JP2005207790A - Drop testing machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a drop testing machine capable of reducing the height of a support, by accelerating weight. <P>SOLUTION: The drop testing machine, constituted of a shift table 2 reciprocating between the center positions between four supports 1a erected on a work floor L at a predetermined interval and the external positions of these supports 1a, to move a placed object W to be tested to the center positions and lowered at the center positions to be placed on an impact-receiving base 1b provided on the work floor L; a weight-adjustable weight 5 raised and, guided by four supports 1a and then dropped; a weight-lifting device 3 provided along four supports 1a to lift the weight 5 to a predetermined height and the weight acceleration device 6, provided to the top parts of four supports 1a and holding the weight 5 lifted by the weight lifting device 3, in a freely suspended state of supporting the same, to release the suspended state and making a push-down force act instantaneously on the weight 5. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a drop test apparatus for testing a subject's deformation and strength by causing a weight to fall vertically and colliding with a subject, and more specifically, accelerating and dropping a weight. The present invention relates to a drop test apparatus that makes it possible.

As an impact test apparatus (drop test apparatus) for vertically dropping a weight, for example, an apparatus having a configuration described later is known. In the drop test apparatus according to the conventional example, a vertical guide (support) standing on the floor is provided with a weight that can slide up and down. An acceleration sensor is provided at the lower end of the weight. A horizontal base is provided immediately below the weight, and a piezoelectric sensor is disposed on the top surface of the base. On the piezoelectric sensor, there is provided a support base that supports a shoe (subject) with the heel portion facing upward, and has a rounded tip. And the output of the said acceleration sensor and the said piezoelectric sensor is comprised so that it may input into an oscilloscope. That is, the drop test apparatus according to this conventional example places the shoe upside down on the support base, lifts the weight to a predetermined height, then drops it and applies an impact force to the heel of the shoe, thereby absorbing the shock. (For example, refer to Patent Document 1).
Japanese Patent Laid-Open No. 10-15003

  Since the drop test apparatus according to the conventional example performs an impact test of a small subject (shoe heel) as described above, for example, a configuration as it is for a large subject such as a passenger car. Is difficult to apply. In addition to the need to be larger and more complex, when performing a drop test on such a large subject, a weight is generally dropped from above at a higher speed onto the subject set on the lower side. There is a need.

  In the case of a large subject such as an automobile, test conditions differ depending on differences in vehicle body weight and vehicle speed. In the case of a drop test device that allows the weight to fall freely, the weight of the weight is adjusted by attaching an auxiliary weight, etc., for the difference in vehicle weight, and the weight drop height is adjusted for the difference in vehicle speed. Be changed. By the way, when the subject is an automobile, it is necessary to perform a higher-speed collision test as the speed increases, and the weight has to be freely dropped from a higher position. For this reason, a drop test device with a very high column is required, and the height of the building that houses the drop test device must be increased accordingly, resulting in an excessive cost of installation of the drop test device. There was a problem.

For example, when the initial speed is 0, the potential energy H h of the mass m at the height _h is mg (acceleration of gravity = 9.8 m / s ² ) h, and the mass that has fallen to the velocity v is h. Since the kinetic energy Ev of m is ½ · mv ² , mgh = ½ · mv ² is established according to the law of conservation of mechanical energy. When the speed of the weight obtained by a general 10 m-high free-fall test apparatus is obtained from v = (2gh) ^1/2 obtained from the above formula, 14.0 m / s, that is, 50.4 km / h per hour. The impact test result corresponding to is obtained. However, when an impact test corresponding to a higher speed, for example, an impact test corresponding to 70 km / h (19.44 m / s), is performed, the weight is 20.8 m high (height h = v ² / 2g = 19.44 ² /2×9.8) must be allowed to fall from.

  Accordingly, an object of the present invention is to provide a drop test apparatus that makes it possible to reduce the height of a column by accelerating the weight.

  The present invention has been made in view of the above circumstances. Therefore, in order to solve the above problems, the means employed by the drop test apparatus according to claim 1 of the present invention is a rail installed on the work floor. It is equipped with rolling wheels and is reciprocated between a center position between a plurality of struts erected on the work floor at a predetermined interval and an outer position of the plurality of struts. The subject is moved to a center position between the plurality of support columns, and is lowered at the center position between the plurality of support columns, and is placed on an impact receiving base provided on the work floor, and A weight-adjustable weight provided with a guide roller for rolling a roller guide provided on opposite sides of the plurality of support columns, and a weight provided along the plurality of support columns, and lifting the weight to a predetermined height A reversibly actuable weight lifting device, A weight acceleration device that is provided on the top of the support column and supports the weight lifted by the weight lifting device so that the weight can be lifted and released freely, and the pressing force is instantaneously applied to the weight. It is characterized by comprising.

  Means employed by the drop test apparatus according to claim 2 of the present invention is the drop test apparatus according to claim 1, wherein the drop test apparatus is a portion where the plurality of struts are opposed to each other and below the weight accelerator. A free fall device having a slide pin that can freely move forward and backward is provided at a plurality of locations by projecting in opposite directions to support the weight and to retreat synchronously. To do.

  The drop test apparatus according to claim 3 of the present invention employs the drop test apparatus according to any one of claims 1 and 2, wherein the weight accelerator includes the plurality of support columns. A pair of openable and closable pairs, each comprising a frame mounted on the top and an engaging claw that is provided on the frame and engages a suspension hook provided on the weight, and is supported by a rotation fulcrum pin. In order to release the engagement of the suspension arms and the engagement claws with respect to the pair of suspension arms, a booster claw removal mechanism that simultaneously pushes the pair of suspension arms is provided. The tip side is rotatably supported by a fixed pin, and a claw removal arm that presses the rotation fulcrum pin of the pair of suspension arms and the engaging claw in opposite directions, and the tip side is a base of the claw removal arm. It is pivotally attached to the end, and is extended and contracted by being guided by a guide. That the arm base end side to the distal end of the extendable rod of the actuating cylinder is characterized in that comprising the closable pair of toggle arms formed by pivotally mounted.

  The means adopted by the drop test apparatus according to claim 4 of the present invention is the drop test apparatus according to any one of claims 1 to 3, wherein the weight acceleration device is provided on the gantry frame. And a spring acceleration device provided with an acceleration spring that is compressed through the suspension arm and the weight by the extension of the rod of the hydraulic cylinder and that exerts a pressing force on the weight by a resilient force It is characterized by comprising.

  The means adopted by the drop test apparatus according to claim 5 of the present invention is the drop test apparatus according to any one of claims 1 to 4, wherein the weight acceleration device is provided on the gantry frame. An accelerating piston having a vertical cylinder body and a lowering rod incorporated in a lower portion of the cylindrical body and applying a pressing force to the weight, and an upper part of the accelerating piston. The seal ring having a smaller diameter than the outer diameter of the cylinder, the upper part of the cylinder, and the high-pressure air introduced from the side surface of the cylinder to squeeze the seal ring so that the inside and outside of the seal ring A seal pressing piston for blocking is provided, and high-pressure air flowing in from a high-pressure air inflow / outflow pipe provided at an upper portion of the cylindrical body is passed through a hollow rod between the seal pressing piston and the acceleration piston. It is characterized in comprising provided with air 圧加 speed cylinder device comprising a positioning cylinder and supplies the.

  The means adopted by the drop test apparatus according to claim 6 of the present invention is the drop test apparatus according to claim 5, wherein the drop test apparatus is provided in the gantry frame in a high-pressure air inflow / outflow pipe provided in an upper portion of the cylinder. The high-pressure air is supplied from the buffer tank.

  The drop test device according to claim 7 of the present invention employs the drop test device according to any one of claims 5 and 6, wherein the spring acceleration device of the weight acceleration device and the means The pneumatic acceleration cylinder device is configured to be able to individually apply a pressing force to the weight.

  The drop test device according to claim 8 of the present invention employs the drop test device according to any one of claims 5 to 7, wherein the positioning cylinder of the pneumatic acceleration cylinder device includes the positioning cylinder. A screw in which the upper end of the hollow rod is connected via a connecting pin, protrudes out of the cylindrical body through a seal above the communication position of the high-pressure air inflow / outflow tube, and a male screw is screwed into the protruding portion. It is configured to be positioned by a positioning mechanism that includes a rod and an adjustment nut that is screwed onto a male screw of the screw rod and adjusts the seal pressing piston to a position where the seal ring is crushed by an appropriate crushing allowance. It is characterized by.

  The means adopted by the drop test apparatus according to claim 9 of the present invention is the drop test apparatus according to any one of claims 5 to 8, wherein the acceleration spring is set on the upper surface of the weight. An interval body attaching portion for attaching an interval body that makes it possible to effectively utilize the entire stroke of the acceleration piston irrespective of the amount of compression is provided.

  According to the drop test apparatus according to claims 1 to 9 of the present invention, the subject on the shift table that is moved to the center position between the plurality of support columns and is lowered and placed on the impact receiving base, The weight lifted to a predetermined height by the weight lifting device and suspended by the weight acceleration device can be accelerated and dropped by the weight acceleration device. Therefore, according to the drop test apparatus according to claims 1 to 9 of the present invention, the height of the support column can be made lower than that of the free drop type drop test apparatus according to the conventional example that can obtain the equivalent drop speed. The height of the building that houses this can also be lowered.

  According to the drop test device according to claim 2 of the present invention, in addition to the fact that the weight can be accelerated and dropped, in the case of a test in which the drop speed of the weight may be slow, the slide pin of the free fall device The weight can be supported and the weight can be freely dropped by synchronously retracting the slide pin.

  According to the drop test device of the third aspect of the present invention, the weight is weighted via the suspension hook by the engagement of the engagement claws of the pair of freely openable and closable suspension arms supported by the rotation fulcrum pins. While being suspended by the weight accelerator, a pressing force is applied by the weight accelerator. And between the rotation fulcrum pins of the pair of suspension arms that suspend the weight and the engaging claws are rotated via the toggle arm by the extension operation of the telescopic rod of the arm operating cylinder of the booster claw removing mechanism. Because the engaging claw of the pair of suspension arms is released from the suspension hooks when the tip side is pressed in the opposite direction by the claw disengagement arms supported rotatably by the fixing pins, a pressing force is applied to the weight. Can be dropped in the state.

  According to the drop test apparatus of the fourth aspect of the present invention, the weight is applied to the weight by the elastic force of the acceleration spring of the spring acceleration device compressed through the suspension arm and the weight by the extension of the rod of the hydraulic cylinder. A pressing force is applied. According to the drop test apparatus of the fourth aspect of the present invention, the engagement claws of the pair of suspension arms are disengaged from the suspension hooks provided on the weight, and the seal by the seal pressing piston of the pneumatic acceleration cylinder device is provided. At the moment when the ring crushing state is released, the acceleration piston moves at a high speed downward under the force of high pressure air pressure applied to the area of the acceleration piston generated by the high pressure air spreading from the inside of the seal ring to the entire area of the acceleration piston. Moving. Therefore, according to the drop test apparatus according to claim 4 of the present invention, in addition to the pressing force due to the elastic force of the acceleration spring of the spring accelerator being applied to the weight, the acceleration of the acceleration piston A pressing force is also applied by the rod.

  According to the drop test apparatus of the sixth aspect of the present invention, high-pressure air is supplied from the buffer tank provided in the gantry frame to the high-pressure air inflow / outflow pipe provided in the upper part of the cylindrical body constituting the pneumatic acceleration cylinder apparatus. Supplied. When the high-speed piston suddenly stops at the stroke end, the inflow of high-pressure air flowing in from the high-pressure air inflow / outflow pipe suddenly stops, and the reaction causes the high pressure in the lower portion of the cylinder, in the hollow rod, and in the high-pressure air outflow / inflow pipe. However, since this pressure is absorbed by the buffer tank, there is no possibility that the lower portion of the cylindrical body, the hollow rod, the high-pressure air inflow / outflow pipe and the like are damaged.

  According to the drop test apparatus of the seventh aspect of the present invention, the pressing force can be applied to the weight only by the spring acceleration device of the weight acceleration device, and the pneumatic acceleration of the weight acceleration device. A pressing force can be applied to the weight only by the cylinder device.

  According to the drop test apparatus according to claim 8 of the present invention, the seal pressing piston can be adjusted to the position where the seal ring is crushed by the adjusting nut of the acceleration piston positioning mechanism via the screw rod and the hollow rod. it can. As a result, even if the acceleration piston starts to descend, the seal pressing piston is secured so that it does not descend together with the acceleration piston.

  According to the drop test device of the ninth aspect of the present invention, the set compression amount of the acceleration spring of the spring acceleration device is small, and there is a gap between the upper surface of the weight and the lower end of the acceleration rod of the pneumatic acceleration cylinder device. However, the entire stroke of the accelerating piston can be effectively used for applying the pressing force by attaching the spacing member to the spacing member mounting portion provided on the upper surface of the weight.

Below, the drop test device concerning the form of the present invention is explained, referring to an accompanying drawing one by one.
1 is an overall front view of the drop test apparatus, FIG. 2 is an overall side view of the drop test apparatus, FIG. 3 is a plan view of a shift table including rails, FIG. 4 is a cross-sectional view taken along line AA in FIG. 1 is an enlarged view of a part B in FIG. 1, FIG. 6 is a sectional view taken along line CC in FIG. 3, FIG. 7 is a sectional view taken along arrow D in FIG. It is the FF sectional view taken on the line. FIG. 10 is an explanatory view of the weight lifting device attached state, FIG. 11 is a structural explanatory view of the weight free-falling device, FIG. 12 is a side view of the weight, FIG. 13 is a plan view of the weight, and FIG. It is a G arrow line view which abbreviate | omits and shows the support | pillar (the support | pillar of the left side in FIG. 12) of the near side of an arrow. 15 is a longitudinal sectional view of the weight acceleration device, FIG. 16 is a sectional view taken along the line HH of FIG. 15, FIG. 17 is a side view of the booster claw removing mechanism, and FIG. FIG. 19 is a longitudinal cross-sectional view of the pneumatic acceleration cylinder device, and FIG.

  First, a schematic configuration of a drop test apparatus according to an embodiment of the present invention will be described with reference to FIGS. The drop test apparatus 1 according to the embodiment of the present invention includes four support pillars 1a erected at positions corresponding to the rectangular apex angles on the foundation 1e, and a center between the four support pillars 1a. An impact receiving base 1b is provided at the position. A reciprocating shift table 2 is provided for moving the subject W set on the outer side of the four columns 1a to a central position between the four columns 1a. In addition, it includes a weight 5 that is guided by the four support pillars 1 a and is lifted and dropped and applies an impact force to the subject W, and a weight lifting device 3 that lifts the weight 5. ing. Further, a free fall device 4 that freely drops the weight 5 is provided at three positions in the vertical direction of the four support columns 1a, and a weight acceleration device 6 that is installed on tops of the four support columns 1a. ing. In addition, what protrudes outward in the top part of the four support | pillar 1a is the upper maintenance deck 1c for maintaining the weight acceleration apparatus 6, and the downward direction of the weight acceleration apparatus 6 of the four support | pillar 1a What protrudes outward in the position is an intermediate portion maintenance deck 1d.

  The shift table 2 is provided with wheels 2a as shown in FIGS. As shown in FIG. 6, when the subject W is compressed and deformed by a predetermined amount due to the fall of a weight 5 to be described later on each of the upper surfaces near the end portions in the left-right direction orthogonal to the moving direction of the shift table 2 There is provided an impact absorbing device 2b for preventing large deformation. Further, between the shock absorbing device 2b on the upper surface of the shift table 2, a subject that is cut between a front seat and a rear seat and that includes a front portion of a passenger car with an engine room side facing upward. W is set, and four load cells 2c for measuring the impact force acting on the subject W are arranged. The shift table 2 is composed of an elevating rail 2d laid at the center position between the four struts 1a and a fixed rail 2g laid on the work floor L at the outer position of the four struts 1a. It is configured to reciprocate on the rail by a driving sprocket 2i rotated by a motor 2h with a speed reducer, a driven sprocket 2j, and a table operating chain 2k that is hung on both the sprockets 2i and 2j. Yes.

  As shown in FIGS. 7 to 9, the end of the elevating rail 2d is guided by a rail guide 2e and is raised and lowered by a hydraulic cylinder 2f provided inside the rail guide 2e. The shift table 2 is moved at the center position between the four columns 1a by the lowering of the elevating rail 2d until the rolling surface of the wheel 2a is below the upper surface of the impact receiving base 1b. It is configured to be placed on the upper surface of the receiving base 1b. Thereby, the impact force acting on the subject W is received by the base 1e that supports the impact receiving base 1b via the load cell 2c, the shift table 2, and the impact receiving base 1b.

  As shown in FIG. 10, the weight lifting device 3 has a direction orthogonal to the movement direction of the shift table 2 of the column 1 a (only one side in FIG. 10 is actually orthogonal to the movement direction of the shift table 2. Are provided on the left and right of the direction of movement). A reversibly rotatable drive motor 3a having a tip of an output shaft supported by a bearing is provided on the top of the column 1a. A drive sprocket 3b is fitted to the output shaft of the drive motor 3a. Also, a driven sprocket 3c is provided at the base end portion of the column 1a, and a lifting projection 3e that lifts the lower surface of the weight 5 through a bolt and nut protrudes from the driven sprocket 3c and the drive sprocket 3b. The lifted chain 3d is hung. That is, the weight lifting device 3 lifts the lower surface of the weight 5 with the lifting protrusion 3e by the forward rotation of the drive motor 3a and lifts it to a predetermined height position, and then lifts the lifting protrusion 3e with the weight 5 by the reverse rotation. It is configured so that it can be lowered to a position that does not hinder falling.

As shown in FIG. 11, the free-falling device 4 is provided in pairs, that is, 12 sets at three positions in the right and left directions in the direction perpendicular to the moving direction of the shift table 2 of the column 1a. ing. Each free fall device 4 is configured as shown in FIG.
That is, a through-hole sharing the center in the radial direction is provided in the plate member corresponding to the first and third strokes of the H-shaped steel constituting the support 1a, and the plate member corresponding to the first and third strokes is provided with the through hole. A boss that shares the radial center of the hole and protrudes in the opposite direction is fixed. More specifically, a front end side boss 4a formed by fitting an oilless bush 4b to the surface of the plate member side corresponding to three strokes of the plate member corresponding to one stroke of the H-shaped steel constituting the support 1a is projected. Yes. Further, a base end side boss 4c projects from a surface on the plate member side corresponding to one stroke of the plate member corresponding to three strokes. A slide pin 4d is slidably fitted to the oilless bush 4b and the base end side boss 4c of the distal end side boss 4a. The slide pin 4d protrudes from the oilless bush 4b of the front end boss 4a by a predetermined length by an air cylinder 4e provided on the opposite boss side of the plate member corresponding to three strokes, and is substantially flush with the oilless bush 4b. It is comprised so that it may evacuate to the position. That is, the weight 5 is supported at a predetermined height position by the protrusion of the slide pin 4d, and the supporting weight 5 is freely dropped by synchronous retraction. In this embodiment, the weight 5 is set so that it can be freely dropped from three stages of height.
In addition, since the number of steps of the free fall height at which the weight 5 is freely dropped can be set as necessary, the number of steps of the free fall height is not limited to three.

  The weight 5 is configured as shown in FIGS. That is, the weight 5 includes a box-shaped weight body 5a. A pair of two types of guide roller units are provided at each of the left and right ends of the weight body 5a. These guide roller units are composed of a first guide roller unit 5b and a first guide roller unit 5b. And a second guide roller unit 5c provided therebetween. The first guide roller unit 5b includes an upper bracket projecting from the upper surface of the end of the weight body 5a, and one or three strokes of the H-section steel supported by the upper bracket and constituting the support column 1a. A guide roller that rolls on the rolling surface of the first roller guide 1f fixed in the vertical direction at the center in the width direction of the corresponding plate member, and a lower surface of the end portion of the weight body 5a. The lower bracket and a roller supported by the lower bracket and rolling on the rolling surface of the first roller guide 1f. The second guide roller unit 5c includes an upper bracket projecting from the upper surface of the end of the weight main body 5a, and one or three H-section steel supported by the upper bracket and constituting the support column 1a. A guide roller that rolls on the rolling surface of the second roller guide 1g fixed along the vertical direction on the end surface of the plate member corresponding to the image, and a lower portion protruding from the lower surface of the end portion of the weight body 5a A bracket and a guide roller supported by the lower bracket and rolling on the rolling surface of the second roller guide 1g.

  Further, a hollow disc-shaped spring seat plate 5d is fixedly attached to the upper surface of the weight body 5a and centering on the centroid of the weight body 5a. A suspension hook 5e that engages with an engagement claw of a suspension arm (to be described later) of the weight acceleration device 6 protrudes from each of the left and right positions sandwiching the spring seat plate 5d of the weight body 5a. It is installed. Further, the weight accelerator 6 will be described later at two locations on the upper surface of the weight body 5a, near the front side (lower side in FIG. 14) and at two locations near the rear side (upper side in FIG. 14). Regardless of the set compression amount of the accelerating spring to be provided, there is provided an interval body attaching portion 5f for attaching an interval body that makes it possible to effectively utilize the entire stroke of the acceleration piston. With the first guide roller unit 5b and the second guide roller unit 5c as described above, the weight 5 can be lifted smoothly while maintaining a horizontal state, and can be dropped smoothly. Note that the bottom surface of the weight main body 5a and fixed to a position where the center of gravity coincides with the centroid of the weight main body 5a is a detachable weight for adjusting the weight of the weight 5 The adjustment weight is 5 g.

  The weight acceleration device 6 is configured as shown in FIGS. 15 to 20, and includes a gantry frame 6a installed on the top of the column 1a. Further, the weight acceleration device 6 includes a spring acceleration device 7 that applies a pressing force to the weight 5 by the elastic force of the spring, and a weight 5 that is suspended by the weight acceleration device 6. A booster claw removing mechanism 8 for releasing the state, a pneumatic acceleration cylinder device 9 that applies a pressing force to the weight 5 together with the spring acceleration device 7 by high pressure air or by itself, and this pneumatic acceleration cylinder device 9 is provided with a buffer tank for supplying high-pressure air. Hereinafter, the configuration of the above devices will be described with reference to the attached drawings.

  The spring acceleration device 7 is configured as shown in FIGS. 15 and 16. That is, a spring compression hydraulic cylinder 7a with a telescopic rod facing upward is vertically attached to the gantry frame 6a. The spring compression hydraulic cylinder 7a is fixed to the gantry frame 6a by bolting a flange portion provided on the rod side of the cylindrical portion. An elevating frame 7b that is guided by a guide member 6b protruding from the gantry frame 6a is attached to the tip of the telescopic rod of the spring compression hydraulic cylinder 7a. A rotation fixing pin 7c is provided at each of the longitudinal ends of the elevating frame 7b, and the rotation fixing pin 7c supports a portion that is slightly lower than the upper end to rotate. An arm 7d is provided. At the lower end of the suspension arm 7d, an engagement claw that engages with the suspension hook 5e of the weight 5 is formed. The bottom side of the arm rotation air cylinder 7e is pivotally attached to one upper end portion of the pair of suspension arms 7d, and the other upper end portion of the telescopic rod of the arm rotation air cylinder 7e. The tip of the extension rod 7f connected to the tip is pivotally attached.

  Six acceleration coil springs 7g are vertically and equidistantly attached to the lower surface side of the gantry frame 6a in a circular shape centering on a central point sharing the radial center of the spring compression hydraulic cylinder 7a. It has been. These acceleration coil springs 7g are configured to cause a resilient force to act on the upper surface of the lifting plate 7h having a pressing boss on the lower surface side. At the center of the pressing boss of the elevating plate 7h, a guide rod 7i that passes through the radial center of the acceleration coil spring 7g and protrudes above the gantry frame 6a by the compression of the acceleration coil spring 7g is installed. Has been. A male screw is threaded on the projecting end of the guide rod 7i from the gantry frame 6a. A nut and a lock nut are screwed onto the male screw so that the guide rod 7i does not fall off. Yes. In the present embodiment, the number of acceleration coil springs 7g is six, but it does not necessarily have to be six. For example, the number may be four, eight, or the like and can be balanced in the X and Y directions.

  Therefore, according to the spring acceleration device 7 configured as described above, when the weight 5 is lifted by the weight lifting device 3 until the spring seat plate 5d comes into contact with the pressing boss of the lifting plate 7h, the weight acceleration device 7 is opened. The suspended arm 7d is rotated in the closing direction by the extension operation of the telescopic rod of the arm rotating air cylinder 7e. When the engaging claw at the tip of the suspension arm 7d is engaged with the suspension hook 5e and suspended, the telescopic rod of the spring compression hydraulic cylinder 7a is extended. Since the elevating frame 7b is lifted by the extension of the telescopic rod, the weight 5 is lifted via the suspension arm 7d, and the acceleration coil spring 7g is compressed by the lift of the weight 5. Next, when the engagement of the engaging claw of the suspension arm 7d with respect to the suspension hook 5e is released by the booster claw removing mechanism 8 having a configuration described later, the weight 5 is applied to the weight 5 by the elastic force of the acceleration coil spring 7g. Since the pressing force acts instantaneously, the weight 5 is flipped downward. Of course, the weight 5 can be freely dropped from the height raised by the weight lifting device 3 until the spring seat plate 5d contacts the pressing boss of the lifting plate 7h.

  The booster claw removing mechanism 8 is configured as shown in FIGS. That is, a pair of vertical fixing pins 8c are provided in the vicinity of the front end of the gantry frame 6a at a predetermined interval (however, only one fixing pin is shown in FIGS. 16 and 17). The tip of the claw removal arm 8a is supported on each of the pair of fixing pins 8c. A tip end portion of a toggle arm 8d that opens in the shape of a letter C is pivotally attached to a base end portion of each of the claw removing arms 8a, and the base end portion of the toggle arm 8d is an empty space disposed in the gantry frame 6a. It is pivotally attached to the tip of the telescopic rod 8f of the pressure-operated arm operating cylinder 8e. The telescopic rod 8f is slidably fitted to the guide cylinder 8g, and consideration is given so as not to cause a difference in opening and closing of the toggle arms 8d and 8d when the telescopic rod 8f is expanded and contracted. An abutting portion 8b is formed at a position slightly closer to the fixing pin 8c side than the center in the longitudinal direction of the claw removing arm 8a. The abutting portion 8b comes into contact with the opposed inner end surfaces of the pair of suspension arms 7d of the spring acceleration device 7. Yes. As shown in FIG. 16, on the side of the abutting portion 8b facing the suspension arm 7d, the claw-removing arm 8a is surely arranged in the width direction of the opposed inner end surface of the suspension arm 7d even in a non-parallel state. An arcuate curved surface is formed so as to be in contact with the vicinity of the center. That is, the booster claw removing mechanism 8 increases the distance on the proximal end side of the claw removing arm 8a through the toggle arm 8d by extension of the telescopic rod 8f of the arm operating cylinder 8e. The engaging arms of the suspension arm 7d are detached from the suspension hooks 5e of the weight 5 by pushing the suspension arms 7d, 7d instantly and simultaneously via the contact portion 8b. Yes.

  The pneumatic acceleration cylinder device 9 is configured as shown in FIGS. Note that four sets of pneumatic acceleration cylinder devices 9 are provided, and all of them have the same configuration. Therefore, one set of pneumatic acceleration cylinder devices 9 will be described. That is, a cylinder body 9a is vertically provided on the gantry frame 6a, and an acceleration piston 9b having a pressing rod 9c for applying a pressing force to the weight 5 is incorporated in a lower portion of the cylinder body 9a. Yes. A seal ring groove having a smaller diameter than the outer diameter of the acceleration piston 9b (about 40% of the outer diameter of the acceleration piston 9b) is engraved on the upper surface of the acceleration piston 9b. For example, a seal ring 9d made of an O-ring is fitted. And the positioning cylinder 9e mentioned later is comprised above this acceleration piston 9b. In the present embodiment, as described above, four sets of pneumatic acceleration cylinder devices 9 are provided, but one set on each of the left and right sides, that is, two sets of pneumatic acceleration cylinder devices 9 may be provided.

  The positioning cylinder 9e includes an upper portion of the cylindrical body 9a and a seal pressing piston 9f that is incorporated in the cylindrical body 9a and crushes the seal ring 9d to block the inside and outside of the seal ring 9d. . On the upper surface of the seal pressing piston 9f, the high-pressure air flowing in from the high-pressure air inflow / outflow pipe 9k protruding in the lateral direction of the T-shaped fitting 9i protruding from the closing lid 9h for closing the upper opening of the cylindrical body 9a is sealed. A hollow rod 9g is provided between the pressing piston 9f and the acceleration piston 9b. The upper end of the hollow rod 9g penetrates the closing lid 9h, and passes through a sealing device 9k provided at a position higher than the high-pressure air inflow / outflow pipe 9j of the T-shaped fitting 9i. It is connected to the lower end. A male screw is threaded on the protruding end of the threaded rod 9l from the T-shaped fitting 9i, and an adjusting nut 9m is threaded onto the male thread. That is, the seal pressing piston 9f can be adjusted to a position where the seal ring 9d is crushed by an appropriate crushing amount by the screwing amount of the adjusting nut 9m.

  A piston-shaped blocking body 9n through which the hollow rod 9g penetrates in an airtight manner is incorporated at a position above the seal pressing piston 9f of the positioning cylinder 9e. And it is comprised so that high pressure air may be introduce | transduced from the high pressure air introduction pipe | tube 9o provided in the side surface of the said cylinder 9a between this interruption | blocking body 9n and the said seal | sticker press piston 9f. The blocking body 9n is fixed to a lower end of an inner cylinder 9p having a tip fixed to the lower surface side of a closing lid 9h that closes the upper opening of the cylinder 9a, and is fixed at a predetermined position so as not to move up and down. ing. That is, the seal pressing piston 9f of the positioning cylinder 9e is lowered by the pressure of the high-pressure air introduced from the high-pressure air introduction pipe 9o to crush the seal ring 9d, and the high-pressure air in the high-pressure air inflow / outflow pipe 9j is separated from the seal ring 9d. It is held without leakage between the acceleration pistons 9b. If the adjusting nut 9m is tightened at the lower end of the screw at this position, the positioning cylinder 9e cannot be lowered even if the acceleration piston 9b starts to be lowered, so that the seal ring 9d is prevented from being lowered together with the acceleration piston 9b. The Further, when the acceleration piston 9b is separated from the seal pressing piston 9f by the high pressure air introduced from the high pressure air introduction pipe 9o, the seal pressing piston 9f moves upward by a gap 9s between the blocking body 9n. The length of the upper thread portion of the screw rod 9l is set to a length that allows this upward movement.

  The lower end of the pneumatic acceleration cylinder device 9 configured as described above when the push-down rod 9c is contracted is the four spacing members provided on the weight body 5a when the acceleration coil spring 7g of the spring acceleration device 7 is maximally compressed. The length is set so as to be in contact with each of the upper surfaces of the attachment portions 5f. By the way, the pressing force with respect to the weight 5 is changed according to the impact test condition of the subject W, and the set compression amount of the acceleration coil spring 7g may be smaller than the maximum compression amount. In such a case, the acceleration piston 9b of the pneumatic acceleration cylinder device 9 must be operated at a position lowered by the difference in compression amount. The pressing force cannot be applied. Therefore, when the set compression amount of the acceleration coil spring 7g is smaller than the maximum compression amount, as shown in FIG. 19, a cylindrical interval having a predetermined height is provided in each of the four interval body mounting portions 5f of the weight body 5a. The body 9r is configured to be attached. As a result, regardless of the set compression amount of the acceleration coil spring 7g of the spring acceleration device 7, the entire stroke of the acceleration piston 9b of the pneumatic acceleration cylinder device 9 is effectively used to exert a pressing force on the weight 5. Can be made. Further, by increasing the height of the cylindrical spacing member 9r, even if the compression amount of the acceleration coil spring 7g is zero, the pressing force is applied to the weight 5 only by the pneumatic acceleration cylinder device 9. be able to.

  As shown in FIG. 20, high-pressure air is supplied to the high-pressure air inflow / outflow pipe 9j and the high-pressure air introduction pipe 9o of the pneumatic acceleration cylinder device 9 from a plurality of buffer tanks provided in the gantry frame 6a. It is configured as follows. In other words, two first buffer tanks 11 having a pair of pipe connection pipes 11a are disposed on the gantry frame 6a, and each of the pipe connection pipes 11a of the one first buffer tank 11 has two sets of pneumatic pressures. The acceleration cylinder device 9 is connected to a high-pressure air inflow / outflow pipe 9j. The gantry frame 6 a is provided with one second buffer tank 12 having a pipe connection pipe 12 a, and the pipe connection pipe 12 a of the second buffer tank 12 includes four sets of pneumatic acceleration cylinder devices 9. It is connected to the high pressure air introduction pipe 9o. Reference numeral 13 denotes a pressure booster that supplies pneumatic air to the first buffer tank 11.

  Hereinafter, the operation mode of the drop test apparatus 1 according to the embodiment of the present invention will be described. First, according to the impact test conditions of the subject W, the weight 5 is lifted up to the position of the free fall device 4 by being supported by the lifting projection 3e provided on the lifting chain 3d of the weight lifting device 3, and by the slide pin 4d. The engaging claw of the suspension arm 7d of the spring acceleration device 7 that constitutes a part of the weight acceleration device 6 is engaged with the suspension hook 5e to support the weight (if necessary, the weight main body 5a A cylindrical interval body 9r and a weight adjusting weight 5g are attached to the interval body attaching portion 5f.) 5 is suspended. When the lifting and lifting operations of the weight 5 as described above are completed, the protrusion 3e is lowered to a position where there is no hindrance to the falling of the weight 5 by the reverse operation of the weight lifting device 3. When the weight 5 is suspended by the suspension arm 7d and the weight 5 is not freely dropped, the telescopic rod of the spring compression hydraulic cylinder 7a of the spring acceleration device 7 is extended. The acceleration coil spring 7g is compressed by raising the weight 5 through the lifting frame 7b and the suspension arm 7d. In parallel with the compression of the acceleration coil spring 7g, the push-down rod 9c of the pneumatic acceleration cylinder device 9 rises. If necessary, the position of the seal pressing piston 9f that can properly crush the seal ring 9d on the upper surface of the acceleration piston 9b is set by the positioning cylinder 9e constituting another part of the weight acceleration device 6. Next, high-pressure air is supplied from each of the first and second buffer tanks 11 and 12 to the pneumatic acceleration cylinder device 9. When the push rod 9c of the pneumatic acceleration cylinder device 9 is raised, the air between the acceleration piston 9b and the seal push piston 9f is pushed by the acceleration piston 9b and passes through the blocking body 9n, T It flows into the first buffer tank 11 via the high-pressure air inflow / outflow pipe 9j and the pipe connection pipe 11a of the mold fitting 9i.

  In parallel with the above operation, the subject W is set on the load cell 2c on the shift table 2 outside the four columns 1a, and the table motor is operated by operating the motor 2h with a speed reducer. The shift table 2 is moved to the center position between the four columns 1a by the chain 2k. Next, when the shift table 2 is placed on the impact receiving base 1b supported by the foundation 1e by reducing the telescopic rod of the hydraulic cylinder 2f and lowering the elevating rail 2d, the subject W is ready for an impact test. finish.

  When the preparation of the impact test for the subject W as described above is completed, the impact test for the subject W is performed as follows. In the case where the weight 5 is freely dropped, if the slide pin 4d of the free fall device 4 supporting the weight 5 is synchronously retracted, the weight 5 is freely dropped, and the subject W is caused to fall by the free fall of the weight 5. An impact test is performed. Even when the weight 5 is suspended by the suspension arm 7d and the acceleration coil spring 7g is not compressed, the weight 5 can be freely dropped. In this case, the telescopic rod 8f of the arm operating cylinder 8e of the booster claw removing mechanism 8 is extended, and the claw removing arm 8a is pushed open through the toggle arm 8d to suspend the engaging claw of the suspension arm 7d. When the holding hook 5e is removed, the weight 5 falls freely, and an impact test of the subject W by the free fall of the weight 5 is performed. Therefore, according to this drop test apparatus 1, the impact test of the subject W can be performed by the free fall of the weight 5 from the positions where the heights of the four places are different.

  Hereinafter, a method of performing an impact test on the subject W that causes the weight 5 to be accelerated and dropped by the weight acceleration device 6 will be described. First, the case where the weight 5 is accelerated and dropped only by the spring acceleration device 7 will be described. As described above, the lifting frame 7b is suspended by the extension of the telescopic rod of the spring compression hydraulic cylinder 7a of the spring acceleration device 7. The weight 5 is raised through the arm 7d, and the acceleration coil spring 7g is compressed. Therefore, the telescopic rod 8f of the arm operating cylinder 8e of the booster claw removing mechanism 8 is extended. Then, the claw removal arm 8a is pushed open through the toggle arm 8d, and the engagement claw of the suspension arm 7d is disengaged from the suspension hook 5e. Therefore, the instantaneous pressing force is exerted by the elastic force of the acceleration coil spring 7g. Thus, the weight 5 is accelerated and dropped, and the impact test of the subject W by the accelerated drop of the weight 5 is performed. In this case, since the compression amount of the acceleration coil spring 7g can be variously set according to the impact test conditions of the subject W, the impact test of the subject W can be performed by freely changing the falling speed of the weight 5. Can do.

Next, the case where the weight 5 is accelerated and dropped only by the pneumatic acceleration cylinder device 9 will be described. That is, in this case, since the acceleration coil spring 7g of the spring acceleration device 7 is not compressed and the amount of compression is 0, the weight 5 is attached to the interval body mounting portion 5f of the weight body 5a. A cylindrical spacing member 9 r having a height corresponding to the maximum compression amount is attached and is suspended by a suspension arm 7 d of the spring acceleration device 7. When the telescopic rod 8f of the arm operating cylinder 8e of the booster claw removing mechanism 8 is extended, the claw removing arm 8a is pushed open through the toggle arm 8d, and the engaging claw of the suspension arm 7d is detached from the suspension hook 5e. . As a result, when the weight 5 starts to fall freely, the acceleration piston 9b moves away from the seal pressing piston 9f, and the crushing state of the seal ring 9d is released and a gap is generated, so that the blocking by the seal ring 9d is released. Is done.
Therefore, the high-pressure air in the first buffer tank 11 flows at a stretch between the acceleration piston 9b and the seal pressing piston 9f, and a force corresponding to the cross-sectional area is instantaneously generated in the acceleration piston 9b.

  Accordingly, as the accelerating piston 9b descends at a high speed, the push rod 9c extends at a high speed, and a push force is applied to the weight 5 via the cylindrical spacing member 9r, so that the weight 5 is accelerated. The impact test of the subject W by the accelerated fall of the weight 5 is performed. In this case, since the pressure of the high-pressure air can be variously set according to the impact test condition of the subject W, the impact test of the subject W can be performed by freely changing the falling speed of the weight 5. In the case of the pneumatic acceleration cylinder device 9, the acceleration piston 9 b that descends at a high speed suddenly stops at the stroke end, so that the high-pressure air is reflected by the reaction at the time of the sudden stop, and in the pneumatic acceleration cylinder device 9, A phenomenon similar to the action will occur. However, since it is absorbed by the first buffer tank 11, there is no possibility that the pneumatic acceleration cylinder device 9 is damaged.

  Furthermore, the case where the weight 5 is accelerated and dropped by the joint operation of the spring acceleration device 7 and the pneumatic acceleration cylinder device 9 will be described. That is, in this case, the acceleration coil spring 7 g of the spring acceleration device 7 is compressed by the weight 5 rising. Further, the push-down rod 9c of the pneumatic acceleration cylinder device 9 is pushed up by the weight 5 directly or via a cylindrical spacing member 9r attached as required, and the seal ring 9d is pushed by the seal of the positioning cylinder 9e. It is properly crushed by the piston 9f. The first and second buffer tanks 11 and 12 communicate with the pneumatic acceleration cylinder device 9 so that high-pressure air can flow from the first and second buffer tanks 11 and 12.

  Accordingly, when the telescopic rod 8f of the arm operating cylinder 8e of the booster claw removing mechanism 8 is extended, the claw removing arm 8a is pushed open through the toggle arm 8d, and the engaging claw of the suspension arm 7d is engaged with the suspension hook 5e. Deviate from. As a result, at the moment when the pressing force is instantaneously applied by the elastic force of the acceleration coil spring 7g and the weight 5 starts accelerating and dropping, the high-pressure air in the first buffer tank 11 is accelerated by the acceleration piston 9b and the seal pressing piston. 9f, the force corresponding to the cross-sectional area is instantaneously generated in the acceleration piston 9b. Accordingly, as the accelerating piston 9b descends at a high speed, the push rod 9c extends at a high speed, and a push force is applied to the weight 5 via the cylindrical spacing member 9r. Therefore, the weight 5 receives a pressing force from the spring acceleration device 7 and the pneumatic acceleration cylinder device 9 and falls at a higher speed. Thereby, the most severe impact test of the subject W is performed. In this case, since the compression amount of the acceleration coil spring 7g and the pressure of the high-pressure air can be variously set according to the impact test conditions of the subject W, the falling speed of the weight 5 can be freely changed to Impact testing can be performed.

  As described above, according to the drop test apparatus 1 according to the embodiment of the present invention, the impact test of the subject W caused by the free fall of the weight 5 and the subject caused by the accelerated fall of the weight 5 as described above. W impact test can be performed. Therefore, according to the drop test apparatus 1 according to the embodiment of the present invention, the height of the column 1a can be made lower than that of the free drop type drop test apparatus according to the conventional example in which the equivalent drop speed can be obtained. Since the height of the building that accommodates the device 1 can also be lowered, it is economically advantageous with respect to the installation cost of the drop test device 1.

  By the way, in the drop test apparatus 1 which concerns on the above form, the case where the weight acceleration apparatus 6 of this drop test apparatus 1 is equipped with two types of acceleration apparatuses, the spring acceleration apparatus 7 and the pneumatic acceleration cylinder apparatus 9, is an example. As explained. However, as is well understood from the above description, even if the weight acceleration device 6 has only the spring acceleration device 7 or only the pneumatic acceleration cylinder device 9, the weight acceleration device 6 has a heavy weight. The weight 5 can be accelerated and dropped. Therefore, it is not limited to the configuration of the drop test apparatus 1 according to the above embodiment.

1 is an overall front view of a drop test apparatus according to an embodiment of the present invention. 1 is an overall side view of a drop test apparatus according to an embodiment of the present invention. It is a top view of the shift table which concerns on the form of this invention and contains the rail of a drop test apparatus. It is the sectional view on the AA line of FIG. It is the B section enlarged view of FIG. It is CC sectional view taken on the line of FIG. It is D arrow line view of FIG. It is the EE sectional view taken on the line of FIG. It is the FF sectional view taken on the line of FIG. It is an attachment state explanatory drawing of the weight lifting apparatus according to the embodiment of the present invention. It is a structure explanatory drawing of the weight free fall apparatus concerning the form of this invention. 1 is a side view of a weight according to an embodiment of the present invention. It is a top view of a weight in connection with the form of this invention. FIG. 13 is a view taken in the direction of arrow G, omitting the column on the near side of the arrow in FIG. 12 (the column on the left side in FIG. 12). It is a longitudinal cross-sectional view of the weight acceleration apparatus concerning the form of this invention. It is the HH sectional view taken on the line of FIG. It is a side view of a booster claw removing mechanism according to an embodiment of the present invention. It is an attachment state explanatory view of a pneumatic acceleration cylinder device concerning an embodiment of the present invention. It is a longitudinal cross-section of a pneumatic acceleration cylinder apparatus concerning the form of this invention. It is a buffer tank arrangement | positioning explanatory drawing in connection with the form of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Drop test apparatus, 1a ... Strut, 1b ... Impact receiving base, 1c ... Upper maintenance deck, 1d ... Intermediate maintenance deck, 1e ... Base, 1f ... 1st roller guide, 1g ... 2nd roller guide 2 ... Shift table, 2a ... wheel, 2b ... impact absorber, 2c ... load cell, 2d ... lift rail, 2e ... rail guide, 2f ... hydraulic cylinder, 2g ... fixed rail, 2h ... motor with speed reducer, 2i ... drive sprocket, 2j ... driven sprocket, 2k ... table operating chain 3 ... weight lifting device, 3a ... drive motor, 3b ... driving sprocket, 3c ... driven sprocket, 3d ... chain for lifting, 3e ... lifting protrusion 4 ... free fall device, 4a ... tip Side boss, 4b ... Oilless bush, 4c ... Base end boss, 4d ... Slide pin, 4e ... Air cylinder 5 ... Weight, 5a ... Weight body, 5b ... First guide roller unit, 5c ... Second guide roller unit, 5d ... Spring seat plate, 5e ... Suspension hook, 5f ... Spacing body mounting part, 5g ... Weight for weight adjustment 6 ... Weight acceleration device, 6a. Mounting frame, 6b. Guide member 7. Spring acceleration device, 7a. Hydraulic cylinder for spring compression, 7b. Elevating frame, 7c ... Rotation fixing pin, 7d ... Suspension arm, 7e ... Arm Rotating air cylinder, 7f ... Extension rod, 7g ... Acceleration coil spring, 7h ... Elevating plate, 7i ... Guide rod 8 ... Boosting claw removal mechanism, 8a ... Claw removal arm, 8b ... Contact part, 8c ... Fixing pin , 8d ... toggle arm, 8e ... arm working cylinder, 8f ... telescopic rod, 8g ... guide cylinder 9 ... pneumatic acceleration cylinder device, 9a ... cylinder body, 9b ... acceleration piston, 9c ... push-down rod, 9d ... seal ring 9e ... positioning cylinder, 9f ... seal pressing piston, 9g ... hollow rod, 9h ... closure lid, 9i ... T-shaped bracket, 9j ... high pressure air inflow / outflow pipe, 9k ... sealing device, 9l ... screw rod, 9m ... adjusting nut , 9n: Blocking body, 9o: High-pressure air introduction pipe, 9p: Inner cylinder, 9r: Cylindrical spacing body, 9s: Clearance between the seal pressing piston and the blocking body 11: First buffer tank, 11a: Pipe connection pipe , 12 ... 1st buffer tank, 12a ... Pipe connection pipe, 13 ... Pressure booster L ... Work floor W ... Subject

Claims (9)

  Provided with wheels that roll on rails laid on the work floor, between the center position between a plurality of support columns that are erected on the work floor at a predetermined interval, and the outer position of the plurality of support columns The reciprocating movement moves the placed subject to the center position between the plurality of support columns, and is lowered at the center position between the plurality of support columns to the impact receiving base provided on the work floor. A shift table to be mounted; a weight-adjustable weight including a guide roller that rolls a roller guide provided on opposite sides of the plurality of columns; and the weight table that is provided along the columns. A weight lifting device capable of reversible operation that lifts the weight to a predetermined height, and the weight lifted by the weight lifting device, which is provided at the top of the plurality of support columns, and is supported to be freely lifted and released. Then, the pressing force acts on the weight instantly Drop test apparatus characterized by comprising; and a weight accelerator for.   The supporting weight is supported by retreating in synchronization with the weight by projecting in the opposite direction at a plurality of positions below the weight acceleration device and at a plurality of positions below the weight acceleration device. The drop test device according to claim 1, further comprising a free fall device having a slide pin that can freely move forward and backward.   The weight acceleration device includes a gantry frame installed on tops of the plurality of support columns, and an engaging claw provided on the gantry frame and engaged with a suspension hook provided on the weight. A pair of openable and closable suspension arms supported by fulcrum pins, and a pair of lifting pawls that simultaneously push the pair of suspension arms to release the engagement of the engagement claws with the pair of suspension arms. This mechanism is provided with a mechanism for removing the booster claw. The claw is supported at its distal end by a fixed pin so as to be rotatable, and presses in a direction opposite to that between the rotation fulcrum pin of the pair of suspension arms and the engaging claw. A pair of openable and closable toggle arms having a release arm and a distal end side pivotally attached to the proximal end side of the claw removal arm, and a proximal end side pivotally attached to the distal end of a telescopic rod of an arm operating cylinder that is guided by a guide to expand and contract A contract characterized by Drop test device according to any one of claim of claim 1 or 2.   The weight acceleration device is compressed through the suspension arm and the weight by the extension of the hydraulic cylinder provided in the gantry frame and the rod of the hydraulic cylinder, and is pressed against the weight by a resilient force. The drop test device according to any one of claims 1 to 3, further comprising a spring acceleration device including an acceleration spring for applying a lowering force.   The weight acceleration device includes a vertical cylinder provided on the gantry frame, an acceleration piston provided in a lower portion of the cylinder, and a pressing rod that applies a pressing force to the weight. The acceleration piston is provided at the top, and has a seal ring having a diameter smaller than the outer diameter of the acceleration piston, the upper portion of the cylindrical body, and the high pressure air that is incorporated into the upper portion and introduced from the side surface of the cylindrical body. A seal pressing piston that crushes the seal ring to shut off the inside and outside of the seal ring, and sends high-pressure air flowing in from a high-pressure air inflow / outflow pipe provided at the upper part of the cylindrical body through the hollow rod. And a pneumatic accelerating cylinder device comprising a positioning cylinder supplied between the accelerating piston and the accelerating piston. Drop test apparatus according to claim.   The drop test according to claim 5, wherein high-pressure air is supplied to a high-pressure air inflow / outflow pipe provided at an upper portion of the cylindrical body from a buffer tank provided in the gantry frame. apparatus.   6. The spring acceleration device and the pneumatic acceleration cylinder device of the weight acceleration device are configured so that a pressing force can be individually applied to the weight, respectively. Or the drop test device according to any one of 6 items.   The positioning cylinder of the pneumatic acceleration cylinder device has an upper end of the hollow rod connected through a connecting pin, and protrudes out of the cylinder so as to be airtight through a seal above a communication position of the high-pressure air inflow / outflow pipe. A screw rod in which a male thread is screwed into the protruding portion, and an adjustment nut that is screwed onto the male screw of the screw rod and adjusts the seal pressing piston to a position that crushes the seal ring by an appropriate crushing allowance. The drop test device according to any one of claims 5 to 7, wherein the drop test device is configured to be positioned by a positioning mechanism. The upper surface of the weight is provided with an interval body attaching portion for attaching an interval body that makes it possible to effectively use the entire stroke of the acceleration piston regardless of the set compression amount of the acceleration spring. The drop test apparatus according to any one of claims 5 to 8, wherein the drop test apparatus is characterized by the following.

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