TWI612284B - Load application device - Google Patents

Description

Load application device

The present invention relates to a load carrying device.

In the test of the durability of a two-wheeled vehicle, a method of testing the durability of a two-wheeled vehicle by a vibration tester is used. Then, as a vibration tester, for example, there is a possibility that a vibration can be applied to a two-wheeled vehicle in a vertical direction and a front-rear horizontal direction.

The vibration tester as described above applies vibration to the two-wheeled vehicle using the axle of the two-wheeled vehicle as a vibration point. Specifically, the vibration tester includes an actuator that imparts vibration in the vertical direction to the front wheel side axle, an actuator that imparts vibration in the horizontal direction, and an actuator that imparts vibration in the vertical direction to the rear wheel axle. Wait for three actuators.

In the vibration tester configured as described above, for example, as disclosed in JPH07140890 (A), three bodies are used to impart vibration in the vertical direction and the horizontal direction to the vehicle body of the two-wheeled vehicle, thereby giving the vehicle body nearly two rounds. The vibration input from the road surface when the vehicle actually travels.

Moreover, in the test of the durability of two-wheeled vehicles, it is required to carry out tests under the same conditions as when people are riding on two-wheeled vehicles, thus replacing people. A load applying device is mounted on the seatpost of the two-wheeled vehicle for testing. The load applying device is composed of a swingable rod mounted by a seat post and a weight scale hammer attached to the front end of the rod, so that the weight of the weight scale hammer is changed even when the two-wheeled vehicle is vibrated. It is often applied vertically to the seatpost.

However, in the case of a two-wheeled vehicle, when driving through a height difference, it usually corresponds to lifting the waist from the seatpost so that it will not be washed. On the other hand, as described above, the load applying device composed of the pendulum type weight scale hammer can directly apply the weight of the weight scale hammer to the two-wheeled vehicle when the vibration of the two-wheeled vehicle is applied to the two-wheeled vehicle. The body of the car, so it is impossible to consider the action of the rider who eases the rushing to carry out the endurance test. That is, in the conventional load-bearing device, it is difficult to perform an endurance test for imparting a load close to the human model.

Here, the present invention has been made in order to solve the above problems, and an object thereof is to provide a load applying device that can impart a load to a riding vehicle close to a human model.

In order to achieve the above object, a load applying device according to the present invention includes a weight scale hammer that applies a load to a seat post, and a cushioning member that is provided between the seat post and the weight scale hammer.

1‧‧‧Vibration machine

2‧‧‧Loading device

3‧‧‧Rack

3a‧‧‧elastic support

3b‧‧‧Base

4‧‧‧First Department of Vibration

5‧‧‧Second Department of Vibration

21‧‧‧Support frame

21a‧‧‧Longitudinal pillar

21b‧‧‧beam

21c‧‧‧Guide beam

22‧‧‧ housing

22a‧‧‧Support plate

22b‧‧‧ Cover

22c‧‧‧Guide beam

23‧‧‧Installation table

24‧‧‧Support table

25‧‧‧ Holding components

31‧‧‧Axle

32‧‧‧Axle

33‧‧‧ seatpost

34‧‧‧ body frame

35‧‧‧ head tube

36‧‧‧ Front fork

41‧‧‧ platform

42‧‧‧First vertical vertical shaft vibrator

43‧‧‧First horizontal axis vibrator

44‧‧‧ pillar

45‧‧‧First Transform Connector

46‧‧‧ Connecting rod

47‧‧‧ Connecting rod

51‧‧‧ platform

52‧‧‧Second vertical straight shaft vibrator

53‧‧‧Second horizontal axis vibrator

54‧‧‧ pillar

55‧‧‧Second Transform Connector

56‧‧‧ Connecting rod

57‧‧‧ Connecting rod

X‧‧‧ horizontal direction

Z‧‧‧Lead direction

T‧‧‧ vibration testing machine

W‧‧‧ weight scale hammer

M‧‧ motor

D‧‧‧ cushioning member

D1‧‧‧First elastic member

D2‧‧‧Second elastic member

B‧‧‧Two-wheeled vehicle

Figure 1 is a vibration test used in a load-bearing device in an embodiment. Side view of the machine.

Fig. 2 is a front elevational view of the vibration testing machine used in the load applying device of the embodiment.

Figure 3 is a side cross-sectional view showing a load applying device in an embodiment.

Fig. 4 is a front elevational view of the load applying device of the embodiment.

Fig. 5 is a view showing the configuration of a controller of a vibration testing machine used in a load applying device according to an embodiment;

Fig. 6 is a flow chart showing the processing procedure of the controller of the vibration testing machine used in the load applying device in the embodiment.

Hereinafter, the present invention will be described based on the embodiments shown in the drawings. In one embodiment, the load applying device 2 is used in the vibration testing machine T. As shown in FIG. 1 and FIG. 2, the vibration tester T is provided with a vibrating machine 1 as a vibration point for the test body, that is, the axles 31 and 32 before and after the two-wheeled vehicle B of the riding vehicle. In each of the axles 31 and 32, the vertical direction (Z-axis direction) in the vertical direction in FIG. 1 and the horizontal direction (X-axis direction) in which the axles 31 and 32 of the two-wheeled vehicle B are close to each other in the left-right direction in FIG. Perform vibration. In addition, the vibration testing machine T is provided with a load-carrying device 2 that applies a load to the seat post 33 of the two-wheeled vehicle B, in addition to the load-carrying device 2 that is actually loaded on the two-wheeled vehicle B, as shown in FIG. A controller C for controlling the vibrator 1 is provided.

Hereinafter, each part of the vibration testing machine T will be described in detail. The vibration machine 1 is provided with: a gantry 3, a gantry 3, and a two-wheeled vehicle B The front wheel side axle 31 is a first vibrating portion 4 that applies vibration to the vertical direction and the horizontal direction, and is movably attached to the gantry 3, and the axle 32 on the rear wheel side of the two-wheeled vehicle B is used as a vibration point. The second vibrating portion 5 that vibrates in the vertical direction and the horizontal direction.

The test body, that is, the two-wheeled vehicle B that rides the vehicle, is composed of the following components: a vehicle body frame 34; a front fork 36 that is rotatably attached to the head pipe 35 provided at the front end of the vehicle body frame 34; the axle 31 It is provided at the front end of the front fork 36; and the axle 32 is provided on the rear side of the vehicle body frame 34. Further, the front wheel and the rear wheel held by the axles 31 and 32 of the two-wheeled vehicle B are subjected to a vibration test in a state where they are removed. Further, the body frame 34 includes a seat post 33 that protrudes upward, and the load bar 33 is attached with the load applying device 2, and a load is applied to the two-wheeled vehicle B.

The gantry 3 includes a plurality of elastic supporting portions 3a and a pedestal 3b provided on the elastic supporting portion 3a, and is oscillated by the first vibrating portion 4 and the second vibrating portion 5 attached to the susceptor 3b. The vibration is absorbed by the elastic support portion 3a so that the load is not applied to the ground.

The first vibrating portion 4 is configured by a platform 41 fixedly attached to the base 3b of the gantry 3, and a first vertical axis actuator 42 standing in a vertical direction and mounted on the platform 41 for telescopic movement; a first horizontal axis actuator 43, which also stands in the vertical direction on the platform 41 and is swingably mounted on the platform 41 for telescopic movement; a post 44 that is vertically disposed on the platform 41; the first conversion connector 45 a rotatably coupled post 44 and a first horizontal axis actuator 43; a coupling rod 46 that is rotatable and coupled to both the first vertical axis actuator 42 and the axle 31 And a connecting rod 47 that can rotate both the first conversion connector 45 and the axle 31 and connect the two.

Further, the first vertical axis actuator 42 and the first horizontal axis actuator 43 are, in this example, a telescopic hydraulic servo cylinder that is expanded and contracted by pressure oil supply from an oil pressure source outside the figure. action.

The connecting rod 46 is rod-shaped, one end of which is hingedly coupled to the first vertical shaft actuator 42, and the other end is hingedly coupled to be detachably coupled to the axle 31.

Therefore, when the first vertical axis actuator 42 expands and contracts, the axle 31 is vibrated in the vertical direction in the vertical direction in FIG. 1 through the connecting rod 46, and the axle 31 is given vibration in the vertical direction. Since the connecting rod 46 rotatably connects the axle 31 and the first vertical shaft actuator 42, even if the horizontal vibration is applied to the axle 31, the vibration is not affected, and the first vertical shaft actuator 42 can be used. The axle 31 is vibrated in the vertical direction.

The pillar 44 is erected on the platform 41, and a first conversion connector 45 having a substantially triangular shape is rotatably attached to the front end thereof. In the first case, the first change connector 45 is coupled to the stay 44 by a hinge of a vertex in the vicinity thereof, and is attached to the stay 44 so as to be allowed to rotate only around the hinge joint.

The connecting rod 47 has a rod shape, and one end thereof is not connected to the stay 44 of the first conversion connector 45 and the first horizontal axis actuator 43, but is coupled to the vicinity of the remaining apex by hinge joint. Further, the other end of the connecting rod 47 is detachably coupled to the axle 31 by a hinge.

Then, when the surface including the X-axis in the horizontal direction in which the axle 31 for the vibration point is vibrated and the axis of the telescopic movement of the first horizontal-axis actuator 43 is used as the reference plane, the first horizontal-axis actuator 43 is used. Each of the first conversion connector 45 and the connecting rod 47 is coupled to be rotatable only on the reference surface.

When the first horizontal axis actuator 43 is extended, the first conversion connector 45 is rotated in the counterclockwise direction with respect to the hinge joint of the support post 44, and the connecting rod 47 is pushed out to the left, so that the axle 31 can be made to face. Driven in the left direction in Figure 1. Conversely, when the first horizontal axis actuator 43 is contracted, the first conversion connector 45 is rotated in the clockwise direction with respect to the hinge joint of the support post 44, and the connecting rod 47 is pulled to the right. The axle 31 is driven in the right direction in FIG. In other words, in the first vibrating portion 4, the first conversion coupling 45 and the support 44 constitute a crank mechanism, and the telescopic motion of the first horizontal axis actuator 43 can be converted into the X-axis direction and transmitted to the vibration point. That is, the axle 31. Further, the first conversion connector 45 has a triangular shape in order to be advantageous in terms of strength, but may have a shape other than a triangular shape such as an L shape.

Thereby, when the first horizontal axis actuator 43 exhibits a telescopic movement, the vertical expansion and contraction motion of the first horizontal axis actuator 43 is converted into the reciprocating motion in the X-axis direction by the first conversion connector 45, and The axle 31 is vibrated in the X-axis direction by the connecting rod 47 to impart vibration. Since the connecting rod 47 rotatably connects the axle 31 and the first conversion coupling 45, even if the vertical vibration is applied to the axle 31, the vibration is not affected, and the first horizontal shaft actuator 43 can be used. The axle 31 is applied horizontally Vibration.

The second vibrating portion 5 is configured by a platform 51 that is attached to the base 3b of the gantry 3 so as to be movable in the X-axis direction before and after the two-wheeled vehicle B; the second vertical axis actuator 52, It stands in a vertical direction and is mounted on the platform 51 and performs a telescopic movement; a second horizontal axis actuator 53, which also stands vertically in the vertical direction on the platform 51 and is swingably mounted on the platform 51 for telescopic movement; the pillar 54, which Standing in the vertical direction on the platform 51; the second change connector 55 rotatably connecting the post 54 and the second horizontal axis actuator 53; the connecting rod 56 to the second vertical axis actuator 52 and the axle Both of the members 32 rotate and connect the two; and the connecting rod 57 rotates and connects both of the second conversion connector 55 and the axle 32.

Although not shown in detail, the stage 51 is attached to the gantry 3 through a linear guide or the like, and is allowed to move in the X-axis direction with respect to the gantry 3, and is mounted on the motor M of the gantry 3 It can be driven in the X-axis direction. Further, the stage 51 can be fixed to the gantry 3 in the vibration test, and the movement in the X-axis direction can be restricted. Thereby, the distance between the vibration point of the two-wheeled vehicle B, that is, the distance between the axles 31 and 32 is adjusted in accordance with the distance between the axles 31 and 32, and the position of the gantry 3 with respect to the second oscillating portion 5 is adjusted in the X-axis direction. The second vibrating portion 5 is positioned at a position suitable for the two-wheeled vehicle B. Thereby, the second vibrating portion 5 can be positioned at an appropriate position without depending on the entire length of the two-wheeled vehicle B, and the first vibrating portion 4 and the second vibrating portion 5 can be attached to the vibration point of the two-wheeled vehicle B, respectively, and vibration can be performed. test.

And a second vertical axis actuator 52 and a second horizontal axis actuator 53, In this example, the telescopic hydraulic servo cylinder is expanded and contracted by pressure oil supply from a hydraulic source other than the figure.

The connecting rod 56 is rod-shaped, one end of which is hingedly coupled to the second vertical shaft actuator 52, and the other end is hingedly coupled to be detachably coupled to the axle 32.

When the second vertical axis actuator 52 expands and contracts, the axle 32 is vibrated in the vertical direction in the vertical direction in FIG. 1 through the connecting rod 56, and the axle 32 is given vibration in the vertical direction. Since the connecting rod 56 rotatably connects the axle 32 and the second vertical shaft actuator 52, even if the horizontal vibration is applied to the axle 32, the vibration is not affected, and the second vertical shaft actuator 52 can be used. The axle 32 is vibrated in the vertical direction.

The pillar 54 is erected on the platform 51, and a second conversion connector 55 having a substantially triangular shape is rotatably attached to the front end thereof. In this case, the second change connector 55 is coupled to the stay 54 by a hinge of a vertex in the vicinity thereof, and is attached to the stay 54 so as to be allowed to rotate only around the hinge joint.

The connecting rod 57 has a rod shape, and one end thereof is not coupled to the stay 54 of the second conversion connector 55 and the second horizontal axis actuator 53, but is coupled to the vicinity of the remaining apex by hinge joint. Further, the other end of the connecting rod 57 is detachably coupled to the axle 32 by a hinge.

Then, when the surface including the X-axis of the horizontal direction in which the axle 32 for the vibration-increasing point is vibrated and the axis of the telescopic movement of the second horizontal-axis actuator 53 is used as the reference plane, the second horizontal-axis actuator 53 is used. Second transformation The connector 55 and the connecting rod 57 are each coupled so as to be rotatable only on the reference surface.

Similarly to the first vibrating portion 4, the second vibrating portion 5 also constitutes a crank mechanism by the second conversion connector 55 and the post 54 to convert the telescopic motion of the second horizontal axis actuator 53 into the X-axis direction. And transmitted to the vibration point, that is, the axle 31. Further, the second conversion connector 55 has a triangular shape in order to be advantageous in terms of strength, but may have a shape other than a triangular shape such as an L shape.

Thereby, when the second horizontal axis actuator 53 exhibits the telescopic movement, the vertical expansion and contraction motion of the second horizontal axis actuator 53 is converted into the reciprocating motion in the X-axis direction by the second conversion connector 55, and The axle 32 is vibrated in the X-axis direction by the connecting rod 57 to impart vibration. Further, since the connecting rod 57 rotatably connects the axle 32 and the second conversion coupling 55, even if the vertical vibration is applied to the axle 32, the vibration is not affected, and the second horizontal shaft actuator 53 can be used. The axle 32 is vibrated in the horizontal direction.

Further, although the respective actuators 42, 43, 52, and 53 are not shown, they are well-known hydraulic servo cylinders, and include: a cylinder body and a sliding body that is slidably inserted into the cylinder and partitioned into a cylinder body. a piston that extends into the side chamber and the pressure side chamber; an output rod that is inserted into the cylinder and coupled to the piston; and a direction switching valve that is connected to the pump that supplies the pressurized oil to one of the extension side chamber and the pressure side chamber and the other to the groove. Each of the actuators 42, 43, 52, 53 may be of a single rod type or a double rod type. Each of the actuators 42, 43, 52, 53 is extensible by the supply of the pressurized oil to the extension chamber, and by the pressure side chamber The supply of pressurized oil can be contracted. Further, each of the actuators 42, 43, 52, and 53 connects the two chambers to the groove, stops the supply of the pressurized oil, and the like, so that the load cannot be exerted, and the unloaded state that is freely stretchable by the external force with little resistance is realized. . Further, the specific configuration of each of the actuators 42, 43, 52, 53 is not limited to the above, and other configurations may be employed as long as the no-load state can be achieved. Further, each of the actuators 42, 43, 52, 53 may be an actuator that is driven by electric or air pressure, and even in this case, it is noted that the aforementioned unloaded state can be realized.

Then, the first change linker 45 and the second change linker 55 are disposed in the same orientation with respect to the pillars 44 and 54, respectively. Thereby, the first horizontal axis actuator 43 and the second horizontal axis actuator 53 of the first vibrating portion 4 and the second vibrating portion 5 are all disposed in the driving direction of the pillars 44 and 54, that is, the X-axis direction. One of the sides, that is, the right side of the pillars 44, 54 in Fig. 1. Further, the first horizontal axis actuator 43 and the second horizontal axis actuator 53 may be disposed on the left side in FIG. 1 on the opposite sides of the support side in the driving direction of the pillars 44, 54.

Further, each of the vertical axis actuators 42 and 52 also uses the same specifications. Further, the specifications of the horizontal axis actuators 43 and 53 are the same, and the lengths of the connecting rods 46 and 47 and the telescopic movement of the horizontal axis actuators 43 and 53 of the respective conversion connectors 45 and 55 are converted to the axle 31. The lever ratio of the movement of the X-axis direction of 32 is equal.

Then, in the vibration testing machine T, the first conversion connector 45 and the second conversion connector 55 are respectively disposed in the same orientation, and the first horizontal axis actuator 43 and the second horizontal axis actuator 53 are arranged. In pillar 44, One of the two sides of the drive direction of 54. Therefore, in the case where the two-wheeled vehicle B is synchronously moved to the right side in FIG. 1, the first horizontal axis actuator 43 and the second horizontal axis actuator 53 may be moved toward the contraction side by the same amount. Conversely, in the case of synchronous movement to the left side in FIG. 1, the first horizontal axis actuator 43 and the second horizontal axis actuator 53 may be traveled toward the extension side by the same amount. Therefore, when the traveling positions of the horizontal axis actuators 43 and 53 are at the same position, it is noted that the relative positions of the axles 31 and 32 in the X-axis direction do not change. Therefore, even if the horizontal axis actuators 43 and 53 are closed and become in an unloaded state and contracted by the weight of the two-wheeled vehicle B, the relative positions of the axles 31 and 32 in the X-axis direction do not change.

Further, when the distance between the vibration points, that is, the X-axis directions of the axles 31 and 32 is to be changed, the horizontal axis actuators 43 can be controlled as long as the amounts of travel of the horizontal axis actuators 43 and 53 are not different. The amount of travel of 53 acts on the test body, that is, the two-wheeled vehicle B.

When the vertical shaft actuators 42 and 52 are expanded and contracted to drive the axles 31 and 32 in the vertical direction, and the horizontal shaft actuators 43 and 53 are simultaneously expanded and contracted, the two-wheeled vehicle may be omitted. B acts on the load in the X-axis direction to move the two-wheeled vehicle B up and down.

Thereby, even if the vertical axis actuators 42 and 52 and the horizontal axis actuators 43 and 53 are closed and become the most contracted state, the relative positions of the axles 31 and 32 in the Z-axis direction and the X-axis direction are also It will not change, and the two-wheeled vehicle B can be moved to the lowest position without burden and will not hurt the two-wheeled vehicle B.

Thereby, according to the vibration tester T, it is possible to monitor the load acting on the axles 31 and 32, and it is not necessary to carry out the load control to be fed back thereto, and the controller C is only required to perform the actuators 42, 43, 52, and 53. Displacement control is enough. Thereby, it is not necessary to switch the control from the displacement control buffer to the load control, so that it is easy to control, and the setting of the load cell or the distortion sensor is not required, so that it is advantageous in terms of cost.

Further, the hydraulic pressures of the all-actuators 42 , 43 , 52 , and 53 are all turned off to be in a no-load state, and the all-actuators 42 , 43 , 52 , and 53 are in the most contracted state. 43, 43, 52, 53 will not squeeze each other. Therefore, in the vibration tester T of this example, the loading and unloading operation of the test vehicle, that is, the two-wheeled vehicle B can be safely performed. Further, even if the actuators 42, 43, 52, 53 are all closed due to the failure, since the actuators 42, 43, 52, 53 do not interfere with each other's movements, the two-wheeled vehicle B can be quickly moved. To the bottom.

Further, the first horizontal axis actuator 43 and the second horizontal axis actuator 53 are disposed on one of both sides in the driving direction of the pillars 44 and 54, but the first horizontal axis actuator is provided. The configuration of the 43 and the second horizontal axis actuator 53 is not limited thereto.

Next, the load applying device 2 of the present invention will be described. As shown in FIG. 3, a weight scale hammer W for applying a load to the seatpost 33 of the two-wheeled vehicle B, and a cushioning member D provided between the seatpost 33 and the weight scale hammer W are provided.

More specifically, the load applying device 2 is configured by a support frame 21 that is disposed on the base 3b of the gantry 3, and a housing 22, It is mounted relative to the support frame 21 so as to be movable in the front-rear direction of the two-wheeled vehicle B, that is, in the X-axis direction, and accommodates the weight scale hammer W and the cushioning member D; the mounting table 23 is rotatably mounted to the seat post 33; a support base 24 which is movably attached to the mounting base 23 in the front-rear direction; a cushioning member D which is laminated on the support base 24; and a weight scale hammer W which is laminated on the cushioning member D.

As shown in FIGS. 1 and 2, the support frame 21 is composed of four vertical pillars 21a which are respectively disposed at the front and rear of the two-wheeled vehicle B, and four beams 21b which are connected to each other. The middle of the vertical strut 21a; and a pair of guide beams 21c are attached across the upper end of one of the longitudinal strut 21a provided in front of and behind the two-wheeled vehicle B.

As shown in FIG. 2 and FIG. 4, the casing 22 includes a pair of support plates 22a which are provided on the left and right sides of the two-wheeled vehicle B and are L-shaped when viewed from the front-rear direction of the two-wheeled vehicle B; The cover 22b of the support plate 22a is at the upper end of each other. Then, the lower ends of the respective support plates 22a are respectively connected to the lower guide beams 21c (see FIG. 1) through the linear guides 22c, and the casing 22 is provided in the left-right direction, that is, two wheels in FIG. The vehicle B moves in the front-rear direction.

The mounting table 23 is hingedly coupled to the grip member 25 for holding the seat post 33, and allows the rotation of the two-wheeled vehicle B in the front-rear direction, that is, the rotation around the axis of the paper in Fig. 3.

Further, on the mounting table 23, a support stand 24 is attached through a linear guide 26 provided in the front-rear direction of the two-wheeled vehicle B. The support table 24 is supported by the linear guide 26 and can be rotated relative to the mounting table 23 The vehicle B moves in the front-rear direction. The support base 24 is attached to the inner side of each of the support plates 22a of the casing 22 so as to be movable in the vertical direction by the linear guides 27 provided in the vertical direction. Thereby, the support table 24 allows only the movement in the vertical direction with respect to the casing 22.

Then, a cushioning member D is laminated on the upper side of the support table 24. The cushioning member D, in this example, is composed of a first elastic member D1 and a second elastic member D2 as elastic members. Each of the first elastic member D1 and the second elastic member D2 is formed of a disc-shaped synthetic resin. Further, the first elastic member D1 and the second elastic member D2 have different attenuation characteristics. In this example, the second elastic member D2 has higher attenuation than the first elastic member D1. Then, in the drawing, the buffer member D is configured by sandwiching the overlapping second elastic members D2 with the two first elastic members D1.

As the synthetic resin forming the first elastic member D1, for example, rubber or urethane rubber or the like may be used, and as the synthetic resin forming the second elastic member D2, for example, a soft polyurethane foam or the like is used to exhibit low resilience and high attenuation. Sex can be. Further, in the present embodiment, the first elastic member D1 and the second elastic member D2 are provided separately, but the number of the laminated sheets is arbitrary. Moreover, the configuration of the cushioning member D is not limited thereto, and may be, for example, a spring or a hydraulic shock absorber interposed between the weight scale hammer W and the support table 24, or a spring and a hydraulic shock absorber. It can be configured in series or in parallel, and can be composed of a spring and a synthetic resin exhibiting high attenuation, or a synthetic resin and a hydraulic shock absorber.

The weight scale hammer W is laminated on the cushioning member D. Specifically, the weight scale hammer W is composed of the following components: each support of the housing 22 The inner side of the plate 22a is attached to the slider 28 which is freely movable in the vertical direction by the linear guide 27 provided in the vertical direction; and the plurality of plates 29 mounted on the slider 28 are laminated. That is, the weight scale hammer W only allows movement in the vertical direction with respect to the casing 22.

The plate member 29 adjusts the number of laminated sheets and adjusts the overall weight of the weight scale hammer W. Moreover, the plate member 29 is provided with a hole which allows the insertion of the bolt 28a which is erected on the slider 28, and the plate member 29 can fix the plate member 29 by sliding the nut 28b of the bolt 28a. Item 28.

Then, when the vibration test of the two-wheeled vehicle B is performed, the housing 22 is moved back and forth with respect to the support frame 21 together with the position of the seat post 33 of the two-wheeled vehicle B to be most suitable for mounting the seat post 33 to the holding member. 25 location. Then, after the grip member 25 is attached to the seat post 33, the housing 22 is fixed so as not to move relative to the support frame 21. When the casing 22 is fixed to the support frame 21, various structures such as bolts may be used. After the casing 22 is fixed as described above, vibration is applied to the two-wheeled vehicle B by the vibrator 1 to perform a vibration test.

The housing 22 is fixed to the support frame 21, but when the seat post 33 of the two-wheeled vehicle B vibrates by the vibrator 1, the grip member 25 is vertically and horizontally aligned with the seat post 33 (X-axis direction). ) Move and rotate the front and rear directions of the two-wheeled vehicle B. Since the mounting table 23 is hingedly coupled to the grip member 25, the rotational vibration of the two-wheeled vehicle B of the seat post 33 in the front-rear direction is not transmitted to the mounting table 23. Further, the mounting table 23 moves in the vertical direction and the horizontal direction together with the grip member 25. However, the support table 24 is horizontally movable with respect to the mounting table 23, so that the horizontal position of the mounting table 23 is The vibration of the direction is not transmitted to the support table 24. Since the support table 24 is allowed to move in the vertical direction by the casing 22, the support table 24 is also vibrated in the vertical direction by the vibration in the vertical direction of the mounting table 23. The vibration in the vertical direction of the support base 24 is absorbed by the cushioning member D to suppress the transmission to the weight scale hammer W. However, the weight scale hammer W is also allowed to move in the vertical direction by the casing 22, so that it can be vertically oriented. vibration. As described above, the load applying device 2 changes the posture even if the two-wheeled vehicle B is vibrated by the vibrating machine 1, and the weight weigh W moves only in the vertical direction, and often acts on the seat post 33 toward the vertical load. . The weight scale hammer W is allowed to move in the vertical direction by the linear guide 27, so that the movement of the seat post 33 in the vertical direction can be allowed and the load is applied to the seat post 33. Further, the weight scale hammer W is allowed to move in the front-rear direction by the linear guide 26 with respect to the seat post 33, so that the movement of the seat post 33 in the front-rear direction and the load on the seat post 33 can be allowed.

Since the load applying device 2 is configured as described above, when the two-wheeled vehicle B is given the load of the upward projection by the vibrating machine 1, the cushioning member D absorbs the flushing, so the two-wheeled vehicle B has the weight of the weighing scale W. The transmission of vibration will be alleviated. Here, in the conventional load applying device in which the weight scale hammer is attached to the seat post in a pendulum type, when the two-wheeled vehicle B acts on the thrust bearing that is upwardly raised, the weight of the weight W is applied to the weight scale hammer W. Due to the inertia, the seat post is subjected to a load that is pushed downward. In the load-lifting device 2 of the present embodiment, the vibration of the weight-weighted hammer W is suppressed by the two-wheeled vehicle B side by the cushioning member D. Therefore, even if the two-wheeled vehicle B is given the load of the upward projection, It can also reduce the impact load of the two-wheeled vehicle B caused by the inertia of the weight scale hammer W. Therefore, according to the load application device 2. It is possible to give the two-wheeled vehicle B a load that is similar to the load-bearing state applied by the person to the two-wheeled vehicle B when the person actually rides on the two-wheeled vehicle B to pass the height difference. Then, according to the load applying device 2, the two-wheeled vehicle B as the riding vehicle can be given a load close to the human model.

In the case where the cushioning member D is configured by an elastic member having different damping characteristics, when the vibrator 1 applies a load to the two-wheeled vehicle B, the vibration is suppressed by the first elastic member D1 having low attenuation. The vibration of the two-wheeled vehicle B is transmitted to the weight scale hammer W, and the vibration of the weight scale hammer W after the vibration of the first elastic member D1 is absorbed is suppressed by the second elastic member D2 having high attenuation. It can prevent the weight of the weight scale hammer W from floating.

Further, since the first elastic member D1 and the second elastic member D2 (elastic member) are formed of synthetic resin, the arrangement between the weight scale hammer W and the support table 24 is relatively simple, and it is changed to a different resin material or By forming the method, it is possible to easily form an elastic member having different attenuation characteristics.

Further, since the cushion member D is formed by laminating a plurality of first elastic members D1 and second elastic members D2 (elastic members), the number of laminated sheets of the first elastic member D1 and the second elastic member D2 can be adjusted. . By adjusting the number of laminated sheets of the elastic member, the vibration transmission characteristic of the weight scale hammer W and the vibration of the weight scale hammer W can be coordinated while receiving the load of the upward projection from the seat post 33. Attenuation characteristics. Therefore, the load close to the human model can be further applied to the two-wheeled vehicle B of the riding vehicle.

Further, the load applying device 2 is provided with a mounting table 23 that is mounted on the seat post 33 so as to be rotatable in the front-rear direction of the two-wheeled vehicle B; 24, the mounting table 23 is mounted to be movable in the front-rear direction; the cushioning member D is laminated on the support table 24; and the weight scale hammer W is laminated on the cushioning member D. Therefore, even if the load-increasing device 2 applies the vertical direction, the front-rear horizontal vibration, and the front-rear rotation vibration to the two-wheeled vehicle B by the vibrating machine 1, the seat bar 33 is often subjected to a weight directly below the vertical direction. The weight of the weight hammer W gives a load closer to the human model.

Further, in the present example, the load applying device 2 includes a casing 22 that accommodates the weight scale hammer W, the cushioning member D, and the support table 24, and allows only the vertical movement of the weight scale hammer W and the support table 24, Moreover, it is mounted on the gantry 3, so that the dumping of the two-wheeled vehicle B in the left-right direction can also be prevented. Further, since the casing 22 is movable in the front-rear direction of the two-wheeled vehicle B with respect to the gantry 3, the two-wheeled vehicle B having a different position of the seatpost 33 can be moved to move the casing 22 to an appropriate position to load the load. The application device 2 is mounted to the two-wheeled vehicle B.

Next, the controller C includes: travel sensors S1, S2, S3, and S4 for detecting displacements of the actuators 42, 43, 52, 53 as shown in FIG. 5; the control unit 61, It is used to drive and control the actuators 42, 43, 52, 53; the distance calculating unit 62, which is based on the actuators 42, 43, 52, 53 detected by the traveling sensors S1, S2, S3, S4. The displacement is obtained to obtain the linear distance LL between the axles 31 and 32, and the stop determination unit 63 determines whether or not to stop the correlation based on the linear distance LL between the axles 31 and 32 obtained by the distance calculation unit 62. The driving of the actuators 42, 43, 52, 53.

The control unit 61 monitors the displacement of each of the actuators 42, 43, 52, and 53 and controls the driving of each actuator in accordance with the vibration information given to the two-wheeled vehicle B by the vibration information given to the two-wheeled vehicle B. 42, 43, 52, 53. Thereby, the controller C drives and controls the actuators 42, 43, 52, and 53 to impart vibration to the axles 31 and 32 of the two-wheeled vehicle B, and performs vibration test.

The distance calculating unit 62 obtains the linear distance LL between the axles 31 and 32 based on the displacements of the actuators 42, 43, 52, 53 detected by the traveling sensors S1, S2, S3, and S4. The axle 31 is oscillated by the first vertical axis actuator 42 and the first horizontal axis actuator 43, allowing displacement in the Z-axis direction and the X-axis direction, but limiting the Y-axis extending through the paper surface in FIG. The movement of the direction is only moved within the ZX plane. Further, in the axle 32, the second horizontal axis actuator 52 and the second horizontal axis actuator 53 are also oscillated to allow displacement in the Z-axis direction and the X-axis direction, but the movement in the Y-axis direction is restricted. Therefore, it only moves within the ZX plane. The ZX coordinate on the ZX plane of the axle 31 is obtained based on the displacement of each of the actuators 42 and 43 of the first vibrating portion 4, and the axle 32 is obtained based on the displacement of each of the actuators 52 and 53 of the second vibrating portion 5. The ZX coordinate on the ZX plane can determine the linear distance LL between the axles 31 and 32. As described above, the distance calculation unit 62 always obtains the distance between the vibration points, that is, the linear distance LL between the axles 31 and 32, based on the displacement of each of the actuators 42, 43, 52, 53 in the vibration test. .

Here, when the load from the first vibrating portion 4 and the second vibrating portion 5 is received, the linear distance LL between the axles 31 and 32 of the two-wheeled vehicle B is The distance (no load distance) between the two of the first vibrating portion 4 and the second vibrating portion 5 is not changed. When the linear distance LL between the axles 31, 32 becomes longer than the no-load distance LU, the two-wheeled vehicle B acts on the tensile load that separates the axles 31, 32, when the straight-line distance LL becomes smaller than the no-load distance When the LU is still short, the two-wheeled vehicle B acts on the compression load that brings the axles 31, 32 closer. By the tensile load and the compression load, when the stress acting on the components constituting the two-wheeled vehicle B becomes a state exceeding the allowable stress of each component, the component is plastically deformed and may be broken due to the situation. By designing the components of the two-wheeled vehicle B, the maximum reference weight and the maximum compression load in the range where the parts are not damaged are determined, and the reference weight and the compression load are determined by the distance between the vibration points. . That is, the maximum length Lmax between the axles 31, 32 to which the maximum tensile load of the two-wheeled vehicle B can be allowed, and the minimum distance between the axles 31, 32 to which the maximum compression load of the two-wheeled vehicle B can be applied The length Lmin is obtained in advance from the design specifications of the components of the two-wheeled vehicle B.

Therefore, in the vibration test, the linear distance LL between the axles 31 and 32 is monitored, and when the linear distance LL becomes equal to or greater than the maximum length Lmax or the minimum length Lmin, the actuators 42, 43, 52, and 53 are rendered unloaded. In this case, there will be no excess load on the two-wheeled vehicle B. In other words, the two-wheeled vehicle B is not allowed to be acted upon if the two-wheeled vehicle B is subjected to damage due to plastic deformation or the like, and the actuators 42, 43, 52, and 53 are allowed to expand and contract by external force. It is sufficient to exceed the maximum allowable tensile load or the maximum allowable compression load above it.

Therefore, the controller C is provided with the stop determination unit 63. The stop determination unit 63 outputs the stop to the control unit 61 when the difference ε between the linear distance LL obtained by the distance calculation unit 62 and the no-load distance LU is equal to or greater than a predetermined threshold value α or a threshold value β or less. Signal. When receiving the stop signal, the control unit 61 turns off the supply of current to each of the actuators 42, 43, 52, and 53 and becomes an unloaded state in which the external force can be expanded and contracted.

The threshold value α is a value obtained by subtracting the value of the safe margin from the distance Lmax between the axles 31 and 32 to which the maximum allowable tensile load is applied, and subtracting the value of the safety margin as a threshold having a positive value. Further, the threshold value β is a value obtained by subtracting the value of the no-load distance LU from the distance Lmin between the axles 31 and 32 to which the maximum allowable compression load is applied, and the value of the safety margin is a threshold having a negative value. When the safety margin is determined in the setting of the threshold value α and the threshold value β, the control unit 61 may cause the actuators 42, 43, 52, and 53 to be in a no-load state by the stop signal of the stop determination unit 63. It is indeed prevented that a load of more than the allowable weight is applied to the two-wheeled vehicle B. That is, as long as the linear distance LL does not reach the threshold value α and exceeds the threshold value β, the vibration test may be performed without causing damage to the test body, that is, the two-wheeled vehicle B, failing to reach the threshold α and exceeding the threshold β. The range is normal. On the other hand, when the linear distance LL exceeds the normal range, that is, when the threshold value α is equal to or higher than the threshold value β, the controller C causes the actuators 42, 43, 52, and 53 to be in an unloaded state. To prevent damage to the test body, that is, the two-wheeled vehicle B. Further, when the threshold value α and the threshold value β are set, the safety margin is not considered, and the threshold α = Lmax - LU and the threshold value β = Lmin - LU.

Specifically, as shown in the flow chart of FIG. 6, on controller C, The value of the no-load distance is subtracted from the distance between the axles 31 and 32 to which the maximum allowable tensile load is applied, and the value of the safety margin is subtracted, and is input as the threshold value α on the positive side (step F1). Further, in the controller C, the value of the no-load distance is subtracted from the distance between the axles 31 and 32 to which the maximum allowable compression load is applied, and the value of the safety margin is input as the threshold value β on the negative side (step F1). ).

The controller C is raised to the vibration neutral position in order to perform the vibration test of the two-wheeled vehicle B. The vibration neutral position is applied to the vibration points of the two-wheeled vehicle B, that is, the axles 31 and 32, and the vibration points are placed at the center of the vibration travel applied during the test.

In order to perform the vibration test, when the two-wheeled vehicle B is placed in the vibration neutral position, the load in the vertical direction and the horizontal direction does not act on the two-wheeled vehicle B, and the distance between the axles 31 and 32 at this time is no. Load distance. Here, the controller C recognizes the no-load distance LU from the ZX coordinates of the axles 31 and 32 at this time (step F2).

Then, the controller C starts the vibration test, and the linear distance LL between the axles 31 and 32 is often obtained in the test (step F3). Next, the controller C obtains the difference ε between the obtained linear distance LL between the axles 31 and 32 and the no-load distance LU (step F4). Further, the controller C determines whether or not the value of the difference ε is equal to or greater than the threshold α or the threshold β (step F5). Then, in the determination of step F5, if the value of the difference ε is equal to or greater than the threshold value α or the threshold value β or less, the process proceeds to step F6. If not, the process proceeds to step F7. In step F6, since the controller C may damage the two-wheeled vehicle B, the actuators 42, 43, 52, 53 are made unloaded. In the state, the load on each of the actuators 42, 43, 52, 53 of the two-wheeled vehicle B is removed. On the other hand, in step F7, since C is not likely to be damaged by the two-wheeled vehicle B, the test is continued and the actuators 42, 43, 52, 53 are continuously controlled, and the two-wheeled vehicle B is vibrated to impart vibration.

As described above, in the vibration tester T, vibration can be input by the four axes in the vertical direction and the horizontal direction before and after the test body, so that the test body can be arbitrarily oscillated in both the vertical direction and the horizontal direction. According to the vibration tester T, it is possible to accurately simulate the vibration of the test body by actually inputting the vibration, and to perform the vibration test or the fatigue test with higher effectiveness. In addition, even if the bicycle having the high rigidity and weak strength of the vehicle body frame 34 is used as the test body, the vibration can be input in four axes, so that the vibration during actual traveling can be accurately reproduced to impart vibration to the test body. .

Further, in the vibration tester T, when the distance between the vibration points exceeds the predetermined normal range, the actuators 42, 43, 52, and 53 are closed, and the vibration machine 1 is placed in a no-load state, so that there is no A load is applied to the test body to be damaged. In the conventional vibration tester, the actuator that vibrates in the horizontal direction is replaced by the rear wheel side axle, and the reaction force jig and the rear wheel axle are connected by a connecting rod, and the horizontal direction is restrained. Shi Zhen, so that the two-wheeled vehicle will not work in the unpredictable horizontal direction of compression or tensile load. On the other hand, in the vibration tester T, even if the test body is vibrated in four directions, the load on the test body does not exceed the allowable load, so that the test piece can be prevented from performing a safe vibration test.

Further, in the vibration testing machine T of the present example, the vibration oscillating machine 1 has a gantry 3, and is attached to the gantry 3 and vibrates one of the vibration points. The first vibrating portion 4 and the second vibrating portion 5 that vibrates the other side, and the second vibrating portion 5 is attached to the gantry 3 so as to be movable in the front-rear direction of the test body. Thereby, the test piece can be appropriately attached to the vibration tester T without performing the vibration test by independently depending on the entire length of the test body. Further, instead of the second vibrating portion 5, the first vibrating portion 4 may be attached to the gantry 3 so as to be movable in the front-rear direction of the test body, and both the first vibrating portion 4 and the second vibrating portion 5 may be attached to the test body. It can also move in the front and rear direction.

Further, in the vibration testing machine T of the present example, the first vertical axis actuator 42 of the first vibrating portion 4, the first horizontal axis actuator 43, and the second vertical axis actuator 52 of the second vibrating portion 5 and the second The two horizontal axis actuators 53 are erected in the vertical direction. Since the all-actuators 42, 43, 52, and 53 are erected in the vertical direction as described above, the length of the vibration tester T in the left-right direction in FIG. 1 can be shortened, and the size can be reduced.

The preferred embodiments of the present invention have been described in detail above, but modifications, changes, and alterations may be made without departing from the scope of the invention.

1‧‧‧Vibration machine

2‧‧‧Loading device

3‧‧‧Rack

3a‧‧‧elastic support

3b‧‧‧Base

4‧‧‧First Department of Vibration

5‧‧‧Second Department of Vibration

21‧‧‧Support frame

21a‧‧‧Longitudinal pillar

21b‧‧‧beam

21c‧‧‧Guide beam

22‧‧‧ housing

22a‧‧‧Support plate

22b‧‧‧ Cover

22c‧‧‧Guide beam

23‧‧‧Installation table

24‧‧‧Support table

25‧‧‧ Holding components

31‧‧‧Axle

32‧‧‧Axle

33‧‧‧ seatpost

34‧‧‧ body frame

35‧‧‧ head tube

36‧‧‧ Front fork

41‧‧‧ platform

42‧‧‧First vertical vertical shaft vibrator

43‧‧‧First horizontal axis vibrator

44‧‧‧ pillar

45‧‧‧First Transform Connector

46‧‧‧ Connecting rod

47‧‧‧ Connecting rod

51‧‧‧ platform

52‧‧‧Second vertical straight shaft vibrator

53‧‧‧Second horizontal axis vibrator

54‧‧‧ pillar

55‧‧‧Second Transform Connector

56‧‧‧ Connecting rod

57‧‧‧ Connecting rod

B‧‧‧Two-wheeled vehicle

D‧‧‧ cushioning member

D1‧‧‧First elastic member

D2‧‧‧Second elastic member

T‧‧‧ vibration testing machine

W‧‧‧ weight scale hammer

M‧‧ motor

Claims (7)

A load applying device comprising: a weight scale hammer that applies a load to a seat post of a riding vehicle; and a cushioning member provided between the seat post and the weight scale hammer. The load applying device according to claim 1, wherein the cushioning member has an elastic member having different attenuation characteristics. The load applying device according to claim 2, wherein the elastic member is a synthetic resin. The load applying device according to claim 2, wherein the cushioning member is formed by laminating a plurality of elastic members. A load applying device according to claim 1, comprising: a mounting table that is assembled to be rotatable in a front-rear direction of the riding vehicle; and a support table that is assembled in front of the mounting table Moving in the direction; the cushioning member is laminated on the support base; and the weight scale hammer is laminated on the cushioning member. A load applying device according to claim 1, comprising: a linear guide that allows movement of the weight scale hammer in a vertical direction. The load applying device according to claim 5, further comprising: a linear guide that allows the weight scale to move in a front-rear direction with respect to the mounting table.