JP7612231B2 - Test Equipment - Google Patents

Description

The present invention relates to a testing device capable of applying a shock of a specified waveform to a test specimen.

Crash tests are conducted to evaluate the safety of passengers in the event of a car crash. Crash tests include full-scale crash tests (destructive tests) in which a real car is crashed into a barrier at a specified speed, and crash simulation tests (sled tests) in which a sled (cart) with a test specimen attached is subjected to an impact (acceleration pulse) similar to that of a real car crash.

Patent document 1 describes a device for performing crash simulation tests. The device described in Patent document 1 non-destructively reproduces the impact acting on a test specimen attached to the sled by contacting the tip of the piston of the launcher with the front end of the sled supported so as to be freely movable in the horizontal direction and firing the piston using hydraulic pressure accumulated in the accumulator of the launcher.

JP 2012-2699 A

The device described in Patent Document 1 can adjust the degree of impact to the same level as a real vehicle collision by setting the piston's thrust stroke, but it cannot control the acceleration waveform. As a result, it was not possible to perform highly accurate testing.

The present invention was made in consideration of the above circumstances, and its purpose is to provide a test device capable of applying a controlled waveform shock to a test specimen.

A testing device according to one embodiment of the present invention includes a table on which a specimen is attached and which can move in a predetermined direction, a drive module capable of generating power to drive the table, a toothed belt capable of transmitting the power, and a control unit capable of controlling the drive module, the control unit being capable of controlling the drive module so as to generate an impact to be applied to the specimen, and the toothed belt transmitting the impact generated by the drive module to the table.

The above test device may be configured to include a pair of toothed pulleys around which a toothed belt is wound, with at least one of the pair of toothed pulleys being a drive pulley driven by a drive module.

The above test device may be configured to include a belt clamp that releasably fixes the toothed belt to the table, the toothed belt is fixed to the table at two fixed positions spaced apart in the length direction, and the effective length of the toothed belt is fixed so as to be adjustable at at least one of the fixed positions.

In the above test device, the drive module may be configured with an electric motor.

In the above test apparatus, the moment of inertia of the electric motor may be 0.02 kg·m ² or less, or 0.01 kg·m ² or less.

In the above test device, one or more drive modules may be equipped with a total of multiple electric motors, and the control unit may be configured to be capable of synchronously controlling the multiple electric motors using optical fiber communication.

In the above test device, the drive module may include a shaft driven by an electric motor and a bearing that rotatably supports the shaft, and the drive pulley may be attached to the shaft.

In the above test device, the drive module may be configured to include a pair of electric motors, with both ends of the shaft connected to the pair of electric motors.

The above-mentioned test device may be configured to have multiple toothed belts arranged in parallel to each other, capable of transmitting impact to the table through the multiple toothed belts, and with the effective lengths of the multiple toothed belts being the same.

The above test device may be configured to include a plurality of drive modules each of which drives a plurality of toothed belts, with at least two of the drive modules being arranged side-by-side in the axial direction of the drive pulley.

The above test device may be configured to include a plurality of drive modules each of which drives a plurality of toothed belts, with at least two of the drive modules being arranged side by side in a predetermined direction.

In the above test device, the drive module may have two drive pulleys, each of which drives two of the multiple toothed belts, and the two drive pulleys may be attached to a single shaft.

The above test device may be configured to include multiple drive modules, each of the pair of toothed pulleys being a drive pulley, and the multiple drive modules may include a first drive module that drives one of the pair of toothed pulleys and a second drive module that drives the other of the pair of toothed pulleys.

The above-mentioned testing device may be configured to include a pusher that pushes the table in a predetermined direction, a linear guide that supports the table and the pusher so that they can move in the predetermined direction, and an impact generating unit that generates an impact on the test specimen by colliding with the table, and a toothed belt that can be fixed to each of the table and the pusher and is releasably fixed to either the table or the pusher, such that when the toothed belt is fixed to the table, the drive module generates an impact on the test specimen and the impact is transmitted to the table by the toothed belt, and when the toothed belt is fixed to the pusher, the table pushed out by the pusher collides with the impact generating unit, generating an impact on the test specimen.

In the above test device, the impact generating unit may be configured to include a fixed unit, an impact unit arranged in a position where the table can collide, and a buffer unit that absorbs the impact between the fixed unit and the impact unit.

In the above test device, the buffer section may be configured to include a movable frame attached to the impact section, a pair of arms attached to the fixed section arranged to sandwich the movable frame in a predetermined direction, and springs sandwiched between the movable frame and each arm.

In the above test device, the table may be configured to have a first collision post protruding toward the impact generating section, the impact generating section may be configured to have a second collision post protruding toward the first collision post, and at least one of the first collision post and the second collision post may be configured as a shock absorbing device having at least one of a damper and a spring.

In the above test device, the linear guide may be equipped with a rail extending in a predetermined direction and a carriage capable of running on the rail via a rolling element, and the carriage may be configured to include a first carriage attached to the table and a second carriage attached to the pusher.

The above-mentioned testing device may be configured to include a linear guide that supports the table so that it can move in a predetermined direction, the linear guide including a rail extending in the predetermined direction and a carriage that can run on the rail via rolling elements, and the carriage fixed to the table.

In the above test device, the rolling elements may be made of a ceramic material containing any one of silicon nitride, silicon carbide, and zirconia.

In the above test device, the toothed belt may have a main body formed from an elastomer, and the elastomer may include either hard polyurethane or hydrogenated acrylonitrile butadiene rubber.

In the above test device, the toothed belt may be configured with a carbon core wire.

The above test device may be configured so that the control unit can control the drive module to apply an impact to the table similar to that caused by a car collision.

According to an embodiment of the present invention, a test device is realized that can apply a controlled waveform shock to a test specimen.

1 is a perspective view of a collision simulation testing device according to a first embodiment of the present invention. 1 is a plan view of a collision simulation testing device according to a first embodiment of the present invention. 1 is a front view of a collision simulation testing device according to a first embodiment of the present invention. 1 is a side view of a collision simulation testing device according to a first embodiment of the present invention. FIG. 2 is a perspective view showing an internal structure of a test unit according to the first embodiment of the present invention. FIG. 2 is a side view of the drive module of the first embodiment of the present invention. FIG. 2 is an exploded perspective view of the belt clamp according to the first embodiment of the present invention. FIG. 2 is a structural diagram of a toothed belt. FIG. 2 is a block diagram showing a schematic configuration of a control system. 1 is a graph showing an example of an acceleration waveform. FIG. 5 is a perspective view of a collision simulation testing device according to a second embodiment of the present invention. FIG. 5 is a plan view of a collision simulation testing device according to a second embodiment of the present invention. FIG. 5 is a front view of a collision simulation testing device according to a second embodiment of the present invention. FIG. 5 is a side view of a collision simulation testing device according to a second embodiment of the present invention. FIG. 11 is a perspective view of a crash simulation testing device according to a third embodiment of the present invention. FIG. 13 is a side view of a servo motor unit according to a fourth embodiment of the present invention. FIG. 13 is a side cross-sectional view of a servo motor according to a fifth embodiment of the present invention. FIG. 13 is a plan view of a collision simulation testing device according to a sixth embodiment of the present invention. FIG. 13 is a plan view of a collision simulation testing device according to a seventh embodiment of the present invention. FIG. 13 is a front view of a collision simulation testing device according to a seventh embodiment of the present invention. FIG. 13 is a side view of a collision simulation testing device according to a seventh embodiment of the present invention. FIG. 13 is a side view of a collision simulation testing device according to a seventh embodiment of the present invention.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings. In the following description, identical or corresponding components are denoted by the same or corresponding reference numerals, and duplicate descriptions will be omitted.

First Embodiment
Fig. 1 is a perspective view of a collision simulation testing apparatus 1000 according to a first embodiment of the present invention. Fig. 2, Fig. 3 and Fig. 4 are a plan view, a front view and a side view of the collision simulation testing apparatus 1000, respectively.

The collision simulation test device 1000 is a device that reproduces the impact that occurs to automobiles, occupants, and equipment of automobiles, etc. when automobiles, etc. (including railway vehicles, aircraft, and ships) collide.

The crash simulation test device 1000 is equipped with a table 1240 which resembles the frame of an automobile vehicle. A test specimen, such as a seat carrying a passenger dummy or a high-voltage battery for an electric vehicle, is attached to the table 1240. When the table 1240 is driven at a set acceleration (e.g., an acceleration equivalent to the impact on the vehicle frame during a collision), the test specimen attached to the table 1240 is subjected to an impact similar to that during an actual collision. The safety of the occupants is evaluated based on the damage sustained by the test specimen at this time (or damage predicted from the measurement results of an acceleration sensor or the like attached to the test specimen).

The crash simulation test device 1000 of this embodiment is configured to drive the table 1240 in only one horizontal direction. As shown by the coordinate axes in FIG. 1, the movable direction of the table 1240 is defined as the X-axis direction, the horizontal direction perpendicular to the X-axis direction as the Y-axis direction, and the vertical direction as the Z-axis direction. In addition, based on the traveling direction of the simulated vehicle, the left direction (X-axis positive direction) in FIG. 2 is called the front, the right direction (X-axis negative direction) is called the rear, the up (Y-axis negative direction) is called the right, and the down (Y-axis positive direction) is called the left. In addition, the X-axis direction in which the table 1240 is driven is called the "driving direction". In the crash simulation test, a large acceleration is applied to the table 1240 in the opposite direction to the traveling direction of the vehicle (i.e., backward).

The crash simulation test device 1000 includes a test section 1200 with a table 1240, a front drive section 1300 and a rear drive section 1400 that drive the table 1240, four belt mechanisms 1100 (belt mechanisms 1100a, 1100b, 1100c, 1100d) that convert the rotational motion generated by each drive section 1300, 1400 into translational motion in the X-axis direction and transmit it to the table 1240, and a control system 1000a (Figure 9).

The test section 1200 is disposed in the center of the crash simulation test device 1000 in the X-axis direction, and the front drive section 1300 and the rear drive section 1400 are disposed adjacent to each other in front and behind the test section 1200.

Figure 5 is a perspective view showing the structure of the testing unit 1200 and the belt mechanism 1100. For ease of explanation, the table 1240 and base block 1210 (described below), which are components of the testing unit 1200, are omitted from Figure 5.

In addition to the table 1240, the testing section 1200 includes a base block 1210 (FIG. 1), a frame 1220 mounted on the base block 1210, and a pair of linear guideways 1230 (hereinafter abbreviated as "linear guides 1230") mounted on the frame 1220. The pair of linear guides 1230 support the table 1240 so that it can move only in the X-axis direction (drive direction).

As shown in FIG. 5, the frame 1220 has a pair of half frames (right frame 1220R, left frame 1220L) connected by multiple connecting bars 1220C extending in the Y-axis direction. The right frame 1220R and the left frame 1220L have the same structure (strictly speaking, they are mirror images), so only the left frame 1220L will be described in detail.

The left frame 1220L has an attachment part 1221 and a rail support part 1222 that each extend in the X-axis direction, and three connecting parts 1223 (1223a, 1223b, 1223c) that extend in the Z-axis direction and connect the attachment part 1221 and the rail support part 1222. As shown in FIG. 1, the length of the attachment part 1221 is approximately equal to the length of the base block 1210 in the X-axis direction, and its entire length is supported by the base block 1210. In addition, the rear ends of the attachment part 1221 and the rail support part 1222 are connected to each other by the connecting part 1223a.

The rail support section 1222 is longer than the mounting section 1221 (i.e., longer than the base block 1210), and its tip protrudes forward beyond the base block 1210 and is positioned above the front drive section 1300.

The linear guide 1230 includes a rail 1231 extending in the X-axis direction and two carriages 1232 that run on the rail 1231 via rolling elements. The rails 1231 of the pair of linear guides 1230 are fixed to the upper surfaces of the rail support parts 1222 of the right frame 1220R and the left frame 1220L, respectively. The length of the rail 1231 is approximately equal to the length of the rail support parts 1222, and the entire length of the rail 1231 is supported by the rail support parts 1222. A plurality of mounting holes (screw holes) are provided on the upper surface of the carriage 1232, and a plurality of through holes corresponding to the mounting holes of the carriage 1232 are provided in the table 1240. The carriage 1232 is fastened to the table 1240 by fitting bolts (not shown) passed through each through hole of the table 1240 into each mounting hole of the carriage 1232. The table 1240 and the four carriages 1232 form a sled.

In addition, the table 1240 is formed with mounting structures such as screw holes for mounting a test piece such as a sheet (not shown), so that the test piece can be mounted directly on the table 1240. This eliminates the need for a mounting plate or other member for mounting the test piece, making it possible to reduce the weight of the moving parts to which the impact is applied, and to apply a high-fidelity impact to the test piece up to high frequency components.

As shown in FIG. 5, each belt mechanism 1100 includes a toothed belt 1120, a pair of toothed pulleys (a first pulley 1140 and a second pulley 1160) around which the toothed belt 1120 is wound, and a pair of belt clamps 1180 for fixing the toothed belt 1120 to the table 1240.

Four toothed belts 1120 (1120a, 1120b, 1120c, 1120d) are arranged in parallel between the right frame 1220R and the left frame 1220L. Each of the toothed belts 1120a-d is fixed to the table 1240 by belt clamps 1180 at two points in the longitudinal direction. The specific configuration for fixing the toothed belts 1120 to the table 1240 will be described later.

As shown in FIG. 2, the front drive unit 1300 includes a base block 1310 and four drive modules 1320 (1320a, 1320b, 1320c, 1320d) mounted on the base block 1310. The rear drive unit 1400 includes a base block 1410 and four drive modules 1420 (1420a, 1420b, 1420c, 1420d) mounted on the base block 1410. Drive modules 1320a-d and 1420a-d have slight differences in their installation positions and orientations, the lengths of their components, and the spacing between them, but they share a basic configuration.

The front drive unit 1300 and the rear drive unit 1400 also have the same basic configuration. Therefore, the configuration of the drive module 1320 of the front drive unit 1300 will be described in detail, and a duplicated description of the rear drive unit 1400 (drive module 1420) will be omitted. Note that in the following description of the front drive unit 1300 (drive module 1320), the reference characters (and names) in square brackets [ ] indicate the reference characters (and names) of the corresponding components in the rear drive unit 1400 (drive module 1420).

Figure 6 is a front view of the drive module 1320 [1420]. The drive module 1320 [1420] includes a servo motor 1320M [1420M], a first motor support 1331 [1431], a second motor support 1332 [1432], a coupling 1340 [1440], and a pulley support 1350 [1450]. The pulley support 1350 [1450] includes a pair of bearings 1361 [1461] and 1362 [1462], and a shaft 1370 [1470] rotatably supported by these bearings.

The servo motor 1320M [1420M] is an ultra-low inertia, high-output AC servo motor with a rated output of 37 kW, with the moment of inertia suppressed to 0.01 kg·m ² or less (approximately 0.008 kg·m ² ). The moment of inertia of a standard AC servo motor with the same output is approximately 0.16 kg·m ² , and the moment of inertia of the servo motor 1320M [1420M] of this embodiment is less than 1/20 of that. By using a motor with such a low moment of inertia, it is possible to drive the table 1240 at a high acceleration exceeding 20 G (196 m/s ² ). The collision simulation test device 1000 of this embodiment can apply an impact of a maximum acceleration of 50 G (490 m/s ² ) to the table 1240. To be used in a crash test device, the moment of inertia of the servo motor must be approximately 0.05 kg·m2 ^or less (preferably 0.02 kg·m2 ^or less, more preferably 0.01 kg· ^m2 or less). Even when using a low-capacity motor of about 7 kW, it is desirable to satisfy this numerical condition for the moment of inertia. Furthermore, a low-inertia servo motor with a ratio N/I of the maximum torque _Nmax to the moment of inertia I of at least 1000 or more (preferably 2500 or more, more preferably 5000 or more) is suitable for a crash simulation test device.

The servo motor 1320M [1420M] includes a shaft 1321 [1421], a first bearing 1325 [1425] and a second bearing 1326 [1426] that rotatably support the shaft 1321 [1421], a first bracket 1323 [1423] (load side bracket) that supports the first bearing 1325 [1425], a second bracket 1324 [1424] (anti-load side bracket) that supports the second bearing 1326 [1426], and a cylindrical stator 1322 [1422] through which the shaft 1321 [1421] passes. The first bracket 1323 [1423] and the second bracket 1324 [1424] are fixed to the stator 1322 [1422].

The first bracket 1323 [1423] is fixed to the base block 1310 [1410] via the first motor support portion 1331 [1431]. The second bracket 1324 [1424] is fixed to the base block 1310 [1410] via the second motor support portion 1332 [1432].

In this way, in the servo motor 1320M [1420M] of this embodiment, the first bracket 1323 [1423] and the second bracket 1324 [1424] that support the first bearing 1325 [1425] and the second bearing 1326 [1426], respectively, are supported by the first motor support part 1331 [1431] and the second motor support part 1332 [1432], respectively. As a result, the first bearing 1325 [1425] and the second bearing 1326 [1426] are held with high rigidity, so that even if a strong torque or bending stress is applied to the shaft 1321 [1421], the swinging motion (precession motion) of the shaft 1321 [1421] is suppressed, and high driving accuracy is maintained even under high load conditions. This effect is particularly noticeable at high loads of 10 kW or more.

The shaft coupling 1340 [1440] connects the shaft 1321 [1421] of the servo motor 1320M [1420M] to the shaft 1370 [1470] of the pulley support 1350 [1450]. The shaft 1370 [1470] is rotatably supported by a pair of bearings 1361 [1461] and 1362 [1462]. The bearings 1361 [1461] and 1362 [1462] are rolling bearings having rolling elements (balls or rollers). In addition to typical steel materials such as stainless steel, ceramic materials such as silicon nitride, silicon carbide, and zirconia may be used for the rolling elements. By using rolling elements made of ceramics such as silicon nitride, seizure of the bearings during high-speed driving is suppressed.

A first pulley 1140 [second pulley 1160] that drives the toothed belt 1120 is attached to the shaft 1370 [1470]. Note that the position at which the first pulley 1140 [second pulley 1160] is attached differs for each drive module 1320 [1420]. In the drive modules 1320a, 1320d [1420a, 1420d] arranged in front of the front drive unit 1300 [rear drive unit 1400], the first pulley 1140 [second pulley 1160] is attached close to the bearing 1361 [1461] side closer to the servo motor 1320M [1420M] as shown in FIG. 6, and in the drive modules 1320b, 1320c [1420b, 1420c] arranged in the rear, it is attached close to the bearing 1362 [1462] side farther from the servo motor 1320M [1420M]. This makes it possible to drive the adjacent toothed belts 1120 by the drive modules 1320a and 1320b, 1320d and 1320c [1420a and 1420b, 1420d and 1420c] arranged in a row in front of and behind.

As shown in FIG. 1-4, in the front drive unit 1300 [rear drive unit 1400], four drive modules 1320a-d [1420a-d] are installed at the four corners of the base block 1310 [1410], with their rotation axes facing the Y-axis direction. In addition, the drive modules 1320a and 1320d [1420a and 1420d] located at the front and the drive modules 1320b and 1320c [1420b and 1420c] located at the rear are arranged facing each other.

The toothed belt 1120a is wound around the first pulley 1140a attached to the drive module 1320a and the second pulley 1160a attached to the drive module 1420a. The toothed belt 1120b is wound around the first pulley 1140b attached to the drive module 1320b and the second pulley 1160b attached to the drive module 1420b. The toothed belt 1120c is wound around the first pulley 1140c attached to the drive module 1320c and the second pulley 1160c attached to the drive module 1420c. The toothed belt 1120d is wound around the first pulley 1140d attached to the drive module 1320d and the second pulley 1160d attached to the drive module 1420d. That is, in this embodiment, each toothed belt 1120a-d is configured to be driven by a pair of drive modules 1320a-d and 1420a-d, respectively.

The eight toothed pulleys (first pulleys 1140a-d and second pulleys 1160a-d) are identical and have the same outer diameter and number of teeth. The four toothed belts 1120a-d are also identical. The spacing (axis distance L) between the first pulleys 1140a-d and the second pulleys 1160a-d around which the toothed belts 1120a-d are wound is also the same, and the effective length of each toothed belt 1120a-d is also the same. Therefore, the response (stretching, etc.) of the toothed belts 1120a-d when driven by each drive module 1320a-d and 1420a-d is approximately the same, so there is no need to set drive conditions for each toothed belt 1120a-d.

Figure 7 is an exploded view of the belt clamp 1180. The belt clamp 1180 includes a table attachment portion 1181 that is detachably attached to the table 1240, and a clamp plate 1182 that tightens and fixes the toothed belt 1120 between the table attachment portion 1181.

A protruding tooth portion 1182t is formed in the widthwise center of the clamp plate 1182, which meshes with the toothed profile 1121t (FIG. 8) formed on the inner peripheral surface of the toothed belt 1120. In addition, a groove 1181g is formed on the underside of the table attachment portion 1181, into which the toothed belt 1120 and the tooth portion 1182t of the clamp plate 1182 are fitted.

The clamp plate 1182 has a plurality of through holes 1182h on both sides in the width direction, sandwiching the tooth portion 1182t, for bolting the clamp plate 1182 to the table mounting portion 1181. In addition, a screw hole (not shown) is formed on the underside of the table mounting portion 1181 at a position opposite each through hole 1182h. The clamp plate 1182 is attached to the table mounting portion 1181 by fitting the bolt 1183 passed through each through hole 1182h into the screw hole formed on the underside of the table mounting portion 1181.

When the toothed belt 1120 is fitted into the groove 1181g of the table attachment portion 1181 and the clamp plate 1182 is attached to the table attachment portion 1181, the toothed belt 1120 is compressed between the table attachment portion 1181 and the clamp plate 1182 and fixed to the belt clamp 1180. At this time, the teeth of the toothed belt 1120 and the teeth portion 1182t of the clamp plate 1182 are engaged with each other, so that even if a strong impact is applied to the toothed belt 1120 in the longitudinal direction (X-axis direction), the toothed belt 1120 does not slip from the belt clamp 1180, and the belt clamp 1180 is driven integrally with the toothed belt 1120.

The upper surface of the table mounting portion 1181 is provided with a plurality of screw holes 1181h for mounting to the table 1240. The table 1240 is also provided with a plurality of through holes (not shown) corresponding to the screw holes 1181h. The table 1240 can be easily replaced by simply attaching and detaching bolts to the through holes and the screw holes 1181h. For example, a dedicated table 1240 can be prepared for the test specimen, and the table 1240 can be replaced depending on the type of test specimen. In this embodiment, the table 1240 is flat, but it may have another shape (for example, a boat shape or a box shape). A part of the vehicle (for example, a frame) may be used as the table 1240. The test specimen can also be directly attached to the belt clamp 1180 and the carriage 1232.

Figure 8 shows the structure of the toothed belt 1120. The toothed belt 1120 has a main body 1121 formed from a high-strength, high-elasticity base material, and multiple core wires 1122 which are bundles of high-strength, high-elasticity fibers. The multiple core wires 1122 are arranged at approximately equal intervals in the width direction of the toothed belt 1120. Furthermore, each core wire 1122 is embedded in the main body 1121 in a state where it is stretched without slack in the length direction of the toothed belt 1120.

The inner peripheral surface (lower surface in FIG. 8) of the toothed belt 1120 is formed with teeth 1121t for meshing power transmission. The surface of the teeth 1121t is covered with a tooth cloth 1123 made of high-strength polyamide fibers or the like that have excellent abrasion resistance. In addition, the outer peripheral surface of the toothed belt 1120 is formed with a plurality of grooves 1121g extending in the width direction at equal intervals in the length direction to increase flexibility.

In the toothed belt 1120 of this embodiment, the core wire 1122 is a carbon core wire formed from lightweight, high-strength, and high-elasticity carbon fiber. By using a carbon core wire, even if the toothed belt 1120 is driven at a large acceleration and a large tension is applied to the toothed belt 1120, the toothed belt 1120 hardly stretches, so the driving force of each driving module 1320, 1420 is accurately transmitted to the table 1240, and the driving of the table 1240 can be controlled with high precision. In addition, by using a lightweight carbon core wire, the inertia of the toothed belt can be significantly reduced compared to when a metal core wire such as a steel wire or a steel cord is used. Therefore, it is possible to drive at a higher acceleration using a motor of the same capacity. In addition, when driving at the same acceleration, it is possible to use a motor of a lower capacity, which makes it possible to make the device smaller, lighter, and less expensive.

In addition, in the toothed belt 1120 of this embodiment, a high-strength, high-hardness elastomer such as high-strength polyurethane or hydrogenated acrylonitrile butadiene rubber (H-NBR) is used for the base material forming the main body 1121. By using a high-strength, high-hardness base material in this manner, the amount of deformation of the tooth profile during drive is reduced, suppressing the occurrence of tooth skipping due to deformation of the tooth profile, and making it possible to control the drive of the table 1240 with high precision. In addition, since the strength of the toothed belt 1120 is improved, the expansion and contraction of the toothed belt 1120 during drive is reduced, making it possible to control the drive of the table 1240 with even higher precision.

A crash simulation test device used to evaluate the crash safety performance of an automobile or the like must generate a large power capable of applying a high acceleration of 20 G (196 m/s ² ) to a test specimen, and must transmit this power accurately to the table 1240 and the test specimen. In order to transmit high acceleration accurately, it is necessary to use highly rigid members in the power transmission system. Examples of highly rigid power transmission systems include a ball screw mechanism, a gear transmission mechanism, a chain transmission mechanism, and a wire transmission mechanism.

During crash simulation testing, the sled reaches a maximum speed of 25 m/s (90 km/h). To achieve this speed using a ball screw mechanism, a lead of over 100 mm is required, but manufacturing a precision ball screw with such a long lead is extremely difficult.

In addition, when using a gear transmission mechanism or a chain transmission mechanism, it is necessary to give the gears or chain a strength that can withstand large acceleration. However, increasing the strength increases the inertia, so a motor with higher output is required. In addition, increasing the output of the motor is accompanied by an increase in the moment of inertia of the motor itself, so further increase in output is required, which significantly reduces energy efficiency and increases the size of the device. In addition, if the inertia of the entire device becomes excessive, it becomes difficult to generate and transmit large acceleration. The acceleration of the gear transmission mechanism or the chain transmission mechanism is limited to about 3G (29m/s ² ), and it is not possible to drive at the acceleration [at least 20G (196m/s ² )] required for the crash simulation test. In addition, if the gear mechanism or the chain mechanism is driven at the high peripheral speed (up to 25m/s) required for the crash simulation test, it will cause seizure.

In addition, although wire transmission mechanisms (wrap-around transmission mechanisms using wires and pulleys) have relatively low inertia, because power is transmitted solely by friction, slippage occurs between the wire and pulley when driven at high acceleration, making it impossible to transmit motion accurately.

In addition, general toothed belts such as timing belts for automobiles use a core wire made of twisted glass fiber or aramid fiber. Therefore, when driven at a large acceleration exceeding 10G (98m/ ^s2 ), the toothed belt expands and contracts more due to insufficient rigidity and strength of the core wire, making it impossible to transmit motion accurately. In addition, general toothed belts use synthetic rubber with low hardness such as nitrile rubber or chloroprene rubber as the base material, which makes it easy for teeth to skip and makes it impossible to transmit motion accurately.

Some systems use servo valves and hydraulic cylinders as the driving source, but their response speed is insufficient and they are unable to accurately reproduce shock waveforms that fluctuate at high frequencies exceeding 200 Hz. Hydraulic systems also require large hydraulic supply equipment in addition to the hydraulic device, so they require a large installation space. Furthermore, hydraulic systems have high maintenance and management costs for the hydraulic supply equipment, and there are problems such as environmental pollution due to oil leaks.

As a result of extensive repeated prototype testing of various types of transmission mechanisms, such as the ball screw mechanism, gear transmission mechanism, chain transmission mechanism, wire transmission mechanism, and belt transmission mechanism, the inventors have succeeded in developing the drive system of this embodiment, which combines an ultra ^- low inertia electric servo motor with a lightweight, high-strength special toothed belt made of a composite of a carbon core wire and a base material of a high elastic modulus elastomer, as the only configuration capable of achieving a large acceleration of up to 20 G (196 m/s2).

Figure 9 is a block diagram showing the schematic configuration of the control system 1000a of the crash simulation test device 1000. The control system 1000a includes a control unit 1500 that controls the operation of the entire device, a measurement unit 1600 that measures the acceleration of the table 1240, and an interface unit 1700 that performs input and output with the outside.

The interface unit 1700 includes, for example, a user interface for inputting and outputting data with a user, a network interface for connecting to various networks such as a LAN (Local Area Network), and one or more of various communication interfaces such as a USB (Universal Serial Bus) or a GPIB (General Purpose Interface Bus) for connecting to external devices. The user interface also includes, for example, one or more of various input/output devices such as various operation switches, displays, various display devices such as an LCD (Liquid Crystal Display), various pointing devices such as a mouse or a touchpad, a touch screen, a video camera, a printer, a scanner, a buzzer, a speaker, a microphone, a memory card reader/writer, etc.

The measurement unit 1600 includes an acceleration sensor 1620 attached to the table 1240, amplifies and digitally converts the signal from the acceleration sensor 1620 to generate measurement data, and sends it to the control unit 1500.

Eight servo motors 1320M and 1420M are connected to the control unit 1500 via servo amplifiers 1800. The control unit 1500 and each servo amplifier 1800 are communicatively connected by optical fiber, enabling high-speed feedback control between the control unit 1500 and each servo amplifier 1800. This enables synchronous control with higher precision (high resolution and high accuracy on the time axis).

The control unit 1500 can apply acceleration to the table 1240 according to the acceleration waveform by synchronously controlling the driving of the servo motors 1320M, 1420M of each drive module 1320a-d, 1420a-d based on the acceleration waveform input via the interface unit 1700 and the measurement data input from the measurement unit 1600. In this embodiment, all eight servo motors 1320M, 1420M are driven in the same phase (strictly speaking, the left drive modules 1320a, 1320b, 1420a, 1420b and the right drive modules 1320c, 1320d, 1420c, 1420d are driven in opposite phases [reverse rotation]).

Acceleration waveforms that can be used include basic waveforms such as sine wave, half sine wave, sawtooth wave, triangular wave, trapezoidal wave, etc., as well as acceleration waveforms measured in actual vehicle crash tests, acceleration waveforms obtained by crash simulation calculations, and any other synthetic waveforms (for example, waveforms generated by a function generator, etc.).

Figure 10 is an example of an acceleration waveform, and is a waveform obtained when a test was conducted using a dummy weight (a stainless steel rectangular block) fixed on the table 1240 as a specimen. In Figure 10, the dashed line indicates the target waveform, and the solid line indicates the measured waveform. In this test, a test acceleration having a waveform measured in a real vehicle crash test is applied to the specimen in the first phase (P1). In the subsequent second phase (P2), a state of zero acceleration (constant speed) is maintained for a predetermined period (e.g., 0.01 seconds). In the subsequent third phase (P3), the vehicle is decelerated at a substantially constant acceleration so that the absolute value of the acceleration is equal to or less than a predetermined value. As shown in Figure 10, it was confirmed that an acceleration waveform that closely matches the target waveform can be applied to the specimen using the crash simulation test device 1000 of this embodiment.

The crash simulation test device 1000 of this embodiment is completely different from conventional sled test devices such as those described in Patent Document 1 (JP Patent Publication No. 2012-2699) in that all movements of the test specimen (or table 1240) during the test are numerically controlled. Since all movements during the test are controlled, it is possible to easily apply impacts of various acceleration waveforms to the test specimen.

In conventional sled testing devices such as that described in Patent Document 1, the sled's movement after impact cannot be controlled, so the sled runs freely. This requires a long running path. In contrast, the collision simulation testing device 1000 of this embodiment can quickly stop the sled with appropriate acceleration (i.e., gentle enough to have no substantial effect on the test results) after impact, so the running path (rail 1231) can be shortened and the installation space for the device can be significantly reduced. For example, the length of the rail 1231 in this embodiment is only 2 m.

In addition, in a conventional sled test device as described in Patent Document 1, it is necessary to perform an operation of returning the run sled to its initial position after the test. In order to perform this operation automatically, it is necessary to further provide a mechanism for returning the sled to its initial position. In addition, since the running distance of the sled is long, the mechanism for returning the sled to its initial position is also large, and the process of returning it to its initial position also takes a certain amount of time. In addition, if a mechanism for self-propelling and returning to its initial position is incorporated into the sled, the mechanism for returning the sled to its initial position can be made smaller, but the load on the sled increases, which causes a problem of a decrease in acceleration during testing. In contrast, the collision simulation test device 1000 of this embodiment can automatically return the table 1240 to its initial position using a mechanism that applies an impact to the table 1240, so there is no need to provide a dedicated mechanism for returning the table 1240 to its initial position. In addition, since the distance that the table 1240 moves during the test is short as described above, the table 1240 can be returned to its initial position in a short time (for example, 1 to 2 seconds).

In addition, in a pressure-accumulation type sled test device that generates an impact using pressure accumulated in an accumulator or the like, as described in Patent Document 1, charging (accumulating pressure) takes time, so a certain interval must be left between tests. In contrast, the collision simulation test device 1000 of this embodiment does not require charging, so tests can be performed continuously without time intervals. This allows tests to be performed more efficiently.

In addition, pressure-accumulating sled test equipment uses ultra-high hydraulic pressure. Therefore, if a hydraulic leak occurs, there is a risk that the worker may be injured by the high-pressure hydraulic oil that is sprayed out. In addition, because the sled is run over long distances in an uncontrolled state, there is a risk that the worker may be injured by colliding with the running sled. In contrast, the collision simulation test equipment 1000 of this embodiment does not use hydraulic pressure and does not run the sled in an uncontrolled state, making it possible to perform tests safely.

As shown in FIG. 2, the four toothed belts 1120a-d are arranged in a staggered pattern, shifted back and forth. This configuration makes it possible to drive each toothed belt 1120 by four pairs of drive modules 1320, 1420 while keeping the axial distance L of the four toothed belts 1120 the same.

Second Embodiment
The crash simulation testing apparatus 1000 of the first embodiment described above is a high-output type apparatus suitable for testing comparatively heavy specimens or tests at higher accelerations, while the crash simulation testing apparatus 2000 of the second embodiment of the present invention described next is a medium-output type apparatus suitable for testing lighter specimens.

Figures 11, 12, 13, and 14 are respectively a perspective view, a plan view, a front view, and a side view of the crash simulation test device 2000.

The second embodiment of the crash simulation test device 2000 employs a configuration in which two pairs of servo motors 2320M and 2420M, half the number of pairs used in the first embodiment, are used to drive two toothed belts 2120a and 2120d.

In addition, the front drive unit 1300 [rear drive unit 1400] of the first embodiment described above has four drive modules 1320a-d [1420a-d] each having one servo motor 1320M [1420M], but as shown in FIG. 12, the front drive unit 2300 (rear drive unit 2400] of this embodiment has a single drive module 2320 [2420] having two servo motors 2320M [2420M]. In other words, this embodiment uses a drive module 2320 [2420] configured by connecting two servo motors 2320M [2420M].

Specifically, the drive module 2320 [2420] has a single shaft 2370 [2470] rotatably supported by three bearings 2361, 2362 and 2363 [2461, 2462 and 2463], and one end of the shaft 2370 [2470] is connected to one servo motor 2320M [2420M], and the other end is connected to the other servo motor 2320M [2420M]. That is, in this embodiment, the single shaft 2370 [2470] of the drive module 2320 [2420] is synchronously driven by two servo motors 2320M [2420M]. Such a servo motor connection structure is realized by high-precision synchronous control using high-speed optical digital communication between the control unit 2500 and each servo amplifier 2800.

In addition, in the drive module 2320 [2420] of this embodiment, the two toothed belts 2120a and 2120d are driven by the two first pulleys 2140a and 2140d [second pulleys 2160a and 2160d] attached to a single shaft 2370 [2470]. Therefore, in the drive module 2320 [2420], complete synchronous control of the two toothed belts 2120a and 2120d is realized.

In addition, in the first embodiment (FIG. 4), the driving modules 1320b and 1320c are arranged under the rail support portion 1222 of the frame 1220 to shorten the axial distance L of each of the belt mechanisms 1100a-d, but this configuration is not adopted in this embodiment. Therefore, as shown in FIG. 13-14, in this embodiment, the height of the rail support portion 2222 of the frame 2220 is low. Accordingly, the height of the belt clamp 2180 (FIG. 13) is thin. This reduction in the height of the belt clamp 2180 reduces the inertia of the belt clamp 2180, so that high acceleration performance can be obtained even with low output. In addition, the reduction in the height of the belt clamp 2180 reduces the moment of force around the Y axis applied to the belt clamp 2180 (and the toothed belt 2120) during driving, and the bending deformation of the toothed belt 2120 is reduced, improving the transmission accuracy of the driving force.

Third Embodiment
15 is a perspective view of a collision simulation test apparatus 3000 according to a third embodiment of the present invention. The collision simulation test apparatus 3000 according to this embodiment is a low-output type apparatus suitable for testing a specimen that is even lighter than the collision simulation test apparatus 2000 according to the second embodiment.

The third embodiment of the crash simulation test device 3000 employs a configuration in which two drive modules 3420a and 3420d, which are one-fourth the number of modules in the first embodiment, are used to drive two toothed belts 3120a and 3120d, respectively.

The collision simulation test device 3000 only has a test section 3200 and a rear drive section 3400 as mechanical sections, and does not have a front drive section. In this embodiment, instead of the front drive section 1300 (specifically, the pulley support sections 1350 of each drive module 1320a and 1320d) of the first embodiment, a pair of pulley support sections 3350a and 3350d are provided at the front end of the test section 3200.

Pulley support parts 3350a and 3350d have the same configuration as pulley support part 1350 of the first embodiment, except for the bearing arrangement interval and the length of shaft 3370. A first pulley 3140a is attached to shaft 3370 of pulley support part 3350a, and a first pulley 3140d is attached to shaft 3370 of pulley support part 3350d. Toothed belt 3120a is wound around first pulley 3140a of pulley support part 3350a and second pulley 3160a of rear drive part 3400. Toothed belt 3120d is wound around first pulley 3140d of pulley support part 3350d and second pulley 3160d of rear drive part 3400. No servo motor is connected to the shaft 3370 of the pulley support parts 3350a and 3350d, and the first pulleys 3140a and 3140d function as driven pulleys.

In belt transmission, power is transmitted by the traction force (tensile force) of the belt. In addition, in impact testing, it is necessary to apply a strong acceleration in the deceleration direction (rearward) to the test specimen. It is possible to place the drive unit in front of the test section 3200 and the driven pulley behind the test section 3200, but in this case, the test specimen is impacted by the traction of the belt on the side connected to the table 3240 after being folded back by the rear driven pulley, so the traction length of the belt becomes longer. As a result, the deterioration of drive accuracy due to the expansion and contraction of the belt increases. Therefore, it is more advantageous in terms of test accuracy to place the drive unit behind the test section 3200, as in this embodiment.

In the first embodiment described above, each toothed belt 1120 is wound around a pair of drive pulleys (first pulley 1140 and second pulley 1160), and the power of two servo motors 1320M and 1420M is combined to provide a large power to the toothed belt 1120. One method for providing even greater power to the toothed belt 1120 is to increase the output of each servo motor. However, if the output of the servo motor is increased simply by increasing the size (diameter) of the rotor, the moment of inertia increases, and it becomes impossible to drive at high acceleration.

To increase the output of a servo motor while maintaining high acceleration performance, it is effective to make the rotor long and thin. Below, we will explain the low-inertia, high-output servo motor (unit) developed by the present inventor based on this design concept. Instead of the servo motors in each of the above-mentioned examples, it is also possible to use servo motors (units) such as those in the fourth, fifth, and sixth embodiments described below.

Fourth Embodiment
Next, a collision simulation test apparatus 4000 according to a fourth embodiment of the present invention will be described. The collision simulation test apparatus 4000 differs from the collision simulation test apparatus 1000 of the first embodiment in that it includes servo motor units 4320M and 4420M (to be described later) instead of the servo motors 1320M and 1420M of the first embodiment. The servo motor units 4320M and 4420M have the same configuration.

Figure 16 is a side view of a servo motor unit 4320M according to a fourth embodiment of the present invention. The servo motor unit 4320M is formed by connecting two servo motors 4320MA and 4320MB in series.

The servo motor 4320MB has the same configuration as the servo motors 1320M and 1420M of the first embodiment. The servo motor 4320MA is a two-axis servo motor in which both ends of the shaft 4320A2 protrude outward to form two connecting shafts (first shaft 4320A2a and second shaft 4320A2b). The servo motor 4320MA has the same configuration as the servo motor 4320MB, except that it has the second shaft 4320A2b and does not have the rotary encoder 4327 described below. The first shaft 4320A2a of the servo motor 4320MA becomes the single output shaft 4322 of the servo motor unit 4320M.

In the following description of the servo motor unit 4320M, the side from which the output shaft 4322 protrudes (the right side in FIG. 16) is called the load side, and the opposite side is called the anti-load side. The two-axis servo motor 4320MA and the servo motor 4320MB are high-output, ultra-low inertia servo motors with a rated output of 37 kW, each generating a maximum torque of 350 N·m and with a moment of inertia of the rotating part suppressed to 10 ⁻² kg·m2 ^or less.

The servo motor 4320MB includes a cylindrical body 4320B1 (stator), a shaft 4320B2, a first bracket 4320B3 (load side bracket), a second bracket 4320B4 (anti-load side bracket), and a rotary encoder 4327. In addition, a pair of screw holes 4320B3t and 4320B4t are provided on the underside of the first bracket 4320B3 and the second bracket 4320B4, respectively.

One end 4320B2a on the load side of the shaft 4320B2 penetrates the first bracket 4320B3 and protrudes outside the motor case to become the output shaft 4320B2a. On the other hand, a rotary encoder 4327 that detects the rotational displacement of the shaft 4320B2 is attached to the mounting surface (left side surface in FIG. 16) of the second bracket 4320B4. The other end 4320B2b of the shaft 4320B2 penetrates the second bracket 4320B4 and is connected to the rotary encoder 4327.

As shown in FIG. 16, the output shaft 4320B2a of the servo motor 4320MB and the second shaft 4320A2b of the two-axis servo motor 4320MA are connected by a shaft coupling 4320C. In addition, the first bracket 4320B3 of the servo motor 4320MB and the second bracket 4320A4 of the two-axis servo motor 4320MA are connected at a predetermined distance by a connecting flange 4320D.

The connecting flange 4320D has a cylindrical body 4320D1 and two flanges 4320D2 extending radially outward from both axial ends of the body 4320D1. Each flange 4320D2 has a through hole for bolt fixing at a position corresponding to a screw hole provided in the mounting seat surface of the first bracket 4320B3 and the second bracket 4320A4, and is fixed to the first bracket 4320B3 and the second bracket 4320A4 with a bolt.

As mentioned above, making the rotor long and thin is an effective way to increase the motor's output while maintaining high acceleration performance, but if the interval at which the shaft is supported by the bearings is made too long, the shaft will not be rigid enough, and deformation vibrations of the shaft, such as bowing, will become more pronounced, which will actually reduce the motor's performance. Therefore, with the conventional configuration in which the rotating shaft is supported only at both ends of the motor case by a pair of bearings, there is a limit to how much capacity can be increased while maintaining a low moment of inertia.

In the servo motor unit 4320M of this embodiment, a long and slender rotor is realized without designing a new dedicated rotor, by a simple configuration in which the shafts of the two servo motors are connected by a shaft coupling. In addition, the support interval of the shafts by the bearings is maintained by a simple configuration in which the main bodies of the two servo motors are connected by a connecting flange. Therefore, even if the rotor is long, it is supported with high rigidity and can operate stably, which makes it possible to generate a large torque that fluctuates at a high frequency that was not possible with conventional servo motors. Note that the servo motor unit 4320M alone (unloaded state) can be driven at an angular acceleration of 30,000 rad/s2 or ^more .

Fifth Embodiment
Next, a collision simulation test apparatus 5000 according to a fifth embodiment of the present invention will be described. The collision simulation test apparatus 5000 differs from the collision simulation test apparatus 1000 according to the first embodiment in that it includes servo motors 5320M and 5420M (to be described later) instead of the servo motors 1320M and 1420M according to the first embodiment. Note that the servo motors 5320M and 5420M have the same configuration, and therefore a duplicated description of the servo motor 5420M will be omitted.

Figure 17 is a vertical view of a servo motor 5320M according to a fifth embodiment of the present invention. In the servo motor unit 4320M according to the fourth embodiment described above, a configuration is adopted in which the main bodies (stators) of two servo motors are connected by the connecting flange 4320D, but in the servo motor 5320M according to this embodiment, the connecting flange 4320D is not used, and a single main body frame formed integrally is used. The main body frame according to this embodiment is longer than the servo motors 4320MA and 4320MB according to the fourth embodiment, and has approximately the same overall length as the servo motor unit 4320M. The main body frame according to this embodiment is provided with three bearings at equal intervals at both ends and in the middle in the length direction. The rotating shaft is rotatably supported by these bearings. A pair of brackets that support the bearings are provided at both ends in the length direction of the cylindrical main body frame. In addition, a bearing support wall that supports the bearings is provided at the center of the length direction on the inner periphery of the main body frame. Furthermore, a coil is attached between each bracket and the bearing support wall on the inner periphery of the main body frame to form a main body (stator). A core is provided on the outer circumference of the rotating shaft, facing each coil, to form the rotor.

In this embodiment, the shaft (rotor) and main body (stator) can be designed specifically for each, which allows for a more optimized design of the entire servo motor 5320M, making it possible to realize a motor with higher performance.

The number of bearings and coils is not limited to the configuration shown in FIG. 17. For example, two or more bearings and bearing support walls may be provided midway along the length of the main body frame. It is also desirable to provide the bearings at approximately equal intervals along the length of the main body frame. In that case, a core and coil may be provided between adjacent bearings.

Sixth Embodiment
Next, a collision simulation test apparatus 6000 according to a sixth embodiment of the present invention will be described. The collision simulation test apparatus 6000 differs from the collision simulation test apparatus 1000 according to the first embodiment in that it includes servo motor units 6320M and 6420M (to be described later) instead of the servo motors 1320M and 1420M according to the first embodiment. The servo motor units 6320M and 6420M have the same configuration.

Figure 18 is a plan view of a collision simulation test device 6000 according to the sixth embodiment of the present invention. The servo motor unit 6320M [6420M] is equipped with two servo motors 6320MA and 6320MB [6420MA and 6420MB] connected in series. The servo motors 6320MA and 6420MA have the same configuration as the servo motors 1320M and 1420M of the first embodiment.

The servo motor 6320MA [6420MA] is a two-axis servo motor in which both ends of the shaft 6320A2 [6420A2] protrude outward to form two shafts (first shaft 6320A2a [6420A2a] and second shaft 6320A2b [6420A2b]). The servo motors 6320MA and 6420MA have the same configuration as the servo motors 1320M and 1420M of the first embodiment, except that they have the second shaft 6320A2b [6420A2b] and do not have a rotary encoder 1327 (Figure 3). The first shaft 6320A2a [6420A2a] of the servo motor 6320MA [6420MA] becomes the single output shaft 6322 [6422] of the servo motor unit 6320M [6420M].

The servo motor 6320MA [6420MA], which is a two-axis servo motor, has a first bracket 6323A [6423A] and a second bracket 6324A [6424A] fixed to a base plate 6320D [6420D] via a first motor support part 6331 [6431], both of which have high rigidity. The base plate 6320D [6420D] is fixed to a base block 6310 [6410].

The servo motor 6320MB [6420MB] is fixed to the base plate 6320D [6420D] by the first bracket 6323B [6423B] via the first motor support portion 6331 [6431] and the second bracket 6324B [6424B] via the second motor support portion (not shown).

That is, in this embodiment, the body of the servo motor 6320MA [6420MA] and the body of the servo motor 6320MB [6420MB] are connected via the base plate 6320D [6420D]. In this embodiment, the first motor support part 6331 [6431] with high rigidity is used to support the second bracket 6324A [6424A] on the anti-load side of the servo motor 6320MA [6420MA], which is a two-axis servo motor, making it possible to connect the body of the servo motor 6320MA [6420MA] and the body of the servo motor 6320MB [6420MB] with sufficient rigidity without using the connecting flange 4320D of the fourth embodiment. By eliminating the connecting flange 4320D, assembly of the servo motor unit 6320M [6420M] becomes easier.

Furthermore, the output shaft 6320B2 [6420B2] of the servo motor 6320MB [6420MB] and the second shaft 6320A2b [6420A2b] of the servo motor 6320MA [6420MA] are connected by a shaft coupling 6320C [6420C].

A total of 16 servo motors 6320MA, 6320MB, 6420MA, and 6420MB are connected to the control unit via individual servo amplifiers and are synchronously controlled by the control unit. In this embodiment, all 16 servo motors 6320MA, 6320MB, 6420MA, and 6420MB are driven and controlled according to the same acceleration waveform.

Seventh Embodiment
Next, a collision simulation testing apparatus 7000 according to a seventh embodiment of the present invention will be described. Figures 19 and 20 are a plan view and a front view, respectively, of the collision simulation testing apparatus 7000. Also, Figures 21 and 22 are side views of the collision simulation testing apparatus 7000.

The collision simulation test device of each of the above-mentioned embodiments is configured to generate an impact (acceleration pulse) of a predetermined waveform to be applied to the specimen by the front drive unit and the rear drive unit, and transmit the generated impact waveform to the table on which the specimen is attached by a belt mechanism. In contrast, the collision simulation test device 7000 of this embodiment is configured to apply an impact of a predetermined waveform to the specimen attached to the table 7240 by colliding the table 7240, which is freely traveling at a predetermined speed, with the impact generating unit 7900 described below. In other words, the collision simulation test device 7000 of this embodiment is configured to be able to perform conventional collision-type impact tests.

The collision simulation test device 7000 of this embodiment, like the collision simulation test device 2000 of the second embodiment, is equipped with a table 7240, a pair of linear guides 7230 that support the table 7240 so that it can move in the X-axis direction, a front drive unit 7300 and a rear drive unit 7400 that drive the table 7240, and a pair of belt mechanisms 7100a, 7100d that transmit the power generated by the front drive unit 7300 and the rear drive unit 7400.

Furthermore, the crash simulation test device 7000 of this embodiment is equipped with an impact generating unit 7900 that applies an impact of a predetermined waveform to the table 7240, and a pusher 7250 that pushes the table 7240 toward the impact generating unit 7900.

Each linear guide 7230 has a rail 7231 and three carriages 7232 that can run on the rail 7231. The carriages 7232 include two carriages 7232a attached to the underside of the table 7240 and one carriage 7232b attached to the underside of the pusher 7250. In other words, the table 7240 and the pusher 7250 are supported by a pair of linear guides 7230 so that they can run in the X-axis direction.

A pair of belt clamps 7180 (FIG. 20) are attached to the underside of the pusher 7250, and the pusher 7250 is fixed to a pair of toothed belts 7120 via the belt clamps 7180. That is, the pusher 7250 is driven by a pair of belt mechanisms 7100a, 7100d. Note that the table 7240 in this embodiment is not connected to the belt mechanisms 7100a, 7100d, and is driven via the pusher 7250 connected to the belt mechanisms 7100a, 7100d.

As shown in FIG. 20, the pusher 7250 has a bottom plate 7251, a push plate 7252 that stands upright on the upper surface of the front end of the bottom plate 7251, and a rib 7253 that connects the bottom plate 7251 and the push plate 7252 to increase rigidity. A pair of carriages 7232b (FIG. 21) of the linear guide 7230 are attached to the lower surface of the bottom plate 7251.

The impact generating unit 7900 includes a fixed unit 7920 fixed on the base block 7310, an impact unit 7940 disposed on the fixed unit 7920, and a buffer unit 7950 that absorbs the impact between the fixed unit 7920 and the impact unit 7940.

A slide plate (not shown) is attached to the underside of the impact part 7940, allowing the impact part 7940 to slide on the fixed part 7920 with low friction.

The buffer section 7950 includes a pair of movable frames 7951 attached to the impact section 7940, two pairs of arms 7953 and a pair of guide rails 7955 attached to the fixed section 7920, four coil springs 7954, and a coil retaining rod 7956. Note that although the coil springs 7954 in this embodiment are compression springs, tension springs may also be used. Also, instead of the coil springs 7954, other types of springs such as leaf springs and disc springs may also be used.

The movable frame 7951 is attached to both the left and right (Y-axis direction) sides of the impact part 7940. The movable frame 7951 has a bottom plate 7251a that is placed on the upper surface of the fixed part 7920, and four ribs 7951b that connect this bottom plate 7251a to the sides of the impact part 7940. The four ribs 7951b are arranged at equal intervals in the X-axis direction.

The pair of guide rails 7955 are attached to the upper surface of the fixed part 7920 so that their length direction faces the X-axis direction and the impact part 7940 is sandwiched from both sides in the Y-axis direction together with the pair of movable frames 7951 (specifically, bottom plates 7251a). The pair of guide rails 7955 limits the movable direction of the impact part 7940 to only the X-axis direction.

In this embodiment, the impact portion 7940 is configured to be guided in a sliding manner by the slide plate and guide rail 7955, but instead of the slide plate and guide rail 7955, a linear guide equipped with a rolling body may be used to guide the impact portion 7940 in a rolling manner.

Two pairs of arms 7953 extending in the Z-axis direction are attached to the four corners of the fixed part 7920 so as to sandwich each movable frame 7951 from both sides in the X-axis direction.

A coil spring 7954 is disposed between each arm 7953 and the adjacent movable frame 7951. A preload adjusted to generate an impact with a predetermined waveform is applied to each coil spring 7954. By sandwiching the movable frame 7951 between a pair of coil springs 7954 on both sides in the moving direction, even if the movable frame 7951 is displaced, it is quickly returned to its initial position by the coil springs 7954. The buffer section 7950 may also be provided with a damper disposed in series or parallel to the coil springs 7954.

The impact unit 7940 of the impact generating unit 7900 has a protrusion 7942 formed in the center in the Y-axis direction facing the table 7240, which protrudes toward the table 7240 (negative direction of the X-axis). In addition, a collision post 7944 protruding toward the table 7240 is attached to the tip of the protrusion 7942.

The table 7240 also includes a main body 7242 and a collision post 7244 that protrudes from the center of the front of the main body 7242.

In this embodiment, collision pillars 7244 and 7944 are rigid bodies integrally formed from a hard material such as steel, but collision pillars 7244 and/or 7944 may be shock absorbers equipped with dampers and/or springs. When collision pillars 7244 and/or 7944 are shock absorbers equipped with both dampers and springs, the dampers and springs may be connected in series or in parallel.

Next, the operation of the collision simulation test device 7000 will be described. First, the table 7240 and the pusher 7250 are placed in the initial position shown in FIG. 20. At this time, the back surface of the table 7240 is in contact with the push plate 7252 of the pusher 7250. Next, the pusher 7250 is driven at a predetermined speed toward the impact generating unit 7900 by the front drive unit 7300 and the rear drive unit 7400 via the belt mechanisms 7100a and 7100d. Since the table 7240 is in contact with the push plate 7252 of the pusher 7250, the table 7240 is driven at a predetermined speed together with the pusher 7250. At this time, the pusher 7250 is gradually accelerated to a predetermined speed so as not to give a large impact to the table 7240 and not to separate from the pusher 7250 until the table 7240 reaches the predetermined speed. When the pusher 7250 reaches the predetermined speed, it decelerates and stops.

When the pusher 7250 decelerates, the table 7240 leaves the pusher 7250 and runs freely on the rail 7231 at a predetermined speed. Eventually, as shown in FIG. 22, the collision column 7244 of the table 7240 collides with the collision column 7944 of the impact section 7940, and the impact caused by this collision is given to the test piece attached to the table 7240. The magnitude and waveform of the impact given to the test piece can be adjusted by the collision speed (predetermined speed) and the spring constant of the coil spring 7954. In addition, by providing a damper to the buffer section 7950 or providing a damper and/or spring to the collision column 7244 and/or 7944 to serve as a buffer device, it becomes possible to generate more diverse impact waveforms. Furthermore, by providing, for example, multiple springs and dampers with different characteristics to the impact generating section 7900 and changing the combination and connection relationship of these, it becomes possible to generate more diverse impact waveforms.

After the test, the pusher 7250 is returned to the initial position by driving the front drive unit 7300 and the rear drive unit 7400 in the opposite direction. The table 7240 is returned to the initial position manually. A mechanism for automatically returning the table 7240 to the initial position may be provided. For example, a connection mechanism for releasably connecting the pusher 7250 and the table 7240 may be provided, and the pusher 7250 and the table 7240 may be connected, and then the pusher 7250 is returned to the initial position, thereby making it possible to return the table 7240 to the initial position. For example, a belt mechanism for returning the table may be provided in addition to the belt mechanisms 7100a and 7100d. In this case, the table 7240 may not be fixed to a toothed belt, and may be configured to push the table 7240 back to the initial position by a pusher attached to the belt, for example.

The belt clamp 7180 is removably attached to the pusher 7250 by a bolt. In addition, a plurality of screw holes are provided on the underside of the table 7240, so that four belt clamps 7180 can be removably attached to the table 7240 by bolts. By removing the belt clamp 7180 from the pusher 7250, attaching the belt clamp 7180 to the table 7240, and connecting the table 7240 to the toothed belt 7120 of the belt mechanisms 7100a and 7100d, it becomes possible to perform a test in which the shock waveform generated by the front drive unit 7300 and the rear drive unit 7400 is directly applied to the table 7240 by the pair of belt mechanisms 7100a and 7100d, as in the crash simulation test device 2000 of the second embodiment.

The above is a description of exemplary embodiments of the present invention. The embodiments of the present invention are not limited to those described above, and various modifications are possible within the scope of the technical ideas expressed by the claims. For example, the embodiments of the present application also include configurations that appropriately combine configurations of the embodiments etc. explicitly shown as examples in this specification and/or configurations of the embodiments etc. that are obvious to a person skilled in the art from the descriptions in this specification.

In each of the above embodiments, the shaft of the servo motor is directly connected to the shaft of the pulley support part, but the servo motor and the shaft of the pulley support part may be connected via a reducer. Using a reducer makes it possible to test specimens with greater weight (inertia). In addition, it becomes possible to use a servo motor with a lower capacity, which allows for a smaller, lighter, and less expensive device.

In each of the above embodiments, the acceleration applied to the table 1240 is controlled (i.e., the impact is expressed by the acceleration), but the present invention is not limited to this configuration. For example, the table 1240 may be controlled by the speed or jerk.

In each of the above embodiments, the acceleration of the table is controlled, but the present invention is not limited to this configuration. For example, the acceleration (impact) at a specific location of a test specimen (e.g., a sheet attached to a table, or a dummy placed on the sheet) may be the object to be controlled.

In each of the above embodiments, a linear guide consisting of a rail and a roughly rectangular parallelepiped carriage is used as the linear motion guide mechanism, but the present invention is not limited to this configuration. For example, instead of or in addition to the linear guide, a rolling guide mechanism using rolling elements such as ball splines or linear bushings may be used.

In each of the above embodiments, balls are used as the rolling elements of the linear motion guide mechanism (linear guide), but the present invention is not limited to this configuration. For example, rollers may be used as the rolling elements.

In each of the above embodiments, silicon nitride is used as the material for the rolling elements of the linear motion guide mechanism (linear guide), but the present invention is not limited to this configuration. For example, other types of ceramic materials such as silicon carbide and zirconia may be used, or stainless steel may be used.

In each of the above embodiments, the table 1240 is supported by a pair of left and right linear guides 23 so that it can move only in the drive direction, but the present invention is not limited to this configuration. For example, the table 1240 may be supported by three or more linear guides 23. By increasing the number of linear guides 23, the support rigidity of the table 1240 is improved. The number of linear guides 23 to be used is determined according to the weight of the test specimen and the required test accuracy.

In each of the above embodiments, two or four toothed belts 1120 are used, but the present invention is not limited to this configuration. For example, one, three, or five or more toothed belts 1120 may be used depending on the weight of the test specimen and the magnitude of the test acceleration.

In each of the above embodiments, the toothed belt 1120 is an endless belt, but the present invention is not limited to this configuration. The toothed belt 1120 is fixed to the table 1240 by the belt clamps 18 at two points spaced apart in the length direction (driving direction), so an open-end belt can also be used.

In each of the above embodiments, the two belt clamps 18 that secure one toothed belt 1120 are formed separately, but they may be formed integrally.

In each of the above embodiments, the table 1240 and the table attachment portion 1181 of the belt clamp 18 are formed separately, but they may be formed integrally. For example, the toothed belt can be fixed directly to the table by providing a groove in the underside of the table into which the toothed belt is fitted and a screw hole for bolting the clamp plate.

In each of the above embodiments, an AC servo motor is used as the drive source, but other types of actuators can be used as long as they allow motion control. For example, a DC servo motor, a stepping motor, an inverter motor, etc. can be used. A hydraulic motor or a pneumatic motor can also be used.

In the above embodiment, the mounting portion 1221, rail support portion 1222, and connecting portion 1223 of the frame 1220 are each a rectangular column-shaped structural member, but the present invention is not limited to this configuration. The mounting portion 1221 may have another shape as long as it has a flat surface on its lower surface for installation on the base block 1210. The rail support portion 1222 may have another shape as long as it has a flat surface on its upper surface for attaching the rail 1231. In addition, the connecting portion 1223 may have another shape as long as it connects the mounting portion 1221 and the rail support portion 1222 with sufficient strength.

The above-described embodiment of the present invention can also be explained as follows.

The crash simulation test device according to one embodiment of the present invention comprises a table on which a test specimen is attached and a toothed belt that drives the table in a driving direction, the toothed belt having a carbon core wire.

The above-mentioned crash simulation test device may be configured to include a pair of toothed pulleys around which a toothed belt is wound, a belt clamp that releasably fixes the toothed belt to the table, and the toothed belt is fixed to the table at two fixed positions spaced apart in the longitudinal direction.

With this configuration, the belt clamp is fixed to the table, which reduces the risk of teeth skipping caused by the toothed belt being shaken by the load of the belt clamp, improving the drive control of the table.

In the above-mentioned crash simulation test device, the toothed belt may be configured so that the effective length of the toothed belt is adjustable at at least one fixed position.

This configuration makes it easy to adjust the effective length of the toothed belt.

The above-mentioned crash simulation test device may be configured to have multiple toothed belts arranged in parallel with each other, and the table may be driven by the multiple toothed belts.

This configuration makes it possible to apply the necessary impact even to test specimens with large mass.

In the above-mentioned crash simulation test device, the effective lengths of the multiple toothed belts may be the same.

With this configuration, the response characteristics of each toothed belt are uniform, making it possible to control each toothed belt under the same conditions (e.g., the same time constant). This makes it possible to drive multiple toothed belts with simpler control, reducing the processing power required for the control device.

In the above-mentioned crash simulation test device, at least one of the pair of toothed pulleys may be a drive pulley, and the device may be configured to include a drive module that drives the drive pulley.

In the above-mentioned crash simulation test device, the drive module may be configured with an electric motor.

With this configuration, hydraulic pressure is not required, so there is no need to install hydraulic supply equipment. This means that a large installation space is not required, and there is no need for the maintenance and burden of hydraulic supply equipment. In addition, the surrounding environment is not contaminated by hydraulic oil, making it possible to conduct tests in a clean and safe environment.

In the above-mentioned crash simulation test device, the electric motor may be a servo motor.

In the above-mentioned crash simulation test apparatus, the moment of inertia of the electric motor may be 0.02 kg·m ² or less.

This configuration makes it possible to generate large acceleration.

In the above-mentioned crash simulation test device, the moment of inertia of the electric motor may be 0.01 kg·m ² or less.

In the above-mentioned crash simulation test device, the drive module may be configured to include a reducer that reduces the output of the electric motor.

This configuration also makes it possible to test specimens with large inertia.

In the above-mentioned crash simulation test device, the drive module may include a shaft driven by an electric motor and a bearing that rotatably supports the shaft, and the drive pulley may be attached to the shaft.

In the above-mentioned crash simulation test device, the drive module may be equipped with a pair of electric motors, and both ends of the shaft may be connected to the pair of electric motors, respectively.

This configuration allows the shaft to be driven with greater power. Also, when two electric motors are used, the shaft can be shared, reducing the number of bearings and making the device more compact.

The above-mentioned crash simulation test device may be configured to include a plurality of drive modules each of which drives a plurality of toothed belts, with two of the drive modules being arranged side-by-side in the axial direction of the drive pulley.

This configuration makes it possible to shorten the power transmission path that drives the drive pulley, lowering the moment of inertia of the power transmission path and enabling driving at greater acceleration.

The above-mentioned crash simulation test device may be configured to include a plurality of drive modules each for driving a plurality of toothed belts, with two of the drive modules arranged side-by-side in the drive direction, sandwiching the toothed belts between them.

This configuration makes it possible to shorten the power transmission path that drives the drive pulley, lowering the moment of inertia of the power transmission path and enabling driving at greater acceleration.

In the above-mentioned crash simulation test device, the drive module may be provided with at least two toothed pulleys each driving at least two of the multiple toothed belts, and the at least two toothed pulleys may be attached to a shaft.

With this configuration, at least two toothed belts are driven by a single shaft, making it possible to perfectly synchronize the drive of the at least two toothed belts, enabling more precise drive.

In the above-mentioned crash simulation test device, the pair of toothed pulleys may both be drive pulleys.

This configuration makes it possible to drive the toothed belt with higher power.

In the above-mentioned crash simulation test device, the drive module may be configured to include a first drive module that drives one of the pair of toothed pulleys, and a second drive module that drives the other of the pair of toothed pulleys.

In the above-mentioned crash simulation test device, one or more drive modules may be equipped with a total of multiple electric motors, and a control unit may be provided for synchronously controlling the multiple electric motors, and the control unit may be configured to control each electric motor at high speed using optical fiber communication.

This configuration makes it possible to drive the table with sufficiently high precision.

The above-mentioned collision simulation test device may be configured to include a pusher that pushes the table in the driving direction, a linear guide that supports the table and the pusher so that they can move in the driving direction, and an impact generating unit that generates an impact on the test specimen by colliding with the table, and a toothed belt that can be fixed to each of the table and the pusher and is releasably fixed to either the table or the pusher, such that when the toothed belt is fixed to the table, the driving module generates an impact on the test specimen and the impact is transmitted to the table by the toothed belt, and when the toothed belt is fixed to the pusher, the table pushed out by the pusher collides with the impact generating unit, generating an impact on the test specimen.

In the above-mentioned collision simulation test device, the impact generating unit may be configured to include a fixed unit, an impact unit arranged in a position where the table can collide, and a buffer unit that absorbs the impact between the fixed unit and the impact unit.

In the above-mentioned collision simulation test device, the buffer section may be configured to include a movable frame attached to the impact section, a pair of arms attached to the fixed section and arranged to sandwich the movable frame in the driving direction, and springs sandwiched between the movable frame and each arm.

In the above-mentioned collision simulation test device, the table may be configured to have a first collision pillar protruding toward the impact generating part, the impact part of the impact generating part may have a second collision pillar protruding toward the first collision pillar, and at least one of the first collision pillar and the second collision pillar may be configured as a shock absorbing device having at least one of a damper and a spring.

In the above-mentioned crash simulation test device, the linear guide may be equipped with a rail extending in the driving direction and a carriage that runs on the rail via a rolling element, and the carriage may be configured to include a first carriage attached to the table and a second carriage attached to the pusher.

In the above-mentioned crash simulation test device, the toothed belt may have a main body portion formed from an elastomer, and the elastomer may include either hard polyurethane or hydrogenated acrylonitrile butadiene rubber.

This configuration reduces the occurrence of tooth skipping, making it possible to drive the table with greater precision.

The above-mentioned crash simulation test device may be configured to include a linear guide that guides the table in the driving direction, the linear guide including a rail extending in the driving direction, and a carriage that runs on the rail via a rolling element.

This configuration suppresses unnecessary movement of the table in directions other than the driving direction, making it possible to drive the table with greater precision. In addition, the use of low-loss rolling guides makes it possible to drive the table with less power, and since the guide means is less likely to seize, the table can be driven with greater acceleration.

In the above-mentioned crash simulation test device, the rolling elements may be made of a ceramic material.

In the above-mentioned crash simulation test device, the ceramic material may be configured to include any one of silicon nitride, silicon carbide, and zirconia.

According to this configuration, the rolling elements made of ceramic material are characterized by being lighter, more heat resistant, and more precise than those made of ordinary steel. This makes it less likely for seizure to occur, and makes it possible to drive the table with greater acceleration.

In the device described in Patent Document 1, the sled pushed out by the piston travels a long distance by inertia, so the overall length of the device is very long and a large installation space is required. According to one embodiment of the present invention, a small, highly accurate crash simulation test device is realized.

1000: Crash simulation test device (first embodiment)
1100: Belt mechanism 1200: Test section 1300: Front drive section 1400: Rear drive section 1500: Control section 2000: Crash simulation test device (second embodiment)
3000: Crash simulation test device (third embodiment)
4000: Crash simulation test device (fourth embodiment)
5000: Crash simulation test device (fifth embodiment)
6000: Crash simulation test device (sixth embodiment)
7000: Crash simulation test device (seventh embodiment)

Claims (6)

a table on which a specimen is attached and which can move linearly in a predetermined direction;
A plurality of drive modules capable of generating power for driving the table;
a belt mechanism that transmits the power generated by the plurality of drive modules to the table ;
A control unit capable of controlling the plurality of drive modules;
Equipped with
The belt mechanism includes:
At least one pair of toothed belts arranged parallel to each other, and at least one of the drive modules is provided for each of the toothed belts;
The drive module includes:
a drive pulley around which one of the pair of toothed belts to be driven is wound;
an electric motor having a moment of inertia capable of generating acceleration equivalent to an impact generated during a collision, the electric motor having a rotating shaft connected to the drive pulley,
The control unit synchronously controls each of the electric motors of the plurality of drive modules in accordance with an acceleration waveform set based on an impact of an assumed collision, thereby applying the impact of the assumed collision to the test specimen.
Test equipment. the pair of toothed belts are first and second toothed belts having the same effective length and folded back at the same folding back position in the predetermined direction,
the plurality of drive modules include a first drive module and a second drive module that drive the first toothed belt, and a third drive module and a fourth drive module that drive the second toothed belt;
the first drive module includes a first drive pulley around which the first toothed belt is wound at one of the turn-back positions of the first toothed belt, and a first electric motor provided for the first drive pulley,
the second drive module includes a second drive pulley around which the first toothed belt is wound at the other turn-back position of the first toothed belt, and a second electric motor provided for the second drive pulley,
the third drive module includes a third drive pulley around which the second toothed belt is wound at one of the turn-back positions of the second toothed belt, and a third electric motor provided for the third drive pulley,
the fourth drive module includes a fourth drive pulley around which the second toothed belt is wound at the other turn-back position of the second toothed belt, and a fourth electric motor provided for the fourth drive pulley,
At the turn-back position of one of the first and second toothed belts, the first electric motor and the third electric motor are disposed facing each other in a direction of a central rotation axis so as to share a central rotation axis with the first and third drive pulleys,
At the other turn-back position of the first and second toothed belts, the second electric motor and the fourth electric motor are disposed facing each other in a direction of a central rotation axis so as to share a central rotation axis with the second and fourth drive pulleys.
2. The test device according to claim 1. the belt mechanism includes a belt clamp that releasably fastens the toothed belt to the table;
The belt clamp is
a clamp plate having protruding teeth formed thereon that mesh with teeth formed on an inner peripheral surface of the toothed belt;
a table attachment portion to which the clamp plate is fixed with the toothed belt sandwiched between the clamp plate and the table, and to which the table is fixed at a predetermined position.
3. A test device according to claim 1 or 2. The toothed belt is
fixed to the table at two fixed positions spaced apart in the longitudinal direction;
At least one of the fixing positions is fixed by the belt clamp so that the effective length of the toothed belt can be adjusted.
4. A test device according to claim 3 . a linear guide that supports the table so as to be movable in the predetermined direction;
The linear guide includes a rail extending in the predetermined direction and a carriage capable of running on the rail.
A test device according to any one of claims 1 to 4 . the pair of toothed belts are first and second toothed belts having the same effective length and folded back at the same folding back position in the predetermined direction,
the plurality of drive modules include at least one pair of drive modules provided at the same turn-back positions of the first and second toothed belts,
the pair of drive modules share a shaft driven by each of the electric motors included in the pair of drive modules;
2. The test device according to claim 1.

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