JP2006208093A - Vehicle-collision testing apparatus - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vehicle-collision testing apparatus for executing test collision runs in a limited space, without requiring much space, as in conventional tests that uses traction by a wire. <P>SOLUTION: The vehicle-collision testing apparatus comprises a hydraulic source apparatus, and an actuator having a piston rod driven by hydraulic oil from the hydraulic source apparatus, and then allows a test vehicle, arranged in contact with the front end of the piston rod to collide with an object that the vehicle collides with and is arranged in the front, while being pushed out by the ejection of the piston rod. The piston rod of an actuator driven hydraulically is driven speedily and is rapidly accelerated so that it reaches a prescribed target vehicle speed, the prescribed identical vehicle speed is also given to the test vehicle, arranged in contact with the front end of the piston rod, and the test vehicle is allowed to collide with the object that the test vehicle collides with, thus obtaining the collision phenomenon that is to be verified. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a vehicle collision test apparatus for performing an actual vehicle collision test that does not require a wide test space and has a simple structure.

  In general, collision tests for vehicles such as automobiles are conducted in actual vehicle collision tests for evaluating the amount of crash and remaining space, and nondestructive for evaluating safety devices such as occupant protection devices represented by airbag systems and seat belts. There is a collision acceleration simulation.

  In the former actual vehicle collision test, a vehicle collision test apparatus as shown in, for example, Japanese Patent Laid-Open No. 7-35651 (Patent Document 1) is generally used. As shown in FIG. 7, the vehicle 201 is towed from the start point P1 by the tow wire 204, and the tow dolly 205 and the tow wire 204 are separated at the release point P2 to collide with the collision barrier 206 at the collision point P3. The drive motor 202 of the take-up drum 203 that winds the pulling wire 204 is controlled so as to have a desired wire speed, that is, a vehicle speed.

  However, the vehicle collision test apparatus as described above requires a traveling distance until the pulling wire 204 obtains a predetermined speed, and there is a problem that the apparatus space is increased. Further, if the vehicle is pulled while being pulled by the pulling wire 204 at the time of the collision of the collision barrier 206, the vehicle 201 does not match the actual situation. Therefore, a mechanism for separating the vehicle 201 from the pulling wire 204 at the release point P2 is also required. Patent Document 2) and the like also show examples of the separation mechanism, but there is a problem that the mechanism is complicated.

  Therefore, as disclosed in, for example, Japanese Patent Application Laid-Open No. 7-271290 (Patent Document 3), there is a collision test apparatus that applies a deceleration acceleration at the time of collision with an actuator to a stopped specimen. As shown in FIG. 8, the carriage 301 on which the specimen 303 is placed and attached is brought into contact with the piston 305 of the actuator 304 at the stroke end on the contraction side, and the target at the time of collision with the specimen 303 from that state. In order to give acceleration (deceleration acceleration in the collision direction of the specimen 303), an input signal for setting a target deceleration waveform is given from the input generator 306 to the control device 307 by the acceleration control system, and control according to the input signal. By actuating the piston 305 of the actuator 304 under the control of the device 307 and launching the carriage 301, an acceleration that simulates the time of collision is given to the specimen 303. After the target acceleration is applied and the carriage 301 reaches the maximum speed, the piston 305 stops operating, and the carriage 301 is run in a state where the acceleration is zero, and is stopped by the shock absorber 308 so as to reduce the impact.

  The collision test apparatus of FIG. 8 may use a specimen 303 with wheels instead of the carriage 301. In this case as well, the piston 305 strikes against the hard point of the specimen 303. The purpose is to simulate the deceleration acceleration at the time of collision through the specific location on the specimen 303 side by the protrusion of the piston 305, and the specimen 303 is simulated using a white body, a simulated vehicle body or the like. The former non-destructive collision acceleration simulation is performed by giving acceleration to. Therefore, an actual vehicle collision test for the purpose of actually verifying a collision phenomenon including complicated and various destruction of the actual vehicle is not performed.

  The acceleration given by the actuator 304 in the collision simulation test apparatus as shown in FIG. 8 needs to reproduce the shock waveform at the time of the actual collision. Therefore, the actuator 304 has a hydraulic cylinder controlled by a large capacity servo valve. However, the large-flow servo valve is a large-scale device with a complicated structure in itself, and is large and expensive.In addition, the cost of the control device is added separately, which increases the cost of the entire device. In general, a servo valve often requires time for adjustment in use, and has a problem that it often induces operational problems.

Japanese Unexamined Patent Publication No. 7-35651 (second page, FIG. 3) JP 2003-21571 A (3rd page, FIGS. 1 and 3) JP-A-7-271290 (3rd, 5th pages, FIGS. 1 and 6)

  An object of the present invention is to provide a vehicle collision test apparatus capable of performing an actual vehicle collision test in a limited space without requiring a lot of space as in the conventional test using wire pulling. It is an object of the present invention to provide a vehicle collision test apparatus using an actuator with a simple structure without using a complicated and high-cost apparatus such as electromagnetic hydraulic control using a combination of a hydraulic actuator and a hydraulic actuator.

  The present invention has been made to solve the above-described problems, and provides the following means (1) to (7), which will be described below in the order of the claims.

  (1) As a first means, a test vehicle including a hydraulic power source device and an actuator having a piston rod driven by hydraulic oil from the hydraulic power source device, and disposed in contact with the front end portion of the piston rod The vehicle collision test apparatus is characterized in that it is configured to be pushed out by the protrusion of the piston rod and collide with an object to be collided forward.

  (2) As a second means, in the vehicle collision test apparatus according to the first means, the actuator includes a housing having a stepped cylindrical space inside, and the front end portion penetrating from the housing and extending to the outside. A hydraulic cylinder with a built-in valve having a piston rod provided with a piston, wherein the stepped cylindrical space is divided by a first chamber and the piston that slides back and forth continuously with the same coaxial diameter. And a third chamber and a small-diameter portion provided between the adjacent first chamber and the second chamber and having a smaller inner diameter than the second chamber, and is provided on the piston rod. The valve body comes into contact with the small diameter portion from the second chamber side as the piston rod moves backward, closes the small diameter portion, and opens the small diameter portion as the piston rod advances. A storage valve is formed with the same small-diameter portion, a hydraulic power source device for supplying high-pressure hydraulic fluid is communicated to the first chamber, and the third chamber is connected to the third chamber via a switching valve when the switching valve is not operated. The hydraulic pressure source device is communicated, and the switching valve is configured to communicate the third chamber to the hydraulic fluid discharge system when the hydraulic valve device is operated, and both the first chamber and the third chamber are connected to the high pressure hydraulic fluid. In which the first chamber pushes the piston rod forward, and the third chamber pushes the piston rod backward to increase the force. A crash test device is provided.

  (3) Further, as a third means, in the vehicle collision test apparatus according to the second means, the first chamber communicates with the hydraulic power source device via a first variable throttle. A vehicle collision test apparatus is provided.

  (4) As a fourth means, in the vehicle collision test apparatus according to the second or third means, the actuator causes the second chamber to communicate with the hydraulic oil discharge system when the piston moves forward by a predetermined stroke or more. Provided is a vehicle collision test apparatus characterized by comprising a hole.

  (5) As a fifth means, in the vehicle collision test apparatus according to the fourth means, the stepped cylindrical space includes a fourth chamber and a fourth chamber with a second small diameter portion sandwiched in front of the third chamber. An oil cushion chamber is continuously provided in front of the chamber, the piston rod has a land portion located in the fourth chamber, and the inner diameter of the second small diameter portion is smaller than that of the fourth chamber. In addition, the outer diameter of the land portion is set to be insertable into the oil cushion chamber, and the land portion closes the second small diameter portion when the built-in valve is closed and the second small diameter when the built-in valve is opened. The second built-in valve that opens the portion is formed together with the second small-diameter portion, and is provided at a position where the piston rod enters into the oil cushion chamber when the piston rod advances a predetermined stroke. The built-in valve communicates with the hydraulic oil discharge system via a fourth chamber and a fourth chamber, and the escape hole is opened by the piston until the piston moves forward by a predetermined stroke from the state where the built-in valve is closed. Provided is a vehicle collision test apparatus which is set to be closed.

  (6) As a sixth means, in the vehicle collision test apparatus of the fifth means, the fourth chamber is connected to the hydraulic oil discharge system via a second variable throttle, and the oil cushion chamber is the third A vehicle collision test apparatus is provided which is connected to the hydraulic oil discharge system via a variable throttle.

  (7) As a seventh means, in the vehicle collision test apparatus according to the sixth means, the first chamber and the third chamber are connected via a fourth variable throttle. A crash test device is provided.

  (1) According to the first aspect of the present invention, since the vehicle collision test device is configured as the first means, the piston rod of the hydraulically driven actuator is driven at high speed. The vehicle is accelerated rapidly until the predetermined vehicle speed is reached, and the predetermined vehicle speed is also given to the test vehicle arranged in contact with the front end of the piston rod. Compared to the actual vehicle collision test such as wire pulling that required a long test distance and a long acceleration distance, it was possible to obtain a collision phenomenon. The installation space and the required space are sufficient, so the test space can be significantly reduced.

  In addition, the hydraulic power source device and the actuator can be configured together in a compact manner, and equipment such as a wire traction device that is installed at a long distance and has a complicated mechanism is unnecessary, so that the equipment cost can be reduced.

  (2) According to the second aspect of the present invention, since the vehicle collision test apparatus is configured as the second means, the actuator used in addition to the operational effects of the first aspect of the invention The internal valve is opened by switching the pressure of the hydraulic oil acting on the piston by the switching valve, and the hydraulic oil is rapidly supplied from the hydraulic power source device, so that the piston rod can be driven at high speed. In addition, the hydraulic cylinder and the piston have a simple structure with a built-in valve, and the necessary valve device that connects the hydraulic power source device and the hydraulic oil discharge system can be configured with a normal valve such as a switching valve. The switching valve is not provided in the main flow path for hydraulic oil, but only acts as a trigger for piston operation, so it does not require a large capacity, and a large capacity servo valve that requires advanced control and its control device It is not necessary, and once it is adjusted and set according to the conditions, it is not necessary to make adjustments for every operation, and adjustment time is not wasted.

  Therefore, in a vehicle collision test device that requires a highly responsive and high-speed drive actuator, the structure is simple and does not require a servo valve, a high-level control device, etc., resulting in an actuator with low equipment cost and low maintenance cost. The actual vehicle collision test can be performed in a limited space without requiring a lot of space to meet the intended purpose, and a complicated and high-cost actuator using electromagnetic hydraulic control is not used. It can be set as the vehicle collision test apparatus which can obtain the stable operation | movement.

  (3) According to the invention of claim 3 of the claims, since the vehicle collision test apparatus is configured as the third means, in addition to the function and effect of the invention of claim 2, the first Since the flow rate of the hydraulic oil flowing into the actuator can be adjusted by the first variable throttle provided between the chamber and the hydraulic power source device, the desired predetermined vehicle speed can be obtained until the piston rod reaches the predetermined stroke. The actuator can be set to

  (4) According to the invention of claim 4 of the claims, since the vehicle collision test device is configured as the fourth means, in addition to the function and effect of the invention of claim 2 or claim 3 When the piston rod driven at a high speed reaches a stroke exceeding a predetermined level, the hydraulic fluid sent from the hydraulic power source device escapes from the escape hole to the outside of the actuator and stops the acceleration of the piston rod. It can prevent the trouble.

  (5) According to the invention of claim 5 of the claims, since the vehicle collision test apparatus is configured as the fifth means, in addition to the function and effect of the invention of claim 4, it is driven at high speed. When the piston rod land enters the oil cushion chamber, the hydraulic oil in the oil cushion chamber is compressed to a high pressure, generating a force that pushes back the piston rod and decelerating the piston rod, allowing high acceleration deceleration and stopping It becomes.

  (6) According to the sixth aspect of the present invention, since the vehicle collision test apparatus is configured as the sixth means, in addition to the operational effects of the fifth aspect, the hydraulic oil Since the flow rate of the hydraulic fluid flowing out from the actuator can be adjusted by the second variable throttle provided on the discharge side of the engine, a desired predetermined vehicle speed can be obtained until the piston rod reaches a predetermined stroke together with the first variable throttle. The actuator can be set in such a way that the acceleration when the piston rod is decelerated can be adjusted by the third variable throttle provided on the side where the hydraulic oil is discharged from the oil cushion chamber, and the decelerating operation balanced with the protruding speed can be set. .

  (7) According to the seventh aspect of the present invention, since the vehicle collision test apparatus is configured as the seventh means, in addition to the function and effect of the sixth aspect, the first aspect The output at the time of piston rod acceleration can be adjusted by a fourth variable throttle provided between the third chamber and the third chamber, and the piston rod thrust force can be set according to the load condition such as the weight of the test vehicle.

  Example 1 and Example 2 will be described below as the best mode of a vehicle collision test apparatus for carrying out the present invention.

  A vehicle collision test apparatus according to Embodiment 1 of the present invention will be described with reference to FIGS. FIG. 1 is an explanatory diagram of a configuration of a vehicle collision test apparatus according to the present embodiment, in which (a) shows a mode in which a test vehicle collides with a barrier, and (b) makes a test vehicle collide with another collision test vehicle. This is the case. FIG. 2 is a structural explanatory view showing a longitudinal section of an actuator used in the vehicle collision test apparatus of this embodiment together with a hydraulic power source apparatus and the like. FIGS. 3 to 5 are operation explanatory views of the actuator shown in FIG. 2, in which FIG. 3 shows an initial state, FIG. 4 shows before the oil cushion portion enters after the start of piston driving, and FIG. 5 shows after the oil cushion portion enters.

  As shown in FIG. 1, the vehicle collision test apparatus of this embodiment includes an actuator 1 having a piston rod 5 that is driven at high speed by hydraulic oil supplied from a hydraulic power source apparatus 10. From the state where the test vehicle 51 is disposed in contact with the front end portion 5b of the piston rod 5 in the retracted state, the piston rod 5 is driven at a high speed to protrude, and the test vehicle 51 is rapidly accelerated so as to reach a predetermined speed by the stroke. After releasing the test vehicle on the road surface 54, the test vehicle 51 is caused to collide with the barrier 52 installed in front of the actuator 1 (a).

  When a vehicle collision test is performed, instead of the barrier 52, a collision test vehicle 53 is installed in front of the actuator 1 and is released onto the road surface 54 as described above to test the test vehicle 51. It is made to collide with the vehicle 53 (b).

  In any case, the vehicle collision test apparatus of this embodiment rapidly drives the piston rod 5 of the actuator 1 that is hydraulically driven to a desired predetermined vehicle speed, and accelerates the front end of the piston rod 5. Similarly, a predetermined vehicle speed is also given to the test vehicle 51 arranged in contact with 5b, and then a collision phenomenon to be verified is obtained by colliding with a barrier 52 as a collision object or a collision test vehicle 53. It is.

  Therefore, compared to the conventional wire towing actual vehicle collision test that requires a long acceleration distance and a large test space, the test space of the vehicle collision test apparatus of this embodiment is the installation space of the hydraulic power source device 10 and the actuator 1 ( In addition to the installation space for the hydraulic oil discharge system or the hydraulic oil circulation system) and the barrier 52 or the collision test vehicle 53, the test vehicle 51 can be released after the ejection stroke of the actuator 1 with a minimum required distance. The test space can be significantly reduced.

  In addition, the hydraulic power source device 10 and the actuator 1 (including attached devices) can be configured in a compact manner, and equipment such as a wire traction device that is installed over a long distance and has a complicated mechanism is unnecessary, so that the equipment cost can be reduced. Will be able to.

  Since the actuator 1 used in the vehicle collision test apparatus of the present embodiment accelerates from a stopped state to a predetermined vehicle speed within the stroke, an actuator 1 capable of high response and high speed driving is required. However, as a suitable example thereof, one having a structure of a hydraulic cylinder with a built-in valve as described below with reference to FIGS. 2 to 5 is used.

  As shown in FIG. 2, the actuator 1 of this embodiment includes a stepped cylindrical space 3 in a housing 2 that is coaxially arranged along the center line X from the head side in the first to fourth chambers 3 a to 3 d, and an oil cushion chamber. 4, the rear end portion (left end portion in the figure) 5a of the piston rod 5 is inserted coaxially into the stepped cylindrical space 3 from the oil cushion chamber 4 side, and the front end portion (left end portion in the figure). ) 5b penetrates from the oil cushion chamber 4 to the outside. As shown in FIG. 1, a test vehicle 51 that is pushed out at a predetermined vehicle speed using a high-speed protrusion and used for an actual vehicle collision test is disposed in contact with the front end portion 5 b of the piston rod 5.

  In the present specification, claims, and abstract, the piston rod 5 is driven at a high speed to drive the piston rod 5 at a high speed, and then the piston rod 5 is driven at a high speed (the left side in the drawing). The direction (right side in the figure) to be performed, that is, the direction in which the test vehicle 51 is pushed out is described as “front”.

  Between the first chamber 3a and the second chamber 3b, the first small diameter portion 6 (the “small diameter portion” of the present invention in this embodiment) having an inner diameter d1 smaller than the first chamber 3a and the second chamber 3b is the housing 2. The valve body 7a provided on the rear end portion 5a of the piston rod 5 abuts from the second chamber 3b side, and the first small diameter portion 6 forms a valve seat. The “built-in valve” of the present invention in the embodiment is formed.

  The second chamber 3b and the third chamber 3c are coaxial and continuous with the same inner diameter d2, and the outer periphery of the piston 5c provided near the rear end 5a of the inserted piston rod 5 is in sliding contact with the inner peripheral surface. The side and the front side are divided into a second chamber 3b and a third chamber 3c.

  Further, between the third chamber 3c and the fourth chamber 3d, the second small diameter portion 8 having an inner diameter d3 smaller than the third chamber 3c and the fourth chamber 3d from the housing 2 side (the present invention in this embodiment). “Second small diameter portion”) is provided, and the piston rod 5 is inserted with a gap. A land portion 5d provided on the piston rod 5 in front of the piston 5c is located in the fourth chamber 3d. When the valve body 7a contacts the first small diameter portion 6 and closes the first built-in valve 7, the land portion The rear part of 5d abuts on or fits into the second small diameter part 8 and is configured to close the second small diameter part 8. The second small diameter part 8 serves as a valve seat and the land part 5d serves as a valve body. The “second built-in valve” of the present invention in this embodiment is formed.

  In front of the fourth chamber 3d, there is an oil cushion chamber 4 that decelerates the protrusion of the piston rod 5 when the land portion 5d enters, but the inner diameter d4 of the inlet 4a of the oil cushion chamber 4 does not fit the land portion 5d. It is set to be insertable (land portion outer diameter d5 ≦ inlet inner diameter d4). The front end side of the oil cushion chamber 4 is closed by a lid member 4b through which the piston rod 5 is inserted. The lid member 4b is attached to the housing 2 by an appropriate means such as screwing, and moves in the direction of the center line X. The volume of the oil cushion chamber 4 can be adjusted.

  A hydraulic pressure source device 10 that includes a hydraulic pump 11 and an accumulator 12 and supplies high-pressure hydraulic fluid communicates with the first chamber 3a through a stop valve 13 and a first variable throttle 14, and the hydraulic pressure source device 10 is also switched. The valve 15 communicates with the third chamber 3c. The accumulator 12 not only simply smoothes the pulsation of hydraulic pressure, but also serves as a hydraulic fluid supply source for supplying a high flow rate of high-pressure hydraulic fluid when the actuator 1 is driven at a high speed such as a high-speed protrusion. The hydraulic pump 11 serves for accumulating pressure in the accumulator 12. Further, the first variable throttle 14 adjusts the flow rate of the hydraulic oil flowing into the actuator 1.

  The switching valve 15 serves as a trigger when the piston 5c is driven, and communicates the hydraulic power source device 10 and the third chamber 3c in the non-operating position shown in FIG. The communication with the three chambers 3 c is closed, and the third chamber 3 c is communicated with a hydraulic oil discharge system, that is, with a drain oil pipe 17 to the tank 16. Further, a drain pipe 18 is provided in the second chamber 3b.

  The fourth chamber 3 d communicates with the oil drain pipe 17 to the tank 16 via the second variable throttle 19 and the closing valve 20, and the second variable throttle 19 adjusts the flow rate of the hydraulic oil flowing out from the actuator 1. The oil cushion chamber 4 communicates with the oil drain pipe 17 to the tank 16 via the third variable throttle 21 and the shutoff valve 20, and the third variable throttle 21 is a piston rod when the land portion 5 d enters the oil cushion chamber 4. Adjust the deceleration of 5.

  Reference numeral 22 denotes a relief hole that opens into the stepped cylindrical space 3, which is in an initial state before the high-speed ejecting operation of the actuator 1 described later in FIG. 3, and before the oil cushion portion enters after the piston driving starts described later in FIG. 4. It is provided at a position to be closed and communicates with the tank 16 via the oil drain pipe 17, and when the piston stroke reaches a predetermined stroke, the second chamber 3b is discharged to the tank 16 as will be described later with reference to FIG. Communicating with the oil pipe 17, the hydraulic oil sent from the hydraulic source device 10 to the first chamber 3 a and the second chamber 3 b is released to the outside of the actuator 1 to stop the acceleration of the piston rod 5. Note that a hydraulic oil circulation system (not shown) that connects the tank 16 and the hydraulic pump 11 may be provided.

  Reference numeral 23 denotes a chamber bypass, which connects the first chamber 3a and the third chamber 3c via a fourth variable throttle 24 and a closing valve 25, and the fourth variable throttle 24 adjusts the output when the piston rod 5 is accelerated.

  The operation of the actuator 1 of the present embodiment configured as described above will be described with reference to FIG. The operation of the actuator 1 of this embodiment is as follows: (i) initial state shown in FIG. 3 (piston stopped state), (ii) after starting the piston drive shown in FIG. 4 / before entering the oil cushion chamber, (iii) shown in FIG. It is divided into three stages after entering the oil cushion chamber.

  (I) In the non-operating state, the shut-off valves 13, 20, 25 in FIG. 2 are closed, but in the initial state for operation, the shut-off valves 13, 20, 25 are opened, and the switching valve 15 is in the non-operating state. Yes. As shown in FIG. 3, the high-pressure hydraulic oil from the hydraulic power source device 10 is sent to the first chamber 3a and the third chamber 3c to form a high-pressure portion (hatched portion in the figure) of the same pressure, and the second chamber 3b The hydraulic oil in the fourth chamber 3d and the oil cushion chamber 4 is at a low pressure. In the first built-in valve 7, the piston rod 5 receives a high pressure forward (rightward in the figure) from the first chamber 3a on the circular surface of the inner diameter d1 of the first small diameter portion 6 at the valve body 7a of the rear end portion 5a. In the three-chamber 3c, the piston 5c having a diameter d2 receives high pressure backward (leftward), and the land portion 5d receives high pressure forward (rightward) on the circular surface of the inner diameter d3 of the second small diameter portion 8.

Therefore, when the condition of d1 ² <(d2 ² -d3 ² ) is satisfied, (the force by which the first chamber 3a pushes the piston rod 5 forward (rightward)) <(the third chamber 3c pushes the piston rod 5 backward) Therefore, the piston rod 5 is pressed backward (leftward), the valve body 7a comes into contact with the first small diameter portion 6, the first built-in valve 7 is closed, and the piston rod 5 does not move. . In this state, the land portion 5d is in contact with or fitted to the second small diameter portion 8, and the second built-in valve 9 is closed.

The actuator 1 of the present embodiment is set so that the condition of d1 ² <d2 ² -d3 ² is satisfied, and in the initial state (piston stop state), the first built-in valve 7 and the second built-in valve 9 are closed, Maintain a stable stop.

  (Ii) When the actuator 1 is operated and the piston rod 5 is driven at high speed, that is, when high-speed ejection is performed, the switching valve 15 is operated to switch to the operating state. As shown in FIG. 4, as the hydraulic oil in the third chamber 3c is discharged to the tank 16 via the switching valve 15, the pressure in the third chamber 3c drops, and as a result, the piston 5c starts moving forward. Then, the first built-in valve 7 is opened, and high-pressure hydraulic oil flows into the second chamber 3b from the first chamber 3a all at once (hatched portion in the figure), and the piston 5c is rapidly accelerated forward (to the right).

  At the same time, the land portion 5d also moves forward (rightward), so that the second built-in valve 9 is also opened, the third chamber 3c and the fourth chamber 3d communicate with each other, and the hydraulic oil in the third chamber 3c is transferred to the fourth chamber 3d. Inflow and discharged to the tank 16 via the second variable throttle 19, that is, the third chamber 3c communicates with the hydraulic oil discharge system via the second built-in valve 9 and the fourth chamber 3d, and further the third chamber Since the pressure in 3c decreases at a stretch, the piston 5c receives the high pressure of the second chamber 3b and performs an operation of protruding the piston rod 5 forward (rightward) at a high speed.

  The first variable throttle 14 adjusts the flow rate of the hydraulic oil flowing from the hydraulic power source device 10 to the first chamber 3a, and the second variable throttle 19 adjusts the flow of hydraulic oil flowing out from the fourth chamber 3d to the hydraulic oil discharge system. A predetermined speed given to the test vehicle 51 can be set by adjusting the flow rate. Further, the output of the piston rod 5 when accelerating can be adjusted by adjusting the amount of bypass of hydraulic oil from the first chamber 3a to the third chamber 3c by the fourth variable throttle 24.

  (Iii) Further, as shown in FIG. 5, when the land portion 5 d enters the oil cushion chamber 4, the hydraulic oil in the oil cushion chamber 4 is elastically compressed to a high pressure (hatched portion in the figure), and the piston rod 5 is A force to push back is generated to decelerate the piston rod 5. The action of the oil cushion at that time can be appropriately set by changing the volume of the oil cushion chamber 4 by adjusting the position of the lid member 4b of the oil cushion chamber 4 in advance. On the other hand, the high-pressure hydraulic oil in the first chamber 3a and the second chamber 3b flows into the tank 16 from the escape hole 22 opened by the movement of the piston 5c, and the pressure in the first chamber 3a and the second chamber 3b decreases. Thus, the piston rod 5 decelerates at a high acceleration and stops.

  At this time, the flow rate of the hydraulic oil flowing out from the oil cushion portion 4 to the hydraulic oil discharge system can be adjusted by the third variable throttle 21, and the acceleration when the piston rod 5 is decelerated can be adjusted.

  Therefore, according to the actuator 1 of the present embodiment, the pressure of the hydraulic oil acting on the piston 5 c is switched by the switching valve 15, thereby causing a rapid supply of the hydraulic oil from the hydraulic power source device 10, and the high speed of the piston rod 5. It is possible to drive, and the hydraulic cylinder and piston have a simple structure with a built-in valve, and the necessary valve device connecting the hydraulic power source device 10 should be a normal closing valve, switching valve, variable throttle, etc. Can do. That is, the high flow rate hydraulic oil supply system is configured by the closing valve 13 and the first variable throttle 14, and the high flow rate hydraulic oil discharge system is the relief hole 22, the closing valve 20, the second variable throttle 19, and the oil drain pipe. 17 and a tank 16, and in particular, the switching valve 15 is not provided in the main flow path of hydraulic oil, but only functions as a trigger for the operation of the piston 5 c, so that a large capacity is not required, and advanced control is performed. The required large-capacity servo valve and its control device are also unnecessary, and once adjusted and set according to the conditions, adjustment for each operation is unnecessary and adjustment time is not wasted. Actuator 1 is obtained.

  In addition, the piston rod 5 driven at high speed is decelerated at the stroke limit by the oil cushion chamber 4 and the land portion 5d. On the other hand, the high-pressure hydraulic oil in the first chamber and the second chamber has a piston stroke up to a predetermined stroke. After reaching, the fluid flows out from the relief hole 22 opened by the movement of the piston 5c to the hydraulic oil discharge system, the pressure in the first chamber and the second chamber decreases, and the piston rod decelerates at high acceleration and stops. Driving and high-acceleration deceleration are possible. In addition to high response and high-speed driving, it is possible to prevent the actuator 1 from being troubled by an impact.

  Further, the flow rate of the hydraulic oil flowing into the actuator 1 is adjusted by the first variable throttle 14 provided between the hydraulic source device 10 and the second variable throttle 19 provided on the hydraulic oil discharge side flows out of the actuator 1. Since the flow rate of the hydraulic oil to be adjusted can be adjusted, the actuator 1 can be set so that the desired predetermined vehicle speed can be obtained until the piston rod 5 reaches the predetermined stroke, and the first chamber 3a and the third chamber 3c can be obtained. Since the output at the time of acceleration of the piston rod 5 can be adjusted by the fourth variable throttle 24 provided between the piston rod 5 and the thrust force of the piston rod 5 according to the load condition such as the weight of the test vehicle, the oil cushion chamber 4 can be set. The acceleration when the piston rod 5 is decelerated can be adjusted by the third variable throttle 21 provided on the hydraulic oil discharge side from You can set the deceleration working that nest.

  Therefore, in a vehicle collision test apparatus that requires a highly responsive and high-speed drive actuator, the actuator has a simple structure and does not require a servo valve, a high-level control device, etc., and the actuator 1 has a low equipment cost and a low maintenance cost. The actual vehicle collision test can be carried out in a limited space without requiring a lot of space to meet the intended purpose, and a complicated and high-cost actuator using electromagnetic hydraulic control is not used. And it can be set as the vehicle collision test apparatus which can obtain the stable operation | movement.

  Based on FIG. 6, the vehicle collision test apparatus which concerns on Example 2 of this invention is demonstrated. FIG. 6 is a structural explanatory view showing a longitudinal section of an actuator used in the vehicle collision test apparatus of this embodiment together with a hydraulic power source apparatus and the like. The present embodiment is the same as the first embodiment in the overall configuration shown in FIG. 1, and the actuator to be used switches the hydraulic oil pressure acting on the piston by the switching valve, so that the hydraulic source device This is the same as that of the hydraulic cylinder with a built-in valve that can rapidly supply the high-pressure hydraulic oil and can be driven at a high speed, but is characterized by a simple structure without the oil cushion chamber and the land portion. Therefore, FIG. 1 is also referred to, and in FIG. 6, the same parts as those in FIGS.

  As shown in FIG. 6, in the actuator 101 of this embodiment, a stepped cylindrical space 103 in the housing 102 is formed along the center line X from the head side in the order of the first to third chambers 103a to 103c. From the third chamber 103 c side, the rear end portion 105 a of the piston rod 105 is inserted coaxially into the stepped cylindrical space 103, and the front end portion 105 b protrudes outside the housing 102.

  Between the first chamber 103a and the second chamber 103b, the first chamber 103a and the small-diameter portion 106 having an inner diameter d1 smaller than the second chamber 103b from the housing 102 side (the “small-diameter portion” of the present invention in this embodiment). The valve body 107a provided on the rod rear end portion 105a of the piston rod 105 comes into contact with the second chamber 103b side, and the small diameter portion 106 forms a valve seat. The "built-in valve") of the invention.

  The second chamber 103b and the third chamber 103c are coaxially continuous with the same inner diameter d2, but the piston 105c of the inserted piston rod 105 is in sliding contact with the inner peripheral surface, and the second chamber 103b and the third chamber are arranged on the rear side and the front side. 103c.

  A hydraulic power source device 10 including a hydraulic pump 11 and an accumulator 12 communicates with the first chamber 103a via a stop valve 13 and a first variable throttle 14. The hydraulic power source device 10 also includes a switching valve 15, a cylinder front end side. Is connected to the third chamber 103c via the hydraulic oil pipe variable throttle 130.

  The switching valve 15 serves as a trigger for driving the piston 105c, and communicates the hydraulic power source device 10 and the third chamber 103c via the hydraulic oil pipe 131 in the non-operating position shown in FIG. Closes the communication between the hydraulic power source device 10 and the third chamber 103 c, and connects the third chamber 103 c to the oil discharge pipe 117 to the tank 16 through the hydraulic oil pipe 131. A drain pipe 118 is provided in the second chamber 103b. Further, the hydraulic oil pipe 131 is provided with a hydraulic oil pipe variable throttle 130.

  Reference numeral 122 denotes an escape hole, which is provided in the third chamber 103c so as to be opened in the initial state before the actuator 101 is driven at a high speed, that is, at a high-speed ejecting operation, and the oil drain pipe 117 to the tank 16 via the pilot check valve 132, As described later, the hydraulic oil in the third chamber 103c is discharged when the piston 105 protrudes at a high speed, and the piston stroke reaches a predetermined stroke or more as shown by a two-dot chain line in FIG. In this case, the escape hole 122 opens into the second chamber 103b, and the high-pressure hydraulic oil sent from the hydraulic power source apparatus 10 to the first chamber 103a and the second chamber 103b as described later is supplied to the pilot check valve 132 and the oil drain pipe 117. Through the hydraulic oil discharge system to stop the acceleration of the piston rod 105 and stop the deceleration. Than it is.

  The pilot check valve 132 uses the hydraulic pressure of the hydraulic oil pipe 131 between the switching valve 15 and the hydraulic oil pipe variable throttle 130 as a pilot pressure, and the hydraulic pressure of the hydraulic power source device 10 is the hydraulic oil pipe when the switching valve 15 is inactive. When 131 is applied, it is closed by the pilot pressure, so that the hydraulic oil in the third chamber 3c is retained and does not flow out to the hydraulic oil discharge system. When the switching valve 15 is in operation and the inside of the third chamber 3c communicates with the oil drain pipe 117 to the tank 16 via the switching valve 15, the inside of the hydraulic oil pipe 131 is reduced in pressure, so that the pilot pressure also decreases, and the pilot check valve 132 Is opened, and the relief hole 122 communicates with the tank 16 through the oil drain pipe 117, that is, the third chamber 103c communicates with the hydraulic oil discharge system. Note that a hydraulic oil circulation system (not shown) that connects the tank 16 and the hydraulic pump 11 may be provided.

  When the piston 105 comes to a position where the escape hole 122 is closed when the piston 105 protrudes at a high speed as indicated by a broken line in FIG. 6, the hydraulic oil in the third chamber 103 c is supplied only from the hydraulic oil pipe variable throttle 130. Since it is discharged, the deceleration of the piston rod 105 can be adjusted by the hydraulic oil pipe variable throttle 130.

  The operation of the actuator 101 of this embodiment configured as described above will be described below. (I) Although the shut-off valve 13 is closed during non-operation, in the initial state during operation, the shut-off valve 13 is opened and the switching valve 15 is in a non-actuated state. The first chamber 3a and the third chamber 3c are fed into the first chamber 3a and the third chamber 3c, and both chambers are high-pressure portions having the same pressure, and the hydraulic oil in the second chamber 103b is low-pressure. In the built-in valve 107, the piston rod 105 receives a high pressure forward (rightward in the figure) from the first chamber 103a on the circular surface of the inner diameter d1 of the small-diameter portion 106 at the valve body 107a of the rear end portion 105a, and in the third chamber 3c. Is subjected to a high pressure backward (leftward) by the piston 5c having a diameter d2.

Therefore, when the diameter of the piston rod 105 is d6 and the condition of d1 ² <(d2 ² -d6 ² ) is satisfied, (the force by which the first chamber 3a pushes the piston rod 105 forward (rightward)) <(third Since the chamber 3c is a force that pushes the piston rod 5 backward (leftward), the piston rod 105 is pushed backward (leftward), the valve body 107a comes into contact with the small-diameter portion 106, and the built-in valve 107 is closed and moved. No state.

The actuator 1 of the present embodiment is set so as to satisfy the condition of d1 ² <(d2 ² -d6 ² ), and in the initial state (piston stop state), the built-in valve 107 is closed and is stably stopped. To maintain.

  (Ii) When the actuator 101 is operated and the cylinder rod 105 is projected at a high speed, the switching valve 15 is operated. As described above, the third chamber 103 c communicates with the oil drain pipe 117 to the tank 16 via the hydraulic oil pipe 131 and the switching valve 15 and becomes a low pressure.

  When the pressure in the third chamber 103c drops, and as a result, the piston 105c starts to move forward (rightward), the built-in valve 107 opens, and high-pressure hydraulic oil flows from the first chamber 103a into the second chamber 103b all at once. 105c is rapidly pressed forward (to the right).

  At the same time, since the pressure of the hydraulic oil pipe 131 decreases, the pilot pressure also decreases and the pilot check valve 132 opens, that is, the third chamber 103c communicates with the hydraulic oil discharge system, and the hydraulic oil in the third chamber 3c escapes the hole 122. The fuel is rapidly discharged to the tank 16 via the pilot check valve 132 and the oil drain pipe 117.

  Accordingly, since the pressure in the third chamber 103c decreases at a stroke, the piston rod 105 receives the high pressure of the second chamber 103b and operates to protrude forward (rightward) at high speed.

  At this time, the flow rate of the high-pressure hydraulic oil flowing from the hydraulic power source apparatus 10 into the first chamber 103a can be adjusted by the first variable throttle 14.

  (Iii) Further, when the piston 105c comes to a position where it closes the escape hole 122 as indicated by a chain line in FIG. 6, the hydraulic oil in the third chamber 103c is discharged only from the hydraulic oil pipe variable throttle 130, so that the pressure becomes high. The protrusion of is slowed down.

  Further, when the piston 105c exceeds the escape hole 122 and the escape hole 122 opens into the second chamber 103b, the high-pressure hydraulic oil in the first chamber 103a and the second chamber 103b is discharged from the relief hole 122 into the hydraulic oil discharge system, that is, The oil flows out into the oil drain pipe 117 and the tank 16, the pressure in the first chamber 103a and the second chamber 103b decreases, and the piston rod 105 decelerates at high acceleration and stops.

  At this time, the flow rate of the hydraulic oil flowing out from the front end of the third chamber 103c can be adjusted by the hydraulic oil pipe variable throttle 130, and the acceleration at the time of deceleration of the piston rod 105 can be adjusted.

  Therefore, according to the actuator 101 of the present embodiment, the hydraulic cylinder and the piston are configured with a simple structure in which the valve is built, and the necessary valve devices for connecting the hydraulic power source device are a normal closing valve, a variable throttle, and a switching valve. A pilot check valve can be used. That is, the high-pressure and high-flow rate hydraulic oil supply system is configured by the shut-off valve 13 and the first variable throttle 14, and the high-flow rate hydraulic oil discharge system is configured by the relief hole 122, the pilot check valve 132, the drainage pipe 117, and the tank 16. In particular, the switching valve 15 is not provided in the main flow path of the hydraulic oil, but only functions as a trigger for the operation of the piston 105c, so that it does not require a large capacity and a large capacity servo valve that requires advanced control. The controller 101 is also unnecessary, and once the adjustment is set according to the conditions, the adjustment for each operation is unnecessary, so that the adjustment time is not wasted, and the actuator 101 can have a simple structure, high response, and high speed operation.

  Further, when the piston rod 105 driven at high speed reaches a predetermined stroke, the hydraulic oil fed from the hydraulic power source device 10 is released from the relief hole 122 to the outside of the actuator 101, and the acceleration of the piston rod 105 is stopped. Therefore, it is possible to prevent the actuator 101 from being disturbed by an impact.

  Particularly in this embodiment, the first chamber 103a to the third chamber 103c and the small diameter portion 106 are only provided in the housing 102, and only the piston 107 and the valve body 107a are provided on the piston rod 5, so the structure of the actuator 101 is as follows. The configuration is simpler and simpler than that of the first embodiment, and the configuration for supplying and discharging the hydraulic oil is further simplified, so that the apparatus cost and the operating cost can be further reduced.

  Further, since the flow rate of the hydraulic oil flowing into the actuator 101 can be adjusted by the first variable throttle 14 provided between the hydraulic power source device 10 and the target predetermined vehicle until the piston rod 105 reaches a predetermined stroke. The actuator 101 can be set so that the speed can be obtained, and the acceleration when the piston rod 105 is decelerated can be adjusted by the hydraulic oil pipe variable throttle 130 provided on the hydraulic oil discharge side from the front end of the third chamber 103c. Balanced deceleration operation can be set.

  Therefore, in a vehicle collision test apparatus that requires a highly responsive and high-speed drive actuator, an actuator with a simpler structure than that of the first embodiment, which does not require a servo valve and a high-level control device, and has a lower equipment cost and a lower maintenance cost. 101, the vehicle collision test apparatus can perform an actual vehicle collision test in a limited space without requiring a lot of space that matches the intended purpose, without using a complicated and high-cost actuator using electromagnetic hydraulic control, A low-cost and stable operation can be obtained by an actuator with a simple structure.

  Although the present invention has been described with reference to the illustrated embodiments, it is needless to say that the present invention is not limited to the above-described embodiments, and various modifications may be made to the specific structure within the scope of the present invention. .

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a configuration explanatory diagram of a vehicle collision test apparatus according to a first embodiment of the present invention, in which (a) shows an aspect when a test vehicle collides with a barrier, and (b) makes a test vehicle collide with another collision test vehicle. An embodiment of the case is shown. BRIEF DESCRIPTION OF THE DRAWINGS It is composition explanatory drawing which shows the longitudinal cross-section of the actuator which concerns on Example 1 of this invention with a hydraulic power unit etc. FIG. It is operation | movement explanatory drawing of the actuator of FIG. 2, and shows an initial state. It is operation | movement explanatory drawing of the actuator of FIG. 2, and shows the state before the oil cushion chamber rush after a piston drive start. It is operation | movement explanatory drawing of the actuator of FIG. It is a structure explanatory drawing which shows the longitudinal cross-section of the actuator which concerns on Example 2 of this invention with a hydraulic power unit etc. FIG. It is explanatory drawing of the conventional vehicle collision test apparatus. It is explanatory drawing of the collision simulation test apparatus used for the conventional nondestructive collision acceleration simulation.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Actuator 2 Housing 3 Stepped cylindrical space 3a 1st chamber 3b 2nd chamber 3c 3rd chamber 3d 4th chamber 4 Oil cushion chamber 4a Inlet 4b Cover member 5 Piston rod 5a Rear end part 5b Front end part 5c Piston 5d Land part 6 1st small diameter part 7 1st built-in valve 7a Valve body 8 2nd small diameter part 9 2nd built-in valve 10 Hydraulic power source device 11 Hydraulic pump 12 Accumulator 13 Stop valve 14 1st variable throttle 15 Switching valve 16 Tank 17 Drain pipe 18 Drain pipe DESCRIPTION OF SYMBOLS 19 2nd variable aperture 20 Stop valve 21 3rd variable aperture 22 Relief hole 23 Chamber bypass 24 4th variable aperture 25 Close valve 51 Test vehicle 52 Barrier 53 Impact test vehicle 54 Road surface 101 Actuator 102 Housing 103 Stepped cylindrical space 103a First 1 chamber 103b second Chamber 103c third chamber 105 piston rod 105a rear end 105b front end 105c piston 106 small-diameter portion 107 built valve 107a valve body 117 oil drain line 118 the drain pipe 122 spill port 130 hydraulic oil pipe variable throttle 131 hydraulic oil pipe 132 pilot check valve

Claims (7)

A hydraulic power source device;
An actuator having a piston rod driven by hydraulic oil from the hydraulic power source device,
A vehicle collision test apparatus configured to cause a test vehicle disposed in contact with a front end portion of the piston rod to be pushed by a protrusion of the piston rod and collide with a collision object disposed in front. The vehicle collision test apparatus according to claim 1,
The actuator is a hydraulic cylinder with a built-in valve having a housing with a stepped cylindrical space inside, and a piston rod that penetrates the front end portion from the housing and goes outside.
The stepped cylindrical space includes a first chamber,
A second chamber and a third chamber, which are separated by the pistons which are coaxial and have the same diameter and which slide back and forth,
A small-diameter portion provided between the adjacent first chamber and the second chamber and having an inner diameter smaller than that of the second chamber;
The valve body provided on the piston rod is
As the piston rod is retracted, a built-in valve is formed together with the small diameter portion to contact the small diameter portion from the second chamber side to close the small diameter portion and open the small diameter portion as the piston rod advances. ,
The first chamber communicates with a hydraulic power source device that supplies high-pressure hydraulic oil,
The hydraulic pressure source device is communicated to the third chamber via a switching valve when the switching valve is not operated.
The switching valve is configured to communicate the third chamber with the hydraulic oil discharge system when the switching valve is operated.
When the high pressure hydraulic oil is supplied to both the first chamber and the third chamber, the third chamber pushes the piston rod backward due to the force of the first chamber pushing the piston rod forward. A vehicle collision test apparatus, wherein the pushing force is set so as to increase. The vehicle collision test apparatus according to claim 2,
The vehicle collision test apparatus characterized in that the first chamber communicates with the hydraulic power source device via a first variable throttle.   4. The vehicle collision test apparatus according to claim 2, wherein the actuator includes an escape hole that communicates the second chamber with a hydraulic oil discharge system when the piston moves forward by a predetermined stroke or more. A vehicle collision test apparatus. The vehicle collision test apparatus according to claim 4,
The stepped cylindrical space of the actuator includes a fourth chamber sandwiching a second small diameter portion in front of the third chamber, and an oil cushion chamber continuously in front of the fourth chamber,
The piston rod has a land portion located in the fourth chamber,
The inner diameter of the second small diameter portion is smaller than that of the fourth chamber, and the outer diameter of the land portion is set to be insertable into the oil cushion chamber,
The land portion closes the second small diameter portion when the built-in valve is closed, and forms a second built-in valve together with the second small diameter portion that opens the second small diameter portion when the built-in valve is opened. Provided at a position where the piston rod enters the oil cushion chamber when the piston rod advances a predetermined stroke;
The third chamber is configured to communicate with the hydraulic oil discharge system via the second built-in valve and a fourth chamber;
The vehicle collision test apparatus according to claim 1, wherein the relief hole is set so as to be closed by the piston until the piston advances a predetermined stroke from a state where the built-in valve is closed. The vehicle collision test apparatus according to claim 5, wherein
The fourth chamber is connected to the hydraulic oil discharge system via a second variable throttle,
The vehicle collision test apparatus, wherein the oil cushion chamber is connected to the hydraulic oil discharge system via a third variable throttle. The vehicle collision test apparatus according to claim 6, wherein
The vehicle collision test apparatus, wherein the first chamber and the third chamber are connected via a fourth variable throttle.

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