JP2002144089A - Pressurizing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a pressurizing device which makes it possible to obtain great working power in a working unit while assuring a relatively large stroke. SOLUTION: A boosting section of the pressure attachment equipped with the boosting section driven by a driving means on a substrate comprises a working cylinder 22, a pump piston 28, a plunger 25 and working piston 26 interposed in the working cylinder and arranged to face each other and a pump piston 29 interposed in the pump cylinder. One end of the plunger and the rod of the pump piston are connected and the rod of the working piston is formed engageably with the body to be pressurized. The plunger and the pump piston are driven by movement of the driving means to the side of the body to be pressurize. The body to be pressurized is worked by the plunger, the liquid in the working cylinder and the working piston.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to, for example, sheet metal working,
The present invention relates to a press working device used for punching and the like of a plate material. In particular, a combination of a reciprocating drive means and a hydraulic cylinder ensures a relatively large stroke and a large operating force on a pressurized body. And a pressurizing device that can obtain the following.

[0002]

2. Description of the Related Art Conventionally, as a means for driving a movable die of a processing unit having a movable die and a fixed die in a press processing device, a hydraulic cylinder has been widely used, and a hydraulic cylinder has been widely used. In a press working apparatus driven by a hydraulic cylinder, when a large operating force is applied to a working unit, a pressure increasing means applying the principle of Pascal is applied.

FIG. 4 is an explanatory view showing an example of a pressure increasing means that has been frequently used. 4, a plunger 101 and a piston 102 are interposed in a hydraulic cylinder 100, and an operating force is applied to a predetermined processing unit by a piston rod 103 connected to the piston 102. Assuming that the cross-sectional areas of the plunger 101 and the piston 102 are A _{1 and} A ₂ respectively, if a force of P ₁ is applied to the plunger 101, an operating force of P ₂ = P ₁ · A ₂ / A ₁ is applied to the piston rod 103. Is obtained.

[0004]

According to the pressure boosting means as shown in FIG. 4 above Disclosed be Solved by the Invention] By setting the ratio of A ₂ / A ₁ to a large, the operating force P ₂ of large become obtained. For example, the diameters of the plunger 101 and the piston 102 are each 40 mm,
Assuming 60 mm, the piston rod has P ₂ = 16P ₁
Is obtained, for example, if P ₁ = 7t, then P ₂
= 7 × 16 = 112 t, and even if the plunger 101 is driven with a relatively small force, a large operating force is obtained on the piston rod 103 that operates the machining unit.

[0005] However, while a large operating force can be obtained with the above-described pressure increasing means, the piston rod 103
Has a drawback that the stroke of the stroke is small. That is,
When the dimensions of the plunger 101 and the piston 102 are the above values, the plunger 101 is
m, the piston rod 103 has 200 × 1
Thus, only a stroke of /16=12.5 mm can be obtained.

In general, a working unit in a press working apparatus needs to insert and remove a work between a movable mold and a fixed mold, and the stroke of the movable mold operated by the piston rod 103 is as described above. For example, when it is small, such as 12.5 mm, in the case of punching or drilling a flat work,
For example, when performing a deep drawing operation, there is a problem that a predetermined stroke cannot be performed because a movable stroke is insufficient.

On the other hand, if the stroke of the plunger 101 is further increased in order to increase the stroke of the movable die, not only will the size of the pressure increasing means be increased, but also the work tact will become longer. Not practical. In order to secure the stroke of the piston rod 103, it is conceivable to separately supply hydraulic oil into the hydraulic cylinder 100 above the piston 102. In this case, it is necessary to prepare a hydraulic unit including a hydraulic pump. In addition to the necessity, there is a problem that energy consumption increases.

SUMMARY OF THE INVENTION It is an object of the present invention to solve the problems existing in the prior art and to provide a pressurizing device capable of obtaining a relatively large stroke while providing a large operating force to a machining unit. .

[0009]

In order to solve the above-mentioned problems, the present invention provides a pressurizing device provided with a pressure increasing portion driven by a driving means on a substrate. , An operating cylinder, a pump cylinder, a plunger and an operating piston interposed in and opposed to the operating cylinder, and a pump piston interposed in the pump cylinder, and one end of the plunger and the pump piston And the rod of the working piston is formed so as to be engageable with the pressurized body, and the plunger and the pump piston are driven by moving the driving means toward the pressurized body. And a means for operating the pressurized body via the liquid in the working cylinder and the working piston.

In the present invention, a check valve is provided in which the rod-side ends of the working cylinder and the pump cylinder are connected so that liquid can flow therethrough, and the piston-side ends of the working cylinder and the pump cylinder are provided in parallel. It is connected via a switching valve, so that the piston-side end of the working cylinder, the rod-side end and the piston-side end of the pump cylinder, and the accumulator can be connected via independent check valves.

Next, in the above invention, the driving means can be constituted by a mechanism including a servomotor and a screw pair, and in this case, the screw pair may be constituted by a ball screw.

[0012]

FIG. 1 is a front view of a main part showing an embodiment of the present invention. In FIG. 1, for example, guide bars 2 are erected at four corners of a substrate 1 formed in a rectangular shape, and a support plate 3 is fixed to an upper end of the guide bar 2 via an appropriate fastening means. Reference numeral 4 denotes a slider, which is interposed on the guide bar 2 so as to be slidable in the vertical direction. Reference numeral 5 denotes a nut member, which is integrally provided on the upper surface of the central portion of the slider 4 and screwed with a screw shaft 7 connected to a main shaft of a servo motor 6 provided on the upper surface of the support plate 3. In this case, the screw shaft 7 and the nut member 5 are preferably ball screws. The above constitutes the main body 8 of the press working device.

Reference numeral 9 denotes a processing unit which includes a pressure-intensifying unit 10 which will be described later, includes a movable die 11 and a fixed die 12, and is provided between the substrate 1 and the slider 4 in a detachable manner. Can be In the processing unit 9, for example, a support plate 15 is fixed to an upper end of a guide bar 14 erected at four corners of a substrate 13 formed in a rectangular shape, and a pressure increasing portion 10 is provided on the support plate 15. Configuration.

The pressure increasing section 10 is driven by the vertical movement of the slider 4 as described later, and further operates the movable mold 11. The movable mold 11 may be configured to be constantly urged upward by, for example, a spring (not shown) or other means. The movable mold 11 and the fixed mold 12 are provided with, for example, a punch pad 16, a stripper 17, and a die 18 in a detachable manner.

FIG. 2 is an enlarged vertical sectional view of a main part showing the pressure increasing portion 10 in FIG. 1. The left side of the center line shows the upper end position of the movable member, and the right side shows the lower end position of the movable member. FIG. 3 is FIG.
FIG. 2 is a sectional view taken along line AA of FIG. 2 and 3, reference numeral 21 denotes a hydraulic cylinder, which is formed, for example, in a hollow cylindrical shape, and is provided at its center with cylinder spaces 23 and 24 constituting an operating cylinder 22 so as to communicate with each other. The cylinder spaces 23 and 24 are preferably formed, for example, so that their axes are the same, but may be formed slightly differently. A plunger 25 and a working piston 26 are interposed in the cylinder spaces 23 and 24 so as to be vertically slidable and opposed to each other, and a rod 27 of the working piston 26 is projected below the hydraulic cylinder 21.

Reference numeral 28 denotes a pump cylinder, which is formed so as to have an axis parallel to the axis of the working cylinder 22, for example, so that the axis is located on the same circumference in the upper half of the hydraulic cylinder 21. Four are provided at equal intervals in the circumferential direction. A pump piston 29 is interposed in the pump cylinder 28 so as to be slidable in the vertical direction, and their rods 30 project upward. Reference numeral 31 denotes a support plate that supports the upper ends of the plunger 25 and the rod 30, and is formed so as to be simultaneously movable.

A cover member 32 is provided at the upper end of the hydraulic cylinder 21 and closes the upper openings of the cylinder space 24 and the pump cylinder 28. The working piston 2
6 and the sliding portion of the pump piston 29 with the cylinder space 23 and the pump cylinder 28 and the hydraulic cylinder 2
An appropriate liquid sealing means such as an O-ring or packing (not shown) is provided at the upper and lower end portions of 1 and the sliding portion between the lid member 32 and the plunger 25 and the rods 27 and 30. The support plate 31 is connected to the slider 4 shown in FIG. 1, and the rod 27 of the working piston 26 is formed so as to be engageable with the movable die 11 of the processing unit 9 shown in FIG.

Next, the ends of the cylinder space 23 and the pump cylinder 28 on the side of the rods 27 and 30 are formed so that liquid can flow therethrough, and the ends of the cylinder space 23 and the pump cylinder 28 on the side of the working piston 26 and the pump piston 29 are respectively formed. The parts are connected via a check valve 33 and a switching valve 34 provided in parallel. The end of the cylinder space 23 on the side of the working piston 26 and the accumulator 35 are connected via a check valve 36, and the end of the pump cylinder 28 on the side of the rod 30 and the end of the pump piston 29 on the side of the accumulator 35 are connected to each other. , Are connected via check valves 37 and 38 and check valves 39 and 40 provided in parallel.

The accumulators 35 are formed, for example, in a cylindrical shape having a closed space, and four accumulators 35 can be provided on the cover member 32 at equal intervals on the same circumference. in this case,
Of course, the support plate 31 and the slider 4 shown in FIG. 1 are provided with appropriate notches or openings at positions corresponding to the accumulator 35 to prevent interference. Further, the accumulator 35 may be provided independently of the hydraulic cylinder 21, and the accumulator 35 may be connected to the pressure increasing unit 10.
, For example, between the pump cylinders 28, 28.

With the above configuration, when the screw shaft 7 is rotated by the operation of the servo motor 6 shown in FIG. 1, the slider 4 moves downward via the nut member 5 screwed with the screw shaft 7. That is, in FIG. 2, the plunger 25, the rod 30, and the pump piston 29 move downward by the downward movement of the support plate 31 connected to the slider 4 shown in FIG. In this case, the switching valve 34 is closed as shown in FIG.

When the plunger 25 and the pump piston 29 move downward from the state shown on the left side of the center line in FIG.
The hydraulic oil in the cylinder space 24 is supplied into the cylinder space 23 above the working piston 26, and the hydraulic oil in the pump cylinder 28 is also supplied into the cylinder space 23 via the check valve 33. , The working piston 26 moves downward. On the other hand, the working oil below the working piston 26 flows above the pump cylinder 28, so that the working piston 26 can be smoothly moved downward. When the working piston 26 moves a predetermined distance, the rod 27 operates the movable mold 11 shown in FIG. 1 to perform a predetermined processing.

In this case, since a relatively large amount of working oil is supplied into the cylinder space 23, the working piston 26
Is also relatively fast. When a load from below is applied to the rod 27 and the working piston 26 by the operation of the movable mold 11, the pressure of the working oil above the working piston 26 rises due to the lowering of the plunger 25, and the check valve 36 Set pressure (for example, 250 kg / cm
² ) rise up. Thereby, the operating force transmitted to the operating piston 26 and the rod 27 becomes a large operating force corresponding to the ratio of the cross-sectional area of the plunger 25 and the operating piston 26, and can operate the movable mold 11 shown in FIG. .

As described above, the rod 30 and the pump piston 29 also move downward at the same time as the plunger 25 moves downward. However, if the pressure rises in the cylinder space 23 above the working piston 26, Although the hydraulic oil below the pump piston 29 cannot flow into the cylinder space 23, the hydraulic oil flows through the check valve 39 to the accumulator 35 and is stored. Therefore, the downward movement of the plunger 25 is performed smoothly, and the plunger 25 is in the state shown on the right side of the center line in FIG. 2, and the pressure of the hydraulic oil in the cylinder space 23 can be increased. In this case, the set pressure of the check valve 39 is lower than that of the check valve 36, for example, 5
kg / cm ² .

Next, a description will be given of a mode of returning from the state shown on the right side of the center line in FIG. 2 to the initial state. In the above state, the plunger 25, the rod 30 and the pump piston 29 are raised via the support plate 31 by the reverse operation of the servo motor 6 shown in FIG.

When the plunger 25 rises, the pressure of the hydraulic oil in the cylinder space 23 above the working piston 26 decreases, while when the pump piston 29 rises, the working oil in the pump cylinder 28 above the pump piston 29 operates. The working piston 26 is also raised by being supplied to the cylinder space 23 below the piston 26. In this case, the hydraulic oil in the cylinder space 23 above the working piston 26 flows into the pump cylinder 28 below the pump piston 29 via the switching valve 34 that has been opened, so that the plunger 25 and the pump The piston 29 is smoothly raised, and returns to the state on the left side of the center line in FIG.

When the pump piston 29 moves in the vertical direction, a shortage due to exhaustion or leakage of hydraulic oil is supplied from the accumulator 35 into the pump cylinder 28 through the check valves 38 and 40. The above-mentioned plunger 25, pump piston 29 and working piston 2
6 can be smoothly moved without any trouble.

In the embodiment described above, the plunger 25, the rod 30, and the pump piston 29 move up and down in synchronization with each other.
0 is attached to the support plate 31 via a spring or the like,
The rod 30 and the plunger 25 may be formed so as to move slightly relative to each other. The set pressure applied to the check valves 33, 36 to 40 can be appropriately selected in consideration of the operating force to be applied to the processing unit 9.

In the above embodiment, the operating piston 26 and the rod 27 have been described as having a solid shape. However, they may be formed into a hollow cylindrical shape having a bottom or a concave portion having an opening at an upper portion. It may be formed so that the lower end of the plunger 25 can enter the hollow portion or the concave portion through a predetermined gap. With this configuration, the strokes of the working piston 26 and the rod 27 can be increased.

Further, in the above embodiment, the example of the hydraulic cylinder using the hydraulic oil has been described, but water or other liquid may be used. In the embodiment of the invention described above, the so-called vertical type in which the substrate 1 and the support plate 3 are arranged in parallel with the horizontal plane and the guide bar 2 connecting them is provided in the vertical direction has been described. 1
And the support plate 3 is parallel to the vertical plane and the guide bar 2
The present invention is also applicable to a so-called horizontal type in which is provided in a horizontal direction.

Next, the present invention is particularly effective for the case where the screw shaft 7 and the nut member 5 are in ball screw engagement. However, the present invention is also applicable to the case where both are in normal screw engagement. is there. Of course, it is also possible to use a multi-thread or a multi-thread, including a ball screw engagement. The servo motor 6 for driving the screw shaft 7 is most commonly connected directly to the screw shaft 7 coaxially. However, the servo motor 6 is configured to transmit power via transmission means such as a gear and a timing belt. Is also good.

The screw shaft 7 is used for moving the slider 4.
Has been described, the screw shaft 7 may be fixed to the slider 4 and the nut member 5 screwed to the screw shaft 7 may be driven by the servo motor 6. Further, a crank mechanism may be used as a driving means of the slider 4.

Further, the guide bar 2 for guiding the movement of the slider 4 is preferably a plurality of guide bars for large ones or those requiring rigidity. However, one guide bar may be used. It may be formed in a beam shape, and the slider 4 slides or slides along the side surface.

Further, in addition to the single use of the pressurizing device of the present invention, a plurality of pressurizing devices may be arranged in tandem, for example, for progressive feeding of a long workpiece. Applicable. The pressurizing device of the present invention can be used for processing of assembling a plurality of parts, press fitting, caulking, and the like, in addition to sheet metal processing for a plate material.

[0034]

According to the present invention, the configuration and operation as described above, the following effects can be obtained.

(1) The movable stroke required for the machining unit can be made relatively large. In particular, the range in which the operating force is small is moved at a relatively high speed, and the range is large during the final relatively short stroke. Operating force can be obtained.

(2) A predetermined large operating force can be obtained at any position between the initial position and the final position of the movable member.

(3) For example, an extremely small amount of hydraulic oil is required to operate the apparatus, and it is not necessary to supply high-pressure hydraulic oil such as a hydraulic unit, so that energy consumption is extremely small.

[Brief description of the drawings]

FIG. 1 is a front view of a main part showing an embodiment of the present invention.

FIG. 2 is an enlarged vertical cross-sectional view of a main part showing a pressure booster 10 in FIG.

FIG. 3 is a sectional view of a main part taken along line AA in FIG. 2;

FIG. 4 is a diagram showing an example of a pressure increasing means that has been frequently used in the related art.

[Explanation of symbols]

 8 Body 9 Processing Unit 10 Booster 22 Working Cylinder 25 Plunger 26 Working Piston 28 Pump Cylinder 29 Pump Piston

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3H086 AA25 AA29 AB03 BA03 BA14 BA19 BC12 4E090 AA01 AB01 BA01 CA03 CC04 HA01

Claims (4)

[Claims] 1. A pressurizing device comprising a pressurizing section driven by driving means on a substrate, wherein the pressurizing section is interposed and opposed to a working cylinder, a pump cylinder, and the working cylinder. The plunger and the working piston are arranged, and a pump piston interposed in the pump cylinder, and one end of the plunger is connected to a rod of the pump piston. The plunger and the pump piston are driven by moving the driving means toward the pressurized body, and the plunger is
A pressurizing device, wherein the pressurized body is operated via a liquid in an operation cylinder and an operation piston. 2. A check valve and a switching valve in which the rod-side ends of the working cylinder and the pump cylinder are connected so that liquid can flow therethrough, and the piston-side ends of the working cylinder and the pump cylinder are provided in parallel. Wherein the end of the working cylinder on the piston side, the end of the pump cylinder on the rod side and the end of the piston, and the accumulator are connected via independent check valves, respectively. Item 2. The pressurizing device according to Item 1. 3. The pressurizing device according to claim 1, wherein the drive means is constituted by a mechanism including a servomotor and a screw pair. 4. The pressurizing device according to claim 3, wherein the screw pair is constituted by a ball screw.