JP5172445B2 - Thrust bearing rotational torque detector - Google Patents

Description

  The present invention relates to a test apparatus for measuring the rotational torque of a thrust bearing, and more particularly to a technique for reproducing an offset load close to an actual load condition applied to a thrust bearing such as a compressor.

  As an evaluation of the rotational torque of the thrust bearing, until now, a uniform thrust load was applied to the raceway ring of the test thrust bearing to detect the rotational torque. An apparatus as shown in FIG. 10 is known as a conventional general thrust bearing rotational torque detection apparatus that applies such a uniform load. This apparatus includes a rotating member A, a torque detecting member B facing the rotating member A, and a mechanism C that applies a load to the torque detecting member B. The torque detection member B has means G for detecting the rotational torque of the test thrust bearing S attached between the rotation member A and the torque detection member B. Then, one and the other of the race rings of the test thrust bearing S are attached to the rotating member A and the torque detecting member B, respectively, and the rotating member A is rotated in the direction of the arrow and a thrust load indicated by the arrow is given. Thus, the rotational torque of the thrust bearing S is detected. According to this apparatus, it is possible to measure the rotational torque of the thrust bearing S by applying a load with uniform contact stress of the raceway in the axial direction.

  On the other hand, the usage methods of thrust bearings have also been diversified, and in fact, in many cases, uneven loads with different contact stresses are applied to the thrust bearings.

  Conventionally, as a test apparatus for imparting such a biased load to a test thrust bearing, for example, one described in Japanese Patent Application Laid-Open No. 2003-120664 (Patent Document 1) is known.

In the test apparatus described in Patent Document 1, the load transmission member is provided at a position eccentric from the axis of the rotation main shaft, and an eccentric load is applied to the thrust trace of the test thrust bearing via the load transmission member. This is to test the rotation performance.
JP 2003-120664 A

  However, the conventional test apparatus has the following problems. That is, in the test apparatus described in Patent Document 1, since it is necessary to interpose a load transmission member at a specific position in the circumferential direction, the number of parts and the number of assembly steps increase. Further, the rotational torque could not be detected.

  Further, in the conventional general test apparatus as shown in FIG. 10, since the mechanism C uses static pressure air, the rotation balance of the static pressure air is not lost while applying a uniform load, A stable rotational torque can be detected. However, if the mechanism C applies an unbalanced load, the rotational balance of the static pressure air is lost, and stable rotational torque cannot be detected. In addition, when the uneven load is large, the air in the static pressure portion may be crushed and it may be difficult to detect the rotational torque.

  In view of the above-described circumstances, the present invention is capable of applying an actual machine load applied to a thrust bearing such as a compressor without increasing the number of assembly steps, and capable of detecting a stable rotational torque. The object is to propose a detection device.

For this purpose, the thrust bearing rotational torque detection device according to the present invention is based on the thrust bearing rotational torque detection device that detects the rotational torque of the test thrust bearing, and is connected to one end side of the rotational shaft and rotates together with the rotational shaft. A first rotating member for contacting with one side of the first thrust bearing to apply a thrust load; and connected to the other end side of the rotating shaft so as to be capable of axial stroke and rotating together with the rotating shaft; It is a disk shape provided with the 2nd rotating member for giving a thrust load in contact with one side, and the center hole which a rotating shaft penetrates, and is arranged between the 1st rotating member and the 2nd rotating member. The end surface on the side facing the first rotating member has a seat surface for applying a thrust load by contacting the other side of the first thrust bearing, and the second end surface on the side facing the second rotating member. Thrust shaft An intermediate member having a seating surface for applying a thrust load in contact with the other side, and the load imparting mechanism that imparts an axial load to the second rotary member, is coupled with the intermediate member, said first thrust bearing And a means for detecting rotational torque input to the intermediate member from the second thrust bearing, and an axial thickness between the seat surface on the first rotating member side and the seat surface on the second rotating member side of the intermediate member There, Ru different in one of the site and the other sites.

  According to the present invention, by appropriately selecting the uneven shape of the seating surface, it is possible to apply various uneven loads to the test thrust bearing, and it is possible to reproduce the uneven load close to the actual load condition. . In addition, it is possible to apply a thrust load having a different contact stress in the radial direction to the test thrust bearing, and it is possible to detect the rotational torque in consideration of the deflection and misalignment of the thrust bearing. In addition, since the load application mechanism itself is not a structure that applies an offset load, the rotation balance is not lost, and stable rotation torque can be detected. Moreover, since it is not necessary to use a load transmission member separately, it is possible to detect a stable rotational torque while avoiding an increase in the number of assembly steps. Further, since the rotational torques of the two thrust bearings are detected at the same time, the rotational balance is good even when an unbalanced load is applied, stable rotational torque can be detected, and detection accuracy is improved.

  When the pair of bearing rings arranged on both sides of the thrust bearing is composed of a front bearing ring and a rear bearing ring having different shapes, the first and second thrusts are included in the thrust bearing rotational torque detector as described below. A bearing is recommended. That is, the seat surface on the first rotating member side of the intermediate member is for contacting and fixing the back raceway of the first thrust bearing, and the seat surface on the second rotating member side of the intermediate member is This is for contacting and fixing the rear raceway ring of the second thrust bearing. According to this embodiment, since one intermediate member contacts the back raceway of two thrust bearings, it becomes possible to arrange the two thrust bearings back to back, and the first thrust bearing and A stable rotational torque can be detected while avoiding the collapse of the axial load balance with the second thrust bearing, and the detection accuracy is improved.

  The intermediate member is not limited to one embodiment, and the axial thickness between the seating surface on the first rotating member side and the seating surface on the second rotating member side of the intermediate member is the same in all parts in the circumferential direction. Equally, one part in the radial direction may be different from another part. According to this embodiment, for example, by increasing the axial thickness toward the inner diameter direction, it becomes possible to increase the contact stress of the raceway toward the inner diameter direction, and the rotational torque under such a load condition Can be detected.

  Alternatively, the axial thickness between the seating surface on the first rotating member side and the seating surface on the second rotating member side of the intermediate member may be different between one site and the other site in the circumferential direction. According to such an embodiment, it becomes possible to apply a load to a specific circumferential portion of the bearing ring to apply an eccentric load to the thrust bearing, and to detect rotational torque under such a load condition. .

  Preferably, the uneven shape of the seating surface of the one end surface of the intermediate member is the same as the uneven shape of the seating surface of the other end surface, and has the same phase in the circumferential direction. According to this embodiment, it is possible to make the load conditions of the two thrust bearings the same, and it is possible to detect the stable rotational torque while avoiding the rotation balance being lost, and the detection accuracy is improved. To do.

  The seating surface of the intermediate member is not limited to one embodiment, and may have a fan-shaped protrusion centered on the rotation axis. According to such an embodiment, it is possible to make the unbalanced loads to be applied to the two thrust bearings the same, to avoid the rotation balance being lost, and to detect a stable rotational torque, and to detect it. Accuracy is improved.

  The intermediate member is not limited to one embodiment, and the axial thickness between the seat surface on the first rotating member side and the seat surface on the second rotating member side of the intermediate member may be constant. According to this embodiment, in the detection device of the present invention, it is also possible to detect rotational torque when a uniform load is applied.

  Preferably, a radial rolling bearing is provided between the central hole of the intermediate member and the rotating shaft, and the outer peripheral surface of the rotating shaft is fitted with an inner ring of the radial rolling bearing with a gap. According to this embodiment, the thrust load is not applied to the radial rolling bearing, and the rotational torque of the radial rolling bearing is hardly transmitted to the intermediate member, and the detection accuracy of the rotational torque is improved.

  As described above, the present invention is based on the thrust bearing rotational torque detecting device that detects the rotational torque of the thrust bearing, is connected to one end side of the rotating shaft, rotates together with the rotating shaft, and comes into contact with one side of the first thrust bearing. A first rotating member for rotation, a second rotating member connected to the other end side of the rotating shaft so as to be capable of axial stroke and rotating together with the rotating shaft, and contacting one side of the second thrust bearing; It is a disk shape provided with a central hole that penetrates, is disposed between the first rotating member and the second rotating member, and contacts the other side of the first thrust bearing on the end surface facing the first rotating member. An intermediate member having a seating surface for contacting the other side of the second thrust bearing on an end surface facing the second rotating member, and an axial load on the second rotating member. A load applying mechanism for applying It is connected to the member, and means for detecting a rotational torque input from the first thrust bearing and the second thrust bearing on the intermediate member. Therefore, by appropriately selecting the uneven shape of the seating surface, it is possible to reproduce the eccentric load applied to the thrust bearing in an actual machine such as a swash plate type swash plate compressor, and without causing a loss of rotational balance, The rotational torque of the bearing can be measured stably.

  Hereinafter, embodiments of the present invention will be described in detail based on examples shown in the drawings. FIG. 1 is a longitudinal sectional view showing a thrust bearing rotational torque detecting device according to this embodiment.

  The thrust bearing rotational torque detection device 21 detects the rotational torque of the test thrust bearing 12. The test thrust bearing 12 may be provided with a bearing ring on both sides, or may be provided with a bearing ring on only one side. It may be composed of a moving body and a cage. In the present embodiment, the case of the test thrust bearing 12 having a pair of race rings 13 will be mainly described. The rotating shaft 22 is rotated in a direction indicated by a thin arrow by a driving source (not shown). One end side of the rotating shaft 22 includes a flange 23 that widens in the outer diameter direction. The first rotating member 24 is fixed to the end surface of the flange 23. That is, the first rotating member 24 is connected to one end side of the rotating shaft 22 and rotates together with the rotating shaft 22. Further, the flange 23 prevents the first rotating member 24 from coming off the rotating shaft 22.

  A second rotating member 25 is connected to the other end side of the rotating shaft 22 so as to be capable of axial stroke. The second rotating member 25 rotates together with the rotating shaft 22.

  An intermediate member 26 is disposed between the first rotating member 24 and the second rotating member 25. The intermediate member 26 is an annular disk member having a central hole 27 through which the rotary shaft 22 passes in the center.

  The thrust bearing rotational torque detection device 21 includes a load applying mechanism 32 on the opposite side to the side where the intermediate member 26 is located, on both axial sides of the second rotating member 25. The load applying mechanism 32 applies an axial load to the second rotating member 25 and presses the second rotating member 25 toward the first rotating member in the direction of the arrow. Thus, a thrust load is applied between the first rotating member 24 and the intermediate member 26 and between the second rotating member 25 and the intermediate member 26 by pinching between the first rotating member 24 and the second rotating member 25.

  Both of the rotating members 24 and 25 have end faces 24m and 25n for mounting the thrust bearing 12 serving as a specimen between the intermediate members 26, respectively. Each of the end surfaces 24m and 25n is recessed with a step in the axial direction from the end surfaces 24c and 25c of the rotating members 24 and 25 on the inner diameter side, ensuring a space for mounting the thrust bearing 12, and the axis O It is easy to attach the thrust bearing 12 coaxially.

  While the load application mechanism 32 operates, a thrust load is applied to the two thrust bearings 12 having the same shape. That is, the end surface 24m on the intermediate member 26 side of both end surfaces of the disk-shaped first rotating member 24 comes into contact with one of the race rings 13 of the first thrust bearing 12m and applies a thrust load to the first thrust bearing 12m. . The seat surface 25n has the same configuration, and during the operation of the load applying mechanism 32, the end surface 25n on the intermediate member 26 side of both end surfaces of the disk-shaped second rotating member 25 is the raceway ring 13 of the second thrust bearing 12n. A thrust load is applied to the second thrust bearing 12n.

  The intermediate member 26 has seat surfaces 26m and 26n on the end surfaces on both sides in the axial direction for contacting the other of the races 13 and receiving the thrust reaction force from the races 13, respectively.

  The intermediate member 26 is connected to the detection unit 28 via a rod 29 extending in the radial direction. The detection unit 28 monitors the tip of the rod 29 extending from the outer peripheral edge of the intermediate member 26, and the rotational torque input from the raceway rings 13 of the first and second thrust bearings 12m and 12n to the both seating surfaces 26m and 26n. Measure. The intermediate member 26 and the rod 29 do not rotate together with the rotary shaft 22 but are allowed to rotate slightly for measuring the rotational torque.

  Next, measurement of the rotational torque of the test thrust bearing 12 (12m, 12n) will be described. The thrust bearing rotational torque detection device 21 of this embodiment detects the rotational torque of the two thrust bearings 12 (12m, 12n) simultaneously. First, with respect to the first thrust bearing 12m, one of the race rings 13 is brought into contact with the seating surface 24m and fixed, and the other of the race rings 13 is brought into contact with the seating surface 26m to fix it. The first thrust bearing 12m is attached between the intermediate member 26 and the intermediate member 26. Similarly, with respect to the second thrust bearing 12n, one of the race rings 13 is brought into contact with the seat surface 25n and fixed, and the other of the race rings 13 is brought into contact with the seat surface 26n to fix it. The second thrust bearing 12n is attached between the member 25 and the intermediate member 26. Next, the load applying mechanism 32 applies a load to the second rotating member 25, presses the second rotating member 25 toward the first rotating member 24, and thrusts the two thrust bearings 12 (12m, 12n). Apply a load. At the same time, the rotating shaft 22 is rotated to relatively rotate one and the other of the race rings 13. At this time, rotational torque is input to the intermediate member 26 from the two thrust bearings 12 attached to both sides of the intermediate member 26.

  Then, the rotational torque detected by the detection unit 28 is divided into two, and the rotational torque per thrust bearing 12 is calculated. In addition, when the thrust bearing 12 is not provided with the bearing ring 13, it is good to make a seat surface contact the rolling element (roller or ball) of the thrust bearing 12.

  The center direction and the direction of the axial load input from the load applying mechanism 32 to the second rotating member 25 coincide with the axis O. FIG. 2 shows an example of the intermediate member 26, where (a) is a front view and (b) is a longitudinal sectional view. In this example, the seating surface 26m and the seating surface 26n are planes perpendicular to the rotation axis, and the axial thickness between the seating surfaces 26m and 26n of the intermediate member 26 having a disk shape is made constant. Thereby, a uniform load can be applied to the thrust bearing 12.

  3A and 3B show another example of the intermediate member 26, where FIG. 3A is a front view and FIG. 3B is a longitudinal sectional view. In this embodiment, the seat surface 26m and a part 26e of the seat surface 26n are projected in the axial direction by a dimension D from the other portion 26f. Thus, by appropriately selecting the concave and convex shapes of the seating surfaces 26m and 26n as will be described later, it becomes possible to increase the contact stress of the portion of the bearing ring 13 that contacts the protruding portion 26e, and the uneven load is thrust. It can be applied to the bearing 12. And it becomes possible to confirm the rotational torque in an actual machine by making it the uneven | corrugated shape matched with actual load distribution. As a thrust bearing to which an unbalanced load is applied, for example, there is a thrust bearing shown in FIGS. 32 and 33 of JP-A-2006-200719. Japanese Patent Laying-Open No. 2006-200719 discloses a thrust bearing for a car air conditioner / compressor in a swash plate type swash plate compressor. Here, an eccentric load is applied to the thrust bearing interposed between the connecting member and the swash plate or between the piston support and the journal when the piston reciprocates.

  When a piston that repeats the cycle of suction, compression, and discharge is provided inside, and the swash plate compressor disclosed in Japanese Patent Application Laid-Open No. 2006-200719 is used as the actual machine, the thrust bearing rotational torque detecting device 21 of the present embodiment uses this actual machine. It is possible to reproduce the eccentric load applied to the thrust bearing used in the above, and to measure a stable rotational torque.

  Further, the thrust bearing rotational torque detecting device 21 according to the present embodiment detects a stable rotational torque because the intermediate member 26 applies an uneven load and does not apply an uneven load with static air. be able to.

  Furthermore, according to the thrust bearing rotational torque detection device 21 of the present embodiment, by replacing the intermediate member 26, it becomes possible to apply various uneven loads to the thrust bearing 12, and in the actual machine in which the thrust bearing 12 is used. Rotational torque can be detected under close load conditions. Further, the load transmitting member as in Patent Document 1 is not interposed at a specific position in the circumferential direction, and assembly is facilitated.

  FIG. 4 is an enlarged longitudinal sectional view showing the two thrust bearings 12 attached to the thrust bearing rotational torque detector 21. The thrust bearing 12 having the central hole will be described. An annular disk having an axial thickness is formed into a pair of race rings 13 arranged coaxially so as to face each other, and a plurality of rollers are provided between these race rings. And a cage that holds the plurality of rollers at equal intervals in the circumferential direction. Alternatively, other structures may be used as long as they are thrust bearings. The outer surface 13g of the race 13 on the side where the rollers do not roll forms a plane perpendicular to the axial direction.

  In the case where the pair of raceways 13 and 13 includes a front raceway ring 13a and a back raceway ring 13b having different shapes, as shown in the longitudinal sectional view of FIG. 4, seat surfaces 26m and 26n on both sides in the axial direction of the intermediate member 26. The thrust bearing 12 is preferably attached to the thrust bearing rotational torque detecting device 21 so as to come into contact with the back raceway rings 13b of the two thrust bearings 12, respectively. As shown in FIGS. 1 and 4, by attaching the two thrust bearings 12 and 12 back to back, the rotational torque input to the intermediate member 26 from both sides in the axial direction becomes equal, and the load balance of the thrust bearing 12 is lost. Therefore, a stable rotational torque can be measured.

  In other words, the inner peripheral edge of the front raceway 13a extends in the axial direction toward the rear raceway 13b. The back raceway 13b is an annular thin disk and does not extend in the axial direction. As shown in FIG. 5, if the rear raceway 13b is fixed to one seating surface 26m in the axial direction and the front raceway ring 13a is fixed to the other seating surface 26n in the axial direction, the thrust bearings 12 and 12 are back-to-back. There is a case where it is not attached and a stable rotational torque cannot be measured.

  Although not shown, the thrust bearing rotational torque detector 21 detects the rotational torque of a thrust bearing having a bearing ring only on one side, or the case of detecting the rotational torque of a thrust bearing without a bearing ring. The thrust bearings 12 and 12 are attached to the thrust bearing rotational torque detector 21 so that the first thrust bearing 12m and the second thrust bearing 12n are arranged symmetrically with respect to the intermediate member 26.

  6A and 6B show another example of the intermediate member 26, where FIG. 6A is a front view seen from the direction of the axis O, and FIG. 6B is a longitudinal sectional view cut along a plane including the axis O. FIG. In this embodiment, the axial thicknesses of both seating surfaces 26m, 26n of the disk-shaped intermediate member 26 are the same in all the parts in the circumferential direction, and are different in one part and the other parts in the radial direction. Specifically, in the cross section including the axis O, the seating surface 26m and the seating surface 26n are formed by curves that are recessed toward the inner side in the axial direction, and the axial thickness is increased toward the outer diameter side. Each of the 26n uneven shapes is formed to be recessed toward the inner diameter side. Alternatively, as shown in the longitudinal sectional view of FIG. 7, the seating surfaces 26 m and 26 n are formed in a straight line in the cross section including the axis O, and the axial thickness is increased toward the outer diameter side. Each of the shapes may be recessed toward the inner diameter side. According to the intermediate member 26 shown in FIG. 6 and FIG. 7, the contact stress of the race 13 becomes smaller toward the inner diameter side. Thereby, the rotational torque can be detected in consideration of the radial deflection of the thrust bearing 12, the radial deflection of the intermediate member 26, and the misalignment of the thrust bearing 12 or the intermediate member 26.

  FIG. 8 also shows another example of the intermediate member 26, where (a) is a front view and (b) is a longitudinal sectional view. Also in this embodiment, the axial thicknesses of the both seating surfaces 26m, 26n of the disk-shaped intermediate member 26 are the same in all the parts in the circumferential direction, and are different in one part and other parts in the radial direction. Is formed in a cross-section including the axis O with a curved surface in which the seating surface 26m and the seating surface 26n swell outward in the axial direction, and the axial thickness decreases toward the outer diameter side, and the unevenness of the seating surfaces 26m and 26n. Each of the shapes is a shape that swells toward the inner diameter side. Alternatively, as shown in the longitudinal cross-sectional view of FIG. 9, the seat surfaces 26m and 26n are formed in a straight line in the cross section including the axis O, and the axial thickness is reduced toward the outer diameter side so that the unevenness of the seat surfaces 26m and 26n. Each of the shapes may be a shape protruding toward the inner diameter side. According to the intermediate member 26 shown in FIGS. 8 and 9, the contact stress of the race 13 is increased toward the inner diameter side. Thereby, the rotational torque can be detected in consideration of the radial deflection of the thrust bearing 12, the radial deflection of the intermediate member 26, and the misalignment of the thrust bearing 12 or the intermediate member 26. The shapes of the seating surface 26m and the seating surface 26n must be symmetric with respect to a straight line perpendicular to the direction of the axis O as shown in FIGS. If the uneven shape is different between the one seat surface 26m and the other seat surface 26n in the axial direction, the thrust load of the thrust bearing 12 is different between the first thrust bearing 12m and the second thrust bearing 12n, and the rotational balance is lost. This is because stable rotational torque measurement becomes difficult.

  When faithfully reproducing an actual machine in which the thrust bearing 12 is used, the seating surfaces 26m and 26n have an uneven shape corresponding to a change in the contact stress of the actual machine, as shown in FIGS. 6B and 8B. An intermediate member 26 may be used. For example, it is preferable to use the intermediate member 26 in which the cross sections of the seating surfaces 26m and 26n are cross sections of a single arc, or a cross section of a composite arc obtained by connecting several different arcs.

  In order to simply determine the influence of the mounting error of the thrust bearing 12, it is preferable to use an intermediate member 26 having seating surfaces 26m and 26n having straight cross sections as shown in FIGS.

  Next, the application of an offset load to the thrust bearing 12 will be described in detail.

  In the embodiment shown in FIG. 3 described above, the axial thickness between both seating surfaces 26m, 26n of the disk-shaped intermediate member 26 is different between the projecting portion 26e and the non-projecting portion 26f in the circumferential direction. Specifically, the protrusions 26e are protruded by a dimension D in the direction of the axis O from the non-protrusion portions 26f to form the uneven shapes of the seating surfaces 26m and 26n. Then, a load is applied only to a portion of the thrust bearing 12 that contacts the protruding portion 26e, and is not applied to a portion of the thrust bearing 12 that does not contact and face the non-projecting portion 26f.

  Thereby, an eccentric load can be applied to the thrust bearing 12. Therefore, the load conditions of the actual machine in which the thrust bearing 12 is actually used can be reproduced by appropriately selecting the projecting portions of the seating surfaces 26m and 26n.

  Preferably, the concave / convex shape of the seating surface 26m provided on one end surface of the disc-shaped intermediate member 26 and the concave / convex shape of the seating surface 26n provided on the other end surface are the same and have the same phase in the circumferential direction. That is, the axial protrusion amount on the one side 26m and the axial protrusion amount on the other side 26n are the same in all the circumferential portions. Specifically, for example, as shown in FIG. 3, both the seating surface 26m and the seating surface 26n have fan-shaped protrusions 26e having the same shape. The amount of protrusion is dimension D for both seating surfaces 26m and 26n. And the protrusion part 26e of the seat surface 26m and the protrusion part 26e of the seat surface 26n correspond in the circumferential direction position. As a result, the rotational torque can be stably detected without losing the rotational balance of the eccentric load applied to the thrust bearing 12. In particular, when the concave and convex shapes of both seat surfaces 26m and 26n are complex, the concave and convex shapes of both seat surfaces 26m and 26n are the same and have the same phase in the circumferential direction, which contributes to stable rotation torque detection. .

  If a radial rolling bearing 30 is provided between the inner peripheral surface of the central hole 27 of the intermediate member 26 and the outer peripheral surface of the rotary shaft 22 passing through the central hole 27, the rotary shaft 22 guides the intermediate member 26. Thus, the alignment of the intermediate member 26 in the thrust bearing rotational torque detector 21 is improved, and the intermediate member 26 can be stably supported. In this case, it is preferable that the outer peripheral surface of the rotary shaft 22 is loosely fitted with a gap with the inner ring 31 of the radial rolling bearing 30. Further, collars 33 are provided on the outer peripheral surface of the rotating shaft 22 on both sides in the axial direction of the inner ring 31 to prevent the inner ring 31 from slipping out of the rotating shaft 22. Thus, the detection unit 28 can avoid detecting the rotational torque of the radial rolling bearing 30 and can stably detect the rotational torque of the thrust bearing 12, and the detection accuracy is improved.

  The axial thickness changes shown in FIGS. 6B and 8B described so far are exaggerated for easy understanding of the present invention. However, it is so small that it is difficult to distinguish.

  As mentioned above, although embodiment of this invention was described with reference to drawings, this invention is not limited to the thing of embodiment shown in figure. Various modifications and variations can be made to the illustrated embodiment within the same range or equivalent range as the present invention.

  The thrust bearing rotational torque detection device according to the present invention is effectively used in a technique for detecting the rotational torque of a thrust bearing.

It is a longitudinal cross-sectional view which shows the thrust bearing rotational torque detection apparatus which becomes one Example of this invention. The intermediate member of the Example is illustrated, (a) is a front view, (b) is a longitudinal cross-sectional view. The intermediate member of the Example is illustrated, (a) is a front view, (b) is a longitudinal cross-sectional view. It is a longitudinal cross-sectional view which expands and shows the test thrust bearing attached to the Example. It is a reference figure for demonstrating the direction of the sample thrust bearing attached to the Example. The intermediate member of the Example is illustrated, (a) is a front view, (b) is a longitudinal cross-sectional view. It is a longitudinal cross-sectional view which shows the modification of the intermediate member shown in FIG. The intermediate member which becomes one Example of this invention is illustrated, (a) is a front view, (b) is a longitudinal cross-sectional view. It is a longitudinal cross-sectional view which shows the modification of the intermediate member shown in FIG. It is a longitudinal cross-sectional view which shows the conventional general thrust bearing rotational torque detection apparatus.

Explanation of symbols

  12 Test Thrust Bearing, 12m First Thrust Bearing, 12n Second Thrust Bearing, 13 Race Wheel, 21 Thrust Bearing Rotation Torque Detection Device, 22 Rotating Shaft, 24 First Rotating Member, 24m End Face, 25 Second Rotating Member, 25n End surface, 26 Intermediate member, 26m Seat surface, 26n Seat surface, 27 Center hole, 28 Detecting portion, 30 Radial rolling bearing, 31 Inner ring of radial rolling bearing, 32 Load applying mechanism.

Claims (7)

A thrust bearing rotational torque detector for detecting rotational torque of a thrust bearing,
A first rotating member connected to one end of the rotating shaft and rotating together with the rotating shaft to contact one side of the first thrust bearing and apply a thrust load ;
A second rotating member that is connected to the other end side of the rotating shaft so as to be capable of axial stroke and rotates together with the rotating shaft, and contacts with one side of the second thrust bearing to apply a thrust load ;
It is a disk shape provided with a central hole through which the rotating shaft passes, and is disposed between the first rotating member and the second rotating member, and the first thrust is formed on an end surface facing the first rotating member. A bearing surface for applying a thrust load in contact with the other side of the bearing is provided, and an end surface on the side facing the second rotating member is contacted with the other side of the second thrust bearing to apply the thrust load . An intermediate member having a seating surface for
A load applying mechanism for applying an axial load to the second rotating member;
Means connected to the intermediate member for detecting rotational torque input to the intermediate member from the first thrust bearing and the second thrust bearing ;
A thrust bearing rotational torque detecting device , wherein an axial thickness between a seating surface on the first rotating member side and a seating surface on the second rotating member side of the intermediate member is different between one part and another part . The first thrust bearing and the second thrust bearing each include a bearing ring on the one side and the other side,
These pair of races are composed of a front race and a rear race with different shapes,
The seat surface on the first rotating member side of the intermediate member is for contacting and fixing the rear raceway ring of the first thrust bearing,
2. The thrust bearing rotational torque detection device according to claim 1, wherein a seating surface of the intermediate member on a second rotating member side is for contacting and fixing a rear raceway ring of a second thrust bearing.   The axial thickness between the seating surface on the first rotating member side and the seating surface on the second rotating member side of the intermediate member is equal in all parts in the circumferential direction, and one part in the radial direction and other parts The thrust bearing rotational torque detection device according to claim 1, wherein the thrust bearing rotation torque detection device is different.   The axial thickness between the seating surface on the first rotating member side and the seating surface on the second rotating member side of the intermediate member is different between one part and another part in the circumferential direction. The thrust bearing rotational torque detection device as described.   5. The thrust bearing rotational torque detection according to claim 4, wherein the uneven shape of the seating surface of the one end surface of the intermediate member is the same as the uneven shape of the seating surface of the other end surface, and is in the same phase in the circumferential direction. apparatus.   The thrust bearing rotational torque detection device according to claim 5, wherein the seating surface of the intermediate member has a fan-shaped protrusion centered on the rotation shaft. A radial rolling bearing is provided between the central hole of the intermediate member and the rotating shaft,
The thrust bearing rotational torque detection device according to any one of claims 1 to 6 , wherein an outer peripheral surface of the rotary shaft is fitted with an inner ring of the radial rolling bearing with a gap.

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