JP2019044781A - Local pressurization device and hydraulic deformation correction device with local pressurization device - Google Patents

Abstract

To easily perform high-accuracy protrusion amount adjustment even in a drafting ranger of a high drafting force and to prevent occurrence of damage or the like.SOLUTION: A local pressurization device comprises: a ball screw mechanism 3 consisting of a screw shaft 10 in which a ball groove 12 is provided, and a nut member 11 threaded to the screw shaft 10 via a ball 13 that is fitted into the ball groove 12; a drive part 4 for imparting a torque to the screw shaft 10 or the nut member 11 of the ball screw mechanism 3; a rod-shaped member 5 which is coupled to the screw shaft 10 or the nut member 11 of the ball screw mechanism 3 and provided in an axial direction of the screw shaft 10; and a brake mechanism 6 which brakes axial movement of the rod-shaped member 5 by radially pressurizing an outer surface of the rod-shaped member and then cancels the pressurization, thereby switching the rod-shaped member 5 in an axially freely movable manner.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a local pressure device and a hydraulic deformation correction device including the local pressure device.

  In die-casting such as aluminum, a molded body of about 600 ° C. is taken out from the mold (hereinafter this molded body is referred to as a “die-cast molded body” regardless of the temperature level) and then subjected to heat dissipation (cooling period) thereafter Although it is sent to the next step, it is known that warpage, bending and the like occur in the die cast molded body due to contraction at the time of heat radiation. Such warpage, bending and the like are generally corrected by performing hammering by a skilled person at the stage when the die cast molded body is cooled to room temperature.

By the way, unlike the case of the die cast molded body, in the process of manufacturing a thin sheet metal chassis, the chassis is strongly pressed by the punch while adjusting the projection amount of the punch to be brought into contact with the one side with the cam. There has been proposed a correction mold for correcting the lack of precision and the like occurring in the chassis (see Patent Document 1).
When such a correction mold is used, the die cast molded body is considerably thicker than the chassis, so that it is not possible to correct the bottom, the warp, the bend, and the like. However, if it is assumed that the die cast molded body is pressed with a large rolling force by using a projection that replaces punch, a hint that warpage, bending or the like occurring in the die cast molded body can be corrected Become

  For example, if the projection is replaced with a hardening bolt (called "cap screw"), adjustment of the degree of screwing to the mounting base allows adjustment of the amount of projection of the projection each time It is considered to be. However, such adjustment of the degree of screwing is troublesome and complicated, and it is not difficult to imagine that the working efficiency is extremely deteriorated. Therefore, it is conceivable to replace the projection with a known hydraulic cylinder with a ball screw mechanism (see Patent Document 2).

A hydraulic cylinder with a ball screw mechanism is a hydraulic cylinder in which a ball screw mechanism driven by an electric motor is incorporated in the cylinder, and the ball screw mechanism and a hydraulic system are used in combination to move the piston.
The hydraulic cylinder with a ball screw mechanism operates only the ball screw mechanism when moving the piston with low load, and operates the combination of the ball screw mechanism and the hydraulic system well when moving the piston with high load. As a result, it is supposed that the good point of both high precision movement by a ball screw mechanism and high load movement by a hydraulic system can be used.

JP 10-98283 A JP-A-7-77210

  In a hydraulic cylinder with a ball screw mechanism, since it is an essential requirement to exhibit smooth expansion and contraction, it is essential to use a ball screw, not a slide screw or a trapezoidal screw, as the main mechanism. Needless to say, with a ball screw, hold the ball in between the screw shaft and the nut member, and make a point contact between the ball and the ball groove provided on the screw shaft or the nut member (make the contact resistance as small as possible). There is technical importance to

On the other hand, smooth operation can be obtained simply by applying an external force along the axial direction to the screw shaft or nut member while stopping relative rotation between the screw shaft and the nut member. Can be said to cause relative rotation between the screw shaft and the nut member.
Therefore, assuming that the die cast molded body is pressed down using a hydraulic cylinder with a ball screw mechanism, the screw shaft and the nut member rotate relative to each other under the pressing force, and the amount of pressing becomes unstable (high precision rolling To face the problem of

In addition, the point contact between the ball and the ball groove of the screw shaft or the nut member means that the high contact pressure during rolling is applied to this contact point, which causes the ball screw mechanism to be damaged. Well, naturally, it is predicted.
The present invention has been made in view of the above circumstances, and it is possible to easily adjust the amount of projection with high accuracy even in the pressure reduction region under high pressure, and to prevent breakage etc., die casting A local pressure device, which can be suitably used in cases where mechanical correction is performed, etc. without relying on manual work or the like of a skilled person, such as warping or bending occurring in a thick molded body such as a body An object of the present invention is to provide a hydraulic deformation correction device provided with a local pressure device.

In order to achieve the above object, the present invention takes the following measures.
That is, in the local pressure device according to the present invention, the screw shaft is provided with a helical ball groove surrounding the outer peripheral surface, and is screwed through the ball screwed in the ball groove to the screw shaft. Ball screw mechanism constituted by a nut member, a drive unit for applying a rotational force to the screw shaft of the ball screw mechanism or the nut member, and extending in the axial direction with respect to the screw shaft of the ball screw mechanism The axial movement of the rod-like member is damped by radially pressing the rod-like member provided or the rod-like member coupled to the nut member and projecting in the axial direction of the screw shaft and the outer surface of the rod-like member And a braking mechanism configured to be able to switch the rod-like member so as to be axially movable by releasing the pressure.

The braking mechanism includes: a chuck member including a through hole through which the rod-like member passes and a slit dividing the through hole in a radial direction; a tightening force directed radially inward on the outer peripheral surface of the chuck member It can comprise by the collet mechanism provided with the holding body which can be made to load or to release the said clamping force.
The ball screw mechanism and the drive unit may constitute an electric cylinder by using an electric motor for the drive unit.

  On the other hand, in the hydraulic deformation correction device including the local pressure device according to the present invention, the slide frame and the bolster are disposed to face each other to form a pressure reduction area between the slide frame and the bolster. And / or the bolster is provided with a projecting member projecting toward the inside of the pressure reduction area, and the projecting member is constituted by the rod-like member of the local pressure device according to the present invention. .

The projecting member constituted by the local pressure device may be provided on both the slide frame and the bolster.
The projection member constituted by the local pressure device may be disposed to face each other between the slide frame and the bolster.

  According to the local pressure device and the hydraulic deformation correction device having the local pressure device according to the present invention, the projection amount adjustment with high accuracy can be easily performed even in the pressure reduction region under high pressure, and moreover, breakage or the like does not occur. As a result, it is suitably used when mechanically correcting warpage, bending, etc. occurring in a thick molded article such as a die cast molded article without relying on the manual work of an expert or the like. be able to.

It is a side view showing a local pressurization device concerning the present invention, and (a) is a contraction state, and (b) is an extension state. It is the side view which partially broken and showed an example of the electrically-driven cylinder used for the local pressurization apparatus which concerns on this invention. It is a side sectional view showing an example of a braking mechanism used for a local pressurization device concerning the present invention. 1 is a perspective view showing a hydraulic deformation correction device according to the present invention. It is the perspective view which showed the local pressurization apparatus used for the hydraulic deformation correction apparatus which concerns on this invention. It is the perspective view which showed an example of the die cast molded object. It is a side view explaining the situation which corrects a die cast molding, and (a) is the situation before correction, and (b) is the situation under correction. It is a side view which explained bending, curvature, etc. which arise in a die cast molded object intelligibly.

Hereinafter, embodiments of the present invention will be described based on the drawings.
1 to 3 show an embodiment of a local pressure device 1 according to the present invention. For example, as shown in FIG. 4 and FIG. 5, this local pressure application device 1 is subjected to deformation such as warpage or bending that has occurred in a die-cast molded body W or the like illustrated in FIG. Are preferably used. First, the local pressure device 1 will be described.

As apparent from FIG. 1, the local pressure device 1 according to the present invention has the ball screw mechanism 3 and the drive unit 4, and the rod member 5 is partially integral with or separate from the ball screw mechanism 3. Further, a braking mechanism 6 is provided to the rod-like member 5.
The ball screw mechanism 3 has a screw shaft 10 and a nut member 11 screwed to the screw shaft 10 as shown in FIG. The screw shaft 10 is provided with a spiral ball groove 12 so as to surround the outer peripheral surface thereof, and a plurality of balls 13 rotatably fitted in the ball groove 12 of the screw shaft 10 are screwed in the nut member 11. It is held so as to be interposed between the shaft 10 and the shaft 10.

  In the present embodiment, a slider 17 shaped to project outward of the nut member 11 is coupled to the nut member 11, and the longitudinal direction of the screw shaft 10 is directed in the axial direction via the slider 17. A hollow cylinder rod 18 is shown connected. Further, the tip end portion (the end portion on the upper side in FIG. 2) of the screw shaft 10 is rotatably held in the cylinder rod 18 via a bearing 19.

The nut member 11 and the slider 17 having the screw shaft 10 as a core are accommodated in the cylinder 20 as a whole, and the tip of the cylinder rod 18 (the end on the upper side in FIG. 2) protrudes from the cylinder 20 It is supposed to be.
The slider 17 is formed of a material or a structure excellent in slidability in the cylinder 20, and is guided so as to be slidable along the axial direction of the screw shaft 10. However, at the same time, it has a detent structure in the cylinder 20, and rotation around the screw shaft 10 during sliding is held in a non-possible state.

Therefore, by rotating the screw shaft 10, the nut member 11 moves in the axial direction of the screw shaft 10, and along with the nut member 11, the cylinder rod 18 expands and contracts with respect to the cylinder 20.
The driving unit 4 is for applying relative rotational force between the screw shaft 10 and the nut member 11 to the ball screw mechanism 3 and has an electric motor and a reduction gear (all not shown). ing. In the present embodiment, the proximal end (the end on the lower side in FIG. 2) of the screw shaft 10 is connected so as to apply rotational drive. As the electric motor, it is preferable to adopt a type capable of controlling the rotational angle and rotational speed of a stepping motor or the like with high accuracy.

By providing the ball screw mechanism 3 and the drive unit 4 as described above, the electric cylinder 21 is configured.
The rod-like member 5 is provided so as to extend the longitudinal direction (the same as the axial direction of the screw shaft 10) with respect to the cylinder rod 18 of the ball screw mechanism 3 as shown in FIG. Specifically, a female screw 23 (see FIG. 2) is provided at the tip of the cylinder rod 18, and the male screw 24 corresponding to the female screw 23 (see FIG. 1) is provided on the rod member 5. The cylinder rod 18 and the rod-like member 5 are connected by screwing the female screw portion 23 and the male screw portion 24 with each other.

As described above, in the present embodiment, since the cylinder rod 18 is connected to the nut member 11 via the slider 17, it can be said that the rod-like member 5 has an indirect coupling relationship with the nut member 11.
In addition, a linear motion guide 25 (referred to as a product name such as "Linear Guide", "LM Guide", "Linear Way", etc.) is provided at the connecting portion between the cylinder rod 18 and the rod-like member 5, The fixed side (the rail side in the illustrated example) is to be fixed to the vertical frame material or the like of the device to be installed.

By providing the linear motion guide 25, rotation of the slider 17 in the rod-like member 5 and the cylinder 20 is suppressed when the ball screw mechanism 3 performs expansion and contraction, and connection of the cylinder rod 18 and the rod-like member 5 is achieved. The effect of reinforcing the space and further stabilizing the expansion and contraction operation of the cylinder rod 18 and the axial movement of the rod-like member 5 can be obtained.
As described above, it is necessary to prevent scratches, for example, when this local pressure device 1 is used in a hydraulic deformation correction device 2 for correcting bending, warp or the like of a die cast molded body W (see FIG. 6). In this case, it is preferable to provide a soft (specifically, polyacetal or the like) working end 28 at the tip end of the rod-like member 5 (the end opposite to the cylinder rod 18 side). However, when there is no need to prevent scratches, the working end 28 may be made of a hard material (high strength metal material or the like) or the working end 28 may be omitted.

  In addition, it is preferable that the screw shaft 10, the cylinder rod 18, and the rod-like member 5 of the ball screw mechanism 3 have a concentric uniaxial arrangement. Further, the motor axes of an electric motor (not shown) used for the drive unit 4 can also be aligned in the same uniaxial arrangement. However, it is also possible to arrange the motor shaft so as to be eccentric or perpendicular to the rod member 5 or the like depending on the combination of the gear mechanisms provided in the reduction gear for the electric motor.

The braking mechanism 6 is fixed to a vertical frame member or the like of a device to be installed in a configuration in which the rod-like member 5 is held. The braking mechanism 6 does not disturb the movement of the rod-like member 5 when not in operation, and by operating, the rod-like member 5 is braked to immobilize the axial movement.
In the present embodiment, the braking mechanism 6 is configured by a collet mechanism 31 as shown in FIG. That is, the braking mechanism 6 (collet mechanism 31) has a chuck member 32 and a gripping body 33, and the gripping body 33 is accommodated in the hydraulic case 34.

  The chuck member 32 is formed in a cylindrical shape with a through hole 35 through which the rod-like member 5 passes. This cylindrical shape is a tapered cylinder whose diameter is reduced at one end surface side (upper side in FIG. 3) in the direction in which the rod-like member 5 is extended by the ball screw mechanism 3. Then, a slit (not shown) is formed which passes through the through hole 35 in the radial direction with respect to the end face on the small diameter side of the cylindrical shape.

  The slit is formed so as to connect the cylindrical circle center and the radially outward, and does not extend to the entire length of the cylindrical shape. That is, although the end face of the small diameter side of the cylindrical shape (having an annular shape) is divided into a plurality of fan-shaped pieces by the slitting, the cutting does not extend to the end face of the large diameter side. The division also does not reach the full length of the cylindrical shape (a part connected in the circumferential direction remains near the end face on the large diameter side).

In addition, the arrangement and formation number of the slices are two (two at 180 ° intervals) dividing the cylindrical end face (annular shape) into two, three (three intervals (120 °)), three equal, etc. It may be four (90 ° intervals) to divide. Of course, other arrangements and numbers may be used.
The gripping body 33 is formed in a cylindrical shape such that the chuck member 32 is fitted around the entire circumference. In the cylindrical hole into which the chuck member 32 is fitted, a taper having the same direction as the taper given to the chuck member 32 is attached.

In the present embodiment, a plurality of balls 36 are held between the chuck member 32 and the gripping body 33 in a row in the axial direction of the rod-like member 5. The gripping body 33 and the chuck member 32 What reduced the sliding resistance between and is illustrated. However, such a ball 36 is not essential.
The hydraulic case 34 is configured to be capable of holding the holding body 33 accommodated therein in a movable state along the axial direction of the rod-like member 5. In the hydraulic case 34, a spring 37 is accommodated so as to hold the gripping body 33 at the same position as the small end surface of the chuck member 32.

Further, an inflow port 38 is provided to apply hydraulic pressure in such a direction as to press the gripping body 33 against the bias position (downward in FIG. 3) in the hydraulic case 34 against the biasing action of the spring 37.
In the braking mechanism 6 having such a configuration, by applying hydraulic pressure to the inflow port 38, the gripping body 33 moves (downward) in the hydraulic case 34 while resisting the spring 37, and the inner circumferential surface of the gripping body 33 The contact relationship between the attached taper and the taper applied to the outer peripheral surface of the chuck member 32 is strengthened, and a radially inward tightening force is applied to the outer peripheral surface of the chuck member 32.

Along with this, the chuck member 32 further reduces the diameter of the end surface on the small diameter side while reducing the slip, and the diameter reduction force strongly pressurizes the outer peripheral surface of the rod-like member 5. The axial movement of the member 5 is immovably braked.
During such operation of the braking mechanism 6 (when the axial movement of the rod member 5 is immovably braked), it is assumed that a large pressing force is loaded on the tip end portion (working end 28) of the rod member 5 Also, this load is absorbed by the vertical frame material or the like of the device to be installed through the braking mechanism 6 and is not transmitted to the ball screw mechanism 3. Therefore, the ball screw mechanism 3 is not damaged or broken.

  On the other hand, by releasing the hydraulic pressure applied to the inflow port 38 of the hydraulic case 34, the gripping body 33 is pushed back to the position before movement by the spring 37, and the clamping force on the outer peripheral surface of the chuck member 32 is released. Because of this, the chuck member 32 is expanded in the form of slices and the diameter reduction is released, and the pressure applied to the outer peripheral surface of the rod-shaped member 5 is also released. Thereby, the rod-like member 5 is held in the state of being movable in the axial direction again.

Next, the hydraulic deformation correction device 2 according to the present invention will be described.
As shown in FIG. 4, the hydraulic deformation correction device 2 according to the present invention has a configuration in which the slide frame 50 and the bolster 51 are disposed to face each other, and the slide frame 50 uses a hydraulic pressure as a drive source and a column. An operation of moving close to and away from the bolster 51 is performed along 52, thereby forming a pressure reduction area between the slide frame 50 and the bolster 51.

Note that the upper and lower molds and the like may be attached to the slide frame 50 and the bolster 51 to constitute a hydraulic press, or the case where the slide frame 50 and the bolster 51 are not attached There is no problem in the practice of the present invention even in the case of exclusive use as 2).
Further, in the illustrated example, the vertical hydraulic deformation correction device 2 in which the slide frame 50 is disposed on the upper side and the bolster 51 is disposed on the lower side is shown, but it is not limited thereto. It is also possible to target a horizontal-type hydraulic deformation correction device in which the

In the hydraulic deformation correction device 2 according to the present invention, the slide frame 50 and the bolster 51 are provided with the projecting members 55 that project toward the inside of the rolling area.
As shown in FIG. 5, in the present embodiment, eleven protrusion members 55 are provided on each of the slide frame 50 and the bolster 51, and these protrusion members 55 are arranged opposite to each other between the slide frame 50 and the bolster 51 ( The figure shows an example in which the coaxial arrangement is made in the vertical direction.

The projecting members 55 are each constituted by the rod-like member 5 (working end 28) of the local pressure device 1 according to the present invention.
In addition, in order to set the mutual spacing of the projecting members 55 narrowly, the installation height of the braking mechanism 6 is shifted to include a point devised to avoid contact interference between the braking mechanisms 6 adjacent to each other.
The correction work of the die cast molded body W performed using the hydraulic deformation correction device 2 of the present invention having such a configuration may be performed based on the following operation principle.

  As shown in FIG. 7A, assuming that warpage, bending or the like (hereinafter simply referred to as “deformation etc.”) is generated in the die cast molded body W, both ends of the die cast molded body W While the lower surface of the portion is supported by the lower arrangement projection member 55D, the upper surface between the both ends of the die cast molded body W (preferably near the summit) is pressed down by the upper arrangement projection member 55U. By doing so, the deformation and the like of the die cast molded body W can be brought closer to a flat state.

However, in an actual die-cast molded body W, as shown in FIG. Therefore, it makes sense to provide a plurality of projecting members 55U on the upper side and a plurality of projecting members 55D on the lower side. It is also meaningful to arrange the projecting members 55U on the upper side and the projecting members 55D on the lower side opposite to each other. Become.
By adopting this arrangement, the functions of both the support and the press can be distributed in a well-balanced manner to the projecting members 55. In addition, it is desirable to adopt a method of retracting the support side by the same amount according to the pressed side between the protruding member 55U on the upper side and the protruding member 55D on the lower side. In this way, it is possible to relieve the localized deformation load on the die cast molded body W, and to obtain an advantage of not disturbing the positional stability of the die cast molded body W.

By the way, as shown in FIG. 7A, the maximum value of the deformation of the die cast molded body W, etc. is h (the height difference from the ideal shape, which will be hereinafter referred to as the “maximum deformation value h”). When it is assumed, how much the projection member 55U in the upper position is pressed down varies depending on the backlash peculiar to the die cast molded body W to be corrected.
That is, various materials such as the material of the die cast molded body W, thickness, planar size, cross sectional shape of the correction portion, temperature at correction, correlation between the magnitude of warpage or bending and mutual spacing in the projection member 55 on the support side It is because it is necessary to judge taking into consideration the conditions.

In particular, as illustrated in FIG. 6, the die cast molded body W is provided with a rib R, an opening H, a step S, a pin P, and the like. Since various shapes may be mixed, such as a portion where the thickness is different due to the root of the pin P, etc., these complicate setting of the pressing amount as a further variable.
From the results of many experiments conducted by the present inventors, it is not enough to cope with such backlash with various changes just by making the pressing amount of the protruding member 55U in the upper position equal to the deformation maximum value h. Thus, as shown in FIG. 7B, it is found that it is necessary to calculate the deformation maximum value h by multiplying the various condition variables α. Note that such various condition variables α can be quantified and made into equations based on empirical rules by the skilled person, statistics by experiments, and the like.

The pressing of the projecting members 55U and 55D against the die cast molded body W may be performed in the following procedure.
First, the die-cast molded body W is appropriately fixed by a clamp or the like in a pressure reduction region between the slide frame 50 and the bolster 51. At this time, the distance between the lower-placed projecting member 55 provided on the bolster 51 and the die cast molded body W is arranged to be accommodated within the expansion and contraction stroke provided in the ball screw mechanism 3 of the local pressure device 1.

Next, the slide frame 50 is idled toward the bolster 51 side, and the ball screw of the local pressure device 1 is also provided for the distance between the projection member 55U disposed on the slide frame 50 and the die cast molded body W. The arrangement is made to fit within the telescopic stroke provided in the mechanism 3.
Next, all the upper and lower local pressing devices 1 are operated to measure the distance until the projection member 55U of the upper arrangement and the projection member 55D of the lower arrangement abut on the die cast molded body W, respectively. The measurement value detected by this measurement is determined as a difference from the measurement value (master value) when the ideal form (the form which is not deformed at all) of the die cast molded body W is measured. That is, this is the “deformation amount” of the die cast molded body W.

  Next, the amount of deformation determined by the protruding member 55U in the upper position is set as the pressing amount (the value obtained by multiplying the maximum value h of deformation by the condition variable α) of the protruding member 55D in the lower position opposed thereto, The amount of deformation obtained by the side-arranged projection member 55D is set as the amount of depression of the upper-side arrangement projection member 55U opposite thereto (the value obtained by multiplying the deformation maximum value h by the condition variable α). That is, the amount of deformation measured for the upper and lower projection members 55 is replaced.

Then, based on the pressing amount, the ball screw mechanism 3 of the local pressure application device 1 constituting the upper projecting member 55U and the lower projecting member 55D is operated.
Although it is necessary to move the projecting member 55U on the upper side and the projecting member 55D on the lower side with high precision of 1/100 [mm] to derive the deformation amount and to realize the pressing amount, these movements are This is achieved by the ball screw mechanism 3 provided in the local pressure device 1 according to the present invention.

Next, the slide frame 50 is moved down to the bolster 51 side so that a state in which all of the projection member 55U of the upper arrangement and the projection member 55 of the lower arrangement press against the die cast molded body W can be obtained. Do.
At this time, in the local pressure device 1, the axial movement of the rod-like member 5 is braked in advance by the braking mechanism 6. Thus, the ball screw mechanism 3 is protected because the high pressure force is not transmitted to the ball screw mechanism 3.

  As is apparent from the above detailed description, in the hydraulic deformation correction device 2 provided with the local pressure device 1 and the local pressure device 1 according to the present invention, the projection amount with high accuracy even in the pressure reduction region of high pressure force. Adjustment can be easily performed and breakage can be prevented. As a result, warpage, bending, etc. occurring in a thick molded body such as die cast molded body W can be relied on by a manual operation of a skilled person or the like. Even if it correct | amends mechanically, it can use suitably.

By the way, the present invention is not limited to the above-mentioned embodiment, and can be suitably changed according to the embodiment.
For example, the die cast molded body W is not limited to one mainly composed of aluminum, and the local pressure device 1 and the hydraulic deformation and correction device 2 according to the present invention may be originally intended for the die cast molded body W It is not limited.

The rod-like member 5 can be extended in the axial direction with respect to the screw shaft 10 of the ball screw mechanism 3.
The rod-like member 5 can be formed integrally with the screw shaft 10 of the ball screw mechanism 3 or integrally formed with the nut member 11.
The drive unit 4 may be provided to impart rotational drive to the nut member 11, and the screw shaft 10 may be axially moved with respect to the nut member 11.

The braking mechanism 6 is not limited to the collet mechanism, and a clamping mechanism or the like can also be employed.
The chuck member 32 of the braking mechanism 6 may have a slit formed on the large diameter side.
The local pressure device 1 according to the present invention is not limited to use for the hydraulic deformation correction device 2 and is widely used in cases where both high precision advancing and retracting operations and high load pressure by hydraulic pressure are required. It is usable. Of course, it is possible to use even when either one of the high precision advancing and retracting operation and the high pressure reduction by the hydraulic pressure is required.

  In the hydraulic deformation correction device 2, the bolster 51 can also be configured to be able to move down to the slide frame 50. In this case, referring to FIG. 7A as an example, the lower-side projecting member 55D to be brought into contact with the lower surfaces of both ends of the die cast molded body W and the upper surface between both ends of the die cast molded body W It is possible to employ a correction operation in which both of the upper-placed projecting member 55U and the pressing member 55U are pushed down toward the die cast molded body W at a rate corresponding to the proportion.

  The hydraulic deformation correction device 2 according to the present invention is not limited to the case of correcting deformation such as warpage or bending that has occurred in a molded body, and is for deforming the molded body into a prescribed shape (causing warpage or bending, etc.) It is also possible to use

DESCRIPTION OF SYMBOLS 1 Local pressurization apparatus 2 Hydraulic deformation correction apparatus 3 Ball screw mechanism 4 Drive part 5 Rod member 6 Braking mechanism 10 Screw shaft 11 Nut member 12 Ball groove 13 Ball 17 Slider 18 Cylinder rod 19 Bearing tool 20 Cylinder 21 Electric cylinder 23 Female screw Section 24 Male thread 25 Linear motion guide 28 Working end 31 Collet mechanism 32 Chuck member 33 Gripper 34 Hydraulic case 35 Through hole 36 Ball 36 Gripper 37 Spring 38 Inflow port 50 Slide frame 51 Bolster 52 Column 55 Protrusor 55D Lower side Arrangement of projection members 55U Upper arrangement of projection members α Condition variable h Maximum deformation H opening P pin R rib S level difference W die cast molding

Claims (6)

A ball screw mechanism including a screw shaft provided with a spiral ball groove surrounding the outer peripheral surface, and a nut member screwed via the ball rotatably fitted to the ball groove with respect to the screw shaft;
A driving unit for applying a rotational force to the screw shaft or the nut member of the ball screw mechanism;
A rod-like member provided to extend in the axial direction with respect to the screw shaft of the ball screw mechanism or a rod-like member connected to the nut member and provided to project in the axial direction of the screw shaft;
A braking mechanism capable of axially switching the rod-like member movably by axially displacing the axial movement of the rod-like member by radially pressing the outer surface of the rod-like member;
And a local pressure device. The braking mechanism is
A chuck member provided with a through hole through which the rod-like member passes and a slit through which the through hole passes in the radial direction;
A gripping body capable of applying a radially inward tightening force to the outer peripheral surface of the chuck member or releasing the tightening force;
The local pressure device according to claim 1, wherein the local pressure device is a collet mechanism provided with:   3. The local pressure device according to claim 1, wherein the ball screw mechanism and the drive unit constitute an electric cylinder by using an electric motor for the drive unit. In a hydraulic deformation correction device in which a slide frame and a bolster are disposed to face each other to form a reduction area between the slide frame and the bolster,
The slide frame and / or the bolster is provided with a projecting member that protrudes into the pressure reduction area,
The said deformation | transformation member is comprised with the said rod-shaped member of the local pressurization apparatus described in any one of the Claims 1 thru | or 3, The hydraulic type deformation correction apparatus provided with the local pressurization apparatus characterized by the above-mentioned.   The hydraulic deformation correction device with a local pressure device according to claim 4, wherein the projecting member constituted by the local pressure device is provided on both the slide frame and the bolster. .   The hydraulic deformation correction according to claim 5, characterized in that the projection member constituted by the local pressure device is disposed opposite to the slide frame and the bolster. apparatus.

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