WO2009144989A1

WO2009144989A1 - Vibration testing device

Info

Publication number: WO2009144989A1
Application number: PCT/JP2009/054615
Authority: WO
Inventors: 繁松本; 博至宮下; 一宏村内; 正伸長谷川; 友隆坂上
Original assignee: 国際計測器株式会社
Priority date: 2008-05-24
Filing date: 2009-03-11
Publication date: 2009-12-03
Also published as: JP4812879B2; TW200949226A; KR101242523B1; KR20100133955A; JPWO2009144989A1; TWI461677B; CN101970999B; CN101970999A

Abstract

A vibration testing device which allows to reduce a space for performing a vibration test and to vertically vibrate the bearing of a vehicle without using a vibration mechanism of large output. The vibration testing device comprises a bearing unit which rotatably supports the axle of the truck of a vehicle an axle drive mechanism which rotates the axle, a vertical vibration unit which vertically vibrates the bearing unit, an air cylinder mechanism which applies an upward load to the bearing unit, and a reaction frame which presses the truck from above.

Description

Vibration test equipment

The present invention relates to a vibration test apparatus that vibrates while applying a compressive static load in the vertical direction to an axle of a railway vehicle or a trailer.

In order to apply vibration equivalent to that during traveling to a freight vehicle such as a railway or a trailer, mainly to observe the behavior of the bearing of the axle of the vehicle, or to conduct a fatigue test of this bearing, as disclosed in JP-A-2005-274211 Vibration test equipment is used.

The vibration test apparatus described in the above publication places a vehicle on a rail wheel, drives the rail wheel to rotate and rotates the wheel of the vehicle, and applies vibration to the bearing of the vehicle by exciting the rail wheel in the axle direction. Is added.

Summary of the Invention

As described above, the conventional vibration test apparatus performs the vibration test in a state where the vehicle body is attached to the entire vehicle, that is, the carriage, so that a large space is required to perform the test. In addition, since the load of the weight of the vehicle body / the number of wheels is applied to each rail wheel, when the vehicle is vibrated in the vertical direction, a vibration output mechanism capable of withstanding this large load is required.

The present invention has been made to solve the above problems. That is, it is an object of the present invention to provide a vibration test apparatus that has a small space for performing a vibration test and can vibrate a vehicle bearing in the vertical direction without using a high-output vibration mechanism.

In order to achieve the above object, a vibration testing apparatus according to an embodiment of the present invention includes a bearing unit that rotatably supports an axle of a vehicle carriage, an axle drive mechanism that rotates the axle, and a bearing unit that extends in the vertical direction. It has an up-and-down direction vibration unit that vibrates, an air cylinder mechanism that applies an upward load to the bearing unit, and a reaction force frame that presses the carriage from above.

According to the vibration test apparatus according to the embodiment of the present invention, the vehicle carriage is sandwiched between the air cylinder mechanism and the reaction force frame. For this reason, by driving the air cylinder mechanism, a compressive static load corresponding to the weight of the vehicle body / the number of wheels can be applied to the bearing of the axle of the carriage. For this reason, the vibration test apparatus according to the embodiment of the present invention does not need to vibrate the entire vehicle, and only the carriage can be attached to the test apparatus for vibration. For this reason, the space for performing the vibration test can be significantly reduced. In addition, since the carriage is supported from below by the air cylinder mechanism, the vertical vibration unit may have a relatively small output enough to withstand the inertia when the carriage is vibrated in the vertical direction.

In addition, since the bearing unit is configured to support the axle at the wheel mounting position of the axle, the state of the carriage when the carriage is attached to the vehicle can be accurately reproduced.

Also, it is preferable that the bearing unit is configured to rotatably support the axle by a self-aligning roller bearing. With such a configuration, it is possible to rotatably support an axle on which a heavy load is applied in a direction orthogonal to the axle.

Preferably, the vertical vibration unit vibrates the bearing unit in the vertical direction by a servo motor and a feed screw mechanism.

In the present invention, the bearing unit is fixed on the vibration table, and the vertical vibration unit vibrates the vibration table in the vertical direction.

Also, an axle direction vibration unit that vibrates the vibration table in the axle direction of the carriage, first connection means for slidably connecting the vibration table to the vertical vibration unit in the axle direction, and the vibration table as the axle. It is preferable to further have a second connecting means that is slidably connected to the direction excitation unit in the vertical direction. According to such a configuration, the vibration table can be vibrated simultaneously in both the vertical direction and the axle direction without crosstalk.

The axle drive mechanism preferably includes a drive pulley that is rotationally driven by a motor, a driven pulley that is attached to the axle of the carriage, and an endless belt that is wound around the drive pulley and the driven pulley. . Thus, since it is the structure which drives an axle shaft by a belt mechanism, it is possible to rotate an axle shaft, vibrating a trolley | bogie. The driven pulley is attached to the approximate center of the axle of the carriage, for example.

Preferably, the reaction force frame applies a downward load to the carriage by abutting against the carriage on both sides in the axial direction of the transverse beam of the carriage and pressing the carriage from above. For example, the reaction force frame has an upright portion that is substantially upright and a pressing portion that is formed so as to extend in two directions substantially parallel to the side beam of the carriage at the upper end of the series portion. The carriage is pressed down in contact with the horizontal beam.

In addition, the first and second connecting means are each provided with a rail, a linear guide mechanism provided with a runner block that engages with the rail and is slidable along the rail, and the table, the vertical excitation unit, and the axle direction acceleration unit. It is good also as a structure which connects a vibration unit so that sliding is possible.

Also, the movement direction of the groove so that the runner block is formed in a recess surrounding the rail, a groove formed in the recess along the movement direction of the runner block, and formed inside the runner block, forming a closed circuit with the groove. It is preferable to include a retreat path connected to both ends, and a plurality of balls that circulate in a closed circuit and that come into contact with the rail when positioned in the groove. Furthermore, four closed circuits are formed in the runner block, and the balls arranged in the grooves of the two closed circuits of the four closed circuits are arranged in the radial direction of the guide mechanism including the rail and the runner block. The ball having a contact angle of approximately ± 45 degrees with respect to each other, and the balls disposed in the grooves of the other two closed circuits have a contact angle of approximately ± 45 degrees with respect to the reverse radial direction of the linear guide mechanism, More preferably.

The linear guide mechanism having such a configuration can smoothly move the runner block along the rail even when a large load is applied in the radial direction, the reverse radial direction, and the lateral direction. And since the table and the vertical and axle direction vibration unit are connected via such a linear guide mechanism, the table does not rattle even when a heavy truck is vibrated, and the rails are smooth. Can be moved to.

Alternatively, the runner block includes a recess surrounding the rail, a plurality of rollers arranged so that its cylindrical surface is sandwiched between the rail and the recess, and attached to the recess. A roller holding member that forms a rolling groove in which the roller rolls in the sliding direction of the runner block; and both ends of the rolling groove in the sliding direction that are formed inside the runner block and form a closed circuit with the rolling groove. A plurality of rollers may circulate in a closed circuit. Preferably, four closed circuits are formed in the runner block, and the four rows of rollers arranged in each of the four closed circuits have their axes every 90 ° on a plane perpendicular to the rail axis. It is arranged as follows. More preferably, the diameter of the roller is smaller than the distance between the runner block and the rail in the rolling groove, and the difference is 1 micrometer or less.

The linear guide mechanism having such a configuration can smoothly move the runner block along the rail even when a heavy load is applied to the runner block. Moreover, each roller, the rail, and the runner block are in contact with each other with a relatively large contact area, and vibrations from the vertical and axle direction vibration units can be transmitted to the table without a response delay. For this reason, the table can be vibrated at a relatively high frequency of several hundred Hz or more.

In addition, it is more preferable that a retainer for preventing contact between the two adjacent rollers is provided. More preferably, the retainer has a cylindrical concave surface that comes into contact with the cylindrical surface of the roller.

In a linear guide mechanism that does not have a retainer, the rollers contact each other with a relatively small contact area, so that a large stress is applied to the contact portion. In contrast, in the linear guide mechanism used in the embodiment of the present invention, the cylindrical surfaces of the roller and the retainer are in contact with each other with a relatively wide contact area, and the stress applied to the roller by this contact is kept relatively small. . Therefore, the roller can be prevented from being damaged or worn as compared with a linear guide mechanism having no retainer.

Furthermore, the linear guide mechanism used in the embodiment of the present invention is configured such that the rollers do not directly contact each other. When the rollers are in direct contact with each other, noise is generated. However, in the linear guide mechanism used in the embodiment of the present invention, such a noise can be suppressed because the retainer is disposed between the rollers.

In addition, the rail has a plurality of through holes arranged along the axial direction, and the rail is fixed to the table, the vertical vibration unit or the axle direction vibration unit through the bolts in each of the through holes, and the bolts are attached. The interval is 50 to 80% of the width of the rail. Preferably, the bolt mounting interval is 60 to 70% of the rail width.

As described above, by relatively shortening the bolt mounting interval, the rail is firmly fixed to the table, the vertical vibration unit or the axle vibration unit without bending.

1 is a top view of a vibration test apparatus according to an embodiment of the present invention. 1 is a front view of a vibration test apparatus according to an embodiment of the present invention. 1 is a side view of a vibration test apparatus according to an embodiment of the present invention. It is the top view which notched the axle direction excitation unit of the vibration test apparatus which concerns on embodiment of this invention partially. It is the front view which notched some up-and-down direction vibration units of the vibration testing device concerning an embodiment of the invention. In the linear guide mechanism of the vibration test apparatus which concerns on embodiment of this invention, it is sectional drawing which cut | disconnected the runner block and the rail by one surface perpendicular | vertical to the major axis direction of a rail. It is II sectional drawing of FIG. It is a perspective view which shows the attachment structure of the rail of the linear guide mechanism which concerns on embodiment of this invention. In the modification of the vibration testing apparatus which concerns on embodiment of this invention, it is sectional drawing which cut | disconnected the runner block and the rail by one surface perpendicular | vertical to the major axis direction of a rail. FIG. 10 is a sectional view taken along line II-II in FIG. FIG. 10 is a cross-sectional view taken along the line III-III in FIG. 9. It is a perspective view of the roller of the runner block of the linear guide mechanism used in the modification of embodiment of this invention. 1 is a block diagram of a vibration test apparatus according to an embodiment of the present invention.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. 1, 2, and 3 are a top view, a front view, and a side view, respectively, of the cart vibration test apparatus of the present embodiment.

The vibration test apparatus 1 according to the present embodiment is an apparatus for exciting the railway vehicle carriage 100. The carriage 100 includes a pair of axles 112, axle boxes 114 (FIGS. 2 and 3) attached to both ends of each axle, and a carriage frame 120.

The carriage frame 120 includes a pair of side beams 122 (FIGS. 1 and 2) extending in a direction substantially horizontal to the axle 112 (that is, a traveling direction of the vehicle), and a pair of lateral beams 124 extending in a direction substantially parallel to the axle 112. And have. The lateral beam 124 is connected to the substantially central portion of the side beam 122 near both ends thereof.

The pair of cross beams 124 are connected to each other at both ends via a top plate 125 and a bottom plate 126 (FIG. 2). An air spring mounting portion 127 is provided on the top plate 125. In the conventional vibration test apparatus, the vehicle body of the vehicle is connected to the carriage 100 via the air spring at the air spring mounting portion 127. However, in the vibration test apparatus of the present embodiment, the vehicle body is not attached.

The axle box 114 incorporates a double-row outward tapered roller bearing 116 (FIG. 3), and the axle 112 is rotatably supported by the axle box 114 via the bearing 116. Moreover, the upper surface of the axle box 114 and the edge part of the side beam 122 are connected via the coil spring 132 (FIG. 2, 3). That is, the carriage frame 120 is supported by the axle box 114 via the coil spring 132. As is clear from the above description, the cart 100 is a substantially rectangular body constituted by a pair of axles 112 and a pair of side beams 122 when viewed from above in FIG. In a substantially central portion, a pair of horizontal beams 124 are arranged in parallel with the axle 112 so as to straddle between the side beams 122. In FIG. 1, the right axle 112 is not shown so that the vertical vibration unit 20, the axle direction vibration unit 30, and the like appear in the drawing.

As shown in FIG. 3, the axle 112 is supported by the bearing unit 12 at the position of the wheel mounting portion 112a. That is, a total of four bearing units 12 are provided, two for each axle. The bearing unit 12 includes a self-aligning roller bearing 12a, and rotatably supports the axle 112 to which a large load is applied in the vertical direction.

Each of the bearing units 12 is fixed on the vibration table 14. Further, a load sensor 16 is provided between the bearing unit 12 and the vibration table 14, and the magnitude of the load along the vertical direction, the axle direction, and the vehicle traveling direction applied to the carriage 100 can be measured.

As shown in FIG. 1, of the four vibration tables 14, two on one end side (lower side in FIG. 1) of each axle 112 are vertically excited units that vibrate the vibration table 14 in the vertical direction. 20 and an axle direction excitation unit 30 for exciting the vibration table 14 in the axle direction. Only two vertical vibration units 20 are provided on the two vibration tables on the other end side (upper side in FIG. 1) of each axle 112.

The structure of the axle direction vibration unit 30 will be described below. FIG. 4 is an enlarged top view of the axle-direction excitation unit 30 of the present embodiment. As shown in FIG. 4, the axle direction vibration unit 30 includes a fixed frame 31, a servo motor 32, a ball screw 33, a coupling 34, a bearing portion 35, and a ball nut 37. The coupling 34 connects the drive shaft 32 a of the servo motor 32 and the ball screw 33. The bearing portion 35 is fixed to a bearing support plate 31b that is welded so as to extend in the vertical direction from the upper surface plate 31a of the fixed frame, and supports the ball screw 33 rotatably. The ball nut 37 engages with the ball screw 33 and is supported so as not to move around its axis. Therefore, when the servo motor 32 is driven, the ball screw rotates and the ball nut 33 advances and retreats in the axial direction (that is, in the axle direction). The movement of the ball nut 37 is transmitted to the vibration table 14 through a coupling mechanism including the rail 44 and the runner block 46, whereby the vibration table 14 is driven in the axle direction. Then, by controlling the servo motor 32 so as to switch the rotation direction of the servo motor 32 at a short cycle, the vibration table 14 can be vibrated in the axle direction with a desired amplitude and cycle.

A motor support plate 31c extending in the vertical direction is welded to the upper surface of the upper surface plate 31a of the fixed frame 31. The motor support plate 31c is provided so as to be substantially perpendicular to the axial direction of the servo motor 32, and the servo motor 32 is cantilevered on one surface thereof (a surface distal to the vibration table 14). . The motor support plate 33c is provided with an opening 31d, and the drive shaft 32a of the servo motor 32 passes through the opening 31d and is connected to the ball screw 33 on the other surface side of the motor support plate 31c.

In addition, since the servo motor 32 is cantilevered by the motor support plate 31c, a large bending stress is applied to the welded portion of the motor support plate 31c, particularly the upper surface plate 31a. In order to relieve the bending stress, ribs 31e are provided at corners formed by the upper surface plate 31a and the motor support plate 31c.

The bearing portion 35 has a pair of

angular ball bearings

35a and 35b combined in a front combination. The

angular ball bearings

35a and 35b are accommodated in the hollow portion of the bearing support plate 31b. A bearing pressing plate 35c is provided on one surface of the angular ball bearing 35b (in a direction proximal to the vibration table 14), and the bearing pressing plate 35c is fastened to the bearing support plate 31b using a bolt. As a result, the angular ball bearing 35 b is pushed in the direction toward the servo motor 32. Further, in the ball screw 33, a threaded portion 33a is formed on a cylindrical surface on the side proximal to the coupling 34, and a collar 35d having a female screw formed on the inner periphery is attached to the threaded portion 33a. It is supposed to be. By rotating the collar 35 d with respect to the ball screw 33 and moving it away from the coupling 34, the angular ball bearing 35 a is pushed in a direction toward the ball nut 37. Thus, since the

angular ball bearings

35a and 35b are pushed in the direction approaching each other, the two are in close contact with each other, and a suitable preload is applied to the

bearings

35a and 35b.

Next, the configuration of the connecting portion 40 that connects the vibration table 14 and the axle direction excitation unit 30 will be described. The connecting portion 40 includes a nut guide 42, a pair of rails 44, and a pair of runner blocks 46 attached to each of the rails 44.

The nut guide 42 is fixed to the ball nut 37. A pair of rails 38 extending in the direction from the servo motor 32 toward the vibration table 14 are fixed to the upper surface plate 31 a of the fixed frame 31 side by side so as to sandwich the ball nut 37 and the nut guide 42. A runner block mounting plate 43 that extends in the direction toward the rail 38 is fixed to the bottom surface of the nut guide 42. A runner block 45 that engages with the rail 38 is fixed to the bottom surface of the runner block mounting plate 43, and the runner block mounting plate 43 and the nut guide 42 advance and retreat with respect to the vibration table 14 along the rail 38. It can slide only in the direction. Thus, since the moving direction of the nut guide 42 is restricted only in the direction in which the nut table 42 moves forward and backward, that is, in the axial direction of the ball screw 33, when the ball screw 33 is rotated, the nut guide 42 is moved to the vibrating table. Move forward and backward with respect to 14.

The rail 44 of the connecting portion 40 extends in the vertical direction, and the runner block 46 is movable along the rail 44 in the vertical direction. The runner block 46 is fixed to the vibration table 14. For this reason, when the vibration table 14 is moved in the vertical direction by the vertical vibration unit 20 to be described later, the runner block 46 slides along the rail 44, so that a vertical load is applied to the axle direction vibration unit 30. In addition, bending stress due to such a load in the vertical direction is not applied to the ball screw 33. On the other hand, the nut guide 42 can be advanced and retracted by driving the ball screw 33, but this displacement is transmitted to the vibration table 14 via the rail 44 and the runner block 46. As described above, according to the configuration of the present embodiment, even when the vibration table 14 vibrates in the vertical direction, the vibration table 14 is moved in the axle direction by the axle direction vibration unit 30 without crosstalk. Can be vibrated.

The rail 44 extending in the vertical direction and the runner block that engages with the rail 44 are also provided between the vibration table 14 and the vertical vibration unit 20 as shown in FIG. The vibration table 14 can be moved smoothly in the vertical direction.

Position detection means 39 is arranged on one side surface (right side in FIG. 4) 43a of the runner block mounting plate 43. The position detection means 39 includes three proximity sensors 39a arranged at regular intervals in the direction from the servo motor 32 toward the vibration table 14, a detection plate 39b provided on the side surface 43a of the runner block mounting plate 43, and the proximity sensor 39a. Has a sensor support plate 39c. The proximity sensor 39a is an element that can detect whether any object is in proximity (for example, within 1 millimeter) in front of each proximity sensor. Since the side surface 43a of the runner block mounting plate 43 and the proximity sensor 39a are sufficiently separated from each other, the proximity sensor 39a can detect whether or not there is a detection plate 39b in front of each proximity sensor 39a. A control means (not shown) of the vibration test apparatus 1 can feedback-control the servo motor 32 using, for example, the detection result of the proximity sensor 39a.

Further, on the upper surface plate 31 a of the fixed frame 31, there are provided restriction blocks 47 arranged so as to sandwich the runner block mounting plate 43 from both sides of the nut guide 42 in the advancing and retreating direction. The restriction block 47 is for restricting the movement range of the nut guide 42. That is, when the servo motor 32 is driven and the nut guide 42 is continuously moved toward the vibration table 14, finally, the restriction block 47 and the runner block mounting plate disposed on the proximal side with respect to the vibration table 14. 43 comes into contact with the nut guide 42 and the nut guide 42 cannot move in the direction toward the vibration table 14 any more. The same applies to the case where the nut guide 42 is continuously moved in the direction away from the vibration table 14, and the restriction block 47 and the runner block mounting plate 47 arranged on the distal side with respect to the vibration table 14 come into contact with each other. Further, the nut guide 42 cannot move away from the vibration table 14.

Next, the structure of the vertical vibration unit 20 that drives the vibration table 14 in the vertical direction will be described. FIG. 5 is a partially cutaway front view of the vertical vibration unit 20 of the present embodiment. In order to clearly show the drive mechanism of the vibration table 14, an air cylinder 72 (FIGS. 1 and 2), which will be described later, is omitted in FIG.

As shown in FIG. 5, the vertical vibration unit 20 includes a fixed frame 21, a servo motor 22, a ball screw 23, a coupling 24, a bearing portion 25, and a ball nut 27. The fixed frame 21 is welded to a base plate 21a fixed to a device base (not shown), a plurality of beams 21b welded so as to extend vertically from the base plate 21a, and a beam 21b so as to cover the top of the beam 21b. A face plate 21c is provided. A bearing support plate 21d for mounting the bearing portion 25 is fixed on the top plate 21c via a bolt (not shown).

The coupling 24 connects the drive shaft 22a of the servo motor 22 and the ball screw 23. The bearing portion 25 is fixed to the above-described bearing support plate 21d, and supports the ball screw 23 so as to be rotatable. The ball nut 27 engages with the ball screw 23 and is supported so as not to move around its axis. Therefore, when the servo motor 22 is driven, the ball screw 23 rotates and the ball nut 27 advances and retreats in the axial direction (that is, the vertical direction). The movement of the ball nut 27 is transmitted to the vibration table 14 so that the vibration table 14 is driven in the vertical direction. Then, by controlling the servo motor 22 so as to switch the rotation direction of the rotating shaft 22a of the servo motor 22 with a short cycle, the vibration table 14 can be vibrated in the vertical direction with a desired amplitude and cycle.

A motor support plate 21f extending in a substantially horizontal direction is fixed to the lower surface of the bearing support plate 21d via two connecting plates 21e. A servo motor 22 is suspended and fixed on the lower surface of the motor support plate 21f. The motor support plate 21f is provided with an opening 21g. The drive shaft 22a of the servo motor 22 passes through the opening 21g and is connected to the ball screw 23 on the upper surface side of the motor support plate 21f.

The bearing portion 25 is provided so as to penetrate the bearing support plate 21d. In addition, since the structure of the bearing part 25 is the same as that of the bearing part 35 (FIG. 4) in the axle-axis direction excitation unit 30, description is abbreviate | omitted.

Next, the configuration of the connecting portion 60 that connects the ball nut 27 and the vibration table 14 will be described. The connecting portion 60 includes a movable frame 62, a pair of rails 64 extending in the axle direction, and a runner block 66 movable along the rails 64.

The movable frame 62 has a frame portion 62a fixed to the ball nut 27, a top plate 62b fixed to the upper end of the frame portion 62a, and a side beam 122 direction (left and right direction in the figure) of the top plate 62b downward from both edges. The side wall 62c is fixed to extend. The pair of rails 64 are arranged and fixed on the top surface of the top plate 62 b of the movable frame 62 in the direction of the side beam 122. The runner block 66 that engages with the rail 64 is fixed to the lower surface of the table 14. For this reason, when the vibration table 14 is moved in the axle direction by the axle direction vibration unit 30, the runner block 66 slides along the rail 64, so that no load in the axle direction is applied to the vertical direction vibration unit 20. Such bending stress due to the load in the axle direction is not applied to the ball screw 23. On the other hand, the ball nut 27 and the movable frame 62 can be advanced and retracted by driving the ball screw 23, but this displacement is transmitted to the vibration table 14 via the rail 64 and the runner block 66. As described above, according to the configuration of the present embodiment, even when the vibration table 14 is vibrating in the bearing direction, the vibration table 14 is moved in the vertical direction by the vertical vibration unit 20 without crosstalk. Can be vibrated.

In the present embodiment, as shown in FIG. 1, two runner blocks 66 are provided, two for each rail 64. Since the relatively heavy weight of the vibration table 14 and the carriage are added to the movable frame 62, the number of the runner blocks 66 is set to four so that an excessive load is not applied to each runner block 66.

Next, a structure for supporting the movable frame 62 will be described. A pair of rails 54 (FIGS. 1 and 5) are fixed to the side wall 62c of the movable frame 62, respectively. The rail 54 is a rail extending in the vertical direction. As shown in FIG. 5, a runner block 56 is engaged with the rail 54, and can slide up and down along the rail 54. The runner block 56 is fixed on the top plate 21 b of the fixed frame 21 via the runner block mounting member 65. The runner block mounting member 65 includes a side plate 65a substantially parallel to the side wall 62c of the movable frame 62, and a bottom plate 65b fixed to the lower end of the side plate 65a, and has an L-shaped cross section as a whole. . In this embodiment, when a particularly heavy and heavy workpiece is fixed on the vibration table 14, a large moment around an axis extending in the horizontal direction is easily applied to the movable frame 62. The runner block mounting member 65 is reinforced by ribs so as to withstand this rotational moment. Specifically, a pair of first ribs 65c are provided at the corners formed by the side plate 65a and the bottom plate 65b at both ends (see FIGS. 3 and 5) of the runner block mounting member 65, and the pair of first ribs is further provided. A second rib 65d is provided between 65c.

Thus, the runner block 56 is fixed to the fixed frame 21 and is slidable in the vertical direction with respect to the rail 64 fixed to the movable frame 62. Therefore, the movable frame 62 is slidable in the vertical direction, and movement of the movable frame 62 other than the vertical direction is restricted. Thus, since the moving direction of the movable frame 62 is restricted only in the vertical direction, when the servo motor 22 is driven to rotate the ball screw 23, the movable frame 62, the movable frame 62, the rail 64, and the runner are rotated. The vibration table 14 connected via the block 66 moves forward and backward.

Further, position detection means (not shown) similar to the position detection means 39 (FIG. 4) of the axle direction vibration unit 30 is also provided in the vertical vibration unit 20. A control means (not shown) of the vibration test apparatus 1 can control the height of the movable frame 62 within a predetermined range based on the detection result of the position detection means.

As described above, in the present embodiment, the vertical vibration unit 20 and the axle vibration unit 30 can simultaneously vibrate the vibration table 14 without crosstalk. For this reason, a complicated vibration in which the vibrations in the axle direction and the vertical direction are combined can be given to the carriage 100.

Next, the linear guide mechanism including the rail 44 and the runner block 46 according to the present embodiment will be described in detail with reference to the drawings. The rail 34 and the runner block 36, the rail 54 and the runner block 56, and the rail 64 and the runner block 66 also have the same structure as the rail 44 and the runner block 46.

6 is a cross-sectional view of the rail 44 and the runner block 46 taken along one plane (that is, a horizontal plane) perpendicular to the major axis direction of the rail 44, and FIG. 7 is a cross-sectional view taken along the line II in FIG. As shown in FIGS. 6 and 7, the runner block 46 is formed with a recess so as to surround the rail 44, and four

grooves

46 a and 46 a ′ extending in the axial direction of the rail 44 are formed in the recess. Has been. Numerous stainless steel balls 46b are accommodated in the

grooves

46a and 46a ′. The rail 44 is provided with

grooves

44a and 44a 'at positions facing the

grooves

46a and 46a' of the runner block 46, respectively, and the ball 46b is formed between the

grooves

46a and 44a or between the grooves 46a 'and 44a'. It is designed to be sandwiched between them. The cross-sectional shape of the

grooves

46a, 46a ′, 44a, 44a ′ is an arc shape, and the radius of curvature thereof is substantially equal to the radius of the ball 46b. For this reason, the ball 46b is in close contact with the

grooves

46a, 46a ′, 44a, 44a ′ with little play.

Inside the runner block 46, four

ball retraction paths

46c and 46c 'are provided which are substantially parallel to the grooves 46a. As shown in FIG. 7, the groove 46a and the retreat path 46c are connected to each other via a U-shaped path 46d, and the groove 46a, the groove 44a, the retreat path 46c, and the U-shaped path 46d A circulation path for circulating the ball 46b is formed. A similar circulation path is also formed by the groove 46a ', the groove 44a', and the retreat path 46c '.

Therefore, when the runner block 46 moves with respect to the rail 44, a large number of balls 46b circulate in the circulation path while rolling in the

grooves

46a, 46a ', 44a, 44a'. For this reason, even if a heavy load is applied in a direction other than the rail axial direction, the runner block can be supported by a large number of balls, and the resistance in the rail axial direction is kept small by rolling the balls 46b. The block 46 can be moved smoothly with respect to the rail 44. The inner diameters of the retreat path 46c and the U-shaped path 46d are slightly larger than the diameter of the ball 46b. For this reason, the frictional force generated between the retreat path 46c and the U-shaped path 46d and the ball 46b is very small, and the circulation of the ball 46b is not hindered.

As shown in the drawing, the two rows of balls 46b sandwiched between the

grooves

46a and 44a form a front combination type angular ball bearing having a contact angle of approximately ± 45 °. In this case, the contact angle means that the line connecting the contact points where the

grooves

46a and 44a contact the ball 46b is the radial direction of the linear guide mechanism (the direction from the runner block to the rail, the downward direction in FIG. 6). It is an angle made with respect to. The angular ball bearings formed in this way are in the reverse radial direction (the direction from the rail toward the runner block, the upward direction in FIG. 6) and the lateral direction (the direction orthogonal to both the radial direction and the advance / retreat direction of the runner block). Yes, the load in the left-right direction in FIG. 6 can be supported.

Similarly, the two rows of balls 46b sandwiched between the grooves 46a ′ and 44a ′ have a contact angle (a line connecting contact points where the grooves 46a ′ and 44a ′ are in contact with the ball 46b is connected to the linear guide mechanism). A front combination angular contact ball bearing having an angle of about ± 45 ° with respect to the reverse radial direction is formed. This angular ball bearing can support radial and lateral loads.

Further, two rows of balls 46b sandwiched between one of the

grooves

46a and 44a (left side in the figure) and one of the grooves 46a 'and 44a' (left side in the figure) are also a front combination type angular ball bearing. Form. Similarly, two rows of balls 46b sandwiched between the other of the

grooves

46a and 44a (the right side in the figure) and the other of the grooves 46a 'and 44a' (the right side in the figure) are also a front combination type angular ball bearing. Form.

Thus, in this embodiment, the front combination type angular contact ball bearing having a large number of balls 46b supports the load acting in each of the radial direction, the reverse radial direction, and the lateral direction. A large load applied in a direction other than the direction can be sufficiently supported.

Next, the rail mounting structure of the linear guide mechanism employed in this embodiment will be described. FIG. 8 is a perspective view showing the rail 44 attached to the nut guide 42. The rail mounting structure is the same for other rails used in the vibration testing apparatus of this embodiment.

As shown in FIG. 8, the nut guide 42 is formed with a groove 42a having substantially the same width as the rail 44, and the rail 44 is fitted in the groove 42a. The rail 44 is formed with a plurality of through holes 44b arranged side by side in the axial direction. Although not shown in the drawing, a plurality of bolt holes are formed at positions corresponding to the through holes 44b at the bottom of the groove 42a. The rail 44 is fixed to the nut guide 42 by passing the bolt 44c through the through hole 44b and screwing it into the bolt hole of the nut guide 42.

In the present embodiment, the interval between the through holes 44b of the rail 44 (and the interval between the bolt holes of Anzaka) s is relatively short, 50 to 80%, preferably 60 to 70% of the width w of the rail 44. Yes. Thus, the rail 44 is firmly fixed to the nut guide 42 without being bent by relatively shortening the mounting interval of the bolts 44c.

In the linear guide mechanism of the present embodiment described above, the runner block 46 is slid with respect to the rail 44 by the rolling of the ball 46b. However, the embodiment of the present invention is not limited to the above configuration. Absent. As in a modification described below, a roller 246b may be used instead of the ball 46b, and a linear guide mechanism that slides the runner block 246 relative to the rail 244 by rolling of the roller 246b may be used.

FIG. 9 to FIG. 12 show modifications of the embodiment of the present invention. FIG. 9 is a cross-sectional view of the runner block 246 and the rail 244 taken along a plane perpendicular to the major axis direction of the rail 244. 10 and 11 are a II-II sectional view and a III-III sectional view of FIG. 9, respectively. As shown in FIG. 9, a recess 246 e is formed in the runner block 246 so as to surround the rail 244. A roller holding member 246f is sandwiched between the recess 246e and the outer peripheral surface of the rail 244. The roller holding member 246f forms four rolling

grooves

246a and 246a 'extending in the axial direction in the gap between the recess 246e and the outer peripheral surface of the rail 244. A large number of stainless steel rollers 246b are accommodated in the rolling

grooves

246a and 246a '. Both ends of the roller 246b in the axial direction are held by a roller holding member 246f, and the cylindrical surface is in contact with both the recess of the runner block 246 and the outer peripheral surface of the rail 244. The distance between the recess of the runner block 246 and the outer peripheral surface of the rail 244 is substantially equal to the diameter of the roller 246b, and the roller 246b is in close contact with the recess 246e of the runner block 246 and the outer peripheral surface of the rail 244 with little play.

Inside the runner block 246, two rail retracting paths 246c 'are provided that are substantially parallel to the rolling grooves 246a. As shown in FIG. 10, the rail retracting path 246c 'is formed by bending a tube that accommodates the roller 246b into a C shape. The rolling groove 246a and the retreat path 246c 'are connected at both ends, and form a circulation path for circulating the roller 246b. Further, as shown in FIG. 11, two rail retreat paths 246 c that are substantially parallel to the rolling grooves 246 a ′ are provided inside the runner block 246, and the retreat paths 246 c and the rolling grooves 246 a ′ are provided. Also forms a similar circuit.

Therefore, when the runner block 246 moves with respect to the rail 244, a large number of rollers 246b circulate in the circulation path while rolling on the rolling

grooves

246a and 246a '. For this reason, even if a heavy load is applied in directions other than the rail axial direction, the runner block 246 can be supported by a large number of rollers 246b, and the resistance in the rail axial direction is kept small by rolling the rollers 246b. The runner block 246 can be smoothly moved with respect to the rail 244.

In this modification, the distance d (FIGS. 10 and 11) between the recess 246e of the runner block 246 and the outer peripheral surface of the rail 244 is a length that is slightly larger (1 micrometer or less) than the diameter of the roller 246b. ing. In such a state, the preload from the roller 246b is applied to the runner block 246 and the rail 244, and the outer peripheral surface of the roller 246b is in close contact with the concave portion 246e of the runner block 246 and the outer peripheral surface of the rail 244. When a load in a direction other than the axial direction of the rail 244 is applied to one of the runner block 246 and the rail 244, the load is transmitted to the other via the roller 246b with almost no response delay. For this reason, even if the vertical direction vibration unit 20 and the axle direction vibration unit 30 are reciprocally driven at a high frequency of about several hundred Hz, the vibration is reliably transmitted to the vibration table 14 via the intermediate stage. That is, according to the vibration test apparatus 1 of the present embodiment, the vibration table 14 can be vibrated at a high frequency.

As shown in FIG. 9, the four rows of rollers 246 b arranged in the four rolling

grooves

246 a and 246 a ′ have their axes every 90 ° on a plane orthogonal to the axis of the rail 244. It is arranged as follows.

Since each roller 246b is arranged in this way, when a load in a direction from the runner block 246 toward the upper surface of the rail 244 (a direction from the top to the bottom in FIG. 9) is applied, this load mainly includes two rolling elements. The two rows of rollers 246b disposed in the moving groove 246a receive. In addition, when a load is applied to the runner block 246 in a direction away from the upper surface of the rail 244 (a direction from the bottom to the top in FIG. 9), this load is mainly disposed in the two rolling grooves 246a ′. Two rows of rollers 246b receive.

Further, when a load is applied to the runner block 246 in the direction from one side surface (left side in the figure) to the other side surface (right side in the figure), the load is mainly caused by the runner blocks of the rolling grooves 246a ′ and 246a. Two rows of rollers 246b arranged on one side (left side in the figure) receive. On the other hand, when a load in the direction from the other side surface to the one side surface is applied to the runner block 246, the load is mainly disposed on the other side of the runner block (right side in the drawing) of the rolling grooves 246a ′ and 246a. The two rows of rollers 246b are received.

Furthermore, when a torsional load around the axial direction of the rail 244 is applied to the runner block 246, if the direction of the torsional load is clockwise in FIG. 9, the load is mainly the other side of the runner block of the rolling groove 246a ( The roller 246b disposed on the right side in the drawing and the roller 246b disposed on one side of the runner block (left side in the drawing) of the rolling groove 246a ′ are received. If the direction of the torsional load is counterclockwise in FIG. 9, the load is mainly arranged on the roller 246b arranged on one side of the runner block of the rolling groove 246a and on the other side of the runner block of the rolling groove 246a ′. The roller 246b receives.

As described above, in this modification, regardless of whether the load in the vertical direction, the horizontal direction, or the torsional direction in FIG. 9 is applied to the runner block 246, these loads are always received by the two rows of rollers 246b. It is like that. For this reason, the linear guide mechanism of this modification does not cause damage to the roller 246b by applying a load only to the roller 246b in a specific row even when a heavy load is applied in these directions, and smoothly rolls. The runner block 246 can be smoothly moved along the rail 244 by the roller 246b.

A perspective view of the roller 246b of the runner block 246 is shown in FIG. As shown in FIG. 12, a retainer 246g is provided between the rollers of the runner block used in the vibration test apparatus 1 of the present embodiment. The retainer 246g has two cylindrical surfaces that are in contact with the outer peripheral surfaces of the two adjacent rollers 246b, and the retainer 246g contacts the roller 246b through the cylindrical surfaces. The axes of the two cylindrical surfaces of the retainer 246g are parallel to each other. Since the retainer 246g is in contact with the roller 246b before and after the retainer 246g, the rollers 246b in the circulation path are aligned so that their axial directions are parallel to each other. For this reason, the roller 246b circulates smoothly in the circulation path without rattling.

Further, in the linear guide mechanism that does not have the retainer 246g, the rollers 246b contact with each other with a relatively small contact area, so that a large stress is applied to the contact portion. On the other hand, in the linear guide mechanism of this modification, the cylindrical surfaces of the roller 246b and the retainer 246g are in contact with each other over a relatively wide contact area, and the stress applied to the roller 246b by this contact is kept relatively small. Therefore, the linear guide mechanism of this modification can suppress the damage and wear of the roller 246b as compared with the linear guide mechanism that does not have a retainer.

Furthermore, the linear guide mechanism used in the modified example of the present embodiment is configured such that the rollers 246b do not directly contact each other. Although noise is generated when the rollers 246b are in direct contact with each other, in the present embodiment, since the retainer 246g is disposed between the rollers 246b, such noise can be suppressed.

The vibration test apparatus 1 according to the present embodiment can apply an upward static load to each vibration table 14 by the air cylinder mechanism 70 (FIGS. 1 to 3). Further, the horizontal beam 124 of the carriage 100 is pressed from above by a reaction force frame 80 (FIG. 2). That is, the carriage 100 is sandwiched between the reaction force frame 80 and the air cylinder mechanism 70 from above and below. When the air cylinder mechanism 70 is applied to apply an upward load to the vibration table 14, the reaction force frame 80. A downward load is applied to the carriage 100. Further, since the carriage 100 is supported from below by the air cylinder mechanism, the downward load applied to the carriage 100 from the reaction force frame 80 and the weight of the carriage 100 itself are caused by the nut 27, the feed screw and the vertical vibration unit 20. 23 and the servo motor 22 are not added. Accordingly, the torque of the servo motor 22 may be sufficiently large with respect to the inertia due to the vertical vibration of the carriage 100. That is, the torque of the servo motor 22 may be approximately the same as the torque of the servo motor 32 of the axle direction vibration unit 30.

As shown in FIGS. 1 to 3, the reaction force frame 80 of the present embodiment is a beam that stands upright from above the apparatus frame 11 that is disposed at a substantially lower center in the side beam 122 direction. At the upper end of the reaction force frame 80, a pressing portion 81 is formed that branches and extends on both sides in the direction of the side beam 122. The reaction force frame 80 has a T-shape as a whole. The lower surface of the pressing portion 81 abuts against the pair of transverse beams 124 and presses them from above. As shown in FIGS. 1 and 3, reaction force frames 80 are provided one on each side in the axial direction of the cross beam 124, and the carriage 100 is provided on both sides in the axial direction of each cross beam 124, that is, a total of four locations. It is pressed down by the reaction force frame 80.

The air cylinder mechanism 70 supplies eight air cylinders 72 (FIG. 1) provided between the fixed frame 21 and the movable frame 28 of each vertical vibration unit 20 and air to the air cylinders 72. And an air tank 74. As shown in FIG. 1, one air tank 74 is provided for each vertical vibration unit 20, and the vibration table 14 is adjusted by adjusting the pressure of the air supplied from the air tank 74 to the air cylinder 72. The load applied every time can be adjusted. The magnitude of the load by the air cylinder mechanism 70 is measured by the load sensor 16, and the pressure of the air sent to the air cylinder 72 by the controller (described later) of the vibration test apparatus 1 based on the measurement result of the load sensor 16. To be adjusted.

In this embodiment, the carriage 100 can be vibrated while the axle 112 of the carriage 100 is rotated by the axle drive mechanism 90 so that the behavior of the carriage in the running railway vehicle can be reproduced. The configuration of the axle drive mechanism 90 will be described below.

The axle drive mechanism 90 has a servo motor 92 and first to fourth pulleys 93 to 96. The first pulley 93 is fixed to the drive shaft of the servo motor 92 and is driven to rotate by the servo motor 92. The fourth pulley 96 is attached to the approximate center of the axle 112. The second and

third pulleys

94 and 95 are disposed directly above the servo motor 92 and at substantially the same height as the fourth pulley 96 (FIG. 3). As shown in FIGS. 1 to 3, the second pulley 94 and the third pulley 95 are fixed to a common rotating shaft 91 and rotate together. Further, the bearing and the servo motor 92 that support the rotating shaft 91 are both fixed on the apparatus frame 11.

As shown in FIG. 3, a first endless belt 97 is wound around the first pulley 93 and the second pulley 94. Similarly, a second endless belt 98 is wound around the third pulley 95 and the fourth pulley 96. Therefore, when the servo motor 92 is driven, the rotational motion of the drive shaft is transmitted from the first pulley 93 to the second pulley 94 via the first endless belt 97, and the second pulley 94 and the third pulley 95. Rotates. Then, the rotational movement of the third pulley 95 is transmitted to the fourth pulley 96 via the second endless belt 98, whereby the axle 112 rotates. Thus, in the configuration of the present embodiment, the first and

second pulleys

93 and 94, the first endless belt 97, the third and

fourth pulleys

95 and 96, and the second endless belt 98 are configured. The axle 112 can be rotated through the two sets of belt-pulley mechanisms. Thus, since the axle 112 is rotated by the belt-pulley mechanism, even if the fourth pulley 96 is slightly displaced in the vertical direction and the axle direction with respect to the other pulleys 93 to 95 by vibration, the first pulley 96 is displaced. The second belt 98 does not loosen with respect to the third and

fourth pulleys

95 and 96. Therefore, the vibration test apparatus 1 according to the present embodiment can vibrate the carriage 100 in the vertical direction and the axle direction at the same time as rotating the axle 112.

Next, control of the vibration test apparatus 1 of the present embodiment will be described. FIG. 13 is a block diagram of the vibration test apparatus 1 of the present embodiment. As shown in FIG. 13, the vibration test apparatus 1 includes a controller 2, a power supply 3, and a servo amplifier 4. The servo amplifier 4 is supplied with electric power from the power supply 3 to generate a three-phase alternating current and supplies it to the

servo motors

22, 32 and 92. The controller 2 can control the servo amplifier 4 to adjust the amplitude and frequency of the alternating current supplied to each

servo motor

22, 32, 92. Thereby, the rotation speed of each

servomotor

22, 32, 92 is controlled.

The controller 2 can feedback control the displacement, speed, and acceleration amplitude of the vibration table 14 based on the detection result of the acceleration sensor 18 provided on the vibration table 14 (FIG. 2). Instead of the acceleration sensor 18, another sensor that measures displacement and speed may be used.

As described above, the load by which the air cylinder 72 lifts the vibration table 14 is measured by the load sensor 16, and the controller 2 is provided between the air tank 74 and the air cylinder 72 based on the measurement result of the load sensor 16. The opening degree of the valve 76 (FIGS. 1 and 3) is adjusted by feedback control. By this feedback control, a static load corresponding to the vehicle load can be applied to the carriage 100.

Claims

A vibration device that vibrates the carriage while applying a vertical compressive static load to the carriage of the vehicle,
A bearing unit that rotatably supports the axle of the carriage;
An axle drive mechanism for rotating the axle;
A vertical vibration unit for vibrating the bearing unit in the vertical direction;
An air cylinder mechanism for applying an upward load to the bearing unit;
A vibration test apparatus comprising: a reaction force frame that presses the carriage from above so that the carriage is sandwiched vertically between the air cylinder mechanism.
2. The vibration test apparatus according to claim 1, wherein the bearing unit supports the axle at a wheel mounting position of the axle.
2. The vibration test apparatus according to claim 1, wherein the bearing unit rotatably supports the axle by a self-aligning roller bearing.
4. The vibration test apparatus according to claim 1, wherein the vertical vibration unit vibrates the bearing unit in the vertical direction by a servo motor and a feed screw mechanism.
The bearing unit is fixed on a vibration table;
The vibration test apparatus according to claim 1, wherein the vertical vibration unit vibrates the vibration table in a vertical direction.
An axle direction excitation unit for exciting the vibration table in the direction of the axle of the carriage;
First coupling means for slidably coupling the vibration table to the vertical excitation unit in an axle direction;
The vibration test apparatus according to claim 5, further comprising second connection means for connecting the vibration table to the axle direction vibration unit so as to be slidable in the vertical direction.
The axle drive mechanism is
A drive pulley that is rotationally driven by a motor;
A driven pulley attached to the axle of the carriage;
The vibration test apparatus according to claim 1, further comprising an endless belt wound around the drive pulley and the driven pulley.
The vibration testing apparatus according to claim 7, wherein the driven pulley is attached to a substantially center of an axle of the carriage.
The vibration test apparatus according to claim 1, wherein the reaction force frame abuts against the carriage on both sides in the axial direction of the transverse beam of the carriage to press the carriage from above.
The reaction force frame includes an upright portion that is substantially upright, and a pressing portion that is formed to extend in two directions substantially parallel to a side beam of the carriage at the upper end of the series portion.
The vibration test apparatus according to claim 1, wherein a lower surface of the pressing portion abuts against a lateral beam of the carriage and the carriage is pressed downward.
Each of the first and second connecting means includes a rail, a linear guide mechanism having a runner block that engages with the rail and is slidable along the rail, and the table, the vertical vibration unit, and the axle direction. The vibration test apparatus according to claim 6, wherein the vibration unit is slidably connected to the vibration unit.
The runner block is
A recess surrounding the rail;
In the recess, a groove formed along the direction of movement of the runner block;
A retreat path formed inside the runner block and connected to both ends of the groove in the moving direction so as to form a closed circuit with the groove;
A plurality of balls that circulate through the closed circuit and are adapted to contact the rail when positioned in the groove;
The vibration test apparatus according to claim 11, comprising:
The runner block has four closed circuits,
The balls arranged in the grooves of two of the four closed circuits each have a contact angle of approximately ± 45 degrees with respect to the radial direction of the linear guide mechanism including the rail and the runner block. The vibration test according to claim 12, wherein the balls disposed in the grooves of the other two closed circuits each have a contact angle of approximately ± 45 degrees with respect to the reverse radial direction of the linear guide mechanism. apparatus.
The runner block is
A recess surrounding the rail;
A plurality of rollers arranged such that the cylindrical surface is sandwiched between the rail and the recess;
A roller holding member that is attached to the recess and guides both axial ends of the roller to form a rolling groove in which the roller rolls in the sliding direction of the runner block;
A retreat path formed inside the runner block and connected to both ends of the rolling groove in the sliding direction so as to form a closed circuit with the rolling groove;
Have
The vibration test apparatus according to claim 11, wherein the plurality of rollers are configured to circulate through the closed circuit.
The runner block has four closed circuits,
The four rows of rollers arranged in each of the four closed circuits are arranged so that their axes are every 90 ° on a plane orthogonal to the axis of the rail. The vibration test apparatus described.
The vibration test apparatus according to claim 14, wherein a diameter of the roller is smaller than an interval between the runner block and the rail in the rolling groove, and a difference thereof is 1 micrometer or less.
The vibration test apparatus according to claim 14, wherein a retainer is provided between two adjacent rollers to prevent contact between the rollers.
The vibration testing apparatus according to claim 17, wherein the retainer has a cylindrical concave surface that comes into contact with the cylindrical surface of the roller.
The rail has a plurality of through holes arranged along the axial direction thereof,
It is fixed to the table, the vertical direction vibration unit or the axle direction vibration unit through a bolt through each of the through holes,
The vibration testing apparatus according to claim 11, wherein the bolt mounting interval is 50 to 80% of the width of the rail.
The vibration test apparatus according to claim 19, wherein the bolt mounting interval is 60 to 70% of the width of the rail.