rotatably inserted through the bearing 63, and a slide 66 is connected to an eccentric portion 64A of the crankshaft 64 via a connecting rod 65. A bifurcated lever portion 64B is formed on the crankshaft 64 between the pair of bearings 63.
And link 6 to the bifurcated main body portion 62A of the main gear 62.
Both ends of 7 are rotatably connected by pins 68 and 69. The rotation center O ₈ of the main gear 62 and the rotation center (axial center of the crankshaft 64) O ₉ of the lever portion 64B are eccentric, and the amount of eccentricity is e ₄ .

When the main gear 62 is rotated by the pinion 61, this rotation is transmitted to the crankshaft 64 via the link 67 and the lever portion 64B, which causes the slide 66 to move up and down. In FIG. 7, the pin 68 on the crankshaft 64 side
Is rotated 180 degrees about O ₉ to reach the position of the dotted line 68 ', in other words, when the crankshaft 64 is rotated 180 degrees, the pin 69 on the main gear 62 side is centered on O ₈ from the position of the solid line. The main gear 62 rotates to the position of the dotted line 69 ', and the rotation angle of the main gear 62 at this time is θ ₅ . When the crankshaft 64 further rotates 180 degrees and the pin 68 returns to the position indicated by the solid line, and the pin 69 also returns to the position indicated by the solid line, the rotation angle of the main gear 62 is θ ₆ . Since O ₉ is eccentric from O ₈ , θ ₅ is smaller than 180 degrees and θ ₆ is larger than 180 degrees. Since the main gear 62 is rotating at a constant speed, when the pins 68 and 69 are in the positions indicated by the solid lines, the position of the slide 66 is set to the bottom dead center, so that the slide 6
The time required for 6 to reach the top dead center from the bottom dead center is shorter than the time required for 6 to reach the bottom dead center, and the slide motion is a quick return motion.

FIG. 8 is a slide motion P obtained by the slider mechanism of FIGS. 4 and 5, and FIGS.
8 shows the slide motion Q obtained by the eccentric link mechanism of FIG. 8 and FIG. 8 shows that the angular phases of the crankshafts of both mechanisms are so arranged that the curves from the bottom dead center to the top dead center of both slide motions P and Q almost overlap. Shows the case where is adjusted and set. In the eccentric link mechanism, when one rotation on the main gear 62 side is transmitted to the crankshaft 64 side via the link 67, the link 67 swings around the pin 69 by a certain angle, and thus the swing of the link 67 causes the crank to move. There are times when the rotation speed of the shaft 64 increases and times when it decreases. By adjusting the position of the link 67 and the like so that the time when the rotation speed of the crankshaft 64 becomes slower coincides with the processing area near the bottom dead center in the slide descending process, the inclination angle of P in this processing area. (Indicating the speed of slide) The inclination angle θ _{11 of} Q can be made smaller than θ ₁₀ , and a so-called pan bottom curve can be made.

According to such a pan bottom curve slide motion Q, the sliding speed in the processing area can be slowed down, so that material processing such as drawing can be performed accurately, and a highly accurate pressed product can be obtained. .

[0009]

The slide drive device of the eccentric link mechanism type having the above advantages also has the following problems. FIG. 9 shows the swing angle of the link 67 that occurs when one rotation of the main gear 62 side in FIGS. 6 and 7 is transmitted to the crankshaft 64 side, and this angle is β. Due to the length component L generated by the swing angle β, the rotation speed on the crankshaft 64 side may be increased or decreased to obtain the slide motion Q. Link 67
The length of the main gear 62 is as shown in FIG.
In order to reliably transmit the rotation of the side to the crankshaft 64 side, the link 67 has to be in a posture inclined in the rotation direction, and therefore a certain length or more is required. In order to swing the long link 67 by the angle β to obtain the predetermined length component L, the eccentricity e ₄ in FIGS. 6 and 7 must be increased.

In order to increase e ₄ in this way, the diameter of the center of rotation where the eccentric portion of the device is provided must be increased, and as a result, the size of the entire device becomes large.

It is an object of the present invention to provide a slide drive device for a press machine in which the diameter of the center of rotation where the eccentric portion of the device is provided is not increased, and therefore the device can be downsized.

[0012]

A slide drive device for a press machine according to the present invention comprises a drive rotary member which is rotated by power from a drive source, and a driven rotary member which is fixed to a crankshaft. The driving rotary member and the driven rotary member are eccentric so as to face each other in the axial direction, and a pin member is provided on either one of the driving rotary member and the driven rotary member so as to project in the axial direction at a position distant from the one rotation center. And a bush member is rotatably fitted to the other at a position distant from the rotation center of the other, and the pin member is inserted into the bush member at a position offset from the rotation center of the bush member. The slide is connected to the eccentric part of the shaft through a connecting rod.

In the above, the drive rotation member may be a main gear rotated by a pinion, or a disk-shaped member or a lever member rotated by power transmitted via a gear train or the like. The driven rotary member may be a lever member, a disk-shaped member, or a lever portion integrally formed with the crankshaft.

[0014]

When the drive rotation member is rotated by the power transmitted from the drive source, this rotation is transmitted to the driven rotation member via the pin member and the bush member, whereby the crankshaft rotates and the slide moves up and down. Since the driving rotating member and the driven rotating member are eccentric, the slide motion becomes a quick return motion. The rotation of the bush member rotates to transmit the rotation from the driving rotary member to the driven rotary member, and the length from the center of this rotation to the position of the pin member inserted in the bush member is the link in the conventional eccentric link mechanism. Since the rotation angle of the bush member when the drive rotating member and the driven rotating member make one rotation can be increased,
Even if the length is short, like the conventional eccentric link mechanism,
It is possible to obtain a length component necessary for the rotation speed of the crankshaft to become faster and slower, so that the eccentric amount of the drive rotary member and the driven rotary member may be small, and the eccentric portion of the device is provided. The diameter of the rotating part can be reduced.

[0015]

An embodiment of the present invention will be described below with reference to the accompanying drawings. FIG. 1 is a front sectional view showing an apparatus according to this embodiment, and FIG. 2 is a schematic side view thereof. In FIG. 1, a pinion 2 is fixedly mounted on a drive shaft 1 that is rotated by power from a motor that is a drive source, and a main gear 3 is meshed with the pinion 2. The main gear 3 is rotatably fitted and supported by a large-diameter bearing member 6 fixed to the boss member 5 of the frame 4, and its rotation center is O ₁ . The main gear 3 is a drive rotating member that is rotated by the pinion 2. A bearing hole 6A is formed through the bearing member 6, and a crankshaft 8 is rotatably inserted through the bearing hole 6A and an inner diameter hole 7A of a boss member 7 fixed to the frame 4. The center of rotation O ₂ is eccentric from O ₁ by e ₁ . The crankshaft 8 is provided with an eccentric portion 8A, which is circular as shown in FIG. 2 and whose center is O ₃ .
O ₃ is offset from O ₂ by e ₂ . An upper end of a connecting rod 9 is fitted to the eccentric portion 8A, and a slide (not shown) is connected to the lower end of the connecting rod 9. The rotation of the crankshaft 8 causes the slide to move up and down with a stroke twice that of e _2. It is supposed to do.

As shown in FIG. 1, one end of the crankshaft 8 projects from the bearing member 6, and a lever member 10 extending in the radial direction is fixed to the projecting end. This lever member 1
Reference numeral 0 denotes a driven rotary member that rotates by the rotational force transmitted from the main gear 3, and its rotation center is O ₂ which is the same as that of the crankshaft 8. Therefore, the lever member 10 and the main gear 3 are eccentric by e ₁ , and the lever member 10 and the main gear 3 face each other in the axial direction.

The main gear 3 has a pin member 11 projecting in the axial direction in the vicinity of the outer peripheral portion away from the rotation center O _1.
11A is inserted and fixed. In addition, a hole 10A is formed in the lever member 10 near the tip end portion away from the rotation center O _2, and a bush member 12 is rotatably fitted in the hole 10A. It is O ₄ shown in FIG. As shown in FIG. 1, the pin member 11
The tip portion 11B of the above is rotatably inserted into the bush member 12, and the insertion center is O ₅ shown in FIG. 2, and this O ₅ is deviated from O ₄ .

Next, the operation will be described. When the main gear 3 rotates about O ₁ in the pinion 2, this rotation is transmitted to the lever member 10 via the pin member 11 and the bush member 12, and the lever member 10 and the crankshaft 8 are O _2.
And the slide moves up and down via the connecting rod 9. When the rotation of the main gear 3 which is the driving rotation member is transmitted to the lever member 10 which is the driven rotation member in this way, the center O ₅ of the pin member 11 which is the member on the main gear 3 side is shown in FIGS. , Draw a rotation locus A around O ₁ , and
The center O ₄ of the bush member 12, which is a member on the side of the lever member 3, draws a rotation locus B around O ₂ . O ₅
Motion to draw the rotation locus A but around the O _1, performed by the bush member 12 is rotated around the O _4, Therefore, the pin member 11 tip portion 11B in the bush member 12 is inserted Means that while O ₅ rotates _once around O _1, that is, while the main gear 3, lever member 10 and crankshaft 8 rotate once, it rotates about O ₄ by a certain angle. This is shown in FIG.

In FIG. 3, when the bush member 12 rotates 180 degrees about O ₂ and reaches the position 12 ', the pin member 11 reaches the position 11'. The rotation angle of O ₁ of the pin member 11 up to this point, in other words, the rotation angle of the main gear 3 is θ ₁ . Further, when the bush member 12 returns from the position 12 'to the original position, the pin member 11 returns from the position 11' to the original position. The rotation angle of the pin member 11 up to this time, that is, the main gear 3 The rotation angle is θ ₂ . Since O ₁ and O ₂ are eccentric by e ₁ , θ ₁ is smaller than 180 degrees and θ ₂ is larger than 180 degrees. Since the main gear 3 is rotating at a constant speed, the positional relationship between the pin member 11 and the eccentric portion 8A of the crankshaft 8 should be set as shown in FIG. 2, and the slide position should be the bottom dead center in FIG. As a result, the time required for the slide to reach the top dead center from the bottom dead center is shorter than the time for the slide to reach the bottom dead center, and the slide motion is a quick return motion.

In FIG. 2, the substantial length of the lever member 10 is C between O ₂ and O ₄ , and the mechanism of the apparatus according to the present embodiment has O _{4 at} the tip of the lever having the length of C. Connect one end of a link having the same length as D, which is the interval of O ₅ ,
It is similar to the structure in which the other end of this link is connected to the main gear 3. This structure is mechanically similar to the structure of the conventional device having the lever portion 64B and the link 67 shown in FIG.

However, in the device according to the present embodiment, the pin member 11 is projectingly provided on the main gear 3 and the pin member 11 is inserted into the bush member 12 rotatably fitted to the lever member 10. The rotation of the main gear 3 is transmitted to the lever member 10 while the bush member 12 is rotated about O ₄ by the pin member 11, and the main gear 3, the lever member 10,
Bushing member 1 when crankshaft 8 makes one revolution
The rotation angle around O ₄ of 2 can be increased.

As described above, the slide motion Q of FIG. 8 capable of high-precision machining of the press material causes the crankshaft to rotate faster and slower.
Although it can be obtained by generating the length component L indicated by, the rotation angle of the bush member 12 around O ₄ can be increased in the present embodiment, so that the length D equal to the interval between O ₄ and O ₅ can be obtained. Assuming the link 13 of FIG. 9 having the above, the swing angle α of the link 13 when the main gear 3 or the like makes one revolution can be increased. Therefore, in order to obtain the length component L having the same length, the length D of the link 13 can be made shorter than the length of the link 67 in FIGS. 6 and 9.

[0023] If shorter D, predetermined length component L can be obtained even by reducing the eccentricity e ₁ between the rotation center O ₂ of the rotation of the main gear 3 the center O ₁ and the lever member 10 and the crankshaft 8, in other words Then, the slide motion Q in FIG. 8 can be obtained with a small eccentricity e ₁ . Therefore, the diameter of the center of rotation where the amount of eccentricity e _{1 of the} device is provided, specifically, the peripheral portion of the crankshaft 8 and the bearing member 6 can be reduced, and the entire device can be downsized.

Further, according to the present embodiment, the lever member 10
Since the bush member 12 may be rotatably fitted to the bush member 12 and the pin 11 on the main gear 3 side may be inserted into the bush member 12, the bush member 12 may be processed into a circular shape by a machine tool such as a lathe. Since this work is labor-free, the workability regarding the processing and manufacturing of the members is improved and the manufacturing cost can be reduced as compared with the conventional eccentric link mechanism type device.

In the embodiment described above, the pin member 11 is provided on the main gear 3 side and the bush member 12 is provided on the lever member 10 side, but this may be reversed.

In the above embodiment, the pin member 12 is fixed to the main gear 3 and rotatably inserted into the bush member 12. However, the pin member is fixed to the bush member and rotatably inserted into the main gear. You may make it the structure.

Further, the drive rotating member of the above-described embodiment is the main gear 3 rotated by the pinion 12,
The drive rotation member is not limited to this, and may be, for example, a disk-shaped member or a lever member that is transmitted by a rotational force via a gear train or a drive shaft. Further, the driven rotary member is not limited to the lever member 10 of the above embodiment, and may be, for example, a disk-shaped member,
Further, a lever portion integrally formed with the crankshaft may be used.

[0028]

According to the present invention, the diameter of the center of rotation where the eccentric portion of the device is provided can be reduced, and therefore the device can be downsized, and the members constituting the device can be made smaller. It can be easily processed and manufactured, which is advantageous in terms of workability and manufacturing cost.

[Brief description of drawings]

FIG. 1 is a front sectional view showing an apparatus according to an embodiment of the present invention.

FIG. 2 is a schematic side view of FIG.

FIG. 3 is a diagram showing the operating principle of FIGS. 1 and 2;

FIG. 4 is a diagram schematically showing a conventional device of a sliding mechanism type.

5 is a diagram showing the operating principle of the device of FIG.

FIG. 6 is a schematic diagram showing an eccentric link mechanism type conventional device.

FIG. 7 is a diagram showing the operating principle of FIG. 6;

FIG. 8 is a diagram showing a slide motion that is a fast return motion.

FIG. 9 is a diagram showing a swing angle of a link for obtaining a constant length component.

[Explanation of symbols]

3 Main gear which is a driving rotary member 8 Crankshaft 8A Eccentric part 9 Connecting rod 10 Lever member which is a driven rotary member 11 Pin member 12 Bushing member O ₁ Rotation center of main gear O ₂ Crankshaft and rotation center of lever member O ₄ Bushing member Center of rotation O ₅ Center of pin member e ₁ Eccentricity between main gear, crankshaft and lever member

Claims (1)

[Claims] 1. A drive rotary member that rotates by power transmitted from a drive source and a driven rotary member fixed to a crankshaft are eccentrically opposed to each other in the axial direction, and the drive rotary member and the driven rotary member. One of the pin members is axially projected at a position away from the one rotation center, and the other bush member is rotatably fitted at a position away from the other rotation center. A slide drive device of a press machine, wherein a pin member is inserted into the bush member at a position displaced from a rotation center of the bush member, and a slide is connected to an eccentric portion of the crankshaft via a connecting rod.