JP2006208094A - Impact testing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an impact testing device having a simple structure, and adding repeatable and arbitrary impact acceleration, without depending on complicated oil pressure control such as an electromagnetic oil-pressure control system that uses a high-response servo valve. <P>SOLUTION: This impact tester is equipped with an oil pressure source device and an actuator, comprising a piston rod driven by hydraulic oil from the source device. This impact tester gives impact acceleration to a specimen attached to the piston rod, by causing the piston rod to make forward-protrusive motion and then rapidly making it stop. The actuator comprises a housing, equipped with a stepped cylindrical space in its interior and the piston rod equipped with a piston; the piston undergoing sliding motion in the housing with at least one end part thereof put out through the housing to the exterior for mounting the specimen thereon. The piston rod is equipped with a land part in the cylindrical space, and the land part is adapted to plunge into an oil cushion chamber provided in the cylindrical space on its front end side, after the piston rod has forwardly protruded by a prescribed stroke. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an impact test apparatus for applying impact acceleration to a test body.

  Conventionally, in order to perform a test for applying an impact acceleration to a test body, a large flow rate servo valve is provided outside the hydraulic actuator 90 as shown in FIG. 91 is installed, the inflow and outflow amount of the hydraulic oil is controlled by the servo valve control device 92 and the hydraulic power source device 95 including the hydraulic pump 93, the accumulator 94, etc., and the piston 96 is driven. A test body 97 is attached to the tip, and impact acceleration is applied to the test body 97 by projecting or retracting the piston 96 by high-speed driving, or although not shown, the test body is dropped or released by a hydraulic actuator to collide with the elastic body. In general, the impact acceleration was obtained.

  However, the electrohydraulic control method using a combination of a high response servo valve and a hydraulic actuator can add a shock acceleration having a complicated waveform, and therefore, a pseudo earthquake test apparatus as disclosed in Japanese Patent Laid-Open No. 2000-171339 (Patent Document 1), etc. However, the servo valve has a complicated structure and is expensive, and the cost of the control device 92 is additionally added, which increases the cost of the entire device. there were. In general, servo valves often require time for adjustment, and often cause operational problems.

  On the other hand, the method of obtaining the impact acceleration by the collision with the elastic body has a problem that it is difficult to obtain an arbitrary reproducible acceleration and the range of the acceleration is limited.

JP 2000-171339 (first page, FIG. 1)

  It is an object of the present invention to provide an impact test apparatus capable of adding an arbitrary impact acceleration with a simple structure and reproducibility, without using complicated hydraulic control of an electromagnetic hydraulic control system by a combination of a high response servo valve and a hydraulic actuator. It is what.

  The present invention has been made to solve the above-described problems, and provides the following means (1) to (10), and will be described below in the order of the claims.

  (1) As its first means, a hydraulic power source device and an actuator having a piston rod driven by hydraulic oil from the hydraulic power source device are provided, and the piston rod is pushed forward and then stopped rapidly. An impact test device that applies impact acceleration to a test body attached to the piston rod, wherein the actuator includes a housing having a stepped cylindrical space inside and at least one end thereof penetrating from the housing. And the piston rod having a piston that slides in the housing, the piston rod having a land portion in the stepped cylindrical space, and the land portion having the piston rod. Is projected forward of a predetermined stroke, and then rushes into an oil cushion chamber provided on the front end side of the stepped cylindrical space. That it formed by providing an impact test apparatus according to claim.

(2) As a second means, in the impact test apparatus of the first means, the actuator is a hydraulic cylinder with a built-in valve, and the stepped cylindrical space has the same diameter as that of the first chamber. A second chamber and a third chamber separated by the piston that slides back and forth continuously, and an inner diameter smaller than that of the second chamber provided between the adjacent first chamber and the second chamber. A first chamber having a first small-diameter portion, a fourth chamber sandwiching a second small-diameter portion in front of the third chamber, and an oil cushion chamber continuous in front of the fourth chamber;
The piston rod includes a valve body located in the second chamber and the land portion located in the fourth chamber, and the valve body is provided with the first small diameter portion as the piston rod moves backward. A first built-in valve that closes the first small-diameter portion in contact with the piston rod and opens the first small-diameter portion as the piston rod advances, together with the first small-diameter portion, and the second small-diameter portion. The inner diameter of the part is smaller than that of the fourth chamber, and the land part closes the second small diameter part when the first built-in valve is closed, and opens the second small diameter part when the built-in valve is opened. The second built-in valve is formed together with the second small-diameter portion, the outer diameter of the land portion is set so as to be fitted into the oil cushion chamber, and a hydraulic pressure source for supplying high-pressure hydraulic oil to the first chamber An apparatus is connected, and the third chamber is connected to a switching valve. Communicate with the hydraulic pressure source device during non-operation of the switching valve, and the switching valve is configured so as to communicate the third chamber when the hydraulic to the hydraulic oil discharged system,
The third chamber is configured to communicate with the hydraulic oil discharge system via the second built-in valve and the fourth chamber, and both the first chamber and the third chamber are operated at high pressure. The first chamber is set so that the force of pushing the piston rod backward by the third chamber is larger than the force of pushing the piston rod forward by the first chamber in a state where oil is supplied. An impact test device is provided.

  (3) Further, as a third means, in the impact test apparatus of the second means, the oil cushion chamber is configured so that the elasticity of the hydraulic oil can be set by changing the volume. apparatus.

  (4) As a fourth means, in the impact test apparatus of the second means, the oil cushion chamber is connected to the hydraulic oil discharge system via a third variable throttle. I will provide a.

  (5) As a fifth means, in the impact test apparatus according to any one of the second to fourth means, the actuator communicates the second chamber to the hydraulic oil discharge system when the piston advances by a predetermined stroke or more. An impact test apparatus comprising: a relief hole configured to be closed by the piston from a state in which the first built-in valve is closed until the piston advances a predetermined stroke. I will provide a.

  (6) As a sixth means, in the impact test apparatus according to the fifth means, the first chamber is communicated with the hydraulic power source device via a first variable throttle. .

  (7) As a seventh means, in the impact test apparatus of the fifth means, the fourth chamber is connected to the hydraulic oil discharge system via a second variable throttle, and the impact test is characterized in that Providing equipment.

  (8) As an eighth means, in the impact test apparatus of the fifth means, the first chamber and the third chamber are connected via a fourth variable throttle, and the impact test is characterized in that Providing equipment.

(9) As a ninth means, in the impact test apparatus of any one of the first to eighth means,
The one end portion is an end portion of a piston rod that protrudes from the housing by the operation of the switching valve.

  (10) As a tenth means, in the impact test apparatus according to any one of the first to eighth means, the one end is an end of a piston rod that is pulled into the housing by the operation of the switching valve. An impact test apparatus characterized by being.

  (1) According to the first aspect of the present invention, since the impact test apparatus is configured as the first means, the piston rod of the hydraulically driven actuator is driven at a high speed and its stroke The test specimen is accelerated rapidly until the desired speed is reached, and the land of the piston rod is plunged into the oil cushion chamber, and the hydraulic oil in the oil cushion chamber is elastically compressed to a high pressure, which pushes the piston rod back. Because the generated piston rod is decelerated and stopped suddenly, impact acceleration is applied to the specimen, and the desired impact test can be performed, and a large-capacity servo valve that requires advanced control and its control device are unnecessary. Once the actuator is adjusted and set according to the conditions, adjustment for each operation is unnecessary, and adjustment time is not wasted, and the impact test apparatus with a simple structure is obtained.

  (2) According to the invention of claim 2, since the impact test apparatus is configured as the second means, in addition to the function and effect of the invention of claim 1, the actuator acts on the piston by the switching valve. By switching the pressure of the hydraulic oil, the hydraulic oil is rapidly supplied from the hydraulic power source device, the piston rod can be driven at high speed, and a predetermined speed can be given to the test body in a short distance. The piston has a simple structure with a built-in valve. In particular, the switching valve is not provided in the main flow path for hydraulic oil, but only functions as a trigger for piston operation. A large-capacity servo valve that requires precise control and its control device are also unnecessary, and the piston rod that is driven at high speed is steep at the stroke limit by the oil cushion chamber and the land portion. Decelerated to be the test body a predetermined impact test can impact acceleration can be performed. Therefore, it is possible to provide an impact test apparatus which can obtain a low-cost and stable operation by an actuator with a simple structure without using a complicated and high-cost actuator using electromagnetic hydraulic control.

  (3) According to the invention of claim 3, since the impact test apparatus is configured as the third means, in addition to the function and effect of the invention of claim 2, the position of the lid member of the oil cushion chamber is adjusted in advance. Thus, the volume of the oil cushion chamber can be changed to appropriately set the elasticity of the hydraulic oil in the oil cushion chamber, and the impact acceleration applied to the specimen can be adjusted and set.

  (4) According to the invention of claim 4, since the impact test apparatus is configured as the fourth means, in addition to the function and effect of the invention of claim 2, the third variable throttle can By adjusting the flow rate of hydraulic oil flowing out to the hydraulic oil discharge system, the acceleration at the time of piston rod deceleration can be adjusted, and the impact acceleration applied to the specimen can be adjusted and set.

  (5) According to the invention of claim 5, since the impact test apparatus is configured as the fifth means, in addition to the function and effect of the invention of any one of claims 2 to 5, the first chamber The high-pressure hydraulic fluid in the second chamber flows out from the relief hole opened by the movement of the piston after the piston stroke reaches a predetermined stroke, and the pressure in the first chamber and the second chamber is Decrease and stop acceleration, and the piston rod decelerates and stops abruptly, enabling higher speed drive and higher acceleration deceleration.

  (6) According to the invention of claim 6, since the impact test apparatus is configured as the sixth means, in addition to the function and effect of the invention of claim 5, the flow rate of hydraulic oil flowing into the actuator is adjusted. The actuator can be set so that the desired speed of the specimen is obtained before the piston rod reaches a predetermined stroke.

  (7) According to the invention of claim 7, since the impact test apparatus is configured as the seventh means, in addition to the function and effect of the invention of claim 5, a second provided on the hydraulic oil discharge side. Since the flow rate of the hydraulic oil flowing out from the actuator can be adjusted by the variable throttle, the actuator can be set so that the target specimen speed can be obtained before the piston rod reaches a predetermined stroke.

  (8) According to the invention of claim 8, since the impact test apparatus is configured as the eighth means, in addition to the function and effect of the invention of claim 5, between the first chamber and the third chamber. Since the output at the time of piston rod acceleration can be adjusted by the fourth variable throttle provided in the piston rod, it is possible to set the protruding force of the piston rod according to the load condition such as the weight of the test body.

  (9) According to the invention of claim 9, since the impact test apparatus is configured as the ninth means, in addition to the function and effect of any of the inventions of claims 1 to 8, after the high-speed ejection operation In the case of using the impact acceleration due to the sudden deceleration stop, there are advantages such as arrangement position and installation.

  (10) According to the invention of the tenth aspect, since the impact test apparatus is configured as the tenth means, in addition to the function and effect of the invention of any one of the first to eighth aspects, after the high-speed pull-in operation In the case of using the impact acceleration due to the sudden deceleration stop, there are advantages such as arrangement position and installation.

  Examples 1 and 2 will be described below as the best mode of an impact test apparatus for carrying out the present invention.

  An impact test apparatus according to Embodiment 1 of the present invention will be described with reference to FIGS. FIG. 1 is a configuration explanatory view showing a longitudinal section of an actuator of an impact test apparatus of this embodiment together with a hydraulic power source device, etc., FIGS. 2 to 4 are operation explanatory views of the actuator of this embodiment, and FIG. FIG. 3 shows the state before the oil cushion chamber enters after the start of the piston drive, and FIG. 4 shows the state after the oil cushion chamber enters.

  As shown in FIG. 1, an impact test apparatus 101 according to the present 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 in which the test body 50 is attached to 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 be ejected and rapidly accelerated so that the test body 50 reaches a predetermined speed by the stroke. Thereafter, when a land portion 5d provided on the piston rod 5 enters the oil cushion chamber 4 as will be described later, the hydraulic oil in the oil cushion chamber 4 is elastically compressed to a high pressure and generates a force to push the piston rod 5 back. Since the piston rod 5 is decelerated and stopped suddenly, impact acceleration is applied to the test body 50 and the intended impact test can be performed. .

  The actuator 1 of the impact test apparatus 101 of this embodiment is a hydraulic cylinder with a built-in valve, and the stepped cylindrical space 3 in the housing 2 is coaxially arranged along the center line X from the head side toward the front in the first to first directions. The four chambers 3a to 3d and the oil cushion chamber 4 are formed in this order, and the rear end portion (left end portion in the figure) 5a of the piston rod 5 is coaxially inserted into the stepped cylindrical space 3 from the oil cushion chamber 4 side. The front end portion (right end portion in the figure) 5b ("one end portion" of the present invention in the present embodiment) penetrates from the oil cushion chamber 4 to the outside, and the front end portion 5b of the piston rod 5 The test body 50 which is a target to which the impact acceleration is applied is fixed.

  The test body 50 is not particularly limited as long as the test body 50 is to be tested by applying a tension or a compressive force by shocking acceleration (for example, an automobile part or the like), and an appropriate bracket or frame body directly or in accordance with the load force direction. For example, an elastic member, a weight for loading an inertial force, and the like are added to the piston rod 5 and the like.

  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 do is described as “front”.

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

  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 suddenly 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 is inserted into the land portion 5d. It is set to be possible (land portion outer diameter d5 ≦ inlet inner diameter d4). Further, 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 a screwing or tightening member and extends in the center line X direction. It can be set by moving the position, and can be set by adjusting the volume of the oil cushion chamber 4.

  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. 1, and the hydraulic power source device 10 and the third chamber 3c in the operating position. 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, which will be described later with reference to FIG. 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. 1 and FIGS. The operation of the actuator 1 of this embodiment is as follows: (i) initial state shown in FIG. 2 (piston stopped state), (ii) after starting the piston driving shown in FIG. 3 / 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. 1 are closed. However, in the initial 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. 2, 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 this embodiment is set so as to satisfy the condition of d1 ² <d2 ² -d3 ² , 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. 3, 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 to move 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 projecting the piston rod 5 forward (rightward) at a high speed to give the test body 50 a predetermined 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. By adjusting the flow rate, the speed applied to the test body 50 can be set. 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. 4, when the land portion 5d 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, the piston rod 5 is rapidly decelerated and stopped, an impact acceleration is applied to the test body, and an intended impact test can be performed.

  The action of the oil cushion at that time can appropriately set the elasticity of the hydraulic oil in the oil cushion chamber 4 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, acceleration to the piston rod 5 is stopped, and the piston rod 5 decelerates and stops abruptly with the action of the oil cushion chamber 4 and the land portion 5d.

  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. The required valve device that can be driven and can give a predetermined speed to the test body 50 at a short distance, has a simple structure in which a hydraulic cylinder and a piston have a built-in valve, and connects the hydraulic power source device 10, A normal closing valve, switching valve, variable throttle, etc. can be used. 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.

  The piston rod 5 driven at high speed is rapidly 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 predetermined piston stroke. After reaching the stroke, the piston 5c moves to escape from the open hole 22 and flows into the hydraulic oil discharge system. The pressure in the first chamber and the second chamber decreases, the acceleration stops, and the piston rod decelerates rapidly. Since it stops, it becomes possible to drive at high speed and decelerate at a high speed, and can give an impact acceleration to the test body 50 and perform a predetermined impact test. At that time, the acceleration at the time of deceleration of the piston rod 5 can be adjusted by the third variable throttle 21 provided on the hydraulic oil discharge side from the oil cushion chamber 4. Further, since the deceleration set by the oil cushion is performed together with the high response and the 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 operating oil to be adjusted can be adjusted, the actuator 1 can be set so that the desired speed of the test body 50 can be obtained before the piston rod 5 reaches a predetermined stroke, and the first chamber 3a and the third chamber Since the output at the time of acceleration of the piston rod 5 can be adjusted by the fourth variable throttle 24 provided between 3c, the protruding force of the piston rod 5 according to the load condition such as the weight of the test body 50 can be set.

  Therefore, in an impact test device that requires an actuator capable of high response, high speed drive, and high acceleration decelerating and stopping, the actuator 1 has a simple structure and does not require a servo valve, advanced control device, etc., and has low equipment cost and low maintenance cost. The impact test apparatus 101 is an impact test apparatus 101 that does not use a complicated and high-cost actuator that uses electro-hydraulic control that matches the intended purpose, and that can achieve low-cost and stable operation using a simple structure actuator. be able to.

  Next, an impact test apparatus 101 'according to Embodiment 2 of the present invention will be described with reference to FIG. FIG. 5 is a structural explanatory view showing a longitudinal section of the actuator of the impact test apparatus of this embodiment together with a hydraulic power source apparatus and the like.

  Instead of penetrating the front end portion 5b 'of the piston rod 5' from the oil cushion chamber 4 of the housing 2 to the outside, the impact test apparatus 101 'of the present embodiment has a rear end portion 5a' (the present embodiment in this embodiment). The “one end portion” of the present invention is the one that passes through the housing 2 from the first chamber 3a side and exits to the outside. The other configuration is the same as that of the first embodiment, but the first built-in valve 7 '(The "built-in valve" of the present invention in this modification) is provided in the middle of the piston rod 5' instead of the rear end 5a '. The lid member 4b 'of the oil cushion chamber 4 does not have an insertion hole for the piston rod 5'.

  By operating the switching valve 15, the piston rod 5 'is driven forward (to the right in the figure) at a high speed in the same manner as in the first embodiment, and the rear end 5a' to which the test body 50 is attached is pulled out at a high speed. The operation is performed, the speed is rapidly decelerated by the action of the oil cushion chamber 4 and the land portion 5d, the impact acceleration is applied to the test body 50, and the action of the escape hole 22 is also added to stop suddenly. Accordingly, in the case of the first embodiment shown in FIGS. 1 to 4, the test body 50 that uses high-speed protrusion is provided at the front end portion 5 b of the piston rod 5 that has come out of the housing 2, so In the case of using the impact acceleration due to deceleration stop, there are advantages in the arrangement position, installation and the like. In the case of the second embodiment, the piston rod 5 ′ protruding outside the housing 2 is pulled into the rear end 5 a ′ at high speed. In the case where the test body 50 to be used is provided and the impact acceleration due to the rapid deceleration stop after the high-speed pull-in operation is used, there are advantages such as the arrangement position and installation, and other operational effects are the same.

  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 It is composition explanatory drawing which shows the longitudinal cross-section of the actuator of the impact test apparatus which concerns on Example 1 of this invention with a hydraulic power unit etc. FIG. FIG. 3 is an operation explanatory diagram of the actuator of Example 1 and shows an initial state. It is operation | movement explanatory drawing of the actuator of Example 1, 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 Example 1, and shows the state after an oil cushion chamber rush. It is composition explanatory drawing which shows the longitudinal cross-section of the actuator of the impact test apparatus which concerns on Example 2 of this invention with a hydraulic power unit etc. FIG. It is a schematic block diagram of the impact test apparatus by the conventional servo valve control hydraulic actuator.

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, 4b 'Lid member 5, 5' Piston rod 5a, 5a 'Rear end part 5b, 5b 'Front end portion 5c Piston 5d Land portion 6 First small-diameter portion 7, 7' First built-in valve 7a, 7a 'Valve body 8 Second small-diameter portion 9 Second built-in valve 10 Hydraulic power source device 11 Hydraulic pump 12 Accumulator 13 Stop valve 14 First variable throttle 15 Switching valve 16 Tank 17 Oil drain pipe 18 Drain pipe 19 Second variable throttle 20 Close valve 21 Third variable throttle 22 Relief hole 23 Chamber bypass 24 Fourth variable throttle 25 Close valve 50 Specimen 101 Impact Test equipment 101 'Impact test equipment

Claims (10)

A test equipped with a hydraulic power source device and an actuator having a piston rod driven by hydraulic oil from the hydraulic power source device, which is attached to the piston rod by pushing it forward and then stopping rapidly An impact test device that applies impact acceleration to a body,
The actuator includes a housing having a stepped cylindrical space inside,
The piston rod comprising a piston that penetrates at least one end from the housing and takes it out and attaches the test body and slides within the housing;
The piston rod has a land portion in the stepped cylindrical space, and the land portion enters the oil cushion chamber provided on the front end side of the stepped cylindrical space after the piston rod protrudes forward by a predetermined stroke. It is comprised so that it may carry out, The impact test apparatus characterized by the above-mentioned. The impact test apparatus according to claim 1,
The actuator is a hydraulic cylinder with a built-in valve,
The stepped cylindrical space includes a first chamber, a second chamber and a third chamber that are separated by the piston that is continuous with the same coaxial diameter and slides back and forth, the adjacent first chamber, and the third chamber. A first small-diameter portion provided between the two chambers and having a smaller inner diameter than the second chamber; a fourth chamber sandwiching the second small-diameter portion in front of the third chamber; A continuous oil cushion chamber in front of the chamber,
The piston rod includes a valve body located in the second chamber and the land portion located in the fourth chamber;
The valve body abuts on the first small-diameter portion as the piston rod moves backward to close the first small-diameter portion, and opens the first small-diameter portion as the piston rod advances. The built-in valve is formed together with the first small diameter portion,
The inner diameter of the second small diameter portion is smaller than that of the fourth chamber,
The land portion closes the second small diameter portion when the first built-in valve is closed, and the second built-in valve that opens the second small diameter portion when the built-in valve is opened together with the second small diameter portion. The outer diameter of the land portion is set so as to be fitted into the oil cushion chamber,
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, and the switching valve is communicated with the third chamber to the hydraulic oil discharge system when the switching valve is operated. Configured,
The third chamber is configured to communicate with the hydraulic oil discharge system via the second built-in valve and the fourth chamber;
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. An impact test apparatus characterized in that the pressing force is set to be large. The impact test apparatus according to claim 2,
The impact test apparatus characterized in that the oil cushion chamber is configured such that the volume of the oil cushion chamber can be changed to set the elasticity of the hydraulic oil. The impact test apparatus according to claim 2,
The impact test apparatus characterized in that the oil cushion chamber is connected to the hydraulic oil discharge system via a third variable throttle.   5. The impact test apparatus according to claim 2, wherein the actuator includes a relief hole that communicates the second chamber with a hydraulic oil discharge system when the piston moves forward by a predetermined stroke or more. The impact test device is characterized in that the escape hole is set so as to be closed by the piston from a state in which the first built-in valve is closed until the piston advances by a predetermined stroke. The impact test apparatus according to claim 5,
The impact test apparatus according to claim 1, wherein the first chamber communicates with the hydraulic power source device via a first variable throttle. The impact test apparatus according to claim 5,
The impact test apparatus, wherein the fourth chamber is connected to the hydraulic oil discharge system via a second variable throttle. The impact test apparatus according to claim 5,
The impact test apparatus according to claim 1, wherein the first chamber and the third chamber are connected via a fourth variable throttle. The impact test apparatus according to any one of claims 1 to 8,
The one end portion is an end portion of a piston rod that protrudes from the housing by the operation of the switching valve. The impact test apparatus according to any one of claims 1 to 8,
The one end portion is an end portion of a piston rod that is pulled into the housing by the operation of the switching valve.

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