JP6148992B2 - Bearing test equipment - Google Patents

Description

  The present invention relates to a bearing test apparatus used for friction measurement and durability testing of bearings such as engines, turbines, and motors.

Since bearings used in rotating machines such as engines, turbines, and motors are very important machine elements, high durability is required. In addition, in order to achieve the recent CO ₂ emission reduction target, development of a highly efficient rotating machine with reduced bearing friction is in progress. In developing such a rotating machine, it is important to correctly evaluate the durability of the bearing and the friction generated in the bearing. In particular, engine bearings are often used under elastohydrodynamic lubrication (lubrication when the bearing is elastically deformed) (Non-Patent Documents 1 and 2), and the friction generated in the bearing in the deformed state of the bearing housing is a problem. Become. For this reason, bearings such as bearings (large-end bearings, small-end bearings) possessed by connecting rods (hereinafter also referred to as “connecting rods”) can perform a friction test using a combination of an actual bearing and a shaft that rotatably supports the bearing. A test device is desired.

JP 2009-80092 A

T. Ozasa, M. Yamamoto, S. Suzuki, Y. Nozawa and T. Konomi: Elastohydrodynamic Lubrication Model of Connecting Rod Big End Bearings; Comparison with Experiments by Diesel Engine, SAE 1995 Transactions Journal of Fuels & Lubricants Section 4-Vol. 104, No. 952549, pp. 2011-2024. 1996 T. Ozasa, T. Noda and T. Konomi: Elastohydrodynamic Lubrication Model of Connecting Rod Big-End Bearings: Application to Real Engines, Transactions of the ASME Journal of Tribology, Vol. 119, July 1997, pp. 568-578. 1997 Toshihiro Komine, Shinichiro Kashiwagi, Koichi Yoroi, Toshihiro Yamada, Toshiaki Ishii, Hiroshi Yabe: Friction measurement and lubrication calculation of journal bearings by the reduction method, S115034, [No.11-1] 2011 Annual Meeting of the Japan Society of Mechanical Engineers -ROM Papers [2011.9.11-14, Tokyo] T. Ozasa, Y. Kajiki, K. Yorizane, A. Yamada, N. Ishii, H. Yabe: Friction Measurement of Journal Bearings Using Deceleration Method: Comparison with Hydrodynamic Lubrication, International Tribology Conference, Hiroshima 2011, October 30-November 3 , 2011, Hiroshima, Japan, P09-03, 2011 Tribology Society of Japan, Friction / Abrasion Tester and its Utilization Yokendo Kazuhiro Yokoyama et al., Research on evaluation of friction torque of bearings in rolling bearings, Journal of Precision Engineering, February 5, 1996, Vol. 60, No. 2, 210-214

Conventional bearing test apparatuses are roughly classified into the following (1) to (3).
(1) A bearing test device in which a bearing other than the test bearing exists for holding the shaft, where the test bearing is directly loaded and the friction is measured on the shaft side. (2) A bearing other than the test bearing is used for holding the shaft. A bearing test device that has a low-friction bearing load-loading unit that applies a load to the test bearing and measures the friction on the bearing side. (3) Holds the shaft only with the test bearing, and reduces its own weight and centrifugal force. Bearing test equipment that applies a load to the test bearing and measures friction on the bearing side

Each of these conventional bearing test apparatuses has the following problems.
The apparatus of (1) is used for measuring the friction of the test bearing under a large load. Rolling bearings with relatively low friction are used for bearings other than test bearings, but even if the friction is small, the friction generated by the rolling bearing is not negligible, especially the friction measurement accuracy on the shaft side using a torque meter Affects.
In the apparatus of (2), since the friction is measured by the rotational force of the bearing (using force balance), the friction generated in the bearing load load portion affects the friction measurement accuracy of the test bearing.
In the apparatus (3), a large load cannot be applied to the test bearing. In addition, a balancing mechanism for centrifugal force is required.

  Further, in the conventional bearing test apparatus, a method in which a test bearing is fixed to a highly rigid test bearing housing for testing is mainstream, and a bearing housing provided in an actual machine is not used. For this reason, the friction actually generated in the machine in which the elastic deformation is caused by the load of the bearing housing is different from the friction measured by the test apparatus.

  The present invention has been made in order to solve the above-mentioned problems, and can suppress the influence other than the bearing to be tested to a small extent, and can reduce friction and wear of the bearing to be tested even when a large load is applied. An object of the present invention is to provide a bearing test apparatus capable of measuring with high accuracy.

A bearing test apparatus according to the present invention, which has been made to solve the above problems,
a) one main shaft rotatably supported by four bearings;
b) two first holding portions respectively connected to two bearings located on the outside of the four bearings via rods;
c) Two second holdings arranged on the opposite sides of the first holding part and the main shaft and connected to two bearings located on the inner side among the four bearings via rods, respectively. And
d) a load applying means for applying a load to the bearing by changing a separation distance between the first holding portion and the second holding portion;
e) a drive mechanism for applying a rotational torque to the spindle;
It is characterized by providing.

In this case, a connecting transmission mechanism for connecting the first holding portion and the load applying means and said second holding portion, said load applying means, the elasticity of the rod between the retaining portion and the front Symbol coupling transmission mechanism and bearings It can be configured to apply a load to the bearing by utilizing it.
As the connection transmission mechanism, many mechanisms such as a mechanism for holding the holding portion and a link mechanism for connecting the load applying means and the holding portion are conceivable, but the simplest and most effective connection transmission mechanism is inserted into the hole of the holding portion. Is the axis.

For example, the connection transmission mechanism includes: one first holding shaft that is inserted through the two first holding portions; and one second holding shaft that is inserted through the two second holding portions. When configured, the load applying means may be configured to apply a load to the bearing using the first holding shaft and the second holding shaft.
Further, as the connection transmission mechanism, in addition to the first holding shaft and the second holding shaft, a shaft holding portion or a holding plate for holding these holding shafts may be used.

  As a representative test object of the bearing test apparatus according to the present invention, there is a part often used for an engine called a connecting rod (connecting rod). FIG. 14 shows an example of a connecting rod. The connecting rod 201 (corresponding to the reference numeral “30” in the embodiment) has a large end bearing 203 and a small end bearing 204 connected by a rod (connecting rod) 41, and when the large end bearing 203 is tested. The small end bearing 204 (corresponding to either “42” or “45” in FIG. 3) is used as a holding portion, and when the small end bearing 204 is tested, the large end bearing 203 is used as a holding portion. 17A and 17B show four connecting rods 201, a main shaft 22 and a first shaft when the large end bearing 203 of the connecting rod 201 is a bearing to be tested and the small end bearing 204 is a holding portion. It is a figure for demonstrating the positional relationship of the holding shaft 211 and the 2nd holding shaft 212 (it respond | corresponds to the code | symbol "132" of FIG. 13, the code | symbol "32" of another Example).

As shown in FIGS. 17A and 17B, one main shaft 22 is rotatably held by the large end bearings 203 of the four connecting rods 201. At this time, the small end bearings 204 of the two connecting rods 201 positioned on the inner side are both positioned on the right side of the main shaft 22 in the drawing, and the small end bearings 204 of the two connecting rods 201 positioned on the outer side are positioned on the left side of the main shaft 22 in the drawing. To position. In FIG. 17A, one first holding shaft 211 is inserted into two small end bearings 204 located on the right side, and one second holding shaft 211 is placed on the small end bearing 204 located on the left side. The shaft 212 is inserted. On the other hand, in FIG. 17B, different first holding shafts 211 are inserted through the two small end bearings 204 located on the right side. These first holding shafts 211 are attached to a shaft holding portion 214 fixed to the right holding plate 213. Further, separate second holding shafts 212 are inserted through the two small end bearings 204 located on the left side. These second holding shafts 212 are attached to a shaft holding portion 216 (corresponding to reference numeral “136” in FIG. 13) fixed to the left holding plate 215. For example, the shaft holding portions 214 and 216 (corresponding to reference numerals “134” and “136” in FIG. 13) are formed with U-shaped support members 218 having holes through which the holding shafts 211 and 212 are inserted, as shown in FIG. The support member 218 can be composed of a shaft member 221 that fixes the support plates 213 and 215 to each other.
The bearing test apparatus of the present invention includes both the modes shown in FIGS. 17 (a) and 17 (b).

  Moreover, in addition to a component formed by connecting two bearings such as connecting rods with a rod, even a component including only one bearing can be a test object of the bearing test apparatus according to the present invention. In this case, the holding part is connected to the bearing via a rod and then used for the test. Two bearings to be tested may be connected by a rod and one may be used as a holding portion, and a bearing having a different form from the bearing may be connected by a rod as a holding portion to the bearing to be tested.

  In the above bearing test apparatus, it is necessary to equalize the load applied to the four bearings in order to accurately measure the friction and wear generated in each bearing. If four bearings are arranged symmetrically on both sides of a predetermined point on the main shaft, the load applied to the four bearings can be made relatively equal by balancing the forces applied to the four bearings. can do. Therefore, it is preferable to provide positioning means for arranging four bearings symmetrically on both sides of a predetermined point on the main shaft.

  In the bearing test apparatus, a compressive load is applied to the bearing by bringing the first holding part and the second holding part closer to each other. Thus, when a compressive load is applied to the bearing, it is necessary to provide a restraining means for restricting the movement of the bearing in the direction perpendicular to the rod between the bearing and the holding portion and the main shaft. However, in the present invention, the two bearings located on the inner side and the two bearings located on the outer side have the holding portions facing in opposite directions across the main shaft, and therefore the direction of applying the compressive load is reversed. . As shown in FIG. 14, when a load is applied to the holding portion, an oil film pressure due to the lubricating oil is generated between the main shaft and the bearing. Such a phenomenon is based on fluid lubrication theory. Further, the shaft center of the main shaft is eccentric with respect to the center of the bearing, and this eccentric position is reversed depending on the load direction.

FIG. 15 is a diagram for explaining a case where loads in opposite directions are applied to two bearings. In FIG. 15, reference numeral 30 denotes a bearing. In FIG. 15, the gap between the rotating main shaft and the bearing is greatly exaggerated so that the eccentricity of the center of the main shaft with respect to the bearing center can be seen.
15A shows a state in which a tensile load is applied to the two bearings 30 (bearing housings), and FIG. 15B shows a state in which the tensile load is applied to the two bearings 30, and the two bearings 30 are applied to the rod 41 and the main shaft 22. The state restrained in the vertical direction, (c) shows the state where a compressive load is applied, (d) shows the state where the compressive load is applied, and the two bearings 30 are restrained in the vertical direction by the rod 41 and the main shaft 22. . As shown in FIGS. 15A and 15C, when a load is applied without restraining the two bearings 30, the shaft center of the main shaft 22 is eccentric with respect to the bearing center, and the positions of the two bearings 30 are shifted.
FIGS. 15B and 15D show the restraining force generated when the bearing 30 (or bearing housing) is restrained in the direction perpendicular to the rod 41 and the main shaft 22. As described above, when a restraining force is generated in the two bearings 30 (or bearing housings), a force other than the measurement target is generated, which affects the estimation of the bearing load and the friction, which is not preferable. When the movement of all four bearings in the vertical direction of the main shaft is restricted, the inner bearing and the outer bearing move in opposite directions, and a force other than a load is generated on the main shaft.

Therefore, in the above bearing test apparatus, as shown in FIGS. 16A and 16B, only the two inner bearings (large end bearing 203) among the four bearings, or the outer two It is preferable to provide a restraining means 220 for restricting movement of only the bearing (large end bearing 203) in a direction perpendicular to the main shaft 22. The restraining means 220 corresponds to a “vertical position restraining plate 53” described later (see FIG. 3). FIG. 16 shows an example in which the bearing (large end bearing 203 ) through which the main shaft 22 is inserted is restrained by the restraining means 220 in the embodiment of FIG. 17 (a). Similarly, the illustrated embodiment can be restrained by restraining means. According to such a configuration, the friction, wear, etc. of the bearing can be measured more accurately.

The first holding shaft and the second holding shaft are mounted so as to span between the pair of load shafts, and the separation distance between the two holding shafts is changed by changing the mounting position of the first holding shaft and the second holding shaft. be able to. In this case, it is held with respect to a load shaft (this corresponds to a “load shaft 34” (see FIGS. 2 and 9 to 11) described later, or a “both screw load shaft 171” (see FIG. 12)). If the shaft is attached using a fastening member such as a screw and a nut, the load shaft and the fastening member become load applying means. In addition to the fastening member, it is also preferable that the load applying means includes a gas pressure or hydraulic piston that changes a separation distance between the first holding shaft and the second holding shaft.

  Furthermore, it is preferable that the load applying unit includes an urging unit that urges the first holding shaft and the second holding shaft in a direction in which the first holding shaft and the second holding shaft are close to or apart from each other.

  Further, the load applying means includes a pair of both screw shafts connecting the first holding shaft and the second holding shaft, and an operation means for rotating the both screw shafts in forward and reverse directions. Thus, the first holding shaft and the second holding shaft may be moved closer to or away from each other by rotating both screw shafts in the forward and reverse directions.

  According to the present invention, since the four bearings are fixed by inserting the first and second holding shafts into the holding portions of the four bearings, the four holding shafts are moved closer to each other. A compressive load is applied to the bearings, and a tensile load is applied to the four bearings by separating the first holding shaft and the second holding shaft. The applied load is shared by the four bearings, but since the two are symmetrically arranged, the load is adjusted so that a large load is evenly applied to the four bearings with a force twice the load per one. be able to.

Further, in the present invention, since four identical bearings are used as test objects, the friction torque generated in the bearings is expanded four times. Therefore, the magnitude and change of the friction torque become clear, and the friction torque can be measured with high accuracy.
Furthermore, in the present invention, since a load is applied via the rod from the holding portions of the four bearings, a test bearing housing that matches the load mechanism is not required. Therefore, the bearing housing actually provided in the bearing can be used as it is.

  In addition, when one bearing of a component formed by connecting two bearings (large end bearing, small end bearing) with a rod, such as a connecting rod, is used as a test object, the other bearing may be used as a holding portion. it can. For this reason, the entire actual part can be set in the bearing test apparatus according to the present invention to perform a bearing test. In this case, if the conditions such as the load applied to the bearing to be tested and the magnitude of the rotational torque to be applied to the spindle are set to the same conditions as the machine on which the bearing to be tested is mounted, the friction generated during use of the bearing to be tested Wear and the like can be accurately measured.

1 is an overall configuration diagram of a bearing test apparatus according to the present invention. The top view (a) which shows the structure of the bearing test part which concerns on Example 1 of this invention along the II-A-II-A line of (c), front view (b), II-C- of (a) Side view along line II-C (c), enlarged view (d) showing the spacer attached to the bearing holding shaft. The figure of the test bearing shown in the state which attached the vertical position restraint board to the bearing housing. Explanatory drawing of the shape of the front-end | tip part of a main axis | shaft. The figure which shows the shape of the bush in the holding part which a test bearing has, and a bearing holding shaft. Explanatory drawing of the load applied to a test bearing. The exploded perspective view of the clutch which consists of an Oldham type shaft joint. The figure which shows the experimental result when a tensile load and a compressive load are applied to a bearing, and shows the relationship between the friction coefficient μ and the Sommerfeld number S. The top view along the IX-A-IX-A line of (c) which shows the principal part of the bearing test part which concerns on Example 2 of this invention (a), front view (b), IX-C of (a) Side view along line IX-C (c). The top view (a) in alignment with the X-A-X-A line of (c) which shows the structure of a bearing test part, the front view (b), and the side view along the X-C-X-C line of (a). The top view along the XI-A-XI-A line of (b) which shows the composition of the bearing test part concerning Example 3 of the present invention (a), along the XI-B-XI-B line of (a) Side view (b). The figure which shows the structure of the bearing test part which concerns on Example 4 of this invention. The top view (a), front view (b), and side view (c) which show the structure of the bearing test part which concerns on Example 5 of this invention. 1 shows a configuration of a connecting rod which is an example of a bearing to be tested in a bearing test apparatus according to the present invention, and describes a load applied to a holding portion, its direction, a rotation direction of a main shaft, an oil film pressure of lubricating oil, and an eccentricity of the shaft center with respect to the bearing center To do. It is a figure which shows the positional relationship of a spindle and a bearing when two bearings are attached to the rotating spindle and a load is applied in the opposite direction, and the relationship between the forces, (a) when a tensile load is applied, (b) When a tensile load is applied and restrained in a direction perpendicular to the main shaft and the rod, (c) When a compressive load is applied, (d) applies a compressive load and constrains in a direction perpendicular to the main shaft and the rod Show the time. Explanatory drawing of the restraint means which controls the movement to the direction perpendicular | vertical to the main axis | shaft of a test object bearing (connecting rod) and the axis | shaft of a rod in the bearing test apparatus which concerns on this invention. The figure which shows the positional relationship of a test object bearing (connecting rod), a main shaft, and the 1st and 2nd holding shaft in the bearing test apparatus which concerns on this invention. The figure which shows a U-shaped shaft holding part.

  The bearing test apparatus according to the present invention is an apparatus that uses four bearings having holding portions connected by rods, supports the main shaft rotatably with these four bearings, and performs a load application test. The four bearings are arranged so that the two inner bearings and the two outer bearings are located on opposite sides of the main shaft.

  According to FIG. 14, if the main shaft is rotated in the same direction with respect to two bearings having the same shape and the same load in the same direction is applied, the center positions of the main shaft and the two bearings are the same according to the fluid lubrication theory. It becomes. If the main shaft is rotated in the same direction with respect to two bearings having the same shape and the same load is applied in the opposite direction, the center positions of the two bearings are shifted. In the bearing test apparatus according to the present invention, the main shaft is rotated in the same direction and the same load in the same direction is applied to the two inner bearings or the two outer bearings. Since the mounting directions of the bearings and the two outer bearings are opposite, the load application directions for the two inner bearings and the two outer bearings are reversed. For this reason, the axial center position of an inner side bearing and an outer side bearing shifts (refer to Drawing 15 (a) and (c)). At this time, if all four bearings are constrained to the same position on a plane perpendicular to the main shaft (XY plane when the main shaft axis is the Z axis), a load other than the axial direction of the rod between the main shaft and the bearing (See FIGS. 15B and 15D), the friction becomes very large. On the other hand, in the present invention, the positions of the two inner bearings (bearing housings) or the two outer bearings (bearing housings) are constrained in the direction perpendicular to the load direction, and the other two bearings. Since the (bearing housing) is unconstrained, it becomes simply a compressive load or a tensile load in the axial direction of the rod, and friction measurement can be performed while suppressing an increase in friction.

Next, a specific embodiment of the bearing test apparatus according to the present invention will be described with reference to the bearing test apparatus shown in FIG. The bearing test apparatus shown in FIG. 1 is an improvement of the above-described conventional test apparatus (3). In the following description, the horizontal direction and the vertical direction in FIG. 1 are defined as the horizontal direction and the vertical direction of the bearing test apparatus. Further, the front side and the back side in FIG. 1 are defined as the front side and the rear side of the bearing test apparatus, respectively.
The bearing test apparatus 1 includes a drive unit 10 and a bearing test unit 20 that are mounted on the base 2, and a clutch 60 that switches the drive unit 10 and the bearing test unit 20 between a connected state and a non-connected state. . For example, an Oldham type joint is used for the clutch 60.
The drive unit 10 is mounted on a slide mechanism 11 and includes a drive shaft 12 and a motor 14 that rotationally drives the drive shaft 12 via a speed change mechanism 13.

The bearing test unit 20 includes a frame 21 fixed on the base 2, a main shaft 22 rotatably supported by the frame 21, a rotation angle detection unit 23 that detects a rotation angle of the main shaft 22, and a main shaft 22. A first disc 24 and a second disc 25 attached, and a positioning plate 26 are provided. The main shaft 22 is connected to the drive shaft 12 by the clutch 60.
The first disc 24 and the second disc 25 are respectively fixed to portions of the main shaft 22 that protrude from the left and right sides of the frame 21 by a pair of fasteners 27.

The rotation angle detection unit 23 includes a slit disk 28 attached to the left end of the main shaft 22 and a rotation angle sensor 29 that detects the rotation angle position of the slit disk 28.
The left end of the main shaft 22 is processed into a conical shape or a spherical shape (see FIG. 4), and is in point contact with the positioning plate 26. When the tip of the main shaft 22 makes point contact with the positioning plate 26, the slit disk 28 is positioned with respect to the rotation angle sensor 29 in the rotation angle detector 23. The drive unit 10 is moved by the slide mechanism 11 when the clutch is disengaged, and an axial force is generated on the main shaft 22 by friction of the clutch groove. In order to prevent contact between the rotation angle sensor 29 and the slit disk 28, it is necessary that the tip of the main shaft 22 is not separated from the positioning plate 26. The main shaft 22 is slightly lower on the positioning plate 26 side, and on the clutch side. And the left end of the main shaft 22 is pressed against the positioning plate 26 by gravity.

  A bearing 30 (hereinafter referred to as “test bearing”) 30 used for the test is attached to the main shaft 22. The main feature of the bearing test apparatus 1 of the present invention is the structure of the bearing test section 20. In the bearing test unit 20, a load is applied between the main shaft 22 and the test bearing 30, which must be during rotation of the main shaft 22. This is because, in a slide bearing, when the main shaft 22 rotates, the oil film pressure generated in the gap between the main shaft 22 and the test bearing 30 prevents direct contact between the main shaft 22 and the test bearing 30. This is because the surface is prevented from being damaged. Further, in the rolling bearing, the roller and the inner and outer rings are prevented from being permanently deformed by the oil film pressure generated around the rollers and between the inner and outer rings when the main shaft 22 rotates. Therefore, in this test apparatus, the operation is started with no load of 0, and the target load is adjusted while rotating at 1000 rpm. Hereinafter, specific examples of the bearing test unit 20 will be described in detail.

FIG. 2 shows a configuration of the bearing test unit 20 according to the first embodiment. 2A, 2B, and 2C are a plan view, a front view, and a side view of the bearing test section 20, respectively.
As shown in FIG. 2, two load shafts 34 perpendicular to the main shaft 22 are fixed between the two front frames 21 and the two rear frames 21. The load shaft 34 corresponds to the load applying means of the present invention. Two of the four load shafts 34 are located higher than the main shaft 22, and the remaining two are located lower than the main shaft 22. Load plates 51 are attached to the two left load shafts 34 and the right two load shafts 34, respectively. One bearing holding shaft 32 parallel to the main shaft is fixed between the load plates 51 and between the two front frames 21. The two bearing holding shafts 32 are on the front side and the rear side of the main shaft 22, and both are positioned at the same height as the main shaft 22.

  Two through holes perpendicular to the mounting direction of the bearing holding shaft 32 are formed in the load plate 51, and the load shaft 34 is inserted through each of the two through holes. Both ends of the load shaft 34 are fixed to the frame 21, respectively. A screw (not shown; a trapezoidal screw is used) is formed on the outer periphery of the load shaft 34 to form a male screw, and the mounting position of the load plate 51 with respect to the load shaft 34 can be moved by the nut 52. The load plate 51 and the frame 21 correspond to the fastening means of the present invention.

  The main shaft 22 is rotatably supported by four test bearings 30. As shown in FIG. 3, the test bearing 30 has a holding portion 45 connected by a rod 41. The test bearing 30 includes a bearing housing 42 and a bearing metal 43 held by the bearing housing 42. The main shaft 22 is supported by a bearing metal 43 of each test bearing 30. The holding part 45 has a bush 44. In this embodiment, the large-end bearing of the connecting rod (hereinafter referred to as “connecting rod”) of the engine is used as the test bearing 30, and the small-end bearing is used as the holding portion 45.

  As shown in FIGS. 2A to 2C, the four test bearings 30 are arranged symmetrically on both sides with a predetermined position of the main shaft 22 interposed therebetween. Among them, one of the two bearing holding shafts 32 (the front bearing holding shaft 32 in FIG. 2) is inserted into the bush 44 of the holding portion 45 of the two inner test bearings 30. The remaining bearing holding shaft 32 (the rear bearing holding shaft 32 in FIG. 2) is inserted into the bush 44 of the holding portion 45 of the outer test bearing 30. With such a configuration, the test bearing 30 is supported by the bearing holding shaft 32 inserted through the holding portion 45.

  2A and 2D, spacers 321 are inserted between the two holding portions 45 of the front bearing holding shaft 32 and between the holding portions 45 and the frame 21, respectively. ing. In addition, spacers 322 are inserted between the two holding portions 45 of the rear bearing holding shaft 32 and between the holding portions 45 and the frame 21. The spacers 321 and 322 respectively have two holding portions 45 on the front side and two holding portions 45 on the rear side at predetermined positions of the bearing holding shaft 32 (in this embodiment, bearing holding positions between the frames 21). This is for arranging at a symmetrical position with respect to the middle point of the shaft 32. Thereby, in this embodiment, four test bearings 30 are arranged symmetrically on both sides of a predetermined point on the main shaft 22. Accordingly, the spacers 321 and 322 function as positioning means of the present invention.

  As shown in FIGS. 2 and 3, vertical position restraining plates 53 are arranged above and below the inner two test bearings 30 among the four test bearings 30. The two upper and lower position restricting plates 53 are connected by bolts (not shown). The vertical position restraint plates 53 are disposed above and below the bearing housing 42 of the two inner test bearings 30. The opposing surfaces of the outer surface of the bearing housing 42 and the upper and lower position restraining plates 53 facing the bearing housing 42 are smooth polished surfaces. By lubricating these surfaces, the test bearing 30 is moved in the axial direction of the rod 41. Slips and is restrained in the direction perpendicular to the rod 41. Thereby, a load can be applied. In the first embodiment, the bearing housing 42 is movable in the rod direction. However, in the second embodiment, which will be described later, four load plates 51 are arranged symmetrically in the front-rear direction with the main shaft 22 as the center. Also fixed. In the third embodiment, as in the first embodiment, the bearing housing 42 is movable in the rod direction.

  Note that the load applied to the bearing 30 is generated by moving the load plate 51 along the load shaft 34 with the nut 52. Specifically, when the nut 52 on the front side of the load plate 51 is tightened and the rear nut 52 is loosened and the load plate 51 is moved to the rear side, a tensile load is generated, and the nut 52 on the rear side of the load plate 51 is tightened. When the front nut 52 is loosened and the load plate 51 is moved to the front side, a compressive load is generated. That is, in this embodiment, the load plate 51, the nut 52, and the load shaft 34 function as a load applying unit. When a load is applied to the test bearing 30, the shaft center position of the test bearing 30 changes and the test bearing 30 is elastically deformed, so that the bearing housing 42 of the test bearing 30 moves slightly in the rod direction. . Further, the bearing housing 42, the rod 41, the bearing metal 43, the holding portion 45, and the bush 44 are all elastically deformed. Therefore, in this embodiment, a strain gauge is affixed on the rod 41 of the test bearing 30, and the strain gauge measuring instrument is verified against the load, and the load applied to the test bearing 30 is obtained from the signal of the strain gauge measuring instrument. ing.

  In this embodiment, both end portions of the load shaft 34 are male threads and are fixed to the frame 21 by nuts 18. Therefore, the load shaft 34 can be moved in the axial direction by tightening the nut 18. Therefore, in the present embodiment, the load shaft 34, the nut 18 and the frame 21 also function as load applying means. When it is difficult to adjust the load with the nut 52 during the experiment (when the main shaft 22 rotates), the four nuts 52 are tightened to fix the load plate 51 to the load shaft 34 and the nut 18 is tightened. The load is adjusted by moving the load shaft 34 in the axial direction. As described above, in this embodiment, since both the mounting position of the load plate 51 with respect to the load shaft 34 and the mounting position of the load shaft 34 with respect to the frame 21 can be changed, the degree of freedom of load adjustment is increased.

  Since the bearing metal mounting surfaces of the two test bearings 30 to be restrained are on the same cylinder, the upper and lower surfaces of the bearing housing 42 are based on the mounting surface of the bearing metal 43 or the inner peripheral surface of the bearing metal 43. In addition, the clearance between the main shaft 22 and the bearing metal 43 is processed with sufficiently high accuracy so that the parallelism between the surface of the main shaft 22 and the surface of the bearing metal 43 is not affected. Thereby, the main shaft 22 can be arranged in a state where there is no inclination with respect to the inner peripheral surface of the bearing metal 43 of the two test bearings 30 to be restrained.

The experiment is performed with sufficient lubrication between the bearing metal 43 of the test bearing 30 and the main shaft 22. Further, the clearance between the bearing metal 43 and the main shaft 22 is set according to the application machine of the test bearing 30. In the present specification, the bearing refers to a bearing housing having a bearing metal inserted therein or a bearing housing having a bush inserted therein. In a bearing without the bearing metal 43 and the bush 44, the bearing housing 42 and the holding portion 45 are not provided. The inner surface corresponds to a bearing.
In a 2-stroke cycle engine, a rolling bearing may be used for the connecting rod. Also in this case, a bearing test can be performed in the same manner as a connecting rod using a sliding bearing. In this case, a rolling bearing including an inner ring, a roller, and an outer ring corresponds to the bearing metal 43.

  FIG. 4 is an enlarged view of the main shaft 22. As described above, the tip of the main shaft 22 is processed into a conical shape, and is a pointed tip at the center of the shaft. The main shaft 22 is positioned when the tip of the main shaft 22 comes into contact with the positioning plate 26. However, when the tip of the main shaft 22 is used as a pointed tip, so as to handle the thrust load, the pointed end of the main shaft 22 and the positioning plate 26 are positioned. The moment of force (axial torque) due to the friction generated between them becomes almost zero, and the influence of the friction generated in this portion can be extremely reduced.

In addition, although the point contact is desirable for the contact between the sharp tip of the main shaft 22 and the positioning plate 26, when the thrust load is large, the sharp tip of the main shaft 22 and the positioning plate 26 may be in surface contact. At this time, it is preferable that the contact surface of the pointed tip with the positioning plate 26 is 10% or less of the diameter of the main shaft 22. In addition to the conical shape as shown in FIG. 4 (a), the shape of the pointed tip of the main shaft 22 is a conical top as shown in FIG. 4 (b) or a conical shape as shown in (c). The top of the shape may be a cone having a larger cone angle than the top. By doing in this way, the intensity | strength of the pointed end of the main axis | shaft 22 can be improved. In order to increase the concentricity between the sharp tip of the main shaft 22 and the main shaft 22, it is preferable to directly process the end of the main shaft 22, but a spherical or conical member formed separately from the main shaft 22 is used as the main shaft. You may attach to the edge part of 22. FIG.

  When the load applied to the test bearing 30 is a dynamic load, the axial center position of the main shaft 22 moves. Therefore, when the tip of the main shaft 22 has a spherical shape, the major axis has an elliptical shape that is long in the radial direction of the main shaft 22. . When the tip of the main shaft 22 is conical, the cone angle is set to 120 ° to 170 °. In this way, when oil is applied to the tip of the main shaft 22, oil film is easily generated by the movement of the main shaft 22, and the influence of the movement of the shaft on the friction measurement can be reduced. The diameter of the tip-shaped portion of the main shaft 22 (cylindrical portions (b) and (c)) is adjusted to about 10 to 30% of the diameter of the main shaft 22 in accordance with the purpose in order to reduce friction and secure strength. It is desirable.

  FIG. 5A shows a cross-sectional view of the holding portion 45 of each test bearing 30. In the present embodiment, the inner surface of the bush 44 held by the holding portion 45 is tapered so as to taper toward the center in the bush 44, and is configured to contact the bearing holding shaft 32 at the tip thereof. Yes. In addition, although the process which makes the inner surface of the bush 44 taper-shaped may be performed about all the four test bearings 30, it may be performed only for two inside or only two outside.

  Thus, by processing the inner surface of the bush 44 into a tapered shape, even if the bearing holding shaft 32 is inserted in the bush 44 with almost no play, the contact area between the two can be reduced. For this reason, there is a degree of freedom in the inclination of the shaft between the bearing holding shaft 32 and the inner surface of the bush 44, and the bearing housing 42 and the bearing metal 43 follow the surface of the main shaft 22, and misalignment is eliminated. Even if the main shaft moves by applying a load, it is possible to prevent misalignment from occurring between the four bearings. Further, the friction generated between the bush 44 and the bearing holding shaft 32 can be reduced.

When the inner surface of the bush 44 is processed into a tapered shape, as shown in FIG. 5B, a slight parallel portion may be left in the center of the tapered portion. Further, instead of the inner surface of the bush 44 being tapered, the cross section may be a curved surface having a circular arc shape (FIG. 5C). Further, the outer surface of the bearing holding shaft 32 is tapered ((d) in FIG. 5), a slight parallel part is left in the center of the tapered part ((e) in FIG. 5), or the cross section is arcuate ( The same effect can be obtained by changing to (f) in FIG. Here, the taper angles shown in FIGS. 5A, 5B, 5D, and 5E are drawn larger than actual. The actual taper angle is geometrically determined by the width of the bush 44, the gap between the bush 44 and the bearing holding shaft 32, the length of the test bearing 30, and the parallelism between the main shaft 22 and the bearing holding shaft 32. It is done. For example, the angle of the inner surface of the bush 44 used in the bearing test apparatus 1 according to the present embodiment is preferably as small as about 3 °. In addition, even when the inner surface of the bush 44 has an arcuate cross section as shown in FIGS. 5C and 5F, the geometrically determined radius of curvature is such that the curved surface cannot be visually recognized. Enlarge.
Some connecting rods or the like do not have a bush 44. In this case, the processing performed on the inner surface of the bush 44 as described above is performed on the inner surface of the holding portion 45.

Next, a load calculation formula for attaching a load measurement sensor (strain gauge) to the bearing test unit 20 will be described. In the following formulas, F1, F2, F3, and F4 indicate forces corresponding to loads applied to the respective test bearings 30 (see FIG. 6).
The two formulas shown in the following “Equation 1” are formulas showing balance of force balance and balance of moment of force, and represent the relationship between F1, F2, F3, and F4. As can be seen from “Expression 1”, when any two of F1, F2, F3, and F4 are determined, the other two are determined depending on each other. Further, from the arrangement of the four test bearings 30, if any two of F1, F2, F3, and F4 are equal, F1 = F2 = F3 = F4.

  Since this bearing test apparatus uses four bearings of the same standard and measures the friction under the same conditions to examine the lubrication state per bearing, if the load on the four bearings is different, the test apparatus cannot be established. Therefore, in order to establish the test apparatus, the position of the load plate 51 may be adjusted while measuring so that any two loads out of the four test bearings are equal.

  However, even if the positions of the two load plates 51 are adjusted in the same way, the way of changing the load at that time is different. Therefore, from the relationship among F1, F2, F3, and F4, it is estimated which of the four test bearings should be adjusted while performing load measurement. Based on “Equation 1”, two equations in “Equation 2” are expressed by F1 and F4 as F2 and F3, and two equations in “Equation 3” are expressed in F2 and F3 by F1 and F4. Similarly, the two equations in “Equation 4” represent the errors of F1 and F4 by the errors of F2 and F3, and the two equations of “Equation 5” represent the errors of F2 and F3 by the errors of F1 and F4. is there.

  From the above equation, the change in F2 and F3 indicating the load on the inner bearing of the test bearing 30 is greater than the change in F1 and F4 indicating the load on the outer bearing, and the load is set by measuring F2 and F3. It can be seen that there is the least error. Therefore, in this embodiment, strain gauges as load measuring sensors are attached to the rods 41 of the two inner test bearings 30 to measure the output against the bearing load.

  Further, the bearing holding shaft 32 that supports the inner test bearing 30 generates a larger bending moment and the stress is larger than the bearing holding shaft 32 that supports the outer test bearing 30. Therefore, the material of the bearing holding shaft 32 that supports the inner test bearing 30 may be a material having higher rigidity than the bearing holding shaft 32 that supports the outer test bearing 30. Here, a hardened S50C, which is known as a hard material, is used for the structural carbon steel for shafts.

FIG. 7 shows the clutch 60 according to the present embodiment. The clutch 60 is made up of a so-called Oldham type shaft joint, and includes a first grooved disk 61 fixed to the end of the drive shaft 12, a second grooved disk 62 fixed to the end of the main shaft 22, and these grooved disks. A floating cam 63 is provided between 61 and 62. Grooves 611 and 621 passing through the shaft centers of the drive shaft 12 and the main shaft 22 are formed on the surfaces of the first groove disk 61 and the second groove disk 62 facing the floating cam 63, respectively. On the other hand, protrusions 631 corresponding to the grooves 611 and 621 are formed on the surface of the floating cam 63 facing the first groove disk 61 and the second groove disk 62, respectively.
With such a configuration, even if the positions of the four test bearings 30 are shifted due to the load and the axial positions of the main shaft 22 and the drive shaft 12 are different, the connection state of the main shaft 22 and the drive shaft 12 can be maintained. it can.

  A long guide hole 64 is formed in the floating cam 63, and a bolt (male screw) 65 having a wide head is inserted into the long guide hole 64. The first grooved disc 61 is formed with a screw hole (female screw) 61a. By screwing a bolt (male screw) 65 into the screw hole 61a, the floating cam 63 is inserted into the first grooved disc 61 with the bolt 65. It is attached so as not to leave. Since the guide long hole 64 is movable along the bolt 65, the movement of the floating cam 63 is not hindered. When the drive unit 10 is moved away from the bearing test unit 20 by the slide mechanism 11, the clutch is disengaged and the connection state between the main shaft 22 and the drive shaft 12 is released. As shown in FIG. 7, the combination of the first grooved disc 61 and the drive shaft 12, the second grooved disc 62 and the main shaft 22 is such that the floating cam 63 is separated from the main shaft 22 during the bearing friction measurement test after the clutch is disengaged. The drive shaft 12 side is preferable. If the vibration of the floating cam 63 can be ignored, the first groove disk 61 and the main shaft 22 and the second groove disk 62 and the drive shaft 12 may be combined.

  FIG. 8 shows an example of a measurement result using the bearing test apparatus 1 having the above configuration. This result shows the relationship between the friction coefficient μ per test bearing and the Sommerfeld number S when a tensile load and a compressive load are applied to the test bearing 30. The experimental conditions were a load of 3000 [N] per bearing, a bearing diameter of 40 [mm], a width of 13.5 [mm], an oil viscosity of 0.0582 [Pas], and a deceleration from 1500 [rpm].

FIG. 9 shows a configuration of a part (bearing test unit) of the bearing test unit 20 according to the second embodiment of the present invention. In this embodiment, the holding portions 45 of the two inner test bearings 30 are provided on the rear bearing holding shaft 32, and the holding portions 45 of the two outer test bearings 30 are provided on the front bearing holding shaft 32. Is attached. Although not shown in FIG. 9, as in the first embodiment, in this embodiment, the inner two holding portions 45 and the outer two holding portions 45 are positioned symmetrically with a predetermined position sandwiched by spacers. It is positioned.
In this embodiment, the compression load by the screw and the tensile load by the hydraulic piston are combined and applied to the test bearing 30. The load can be varied by controlling the hydraulic piston. In this embodiment, the load shaft spring 71 is attached to the load shaft 34 with a nut 52.

  The four load shafts 34 inserted through the through holes of the four load plates 51 are fixed to the load plate 51 with nuts 52 with load shaft springs 71 sandwiched between the load plates 51. In addition, a hydraulic cylinder 73 is assembled to the load plate 51 in pairs with the load shaft 34. The four hydraulic cylinders 73 are connected in parallel.

FIG. 10 shows a state in which a part of the bearing test unit shown in FIG. The bearing test unit is assembled to the frame 21 by four load shafts 34.
The four load shafts 34 are fitted in the four through holes of the frame 21 and are movable in the axial direction. Of the test bearings 30, the two inner test bearings are restrained by a vertical position restraint plate 53. In this embodiment, the two inner test bearings 30 are constrained in both a direction parallel to the rod 41 and a direction perpendicular thereto. The vertical position restricting plate 53 is fixed to the base 2 by legs 78 .
In this embodiment, a compressive load can be applied by tightening the nut 52. This is the maximum compressive load. Next, the same hydraulic pressure is applied to the four hydraulic cylinders 73 to apply a tensile load. The tensile load is the hydraulic load minus the compressive load caused by tightening the nut 52. When the hydraulic pressure is dynamically applied, a variable load equal to the four test bearings 30 is generated.

FIG. 11 shows the basic structure which is the same as that of the bearing test section 20 of the first embodiment, but is modified with a variable load as a target. In this embodiment, a compression load is generated by a spring 81 and a cam 82 instead of the hydraulic cylinder of the second embodiment. In order to equalize the load of the two left and right test bearings 30 that form a pair inside or outside, the load plate 51, the joining plate 85, and the two arms are connected to the connection of the spring 81 and the two load plates 51. A truss mechanism 84 in which 842 is coupled by three pins 841 is used. The truss mechanism 84 by the coupling of the pins 841 is used to distribute the load evenly to the two load plates 51 by using the pin coupling that does not have rotational constraints and does not generate a moment of force in the support portion, and the same bearing. This is because the load is not biased to one of the bearings in which the holding portion 45 is attached to the holding shaft 32. A load shaft spring 71 is attached to the load shaft 34 of the bearing test section 20 and tightened with a nut 52 to apply a tensile load to the bearing. Here, there are only four nuts 52 on the tensile load side, and there are no four nuts on the compression load side as shown in the first embodiment.

The cam 82 is joined to the cam shaft 83 as one body, and is attached to the frame 21 so as to be rotatable about the cam shaft 83. The load plate 51 is attached to one end of a spring 81 via a truss mechanism 84 in which a joining plate 85 and two arms 842 are coupled by three pins 841, and the other end of the spring 81 is in contact with the cam 82. Yes. With such a configuration, if the cam 82 is rotated via the cam shaft 83, the compressive load applied to the load plate 51 through the spring 81 can be varied. The compressive load is a value obtained by subtracting the tensile load closed by the nut 52 from the contracted load of the spring 81. A large torque is required for the rotation of the cam 82. The cam 82 may be rotated by a motor. Further, the spring 81 may be displaced by a method such as a hydraulic piston instead of the cam 82.

  Further, the load shaft spring 71 and the nut 52, the cam shaft 83, the cam 82, and the truss mechanism 84 of the load shaft 34 are disposed on the left and right sides opposite to the load plate 51, and the compression load is applied by the load shaft spring 71 and the nut 52. It is also possible to apply a tensile load with the cam shaft 83, the cam 82 and the truss mechanism 84. However, in this case, the tensile load generating mechanism must be moved to a position higher or lower than the mounting position of the bearing, and the configuration becomes complicated.

In Examples 1 to 3 described above, an example is shown in which the inner test bearing of the test bearing 30 is restrained by the vertical position restraint plate 53. Even if the outer test bearing is restrained, the same functions and effects are obtained. can get. The positions of the holding portion 45 of the two outer test bearings 30 and the holding portion 45 of the two inner test bearings 30 are either one on the front bearing holding shaft 32 and the other on the rear. What is necessary is just to attach to the bearing holding shaft 32 of the side. Further, the first disk 24 and the second disk 25 may be anywhere as long as they are arranged symmetrically. Moreover, if it arrange | positions symmetrically, two or more discs may be sufficient, and when arrange | positioning in the center, one disc may be sufficient.
Further, the first disc 24 and the second disc 25 may be omitted in a test that does not require the moment of inertia, such as a test that is performed while the clutch 60 is engaged, for example, a durability test.

  FIG. 12 shows a fourth embodiment of the present invention. This embodiment is characterized in that a load is applied while suppressing displacement of the main shaft.

  In this embodiment, a double screw load shaft 171 is used instead of the load shaft 34, and a handle 174 is attached to the end of the double screw load shaft 171. When the handle 174 is rotated clockwise, both screw load shafts 171 rotate clockwise and the right screw load plate 191 moves outward (to the left). Thereby, the inner two test bearings 30 move leftward. At the same time, the left screw load plate 192 moves to the right, thereby moving the two outer test bearings 30 to the right. As a result, a tensile load is applied to the four test bearings 30.

  On the other hand, when the handle 174 is turned counterclockwise, both screw load shafts 171 rotate counterclockwise, the right screw load plate 191 moves inward (rightward), and the left screw load plate 192 moves outward (leftward). . As a result, the two inner test bearings 30 move inward (rightward), and the two outer test bearings 30 move outward (leftward). As a result, a compressive load is applied to the four test bearings 30.

  It should be noted that both screw load shafts 171 only need to have a right-hand screw and a left-hand screw, respectively, and the positions thereof may be on either the left side or the right side. In this case, the positions of the right screw load plate 191 and the left screw load plate 192 must coincide with the screw directions of the both screw load shafts 171.

  Instead of the handle 174, a motor may be used. A high torque is required for the motor, but this can be realized by using a reduction motor, a stepping motor with a high reduction ratio, a hydraulic swing motor, or the like. When a highly accurate motor is used, the test can be performed while applying a dynamic load.

FIG. 13 shows a bearing test section 20 according to Embodiment 5 of the present invention. FIGS. 13A to 13C correspond to FIGS. 2A to 2C, and are a top view, a front view, and a side view, respectively, of the bearing test unit 20. FIG.
The bearing test section 20 of the fifth embodiment has the same basic structure as the bearing test section 20 (see FIG. 2) of the first embodiment, but the configuration of the bearing holding shafts (first and second holding shafts) is the embodiment. Different from 1. That is, in this embodiment, different bearing holding shafts 132 are inserted into the holding portions 45 of the four test bearings 30.

  Specifically, a first holding plate 133 is spanned between the two front frames 21, and two U-shaped shaft holding portions 134 (FIG. 18) are placed on the first holding plate 133. Reference) is fixed. The bearing holding shafts 132 that are inserted through the bushes 44 of the holding portions 45 of the two test bearings 30 on the inner side among the four test bearings 30 are respectively attached to the two shaft holding portions 134. .

  A second holding plate 135 is stretched over the left and right load plates 51, and two U-shaped shaft holding portions 136 (see FIG. 18) are fixed to the second holding plate 135. . The bearing holding shafts 132 that are inserted into the bushes 44 of the holding portions 45 of the two outer test bearings 30 of the four test bearings 30 are respectively attached to the two shaft holding portions 136. .

With such a configuration, also in this embodiment, the load applied to the test bearing 30 can be adjusted by adjusting the mounting position of the load plate 51 and the mounting position of the load shaft 34 with respect to the frame.
Furthermore, in this embodiment, since the bearing holding shafts 132 are inserted into the holding portions 45 of the four test bearings 30, even if the four test bearings 30 are different in size, The test can be performed using the shaft holding portion and the bearing holding shaft having the optimum size and shape. Further, in the bearing test apparatus of the present embodiment, a load measuring sensor (strain gauge) is attached to the shaft holding portions 134 and 136 (note that the shaft holding portions 134 and 136 may be anywhere, but in FIG. It is preferable to affix to the shaft member shown.), The load of each test bearing 30 can be measured. If a load measurement sensor (strain gauge) is attached to the rod part of the bearing, the load signal must be verified with a load meter each time the bearing is changed, but the load measurement sensor is attached to the shaft holder. In this case, if the strain signal is verified once with a load meter, the load can be obtained even if the bearing is changed.

  In each of the above-described embodiments, the case where the large-end bearing of the connecting rod is used as the test bearing has been described as an example, but the small-end bearing may be used as the test bearing. Further, in the case of a component having only one bearing, the bearing test apparatus according to the present invention can be provided by connecting a holding portion to the bearing via a rod.

  Furthermore, in the above embodiment, the connecting rod generally used in the engine has been described as an example. However, the bearing test apparatus according to the present invention is a general-purpose test apparatus that can be used in the entire field of tribology (friction, wear, lubrication). It is. Therefore, the bearing test apparatus according to the present invention can be used for measuring friction and the like of various bearings from a micro bearing used as a part of a personal computer to a large bearing used in a construction structure (movable bridge). it can.

DESCRIPTION OF SYMBOLS 1 ... Bearing test apparatus 2 ... Base stand 10 ... Drive part 11 ... Slide mechanism 12 ... Drive shaft 13 ... Transmission mechanism 14 ... Motor 20 ... Bearing test part 21 ... Frame 22 ... Main shaft 23 ... Rotation angle detection part 24 ... 1st circle Plate 25 ... Second disc 26 ... Positioning plate 27 ... Fitting tool 28 ... Slit disc 29 ... Rotation angle sensor 30 ... Test bearing 32 ... Bearing holding shaft 321 and 322 ... Spacer 34 ... Load shaft 41 ... Rod 42 ... Bearing Housing 43 ... Bearing metal 44 ... Bush 45 ... Holding part 51 ... Load plate 53 ... Vertical position restraining plate 60 ... Clutch 61 ... First groove disk 62 ... Second groove disk 63 ... Floating cam 132 ... Bearing holding shaft 133 ... First holding plates 134, 136 ... shaft holding portion 135 ... second holding plate 171 ... double screw load shaft 174 ... handle 191 ... right screw load plate 192 ... left screw load plate 220 ... Bundle means

Claims (8)

a) one main shaft rotatably supported by four bearings;
b) two first holding portions respectively connected to two outer bearings among the four bearings via rods;
c) Two second holdings arranged on the opposite sides of the first holding part and the main shaft and connected to two bearings located on the inner side among the four bearings via rods, respectively. And
d) load applying means for applying a load to the bearing by changing a separation distance between the first holding portion and the second holding portion;
e) a drive mechanism for applying rotational torque to the main shaft;
A bearing test apparatus comprising: The bearing test apparatus according to claim 1,
A bearing test apparatus comprising restraining means for restricting movement of two inner bearings or two outer bearings of the four bearings in a direction perpendicular to the main shaft and perpendicular to the rod. In the bearing test apparatus according to claim 1 or 2,
A connection transmission mechanism for connecting the load applying means to the first holding portion and the second holding portion;
The load applying means changes a separation distance between the first holding part and the second holding part via the connection transmission mechanism. The bearing test apparatus according to claim 3,
The load applying means comprises a load shaft;
Fastening means for attaching the connection transmission mechanism to the load shaft;
The bearing test apparatus, wherein the load applying means applies a load to the bearing based on a change in distance of the fastening means. The bearing test apparatus according to claim 3,
It said load applying means, a bearing testing apparatus, characterized in that it comprises a pressure piston for changing the distance of the second holding portion and the first holding portion via the coupling transmission mechanism. The bearing test apparatus according to claim 3,
The load applying means includes a biasing means that biases the first holding part and the second holding part in a direction in which the separation distance is close or in a direction in which the first holding part and the second holding part are close to each other via the connection transmission mechanism. Test equipment. In the bearing test device according to any one of claims 1 to 6,
The load applying means includes a pair of both screw shafts connecting the first holding portion and the second holding portion, and operating means for rotating the screw shafts in forward and reverse directions. bearing test device the first holding portion and the second holding portion by rotating the two screw shafts in the forward and reverse directions, characterized in that the proximity or separated. In the bearing test apparatus according to any one of claims 3 to 7,
The connection transmission mechanism includes one or a plurality of first holding shafts inserted through the first holding unit, and one or a plurality of second holding shafts inserted through the second holding unit. Bearing test equipment.

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