JP2009008593A - Torque measuring device of tapered roller bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an inexpensive torque measuring device of a simple constitution, which measures a torque between a collar of a bearing ring and a large end surface of a tapered roller. <P>SOLUTION: This torque measuring device comprises a shaft 1 integrally engaging with an inner ring 31 of the tapered roller bearing 30 as a torque measuring object, and a housing 2 integrally engaging with an outer ring 32 of the tapered roller bearing 30. A cylindrical body 13 having a collar corresponding part 12 coming into contact with the end surface on the large end side of a tapered roller 33 of the bearing 30 is disposed separately from the inner ring 31. The cylindrical body 13 is supported by the shaft 1 via a rolling ball bearing 14, the rotation with respect to the shaft 1 is restrained by a restraining means 16A, and a drive force measuring means 20A for measuring a drive force acting on the cylindrical body 13 is provided. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a torque measuring device for a tapered roller bearing that measures torque generated between a roller end surface of a tapered roller bearing and a collar of a raceway ring that is in contact with the roller end surface.

FIG. 6 is a schematic diagram of an apparatus capable of separately measuring the total torque acting on the inner ring rotating / outer ring stationary type tapered roller bearing and the torque between the inner ring collar and the large end face of the tapered roller. In addition, a description of this apparatus is described in Chapter 3 of the same document.
FIG. FIG. 11 shows a part of FIG. A tapered roller bearing 100 that is a torque measurement object includes an inner ring 101, an outer ring 102, and tapered rollers 103 that are interposed between the raceway surfaces of the inner and outer rings 101, 102.

  A housing 104 is integrally fitted on the outer periphery of the outer ring 102, and the housing 104 is supported in a non-contact manner by a static pressure gas journal bearing 105 and a static pressure gas thrust bearing 106 with a sufficiently small frictional force. Therefore, the tapered roller bearing 100 is in a state of floating in the radial direction and the axial direction. The rotational movement of the outer ring 102 in the circumferential direction is constrained by a force measurement gauge 107, and this force measurement gauge 107 can measure the rotational torque acting on the entire bearing transmitted from the outer ring raceway surface to the outer ring 102 side.

  On the other hand, a rotating shaft 108 is fitted in the inner periphery of the inner ring 101 in a fixed state, and the rotating shaft 108 is supported in a non-contact manner by a static pressure gas journal bearing 105 and a static pressure gas thrust bearing 106 with a sufficiently small frictional force. ing. In the original tapered roller bearing, the inner ring 101 is provided with a large collar that is in contact with the end surface on the large end side of the tapered roller 103. However, in the tapered roller bearing 100 for testing incorporated in this apparatus, the large collar is removed. Instead of this, a member 109 corresponding to the large collar separate from the inner ring 101 is provided. This large brim equivalent member 109 is connected to the inner ring 101 by three support arms 110, and the torque acting on the large brim of the inner ring 101 is measured by measuring the distortion of the support arm 110 with the strain gauge 111. Can do.

According to this configuration, it is possible to know the torque of the entire bearing and the torque of the large brim from the outputs of the force measuring gauge 107 and the strain gauge 111, respectively. Further, the torque on the inner and outer ring raceways is obtained by subtracting the large collar torque from the torque of the entire bearing.
Co-authored by RSZhou and MR Hoeprich, “Torque of Tapered Roller Bearings”, Transactions of the ASME, Journal of Tribology (Journal) of Tribology), 113, July 1991, p. 590-597

  A feature of tapered roller bearings that differ from other types of rolling bearings is that torque is generated by the collar of the bearing ring. Knowing the torque generated by the above-mentioned flange when designing or newly designing tapered roller bearings Is particularly important. Therefore, an apparatus for measuring this torque has become necessary. Ideally, for this type of device, it is desirable to be able to measure the torque of the entire bearing in addition to the collar torque, but in reality, if the torque of the collar can be measured, there is sufficient utility value. Even a device that can measure only the brim torque may be required to be a simple and inexpensive device.

  The torque measuring device described in Non-Patent Document 1 is a case where the outer ring 102 side is fixed to a stationary system and only the torque between the large brim of the inner ring 101 and the large end surface of the tapered roller 103 is measured. The gas journal bearing 105 and the static pressure gas thrust bearing 106 are required. The static pressure gas bearings 105 and 106 have an advantage that their friction torque is extremely small, but they are expensive and have a problem of requiring an external air supply device.

  The present invention has been made under the above background, and its purpose is to measure the torque between the collar of the bearing ring and the large end surface of the tapered roller, and to measure the torque of a tapered roller bearing with a simple configuration and at low cost. Is to provide a device.

  A torque measuring device for a tapered roller bearing according to a first aspect of the present invention includes a shaft that is integrally fitted to an inner ring of a tapered roller bearing that is a torque measurement object, and a fitting that is integrally fitted to an outer ring of the tapered roller bearing. A cylindrical body having a flange-corresponding portion in contact with the end face on the large end side of the tapered roller of the tapered roller bearing is provided separately from the inner ring, and the cylindrical body is provided via the rolling ball bearing. A driving force measuring means is provided that measures the driving force acting on the cylindrical body by supporting the shaft and restraining the rotation of the shaft by the restraining means. Here, integrally fitting means that they are fixed to each other by fitting.

  In the tapered roller bearing torque measuring device having this configuration, as the tapered roller bearing which is a to-be-measured object, a tapered roller bearing which is originally provided integrally with the inner ring and which removes the collar contacting the end surface on the large end side of the tapered roller is used. . And the collar equivalent part corresponding to this inner ring collar is provided in the cylindrical body separate from the inner ring. When the shaft or the housing rotates, torque is generated between the corresponding portion of the collar and the end surface on the large end side of the tapered roller. Since the cylindrical body is restrained from rotating with respect to the shaft by the restraining means, the portion corresponding to the collar is always maintained in the same phase relative to the inner ring around the bearing central shaft. Therefore, the torque generated between the corresponding part of the collar and the end face on the large end side of the tapered roller is generated between the inner ring collar and the end face on the large end side of the tapered roller in the original tapered roller bearing in which the flange is integrally provided on the inner ring. Equivalent to the torque The torque is transmitted from the collar portion to the cylindrical body, and a driving force acts on the cylindrical body. This driving force is measured by driving force measuring means. The torque can be calculated or estimated from the measurement result of the driving force measuring means.

  According to this structure, it can be set as the apparatus using a comparatively cheap rolling bearing, without using an expensive static pressure gas bearing. The torque generated in the rolling bearing is large compared to the torque generated in the static pressure gas bearing, but is sufficiently small compared to the torque generated between the corresponding portion of the collar and the end face on the large end side of the tapered roller. Usually, it is 1/10 or less, and it is not a level causing a problem in measurement accuracy. In addition, since the rolling bearing is grease-lubricated, no auxiliary equipment for lubrication is required. For these reasons, the torque measuring device can be manufactured with a simple configuration at low cost.

In the first invention, the housing may be fixed to a stationary system, and the shaft may be driven to rotate.
In this case, it is possible to measure the torque generated between the inner ring collar and the end face on the large end side of the tapered roller, which is generated by the rotation of the inner ring.

In the first invention, the housing is rotatably supported by a static pressure gas thrust bearing with respect to a stationary system, and the shaft is driven to rotate to measure the rotational force acting on the housing. A measuring means may be provided. In this case as well, it is possible to measure the torque generated between the inner ring collar and the end surface on the large end side of the tapered roller, which are generated when the inner ring rotates. In addition, the torque generated in the entire tapered roller bearing can be measured from the measurement result of the rotational force measuring means. The torque of the entire tapered roller bearing is the sum of the torque of the raceway surface of the inner and outer rings and the torque of the inner ring collar if the torque caused by the cage is sufficiently small. Therefore, by measuring the torque of the entire tapered roller bearing and the torque of the inner ring collar, the torque of the raceway surfaces of the inner and outer rings can also be known.

Further, in the first invention, the shaft may be fixed to a stationary system, and the housing may be driven to rotate.
In this case, it is possible to measure the torque generated between the inner ring collar and the end face on the large end side of the tapered roller generated by the rotation of the outer ring.

Furthermore, in the first invention, the shaft is rotatably supported by a static pressure gas thrust bearing with respect to a stationary system, and the housing is driven to rotate to measure the rotational force acting on the shaft. A measuring means may be provided.
Also in this case, it is possible to measure the torque generated between the inner ring collar and the end face on the large end side of the tapered roller generated by the rotation of the outer ring. In addition, the torque generated in the entire tapered roller bearing can be measured from the measurement result of the rotational force measuring means. For the same reason as described above, the torque on the raceway surface of the inner and outer rings can also be known.

The restraining means may be an elastic connecting plate that connects the shaft and the cylindrical body, and the driving force measuring means may be a strain gauge that measures strain of the connecting plate.
When the restraining means is an elastic connecting plate that connects the shaft and the cylindrical body, distortion appears in the connecting plate when a driving force is applied to the cylindrical body. The torque can be detected with high accuracy by measuring the distortion appearing on the connecting plate with a strain gauge which is a driving force measuring means.

  A torque measuring device for a tapered roller bearing according to a second aspect of the present invention is integrally fitted with a shaft that is integrally fitted to an inner ring of a tapered roller bearing that is a torque measurement object, and an outer ring of the tapered roller bearing. A cylindrical body having a flange-corresponding portion in contact with the end face on the large end side of the tapered roller of the tapered roller bearing is provided separately from the outer ring, and the cylindrical body is provided via the rolling ball bearing. A driving force measuring means is provided which measures the driving force acting on the cylindrical body by supporting the housing and restraining the rotation of the housing by the restraining means.

  In the tapered roller bearing torque measuring device having this configuration, as the tapered roller bearing that is a torque measurement object, a tapered roller bearing that is originally provided integrally with the outer ring and that removes the flange that contacts the end surface on the large end side of the tapered roller is used. . And the collar equivalent part corresponding to this outer ring collar is provided in the cylindrical body separate from the outer ring. When the shaft or the housing rotates, torque is generated between the corresponding portion of the collar and the end surface on the large end side of the tapered roller. Since the cylindrical body is restrained from rotating with respect to the shaft by the restraining means, the portion corresponding to the collar is always maintained in the same phase relative to the outer ring around the bearing center shaft. Therefore, the torque generated between the corresponding part of the collar and the end face on the large end side of the tapered roller is generated between the outer ring collar and the end face on the large end side of the tapered roller in the original tapered roller bearing in which the flange is integrally provided on the outer ring. Equivalent to the torque The torque is transmitted from the collar portion to the cylindrical body, and a driving force acts on the cylindrical body. This driving force is measured by driving force measuring means. The torque can be calculated or estimated from the measurement result of the driving force measuring means.

  Similarly to the configuration of the first invention, the configuration of the second invention can be a device using a relatively inexpensive rolling bearing without using an expensive static pressure gas bearing, and can be lubricated. Therefore, it can be manufactured at low cost with a simple configuration.

In the second invention, the housing may be fixed to a stationary system, and the shaft may be driven to rotate.
In this case, it is possible to measure the torque generated between the outer ring collar and the end face on the large end side of the tapered roller generated by the rotation of the inner ring.

In the second aspect of the invention, the housing is rotatably supported by a static pressure gas thrust bearing with respect to a stationary system, and the shaft is driven to rotate to measure the rotational force acting on the housing. A measuring means may be provided.
Also in this case, it is possible to measure the torque generated between the outer ring collar and the end face on the large end side of the tapered roller that are generated by the rotation of the inner ring. In addition, the torque generated in the entire tapered roller bearing can be measured from the measured value of the rotational force measuring means. For the same reason as described above, the torque on the raceway surface of the inner and outer rings can also be known.

Further, in the second invention, the shaft may be fixed to a stationary system, and the housing may be driven to rotate.
In this case, it is possible to measure the torque generated between the outer ring collar and the end face on the large end side of the tapered roller, which is generated by the rotation of the outer ring.

Further, in the second invention, the shaft is rotatably supported by a static pressure gas thrust bearing with respect to a stationary system, and the housing is driven to rotate to measure the rotational force acting on the shaft. A measuring means may be provided.
Also in this case, it is possible to measure the torque generated between the outer ring collar and the end face on the large end side of the tapered roller that is generated by the rotation of the outer ring. In addition, the torque generated in the entire tapered roller bearing can be measured from the measured value of the rotational force measuring means. For the same reason as described above, the torque on the raceway surface of the inner and outer rings can also be known.

  The rolling bearing may be an angular ball bearing. Angular ball bearings are suitable for simplifying the structure of a torque measuring device because they can support a relatively large axial load among rolling bearings and have a small torque.

  A torque measuring device for a tapered roller bearing according to the present invention comprises a shaft that is integrally fitted to an inner ring of a tapered roller bearing that is a torque measurement object, and a housing that is integrally fitted to an outer ring of the tapered roller bearing. A cylindrical body having a flange-corresponding portion that contacts the end surface of the tapered roller at the large end side of the tapered roller bearing is provided separately from the inner ring, and the cylindrical body is connected to the shaft via a rolling ball bearing. And a driving force measuring means for measuring the driving force acting on the cylindrical body by restricting the rotation with respect to the shaft by the restraining means, or an end face on the large end side of the tapered roller of the tapered roller bearing. A cylindrical body having a collar-corresponding portion that is in contact with the outer ring is provided separately from the outer ring, and the cylindrical body is supported by the housing via a rolling ball bearing and rotated with respect to the housing by a restraining means. A driving force measuring means that restrains and measures the driving force acting on the cylindrical body is provided, so it is possible to measure the torque between the collar of the bearing ring and the large end surface of the tapered roller, and it can be manufactured inexpensively with a simple configuration it can.

  An embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a diagram showing an overall configuration of a torque measuring device for a tapered roller bearing according to an embodiment of the first invention. This torque measuring apparatus for a tapered roller bearing includes a shaft 1 that is integrally fitted to an inner ring 31 of a tapered roller bearing 30 that is a torque measurement object, and a housing 2 that is integrally fitted to an outer ring 32. The axis 1 is oriented in the vertical direction. The inner ring 31 and the shaft 1 and the outer ring 32 and the housing 2 are integrally fixed to each other in the fitted state. In this torque measuring device, the housing 2 is fixed to the stationary system 3 and the shaft 1 is rotated.

  The shaft 1 is fitted to the inner circumference of the inner ring 31 of the tapered roller bearing 30 and has an inner collar portion 1aa formed at the lower end portion, and the lower end is fitted to the inner circumference of the outer cylinder portion 1a. The inner cylinder part 1b supported by the inner collar part 1aa of the outer cylinder part 1a, the drive transmission part 1c extending upward from the upper end of the inner cylinder part 1b, and the inner cylinder part 1b and the drive transmission part 1c are connected. It has a shoulder portion 1d and a centering portion 1e for centering the drive transmission portion 1c with respect to the inner cylinder portion 1b. The drive transmission portion 1 c is rotatably supported by a shaft support portion 3 a integrated with the stationary system 3 by a plurality of rolling bearings 4, for example, angular ball bearings, and is driven and rotated by a belt transmission device 5. The belt transmission device 5 is configured such that a transmission belt 5c is wound around a belt wheel 5a attached to an output shaft of the drive motor 6 and a belt wheel 5b attached to an upper end portion of the drive transmission portion 1c.

  As shown in FIG. 2 (A), a tapered roller bearing 30 which is a to-be-measured object includes an inner ring 31, an outer ring 32, a plurality of tapered rollers 33 interposed between the inner and outer rings 31, 32, and a tapered roller. And a retainer 34 for retaining 33. The inner ring 31 is formed with a raceway surface 31a made of a conical surface on the outer periphery, and has a small collar 31b on the small diameter side of the raceway surface 31a. The inner ring 31 of the original tapered roller bearing 30 has a large brim 31c on the large diameter side of the raceway surface 31a as shown in FIG. 2B, but this torque measuring device is shown in FIG. The one with the large collar 31c removed along the cutting line L is used. The outer ring 32 is formed with a raceway surface 32a that is opposed to the raceway surface 31a of the inner ring 31 on the inner periphery, and has no collar. The outer circumference of the tapered roller 33 is formed as a rolling surface 33a, and is freely rollable between both the raceway surfaces 31a and 32a. Each tapered roller 33 is placed in a pocket of the cage 34 and is held at a predetermined interval in the circumferential direction.

  The inner ring 31 of the tapered roller bearing 30 has an upper end surface that abuts against a convex portion 1ab formed on the outer periphery of the outer shaft cylindrical portion 1a, and a lower end surface that fits integrally with the outer peripheral lower end of the outer shaft portion 1a. Is positioned in the axial direction. The outer ring 32 is positioned in the axial direction by the upper and lower outer ring spacers 8 and 9 and is fixed from above by the spacer 10 and the pressing member 11.

  A ring-shaped collar corresponding portion 12 corresponding to the large collar 31 c of the inner ring 31 is provided separately from the inner ring 31. The collar-corresponding portion 12 is provided in a fixed state on the cylindrical body 13 and is in direct contact with the large end surface 33b of the tapered roller 33 (FIG. 2). The cylindrical body 13 is rotatably supported by the inner cylindrical portion 1 b of the shaft 1 by a pair of rolling bearings 14. In this embodiment, the pair of rolling bearings 14 are both angular ball bearings. The inner ring 14a of the rolling bearing 14 is axially positioned by an enlarged diameter portion 1ba and an outer cylindrical portion 1a formed at the upper end of the inner cylindrical portion 1b. The outer ring 14 b is positioned in the axial direction by an inner collar portion 13 a formed at the lower end of the cylindrical body 13 and a bearing retainer 15 fixed to the upper end of the cylindrical body 13.

  The bearing retainer 15 is connected to the shaft 1 at one place in the circumferential direction via a connecting plate 16A having elasticity with respect to a moment about the bearing central axis O. The shape of the connecting plate 16A is, for example, a strip shape whose thickness in the front-rear direction is thinner than the width in the vertical direction. The connecting plate 16A is disposed in a notch 1f formed from the shoulder 1d to the centering portion 1e of the shaft 1 and a notch 15a formed in the bearing retainer 15, and the shaft 17 is connected to the shaft by a connecting tool 17 such as a connecting pin. 1 and the bearing retainer 15. The connecting plate 16 </ b> A is a restraining means that restrains the rotation of the cylindrical body 13 with respect to the shaft 1.

  A strain gauge 20A as a driving force measuring means for measuring a driving force for rotating the cylindrical body 13 synchronously with the shaft 1 is attached to the surface of the connecting plate 16A. The strain gauge 20A detects the driving force acting on the cylindrical body 13 as the strain of the connecting plate 16A. A wiring 21 is connected to the strain gauge 20 </ b> A, and the wiring 21 is led to the upper end of the shaft 1 through the through hole 22 provided in the shaft core portion of the drive transmission portion 1 b of the shaft 1. A slip ring 23 is provided opposite to the upper end of the shaft 1, and a detection signal of the strain gauge 20 </ b> A is transmitted from the wiring 21 to the slip ring 23. The slip ring 23 is connected to the signal processing circuit 25 via the wiring 24. The signal processing circuit 25 has relationship setting means (not shown) such as a calculation formula or a table in which the relationship between the magnitude of the strain detected by the strain gauge 20A and the driving torque is set, and the detection of the strain gauge 20A. It is a circuit that calculates or estimates the torque by checking a signal with the relationship setting means.

  When measuring the torque of the tapered roller bearing 30 with the torque measuring device having this configuration, the torque is output to the drive motor 6 to drive and rotate the shaft 1. At this time, the housing 2 fixed to the stationary system 3 is maintained in a stationary state. Due to the rotation of the shaft 1 and the inner ring 31, torque is generated between the collar-corresponding portion 12 and the end surface 33 b on the large end side of the tapered roller 33. Since the cylindrical body 13 integral with the collar equivalent portion 12 is connected to the shaft 1 via the connecting plate 16A, the collar equivalent portion 12 revolves around the bearing center axis O at the same rotational speed as the inner ring 31. In other words, the collar-corresponding portion 12 is always maintained in the same phase relative to the inner ring 31 around the bearing center axis O. Therefore, the torque generated between the collar-corresponding portion 12 and the end face 33b on the large end side of the tapered roller 33 is the inner ring large collar 31c and the tapered roller 33 in the original tapered roller bearing in which the large collar 31c is integrally provided on the inner ring 31. This is equivalent to the torque generated between the end surfaces 33b on the large end side.

  The torque is transmitted from the collar-corresponding portion 12 to the connecting plate 16A via the cylindrical body 13, and distortion occurs in the connecting plate 16A. The strain of the connecting plate 16A is measured with a strain gauge 20A. The torque can be calculated or estimated by processing the detection signal of the strain gauge 20A by the signal processing circuit 25.

  This torque measuring device is a device using a relatively inexpensive rolling bearing 14 without using an expensive static pressure gas bearing. The torque generated in the rolling bearing 14 is larger than the torque generated in the static pressure gas bearing, but is sufficiently smaller than the torque generated between the collar-corresponding portion 12 and the end surface 33b on the large end side of the tapered roller 33. Usually, it is 1/10 or less, and it is not a level causing a problem in measurement accuracy. Further, since the rolling bearing 14 is grease-lubricated, no auxiliary equipment for lubrication is required. For these reasons, the torque measuring device can be manufactured with a simple configuration at low cost.

  FIG. 3 shows a different embodiment of the first invention. This embodiment is different from the above-described embodiment (FIG. 1) in that the housing 2 is installed on a horizontal pedestal 40 and the pedestal 40 is supported by a static pressure gas thrust bearing 41. The hydrostatic gas thrust bearing 41 supports the housing 2 together with the pedestal 40 from the lower side by ejecting compressed air 43 from the nozzle 42 between the lower surface of the pedestal 40 and the upper surface of the hydrostatic gas thrust bearing 41. To do. The rotational movement of the pedestal 40 in the circumferential direction is restricted by a force measurement gauge 44 which is a rotational force measuring means. The force measurement gauge 44 causes the rotational force of the housing 2, that is, the rotational direction acting on the entire tapered roller bearing 30. Torque can be measured. The other configuration is the same as that of the above embodiment.

In this embodiment, both the torque generated between the flange of the inner ring 31 and the end surface 33b on the large end side of the tapered roller 33 and the torque generated in the entire tapered roller bearing 30 can be measured. The torque of the entire tapered roller bearing is the sum of the torque of the raceway surface of the inner and outer rings and the torque of the inner ring collar if the torque caused by the cage 34 is sufficiently small. By measuring the torque, it is also possible to know the torque of the raceway surfaces of the inner and outer rings.
Since the torque measuring device of this embodiment is provided with the static pressure gas thrust bearing 41, the configuration is more complicated and the cost is higher than that of the embodiment. However, it can be manufactured at a low cost with a simple structure as compared with the one provided with both the static pressure gas thrust bearing and the static pressure gas journal bearing.

  While the embodiment of FIG. 1 and the embodiment of FIG. 3 are stationary on the outer ring and rotating the inner ring, the embodiment of FIG. 4 and the embodiment of FIG. 5 are stationary on the inner ring and rotated on the outer ring. Let In the embodiment of FIG. 4, the shaft 1 is fixed to the stationary system 3. In the embodiment of FIG. 5, the shaft 1 is installed on a horizontal pedestal 40, and the pedestal 40 is supported by a static pressure gas thrust bearing 41. 4 and 5, a shaft portion 2 a is formed on the housing 2, the shaft portion 2 a is rotatably supported by a plurality of angular ball bearings 4, and is driven and rotated by a belt transmission device 5. It is like that. The rest is the same as the embodiment of FIGS. 1 and 3 except that the top and bottom are reversed.

  When measuring the torque according to the embodiment of FIGS. 4 and 5, the torque is output to the drive motor 6 to drive and rotate the housing 2. At this time, the shaft 1 is kept stationary. Along with the rotation of the housing 2 and the outer ring 32, torque is generated between the collar equivalent portion 12 and the end face 33 b on the large end side of the tapered roller 33. Since the tubular body 13 provided with the collar equivalent portion 12 is connected to the shaft 1 via the connecting plate 16A, the collar equivalent portion 12 is always in phase with the inner ring 31 around the bearing center axis O. Maintained. Therefore, the torque generated between the collar-corresponding portion 12 and the end face 33b on the large end side of the tapered roller 33 is the inner ring large collar 31c and the tapered roller 33 in the original tapered roller bearing in which the large collar 31c is integrally provided on the inner ring 31. This is equivalent to the torque generated between the end surfaces 33b on the large end side. This torque is measured by the strain gauge 20A as the strain of the connecting plate 16A as described above.

  In the case of the embodiment of FIG. 5, in addition to the torque of the front wheel collar, the force measuring gauge 44 can measure the rotational force of the housing 2, that is, the torque in the rotational direction acting on the entire tapered roller bearing 30. Further, the torque of the raceway surfaces of the inner and outer rings can be known from the torque of the entire tapered roller bearing and the torque of the inner ring collar.

In these embodiments, the same effects as those of the above-described embodiment can be obtained. That is, the embodiment of FIG. 4 can be configured simply by using only the relatively inexpensive rolling bearing 14 without using an expensive static pressure gas bearing. Further, the embodiment of FIG. 5 is more complicated and expensive than the embodiment of FIG. 4 because the hydrostatic gas thrust bearing is used, but the conventional hydrostatic gas thrust bearing and the hydrostatic gas journal bearing are both provided. Compared to those, it can be manufactured inexpensively with a simple configuration.
In these embodiments, since the detection signal of the strain gauge 20A is taken out through the inside of the shaft 1 on the stationary side, the slip ring 23 is unnecessary.

  FIG. 6 is a diagram showing the overall configuration of a tapered roller bearing torque measuring apparatus according to an embodiment of the second invention. This torque measuring apparatus for a tapered roller bearing includes a shaft 1 that is integrally fitted to an inner ring 31 of a tapered roller bearing 30 that is a torque measurement object, and a housing 2 that is integrally fitted to an outer ring 32. The axis 1 is oriented in the vertical direction. The inner ring 31 and the shaft 1 and the outer ring 32 and the housing 2 are integrally fixed to each other in the fitted state. In this torque measuring device, the housing 2 is fixed to the stationary system 3 and the shaft 1 is rotated.

  The shaft 1 includes a cylindrical portion 1a ′ fitted to the inner periphery of the inner ring 31 of the tapered roller bearing 30, a drive transmission portion 1c extending above the cylindrical portion 1a ′, and a cylindrical portion 1a ′. A shoulder portion 1d that connects the portion 1c and a centering portion 1e that centers the drive transmission portion 1c with respect to the tubular portion 1a ′. The drive transmission portion 1 c is rotatably supported by a shaft support portion 3 a integrated with the stationary system 3 by a plurality of rolling bearings 4, for example, angular ball bearings, and is driven and rotated by a belt transmission device 5. The belt transmission device 5 is configured such that a transmission belt 5c is wound around a belt wheel 5a attached to an output shaft of the drive motor 6 and a belt wheel 5b attached to an upper end portion of the drive transmission portion 1c.

  As shown in FIG. 7 (A), a tapered roller bearing 30 as a torque measurement object includes an inner ring 31, an outer ring 32, a plurality of tapered rollers 33 interposed between the inner and outer rings 31, 32, and a tapered roller. And a retainer 34 for retaining 33. The inner ring 31 is formed with a raceway surface 31a made of a conical surface on the outer periphery, and has a small collar 31b on the small diameter side of the raceway surface 31a. The outer ring 32 is formed with a raceway surface 32a that is opposed to the raceway surface 31a of the inner ring 31 on the inner periphery, and has no collar. The outer ring 32 of the original tapered roller bearing 30 has a collar 32b on the large diameter side of the raceway surface 32a as shown in FIG. 7B, but this torque measuring device is shown in FIG. The outer ring collar 32b is removed along the cutting line L. The outer circumference of the tapered roller 33 is formed as a rolling surface 33a, and is freely rollable between both the raceway surfaces 31a and 32a. Each tapered roller 33 is placed in a pocket of the cage 34 and is held at a predetermined interval in the circumferential direction.

  The inner ring 31 of the tapered roller bearing 30 has an upper end surface that abuts on a convex portion 1aa ′ formed on the outer periphery of the shaft cylindrical portion 1a ′, and a lower end surface that is integrally fitted with an outer peripheral lower end of the shaft cylindrical portion 1a ′. Positioning in the axial direction is performed by contacting the inner ring support 7. The outer ring 32 is positioned in the axial direction in contact with the lower outer ring spacer 8.

  A ring-shaped collar equivalent portion 12 corresponding to the collar 32 b of the outer ring 32 is provided separately from the outer ring 32. The collar-corresponding portion 12 is fixed to the cylindrical body 13 and is in direct contact with the large end surface 33b of the tapered roller 33 (FIG. 7). Specifically, the cylindrical body 13 has a flange portion 13b that expands to the outer diameter side at the lower end, and a flange-corresponding portion 12 is provided at the lower surface outer diameter end of the flange portion 13b. The cylindrical body 13 is rotatably supported on the inner periphery of the housing 2 by a rolling bearing 14. In this embodiment, the rolling bearing 14 is an angular ball bearing. The rolling bearing 14 is positioned in the axial direction by the lower end surface of the inner ring 14a contacting the tubular flange portion 13b and the upper end surface of the outer ring 14b contacting the inner collar portion 2b of the upper end of the housing 2. .

  A restraining member 16B as restraining means is attached to the bearing retainer 15 in a fixed state. The restraining material 16B is, for example, a rod-like member, and the tip side protrudes horizontally outward. A force measuring gauge 20B as a driving force measuring means is installed on the upper surface of the housing 2, and the rotational movement of the restraining material 16B is restricted by the force measuring gauge 20B. By measuring the driving force received from the restraining material 16B with the force measuring gauge 20B, the driving force acting on the cylindrical body 13 can be measured. The force measurement gauge 20B is connected to the signal processing circuit 25. The signal processing circuit 25 is a calculation formula in which a relationship between the magnitude of the driving force detected by the force measuring gauge 20B and the torque (driving torque) generated between the collar equivalent portion 12 and the large end surface 33b of the tapered roller 33 is set. The circuit has a relationship setting means (not shown) such as a table, and calculates or estimates the torque by collating the detection signal of the strain gauge 20B with the relationship setting means.

  When measuring the torque of the tapered roller bearing 30 with the torque measuring device having this configuration, the torque is output to the drive motor 6 to drive and rotate the shaft 1. At this time, the housing 2 fixed to the stationary system 3 is maintained in a stationary state. Due to the rotation of the shaft 1 and the inner ring 31, torque is generated between the collar-corresponding portion 12 and the end surface 33 b on the large end side of the tapered roller 33. Since the tubular body 13 provided with the collar equivalent portion 12 is restrained from rotating with respect to the housing 2 by restraining means such as a restraining member 16B, the collar equivalent portion 12 always has the outer ring 32 around the bearing center axis O. The relative phase is maintained. Therefore, the torque generated between the collar-corresponding portion 12 and the end face 33b on the large end side of the tapered roller 33 is large in the outer ring collar 32b and the tapered roller 33 in the original tapered roller bearing in which the collar 32b of the outer ring 32 is integrally provided. This is equivalent to the torque generated between the end faces 33b on the end side.

  The torque is transmitted from the collar-corresponding portion 12 to the cylindrical body 13, and a driving force acts on the cylindrical body 13. The driving force of the cylindrical body 13 is measured with a force measurement gauge 20B. The torque can be calculated or estimated by processing the detection signal of the force measuring gauge 20B by the signal processing circuit 25.

  This torque measuring device is a device using a relatively inexpensive rolling bearing 14 without using an expensive static pressure gas bearing. The torque generated in the rolling bearing 14 is larger than the torque generated in the static pressure gas bearing, but is sufficiently smaller than the torque generated between the collar-corresponding portion 12 and the end surface 33b on the large end side of the tapered roller 33. Usually, it is 1/10 or less, and it is not a level causing a problem in measurement accuracy. Further, since the rolling bearing 14 is grease-lubricated, no auxiliary equipment for lubrication is required. For these reasons, the torque measuring device can be manufactured with a simple configuration at low cost.

  FIG. 8 shows a different embodiment of the second invention. This embodiment is different from the above-described embodiment (FIG. 6) in that the housing 2 is installed on a horizontal pedestal 40 and this pedestal 40 is supported by a static pressure gas thrust bearing 41. The hydrostatic gas thrust bearing 41 supports the housing 2 together with the pedestal 40 from the lower side by ejecting compressed air 43 from the nozzle 42 between the lower surface of the pedestal 40 and the upper surface of the hydrostatic gas thrust bearing 41. To do. The rotational movement of the pedestal 40 in the circumferential direction is restricted by a force measurement gauge 44 which is a rotational force measuring means. The force measurement gauge 44 causes the rotational force of the housing 2, that is, the rotational direction acting on the entire tapered roller bearing 30. Torque can be measured. The other configuration is the same as that of the above embodiment.

In this embodiment, both the torque generated between the flange of the outer ring 32 and the end surface 33b on the large end side of the tapered roller 33 and the torque generated on the entire tapered roller bearing 30 can be measured. The torque of the entire tapered roller bearing is the sum of the torque of the raceway surface of the inner and outer rings and the torque of the outer ring collar if the torque caused by the cage 34 is sufficiently small. By measuring the torque, it is also possible to know the torque of the raceway surfaces of the inner and outer rings.
Since the torque measuring device of this embodiment is provided with the static pressure gas thrust bearing 41, the configuration is more complicated and the cost is higher than that of the embodiment. However, it can be manufactured at a low cost with a simple structure as compared with the one provided with both the static pressure gas thrust bearing and the static pressure gas journal bearing.

  While the embodiment of FIG. 6 and the embodiment of FIG. 8 are stationary on the outer ring and rotating the inner ring, the embodiment of FIG. 9 and the embodiment of FIG. 10 are stationary on the inner ring and rotated on the outer ring. Let In the embodiment of FIG. 9, the shaft 1 is fixed to the stationary system 3. In the embodiment of FIG. 10, the shaft 1 is installed on a horizontal pedestal 40, and the pedestal 40 is supported by a static pressure gas thrust bearing 41. 9 and 10, the shaft portion 2 a is formed on the housing 2. The shaft portion 2 a is rotatably supported by a plurality of angular ball bearings 4 and is driven to rotate by the belt transmission device 5. It is like that. The rest of the configuration is the same as the embodiment of FIGS. 6 and 8, except that the top and bottom are reversed.

  When measuring torque according to the embodiment of FIGS. 9 and 10, the torque is output to the drive motor 6 to drive and rotate the housing 2. At this time, the shaft 1 is kept stationary. Along with the rotation of the housing 2 and the outer ring 32, torque is generated between the collar equivalent portion 12 and the end face 33 b on the large end side of the tapered roller 33. Since the tubular body 13 provided with the collar equivalent portion 12 is restrained from rotating with respect to the housing 2 by restraining means such as a restraining member 16B, the collar equivalent portion 12 always has the outer ring 32 around the bearing center axis O. The relative phase is maintained. Therefore, the torque generated between the collar-corresponding portion 12 and the end face 33b on the large end side of the tapered roller 33 is large in the outer ring collar 32b and the tapered roller 33 in the original tapered roller bearing in which the collar 32b is integrally provided on the outer ring 32. This is equivalent to the torque generated between the end faces 33b on the end side. This torque is measured with the force measuring gauge 20B as described above.

  In the case of the embodiment of FIG. 10, in addition to the torque of the outer ring collar, the force measuring gauge 44 can measure the rotational force of the housing 2, that is, the rotational torque acting on the entire tapered roller bearing 30. Further, the torque of the raceway surface of the inner and outer rings can be known from the torque of the entire tapered roller bearing and the torque of the outer ring collar.

  In these embodiments, the same effects as those of the above-described embodiment can be obtained. That is, the embodiment of FIG. 9 can be configured simply by using only the relatively inexpensive rolling bearing 14 without using an expensive static pressure gas bearing. Further, the embodiment of FIG. 10 is more complicated and expensive than the embodiment of FIG. 9 by the amount of using the static pressure gas thrust bearing, but the conventional configuration in which both the static pressure gas thrust bearing and the static pressure gas journal bearing are provided. Compared to those, it can be manufactured inexpensively with a simple configuration.

It is the figure which combined the block diagram of the power transmission system diagram and the control system with sectional drawing of the torque measuring device of the tapered roller bearing concerning embodiment of 1st invention. (A) is sectional drawing of the same tapered roller bearing, (B) is sectional drawing which shows the state before the process. It is the figure which combined the block diagram of the power transmission system diagram and the control system with sectional drawing of the torque measuring device of the tapered roller bearing concerning different embodiment of 1st invention. It is the figure which combined the block diagram of the power transmission system diagram and the control system with the sectional view of the torque measuring device of the tapered roller bearing concerning still another embodiment of the 1st invention. It is the figure which combined the block diagram of the power transmission system diagram and the control system with the sectional view of the torque measuring device of the tapered roller bearing concerning still another embodiment of the 1st invention. It is the figure which combined the block diagram of the power transmission system diagram and the control system with sectional drawing of the torque measuring device of the tapered roller bearing concerning embodiment of 2nd invention. (A) is sectional drawing of the same tapered roller bearing, (B) is sectional drawing which shows the state before the process. It is the figure which combined the block diagram of the power transmission system diagram and the control system with sectional drawing of the torque measuring device of the tapered roller bearing concerning different embodiment of 2nd invention. It is the figure which combined the block diagram of the power transmission system diagram and the control system with the sectional view of the torque measuring device of the tapered roller bearing concerning further another embodiment of the 2nd invention. It is the figure which combined the block diagram of the power transmission system diagram and the control system with the sectional view of the torque measuring device of the tapered roller bearing concerning further another embodiment of the 2nd invention. It is the schematic of the torque measuring apparatus of the conventional tapered roller bearing.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Shaft 2 ... Housing 3 ... Static system 12 ... Collar equivalent part 13 ... Cylindrical body 16A ... Connecting plate (restraint means)
16B: Restraint material (restraint means)
20A ... strain gauge (driving force measuring means)
20B ... Force measuring gauge (driving force measuring means)
DESCRIPTION OF SYMBOLS 30 ... Tapered roller bearing 31 ... Inner ring 31c ... Inner ring large collar 32 ... Outer ring 32b ... Outer ring collar 33 ... Tapered roller 33a ... Large end surface 41 ... Static pressure gas thrust bearing 44 ... Force measuring gauge (rotational force measuring means)

Claims (12)

  An end face on the large end side of the tapered roller of the tapered roller bearing, comprising: a shaft that is integrally fitted to an inner ring of a tapered roller bearing that is a to-be-measured object; and a housing that is integrally fitted to an outer ring of the tapered roller bearing. A cylindrical body having a collar-corresponding portion in contact with the inner ring is provided separately from the inner ring, the cylindrical body is supported on the shaft via a rolling ball bearing, and the rotation with respect to the shaft is restrained by restraining means, A torque measuring device for a tapered roller bearing, characterized in that driving force measuring means for measuring a driving force acting on a cylindrical body is provided.   2. The torque measuring device for a tapered roller bearing according to claim 1, wherein the housing is fixed to a stationary system, and the shaft is driven to rotate.   2. The rotational force measuring means according to claim 1, wherein the housing is rotatably supported by a static pressure gas thrust bearing with respect to a stationary system, and the shaft is driven to rotate to measure the rotational force acting on the housing. Torque measuring device for tapered roller bearings.   2. The torque measuring device for a tapered roller bearing according to claim 1, wherein the shaft is fixed to a stationary system and the housing is driven to rotate.   2. The rotational force measuring means according to claim 1, wherein said shaft is rotatably supported by a static pressure gas thrust bearing with respect to a stationary system, and said housing is driven to rotate and rotational force acting on said shaft is measured. Torque measuring device for tapered roller bearings.   6. The device according to claim 1, wherein the restraining means is an elastic connecting plate that connects the shaft and the cylindrical body, and the driving force measuring means is configured to reduce distortion of the connecting plate. Torque measurement equipment for tapered roller bearings, which are strain gauges to measure.   An end face on the large end side of the tapered roller of the tapered roller bearing, comprising: a shaft that is integrally fitted to an inner ring of a tapered roller bearing that is a to-be-measured object; and a housing that is integrally fitted to an outer ring of the tapered roller bearing. A cylindrical body having a collar-corresponding portion in contact with the outer ring is provided separately from the outer ring, and the cylindrical body is supported by the housing via a rolling ball bearing, and the rotation with respect to the housing is restrained by restraining means, A torque measuring device for a tapered roller bearing, characterized in that driving force measuring means for measuring a driving force acting on a cylindrical body is provided.   8. The torque measuring device for a tapered roller bearing according to claim 7, wherein the housing is fixed to a stationary system and the shaft is driven to rotate.   8. The rotational force measuring means according to claim 7, wherein the housing is rotatably supported by a static pressure gas thrust bearing with respect to a stationary system, and the shaft is driven to rotate to measure rotational force acting on the housing. Torque measuring device for tapered roller bearings.   8. The torque measuring device for a tapered roller bearing according to claim 7, wherein the shaft is fixed to a stationary system and the housing is driven to rotate.   8. The rotational force measuring means according to claim 7, wherein said shaft is rotatably supported by a static pressure gas thrust bearing with respect to a stationary system, and said housing is driven to rotate and rotational force acting on said shaft is measured. Torque measuring device for tapered roller bearings.   The torque measuring device for a tapered roller bearing according to any one of claims 1 to 11, wherein the rolling bearing is an angular ball bearing.

Images