JPS6123543A - Solid body compressing device - Google Patents

Abstract

PURPOSE:To elevate the dimensional accuracy of products by moving a tool back and forth with the shaft supported by a holder via a crank shaft and by adjusting the initial position with screwing and rotating the holder and shaft as well. CONSTITUTION:The connecting rod 56 provided on a crank shaft 48 is brought into contact slidably with an outer block 58. The shaft 60 supported by the outer block 58 moves back and forth the forging tool 64 fixed on a inner block 62 via the crank shaft 48. The screw part 68 formed at the tip of the shaft 60 and the nut 66 of the inner block 58 are screwed and the rear end part of the shaft 60 forms a spline part and is rotated by a driver 80 as well. With the rotation thereof the shaft 60 is moved to the axial direction with the outer block 58 as a cardinal point via the spline part and the initial stage position of the tool 64 is adjusted. With said mechanism the rigidity of the device is elevated and the dimentional accuracy of products is elevated.

Description

[Detailed Description of the Invention] [Field of Application of the Invention] The present invention relates to a compression device for solid materials, and is particularly suitable for compressing the width of hot rolling slab materials, which requires high-mix, low-volume production and high operating rates. The present invention relates to solid compaction equipment.

[Background of the invention]

Conventionally, there is a solid compression device shown in Figure 4 (
(Precision Machinery Vol. 49, No. 8, p. 25). This device is comprised of a pair of compression mechanisms and a pair of initial position setting mechanisms.

The compression mechanism has a gearwheel io, 12, connected to a drive motor (not shown) for transmitting its power, and an eccentric cam 14 is provided in contact with this gearwheel 10.12. This eccentric cam 14 is provided with a pitman 16 that converts rotational motion into reciprocating motion, and the reciprocating motion of the pitman 16 is transmitted to a pair of forging tools 8 disposed on both sides of the workpiece (not shown). introduce. This power transmission is carried out by Pitman 16
A swing link 20 and a link 22 arranged between the forging tool 18 and a slide 26 that slides within the C-shaped frame 24 by the link 22, and a pin 28 that connects these links.
30.32, and a C-shaped frame 24 on which a set of these is mounted.

Further, the initial position setting mechanism includes a ring-shaped frame 34 horizontally mounted on the C-type 7 frame 24, a hydraulic cylinder 38 having a built-in piston rod 36 and disposed horizontally within the frame 34, and a hydraulic cylinder 38 horizontally disposed within the frame 34. The pin 40 is attached to the tip of the piston rod 36 and connects the swing link 20 to the piston rod 36.

The operations of this conventional solid compression device are roughly divided into a small stroke, high cycle compression operation and a large stroke, low cycle initial position setting operation. First, in the compression operation, when a drive electric motor (not shown) is driven, the eccentric cam 14 rotates via the gear 10.12, and the pin 28 incorporated in the pitman 16 reciprocates. Since the intermediate portion of the swing link 20 is supported by the piston rod 36 by the pin 40, the swing link 20 swings about the piston 40, which is located at a preset position by the piston rod 36, as a swing center.

This rocking motion causes pins 30, 32,! The slide 26 is reciprocated via the joint 22, and the forging tool 18 reciprocates along with the slide 26 on the C-shaped frame 24.

The compression mechanism consists of a pair of mechanisms arranged symmetrically, and two gears, namely gears 10 and 12, are arranged between the left and right pair of eccentric cams 14, so that the rotation of the gear 10 is prevented. As a result, the pair of eccentric cams 14 operate symmetrically.

The operation of the pair of eccentric cams 14 causes the entire pair of left and right compression mechanisms including the forging tool 18 to operate symmetrically. Therefore, when a workpiece (not shown) is inserted between the pair of forging tools 18, the workpiece can be forged through these devices by rotation of a drive motor (not shown).

Next, the initial position setting operation is performed using a pressure oil supply device (not shown).
When pressure oil is supplied into the hydraulic cylinder 38 or pressure oil is discharged from the hydraulic cylinder 38, the piston rod 3
6, the pin 40 moves, and the swing link 20 moves through the pin 4.
Performs rotational movement with 0 as the fulcrum. Therefore, the swing link 20 horizontally moves the forging tool 18 along with the slide 26 on the C-shaped frame 24 via the link 22. Therefore, by supplying an appropriate amount of pressure oil into the hydraulic cylinder 38 or discharging pressure oil from the hydraulic cylinder, the forging tool 18 can be placed in an appropriate position when the compression device is not operating (initial position). A forging tool 18 can be installed. Also,
The initial position setting mechanism consists of a pair of mechanisms that are arranged symmetrically, so by supplying or discharging the same amount of pressure oil into the left and right hydraulic cylinders 38, the pair of piston rods 36 can be operated symmetrically, and furthermore, the entire pair of left and right initial position setting mechanisms including the forging tool 18 can be operated symmetrically.

Therefore, by supplying pressure oil to the hydraulic cylinder 38 or discharging pressure oil from the hydraulic cylinder 38, the initial positions of the pair of forging tools 18 can be adjusted appropriately through the equipment that constitutes the initial position setting mechanism. Can be set to Further, the pair of forging tools 18 are reciprocated on the C-shaped frame 24 from the initial setting position by the equipment constituting the compression mechanism described above, and the workpiece inserted between the pair of forging tools 18 is Can be forged.

However, with this conventional device, there are problems that must be fully recognized in terms of the dimensional accuracy of the forged product. First, regarding the initial position setting mechanism, a pin 40 serving as a fulcrum of the swing link 20 is supported by a hydraulic cylinder 38 via a piston rod 36. Therefore, even if the amount of internal pressure oil in the hydraulic cylinder 38 is set appropriately, the pressure oil in the hydraulic cylinder 38 is compressed by the large forging force, and the pin 40 moves via the piston rod 36, causing the forging tool 18 to move. The setting position changes. Furthermore, since this amount of movement changes depending on the forging force, it has a large effect on the dimensional accuracy of the product.

The solid line in Fig. 5 is a trial calculation of the product dimensional error due to compression of the pressure oil in the hydraulic cylinder 38 (cylinder diameter 1000++ m, tool stroke 100W) f When the forging load is 2000 tons, the product dimensional error is as high as 3111II+. It can be seen that this is suitable for compressors with large dimensional errors and large loads.

Next, the compression mechanism transfers the reciprocating motion of the pitman 16 to the forging tool 18 through a number of links that reduce the rigidity of the mechanism.
is being communicated to. Therefore, the rigidity of the compression mechanism is also low, resulting in a decrease in product dimensional accuracy. This also becomes an impediment to increasing the size (larger capacity ratio).

In order to obtain a product with good dimensional accuracy using the conventional device described above, the position of the forging tool 18, which is affected by the displacement of the piston rod 36 and the deformation of the swing links 20 and 22 under load, must be sequentially detected. , it is necessary to sequentially control the pushing position of the piston rod 36, and a complicated control mechanism is required.

[Purpose of the invention]

An object of the present invention is to provide a highly rigid solid compression device that does not undergo large deformation during forging.

[Summary of the invention]

The present invention allows a tool that applies an external force to a workpiece to be reciprocated by a shaft supported by a holder that moves back and forth with a crankshaft, and the holder and the shaft are screwed together to rotate the shaft. The length of the part of the shaft protruding from the holder can be adjusted, the initial position of the tool can be adjusted, and the link mechanism and hydraulic cylinder mechanism with low rigidity are eliminated, so that a highly rigid solid compression device can be obtained. It is something.

[Embodiments of the invention]

A preferred embodiment of the solid compaction apparatus according to the present invention will be described in detail with reference to the accompanying drawings.

FIG. 1 is a partially sectional plan view of an embodiment of a single trout compression device according to the present invention. In FIG. 1, the solid compression device is comprised of a pair of compression mechanisms and a pair of initial position setting mechanisms.

The compression mechanism is driven by a crankshaft 48 connected by a frame 42 and supported by a pair of housings 44,46. A shaft 50 is connected to one end of the crankshaft 48, and the crankshaft 48 is rotationally driven by a drive motor 54 via a drive machine 52. A connecting rod 56 is provided on the crankshaft 48, and this connecting rod is adapted to be in sliding contact with an outer block 58 provided on the housing 44.46. This outer block 58 serves as a holder that supports the shaft 60. The shaft 60 has its tip (the left end in FIG. 1) in contact with an inner block 62 provided in the housing 44.degree. 62 for longitudinal reciprocating movement of the housing 44,46.

On the other hand, the initial position setting mechanism includes a nut 66 provided on the inner block 58 and a threaded portion 68 formed at the tip of the shaft 60 that is screwed into the nut 66. shirt)
The rear end side of 60 is a spline part 70, and this spline part 70 is provided in gear case 72.
It meshes with 4. The gear 74 meshes with a gear 76, and this gear 76 is rotated by a drive motor 82 via an input shaft 78 and a drive machine 80. Further, as shown in FIG. 2, the upper end of the inner block 62 is connected to a piston rod 86 of a balance cylinder 84 provided at the upper part of the frame 42. Furthermore, the reference numeral 88 shown in FIG. 1 indicates the center of the path of the workpiece.

The operation of the embodiment configured as described above is roughly divided into a small stroke high cycle compression operation and a large stroke low cycle initial position setting operation. The compression operation is performed by a drive motor 54.
The crankshaft 48 supported within the housing 44.46 rotates via the driving machine 52 and the shaft 50, and the eccentricity of the crankshaft 48 causes the connecting rod 56 to slide inside and outside the housing 44.46. block 62゜5
8 moves in the longitudinal direction of the housing 44, 46, and a forging tool 64 fixed to the inner block 62 reciprocates. That is, when the connecting rod 56 moves toward the path center 88, the forging tool 64 is pressed by a series of compression mechanisms and operates.
Furthermore, when the connecting rod 56 moves in a direction away from the path center 88, the balance cylinder 84 disposed on the frame 42 moves to the inner block 6 through the piston rod 86.
2 to the end of the shaft 60. Therefore, during the compression operation, the forging tool 64 always moves toward the crankshaft 48.
It performs reciprocating motion following the rotation of. Also, shaft 6
0 is because the threaded part 68 is engaged with the nut 66,
The shaft 6 together with the outer block 5g that houses the nut 66
0 also performs reciprocating motion.

At this time, a spline part 70 is formed at the rear end of the shaft 60, and this spline part 70 meshes with a gear 74, and since the gear 74 is fixed in the axial direction by a gear case 72, the gear 74 is fixed during the compression operation. The internal teeth of the shaft 60 and the spline portion 70 of the shaft 60 constantly perform sliding motion.

The initial position setting operation is performed as follows.

When the drive motor 82 is driven, the input shaft 78 and gears 76 and 74 supported by the gear case 72 via the drive machine 80
, the shaft 60 rotates, and the nut 66 and the threaded portion 68 of the shaft 60 connect the shaft 66 to the spline portion 70.
While sliding between the inner teeth of the gear 74 and the inner teeth of the gear 74, the outer block 5
8 as a base point and move in the axial direction. Also, inner block 6
2 is pressed against the tip of the shaft 60 by the balance cylinder 84. Therefore, as the input shaft 78 rotates, the gap between the inner block 62 and the outer block 58 increases or decreases, and the distance between the forging tool 64 and the connecting rod 56 increases or decreases.

The pair of left and right compression mechanisms and the pair of left and right initial position setting mechanisms are arranged approximately symmetrically with respect to the path center 88, and the left and right mechanisms can also be operated symmetrically with respect to the path center 88. Moreover, it is also possible to operate asymmetrically left and right if necessary.

FIG. 3 shows the trajectory of the pair of left and right forging tools 64 by each mechanism, and the initial position of the pair of left and right forging tools 64 is set by the initial position setting mechanism according to the dimensions of the workpiece and the amount of forging. However, it can be seen that forging can be performed by reciprocating the forging tool 64 using a compression mechanism and inserting a workpiece (not shown) in between. In the embodiment configured as described above, the inner and outer blocks 62.58 and the shaft 60.3 support the forging force generated on the forging tool 64 substantially on the extension of the line of action of the forging force. 1.
56ゎ15yl1m48 and 1. Since it is installed in the Aeca), the amount of deformation of the entire mechanism due to forging force can be kept to a minimum. In addition, an electric screw mechanism is adopted for the initial position setting mechanism, and assuming that the diameter of the shaft 6o is 350III11 and the tool stroke is 100 pieces, the amount of variation in the initial position due to forging force can be minimized as shown by the broken line in Figure 5. It can be kept to a small value. Therefore, the solid compression device of the example is a highly rigid device with less device deformation due to forging force compared to conventional devices.
It is possible to easily obtain products with good dimensional accuracy, and it can be said that it is a mechanism suitable for increasing machine performance and capacity.

Note that the balance cylinder 84 may be operated so as to press the inner block 62 against the tip of the shaft 60 at all times, but the drive energy of the compression mechanism can be reduced by operating it synchronously when the connecting rod 56 retreats. Then a tortoise is formed. Further, in the embodiment, the crankshaft 48
Although the outer block 58 is made to slide via the connecting rod 56 provided on the crankshaft 48, the outer block 58 may be provided directly on the crankshaft 48. Furthermore, the tip of the shaft 6o,
By rotatably coupling it to the inner block 62, the balance cylinder 84 can be omitted.

〔Effect of the invention〕

As explained above, according to the present invention, it is possible to obtain a highly rigid solid compression device that does not undergo large deformation during forging.

[Brief explanation of drawings]

FIG. 1 is a plan view showing a cross section of a part of an embodiment of the solid compression device according to the present invention, FIG. 2 is a side view of a part of the embodiment of the solid compression device according to the present invention, and FIG. The figure shows the locus of a forging tool in a solid compaction device according to an embodiment of the present invention, FIG. 4 is a side view of a conventional solid compaction device, and FIG. 5 shows a conventional solid compaction device and an embodiment according to the present invention. It is a figure showing a comparison of the dimensional error of the product by the forging load with the solid compaction device of . 44.46...housing, 48...crankshaft,
52.80... Drive mechanism, 54.82... Drive motor, 56... Connecting rod, 58... Outer block, 6
o...shaft, 62...inner block, 64...
Forging tool, 66... Nut, 68... Threaded part, 7o
...Spline part, 74.76...Gear, 84...
・ノ(Lance cylinder.

Claims (1)

[Scope of Claims] 1. A pair of slidable tools that apply an external force to a workpiece, which are disposed opposite to each other in a housing, and a drive device that applies reciprocating motion to the tools and moves them toward and away from each other; A solid compaction device having a position adjustment device that determines the initial position of the tool, wherein the drive device includes a crankshaft that rotates and a holder that is slidable forward and backward by the crankshaft;
A solid compression device comprising a shaft supported by the holder and for sliding the tool, and wherein the position adjustment device is a screw mechanism into which the shaft formed in the holder is screwed. 2. Each of the tools and the shaft are in surface contact, and each of the tools is connected to a cylinder that is biased in a direction to separate from each other when the shaft retreats. The solid compression device shown in Figure 1.