JPH0373399B2 - - Google Patents

Description

[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a method for coupling a main crankshaft and a sub-crankshaft of a press machine. It can be used for press machines that have

[Background technology and its problems]

There are various types of press machines depending on the purpose of work, and the types of press processing performed with these press machines include (A) general-purpose press processing, which mainly performs deep drawing, and (B) transfer press processing. and (C) progressive pressing. Due to its press processing characteristics and automation compatibility, these press machines have
Each requires a different slide motion, which changes the ratio of the working area to the total stroke length of the slide of the press machine. In addition, in press machines for the purpose of (B) or (C) above, when automating the press machine, it is necessary to prevent interference between the clamping and unclamping operations of the feed bar and the slide operation, not only in the processing area but also when automating the press machine. Therefore, it is necessary to fully consider the ratio of areas other than the machining area. For this reason, in various press machines, it is necessary to determine the slide motion including the ratio of the machining area according to the type of machining so that appropriate machining can be performed.

For this reason, in conventional press machines, the above (A) to (C)
It was necessary to design and manufacture a press machine having an appropriate ratio of the working area to the total stroke length of the slide according to each type of press working. However, if a press machine is designed and manufactured for each type of press work in this way, there is a problem that production efficiency cannot be achieved.

In order to solve such problems, the present applicant provided a drive device for a press machine in Japanese Patent Application No. 58-231000 (Japanese Patent Application Laid-Open No. 60-124498). This drive device divides the crankshaft of a press machine into a main crankshaft and a sub-crankshaft, and unitizes a mechanism constituted by the sub-crankshaft and members disposed around the sub-crankshaft. A main gear is arranged around the sub-crankshaft and transmits rotational force by meshing with the pinion gear of the drive shaft, which has a flywheel, a clutch, and a brake.The sub-crankshaft is eccentric to the main gear, and is connected to the main gear via a link at the eccentric portion. A plurality of units consisting of such sub-crankshafts, main gears, etc. are prepared with different amounts of eccentricity between the sub-crankshafts and the main gears, and the sub-crankshafts of these units are detachably connected to the main crankshaft. The unit can now be replaced. Further, the main crankshaft is provided with an eccentric portion, and a slide is connected to this eccentric portion via a connecting rod.

When the rotational force from the drive shaft is transmitted to the main gear via the pinion gear, the main gear rotates the auxiliary crank and the main crankshaft via the link, and these rotations are caused by eccentricity between the auxiliary crank and the main gear. The rotational speed during one rotation is unequal, and the slide moves up and down in a rapid return motion.

When the above unit is replaced, the amount of eccentricity between the sub-crankshaft and the main gear changes, so the vertical motion of the slide changes, resulting in (A) to (C)
It is possible to obtain a slide motion suitable for a predetermined type of press work among the types of press work.

However, with the above drive device for a press machine, it is necessary to manufacture a plurality of units with different eccentricities between the sub-crankshaft and the main gear, which poses a problem of increased manufacturing costs.

In addition, the applicant has also proposed a device that can change the slide motion as described above.
60-198816 (Utility Model No. 62-105799) is proposed.
In this device, the crankshaft is not divided into a main crankshaft and a sub-crankshaft, but the
Like the 231000, the crankshaft is eccentric to the main gear, and the eccentric part of the crankshaft and the main gear are connected via a link.
In addition, with this device, the main gear is moved in an arc around the drive shaft that transmits rotational force to the main gear, and this arc movement changes the amount of eccentricity between the crankshaft and the main gear, changing the slide motion. I have to.

According to this device, it is necessary to provide a mechanism for moving the main gear in an arc around the drive shaft, which causes the problem that the device becomes complicated and the manufacturing cost increases.

[Purpose of the invention]

Each of the above devices attempts to obtain a slide motion suitable for each type of press work by changing the amount of eccentricity between the sub-crankshaft or crankshaft and the main gear. It was discovered that a slide motion suitable for each type can be obtained by changing the angular phase difference between the eccentric portion of the main crankshaft and the eccentric portion of the sub-crankshaft.

SUMMARY OF THE INVENTION An object of the present invention is to provide a method for connecting a crankshaft of a press machine that does not make the device complicated and can reduce manufacturing costs.

[Means and actions for solving problems]

In the crankshaft coupling method for a press machine according to the present invention, the main crankshaft has a slide connected to the eccentric part via a connecting rod, and the rotational force is transmitted by meshing with the pinion gear of the drive shaft, which has a flywheel, clutch, and brake. A method for coupling a crankshaft of a press machine to a sub-crankshaft that is eccentric with respect to a main gear and has an eccentric portion that is connected to the main gear via a link. The eccentric portion of the main crankshaft and the sub-crankshaft are suitable for performing three types of press processing, including general press processing, transfer press processing, and progressive press processing, before being coupled to the sub-crankshaft. The three angular phase differences between the eccentric parts and the eccentric parts are determined, and then the positional relationships of these eccentric parts in the main and sub-crankshaft rotational directions are adjusted so that the angular phase differences of these eccentric parts are the same as the three types described above. The main crankshaft and the sub-crankshaft are coupled after an angular phase difference that is compatible with a predetermined press work performed by a press machine during the press work is achieved.

That is, in the present invention, when designing a press machine, the location of the main gear connected to the eccentric part of the sub-crankshaft via a link, the length of the link, and the amount of eccentricity between the sub-crankshaft and the main gear are determined in advance. Based on the determined design conditions, three angular phase differences between the eccentric part of the main crankshaft and the eccentric part of the sub-crankshaft are suitable for general-purpose press working, transfer press working, and progressive press working. When assembling the press machine, the user of the press machine rotates and adjusts the main crankshaft and sub-crankshaft until the angular phase difference is suitable for the type of press work that the user wants to perform with the press machine.
After this, the main crankshaft and the sub-crankshaft are connected.

For this reason, when assembling a press machine, the predetermined demands of the press machine user can be achieved by simply connecting the main crankshaft and sub-crankshaft with different angular phase differences of the eccentric parts of these crankshafts. It is possible to manufacture a press machine that can perform different types of press work, and it is possible to provide the same model of press machine for different types of press work according to the needs of each user.

〔Example〕

An embodiment of the present invention will be described below based on the drawings.

In FIG. 1, a slide 2 is disposed on a column 1A of a press machine so as to be movable up and down, and this slide 2 is suspended from a crown 1B via a balance cylinder 3. Further, the slide 2 is connected via connecting rods 5 to eccentric portions 4A of the left and right main crankshafts 4 rotatably supported by the crown 1B, and is configured to move up and down as the main crankshafts 4 rotate.

One end (inner end) of the main crankshaft 4 is connected to the output member of the drive unit 6, that is, the sub-crankshaft 18, via a flange joint type coupling 21, respectively.
is connected to. The drive section 6 is unitized and attached to the crown 1B, and the input side of the drive section 6 is connected to a flywheel 7, a clutch 8A, and a brake 8B.

The drive unit 6 is shown enlarged in FIGS. 2 and 3. In addition, Figures 2 and 3 are slide 2.
This shows the state when is at the bottom dead center. In FIG. 2, a drive shaft 11 is rotatably mounted relatively above the housing 9 of the drive unit 6 via a bearing 10, and this drive shaft 11 includes the flywheel 7, clutch 8A, and brake 8B.
A pinion gear 12 is provided within the housing 9 .

Holes 9 formed on both sides of the housing 9
A is a main gear guide 1 that is approximately cylindrical and has a predetermined wall thickness.
3 and 13 are respectively attached with bolts. A main gear 14 is rotatably attached to the outer periphery of the main gear guides 13, 13 inside the housing 9, and this main gear 14 meshes with the pinion gear 12.
This main gear 14 includes a main gear guide 13,
gear body 15 supported by gear body 13;
A gear pin 17 is attached to the body of the gear body 15.

As shown in FIG. 3, the main gear guides 13, 13 rotatably support the sub-crankshaft 18, which has a center O ₁ eccentric by a distance A with respect to the rotation center O of the main gear 14. There is. This sub-crankshaft 18 has an eccentric portion 18A.
is formed between the main gear guides 13, 13, and a crank pin 19 is attached to this eccentric portion 18A. A link 20 of a predetermined length is spanned between the crank pin 19 and the gear pin 17, and the connecting portions between the link 20 and each pin 19, 17 are rotatable.

As mentioned above, the sub-crankshaft 18 and the main crankshaft 4 are connected by the coupling ring 21,
This connection is performed so that the angular phase difference θ shown in FIG. 3 between the eccentric portion 18A of the sub-crankshaft 18 and the eccentric portion 4A of the main crankshaft 4 becomes a predetermined value. This angular phase difference θ is made to vary depending on the type of press work that the user of the press machine intends to perform with the press machine. For example, the angular phase difference θ is (A) 120 degrees in general-purpose press working that mainly performs deep drawing, (B) 130 degrees in transfer press work, and (C) 140 degrees in progressive press work.

Such setting of the angular phase difference θ is performed before coupling the sub-crankshaft 18 and the main crankshaft 4, specifically when designing the press machine.
The angular phase difference θ is examined and determined based on the length of the , the magnitude of the eccentricity A, etc., and when assembling the press machine, the sub crankshaft 18 or the main crankshaft 4 is rotated so that these crankshafts 18 , 4, and after the angular phase difference θ between these eccentric parts 18A, 4A reaches a predetermined value, the sub crankshaft 18 and the main crankshaft 4 are coupled with a coupling 21. do.

In addition, when connecting the main crankshaft 4 and the sub-crankshaft 18, there are various possible means for differentiating the angular phase difference θ between the eccentric parts 4A and 18A.
For example, the eccentric portion 4 of the main and sub crankshafts 4, 18
A, 18A, the position of the keyway formed in the portion of each crankshaft 4, 18 where the coupling ring 21 is engaged may be made different, or the position of the keyway may be kept constant and each Couplings 21 having different coupling angle phases may be used for each press machine, or other means may be used.

Next, the operation of the press machine manufactured in this way will be explained.

When the drive shaft 11 rotates counterclockwise in FIG. 3, the main gear 14 rotates clockwise, and accordingly, the link 20, sub-crankshaft 18, and main crankshaft 4 also rotate clockwise, and the slide 2 moves up and down. do.

When the main gear 14 rotates, as shown by the solid line in FIG. 3, when the connecting rod 5 is at the lowest position, that is, when the slide 2 is at the bottom dead center position, the gear pin 17 is at the highest position, and , since the crank pin 19 is set to be on the right side, until the slide 2 moves from the bottom dead center position shown in the figure to the top dead center position, that is,
The eccentric portion 4A of the main crankshaft 4 is rotated 180 degrees clockwise from the position shown by the dotted line, and the crank pin 19 provided on the eccentric portion 18A of the sub-crankshaft 18 is rotated 180 degrees clockwise from the position shown by the solid line. Before moving to the position indicated by the chain line 19' in the figure, the gear pin 17 rotates by an angle α from the uppermost solid line position to the position indicated by the chain line 17' in the figure, and this angle α is the rotation angle of the main gear 14. The rotation angle α at this time is smaller than 180 degrees.

On the other hand, the slide 2 that has reached the top dead center position is moved to the bottom dead center position by crank pin 19' at the chain line position.
is done by continuing to rotate 180 degrees clockwise to solid line position 19, and this crank pin 19
During the 180 degree rotation, the gear pin 17 also rotates by an angle β from the chain line position 17' to the solid line position 17,
This angle β is the rotation angle of the main gear 14.
The rotation angle β at this time is greater than 180 degrees, and
It is an angle equal to (360 degrees - α).

By the way, since the main gear 14 rotates at a constant speed with the driving force from the drive shaft 11, the main gear 14
4. That is, the slide 2 moves from the bottom dead center to the top dead center when the rotation angle α of the gear pin 17 is 180 degrees or less, and on the other hand, it moves from the top dead center to the bottom dead center when the rotation angle β is 180 degrees or more. , indicating that the return to the top dead center side is fast and the transition to the bottom dead center side is slow. Therefore, the structure of the drive unit 6 of this embodiment functions as a quick return mechanism.

In this way, the drive unit 6 of this embodiment acts as a quick return mechanism, and its structure is similar to the previously proposed device (Japanese Patent Application Laid-open No. 60-124498), but in such a structure, changing the rotational movement of the main crankshaft 4, that is, the vertical movement (slide motion) of the slide 2, is the same as that of the main gear 14 in the previously proposed invention. This is done by changing the eccentricity A between the rotation center O of the sub-crankshaft 18 and the rotation center _O1 of the sub-crankshaft 18, but according to subsequent research by the present inventor, while keeping the eccentricity A constant,
As mentioned above, when connecting the eccentric portion 4A of the main crankshaft 4 and the eccentric portion 18A of the sub-crankshaft 18,
It was confirmed that a similar effect can be obtained by changing the angular phase difference θ between both eccentric portions 4A and 18A.

Figures 4 to 6 are diagrams explaining changes in slide motion when changing the angular phase difference θ. Figure 4 shows the angular phase difference θ = 120 degrees and FIG. 5 shows the case where the angular phase difference θ=130 degrees for the press working in (B), and FIG. 6 shows the case where the angular phase difference θ=140 degrees for the press working in (C). These figures are diagrams showing the relationship between the slide speed V, acceleration Ac, and stroke St during each slide operation and the rotation angle of the main gear 14. From these figures, each of (A) to (C) It can be seen that various types of press working can be performed appropriately. For example, the rotation angle β of the main gear 14 from the top dead center to the bottom dead center of the slide 2 is the fourth rotation angle β in (A) above.
210 degrees as shown in the figure, 203 degrees as shown in Figure 5 in (B),
In (C), the angle is 196 degrees as shown in Figure 6, so the quick return speed of the slide is the fastest in (A), followed by (B) and (C).
On the other hand, the slide descending speed is in the opposite order. In addition, the machining area where the material is being processed is moved upward from the bottom dead center of the slide 2, and the total stroke of the slide is 4/9 in (A) and 3/9 in (B).
(=1/3), and (C) up to the 2/9 position, the range shown by L in the figure is the machining area at the rotation angle of the main gear, and within the machining area of (A) to (C) above, The speed V and acceleration Ac of the slide have values suitable for each type of press working (A) to (C), and a slide motion suitable for these can be obtained.

According to this embodiment, when the main crankshaft 4 and the sub-crankshaft 18 are connected, the eccentric portion 4A of the main crankshaft 4 and the sub-crankshaft 18 can be connected without changing the internal structure of the drive section 6. Eccentric portion 18 of shaft 18
By varying the angular phase difference with A, each slide motion required for a press machine can be obtained, and it is extremely easy to obtain a press machine with different ratios of the working area to the total stroke length of the slide 2. . Therefore, it is possible to provide press machines of the same model for press processing of any of the press processing types (A) to (C) according to the needs of each user using these press machines. , it is possible to realize general-purpose press machines, and
This can be achieved without complicating the structure of the press machine or increasing manufacturing costs.

In carrying out the present invention, the angular phase difference θ is not limited to the value of the embodiment described above, but can be changed depending on the required slide motion. In addition, the main crankshaft 4 and the sub-crankshaft 18
The coupling 21 that connects the two is not limited to the flange coupling type as in the embodiment described above, but may be another type of coupling, such as a carboxylic coupling whose engagement angle can be changed. Further, the drive section 6 does not necessarily need to be integrated as in the previous embodiment, and the housing 9 may not be provided, and the parts supported by the housing 9 may be supported directly on the crown 1B of the press. Further, the present invention can also be applied to straight-sided press machines and C-type press machines.

〔Effect of the invention〕

As described above, according to the present invention, each press machine for performing different types of press processing can be obtained without complicating the structure or increasing manufacturing costs, and it is possible to obtain press machines for performing different types of press processing without complicating the structure or increasing manufacturing costs. It becomes possible to manufacture press machines that perform the type of press processing desired by each user.

[Brief explanation of drawings]

Fig. 1 is a sectional view showing the crown portion of a press machine according to an embodiment of the present invention, Fig. 2 is an enlarged sectional view of the main part of Fig. 1, and Fig. 3 is a view taken along the line - in Fig. 2. The cross-sectional views, Figures 4 to 6, respectively, show the slide speed V, acceleration A _c , stroke S _t , and main gear when the angular phase difference between the eccentric part of the main crankshaft and the eccentric part of the sub-crankshaft is different. FIG. 3 is a diagram showing the relationship between the rotation angle and 1B...Crown, 2...Slide, 4...Main crankshaft, 4A...Eccentric part of main crankshaft, 5
...Conrod, 6...Drive section, 7...Flywheel, 8A...Clutch, 8B...Brake,
11... Drive shaft, 12... Pinion gear, 14...
...Main gear, 18... Sub-crankshaft, 18A...
...Eccentric part of sub-crankshaft, 20...Link, θ...
...Angular phase difference.

Claims (1)

[Claims] 1. A main crankshaft to which a slide is connected to the eccentric part via a connecting rod, and a main gear to which rotational force is transmitted by meshing with a pinion gear of a drive shaft having a flywheel, clutch, and brake. A sub-crankshaft that is eccentric and has an eccentric part connected to the main gear via a link, in a method for coupling a crankshaft of a press machine, Before joining, the eccentric part of the main crankshaft and the eccentric part of the sub-crankshaft are connected to each other, which are suitable for performing three types of press working: general-purpose press working, transfer press working, and progressive press working. The three angular phase differences are determined, and then the positional relationship of these eccentric parts in the main and sub-crankshaft rotation directions is adjusted, and the angular phase difference of these eccentric parts is determined by A method for coupling a crankshaft of a press machine, characterized in that the main crankshaft and the sub-crankshaft are coupled after an angular phase difference that is compatible with a predetermined press working performed by the machine is achieved.