JP2007212179A - Support device for measuring characteristics of rolling bearing, and characteristics measuring device of the rolling bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a structure capable of measuring characteristic of a rolling bearing 1 with an outer ring 3 tilted with respect to an inner ring 5, and a structure capable of loading a heavier axial load, and directly measuring the inclination of the outer ring 3. <P>SOLUTION: The outer ring 3 is inserted into an inside housing 12 and fixed, and a projection part 28 is formed on the center part in the width direction of the outer ring 3 on the outer peripheral surface of the inside housing 12. An outside housing 13 is fitted around the projection part 28, and the inside housing 12 can be tilted with respect to the outside housing 13. Axial load is applied to the outside housing 13 by a load application mechanism 9. A pressurizing member 34, constituting the load application mechanism 9, is supported rotatably by a pair of angular type ball bearings 35a, 35b relative to a load loading rod 33. Hereby the problems can be solved. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention is a general-purpose rolling bearing used in various applications such as a heater for heating and a device for stirring gas filled in a box, and the outer ring is inclined with respect to the inner ring. Furthermore, the present invention relates to a support device for measuring characteristics of a rolling bearing used for measuring characteristics such as behavior of a cage incorporated in the rolling bearing, and improvement of a characteristic measuring apparatus for a rolling bearing incorporating the rolling bearing.

  When designing various mechanical devices, it is necessary to examine the characteristics of the rolling bearing incorporated in the rotation support portion of the mechanical device. For example, in an actual use state, the outer ring constituting the rolling bearing may be inclined with respect to the inner ring due to an assembly error or the like. Furthermore, an axial load may be applied to the rolling bearing with the outer ring inclined with respect to the inner ring. When the outer ring and the inner ring rotate relative to each other in a state where the outer ring is inclined with respect to the inner ring or is further loaded with an axial load, the outer ring is disposed between the outer ring and the inner ring. Further, the behavior of the cage that holds a plurality of rolling elements becomes unstable. In addition, the life of the rolling bearing is reduced. Therefore, if the above-described state can be reproduced when examining the characteristics of the rolling bearing, the behavior of the cage in this state can be grasped, and it can be confirmed whether or not the strength of the cage is appropriate. If various data can be obtained by reproducing the above state, it is useful for improving each member constituting the rolling bearing, including the cage. Furthermore, it is possible to examine the life of the rolling bearing in the above state.

  For example, Patent Documents 1 to 3 describe a technique for measuring the dynamic torque of a rolling bearing in order to improve the performance of the rolling bearing. In the case of the inventions described in these Patent Documents 1 to 3, a rolling bearing is installed in a normal state, and characteristics such as dynamic torque are measured. That is, in a state where a plurality of rolling bearings are incorporated in the measuring apparatus, the center axes of the inner ring and the outer ring that constitute the rolling bearing are substantially matched. In such a state, the dynamic torque of the rolling bearing is measured. On the other hand, Patent Document 4 describes a technique related to an apparatus capable of measuring the dynamic torque of a rolling bearing while the outer ring is inclined with respect to the inner ring. Therefore, by using this device, it is possible to reproduce the state in which the outer ring is inclined with respect to the inner ring and to examine the behavior of the cage as described above.

  However, the structure described in Patent Document 4 is intended for a relatively small diameter rolling bearing such as a rolling bearing incorporated in a fan motor of an air conditioner. In the case of such a small-diameter ball bearing, the axial load acting in actual use is not so large. In other words, it is rarely used in a situation where a large axial load is applied. Therefore, in the case of the structure described in Patent Document 4, an axial load is applied by the expansion / contraction force of a spring material or the like. Since the absolute value of the force generated by the expansion and contraction force of such a spring material is limited, the structure described in the above-mentioned Patent Document 4 should be used when a larger axial load is to be applied. Is difficult (further design changes are required). In the case of the structure described in Patent Document 4, the actual inclination of the outer ring is indirectly measured by an expensive laser micro displacement meter.

JP 2000-155073 A JP 2000-162092 A JP 2001-194270 A JP 2005-69884 A

  In view of the circumstances as described above, the present invention has a structure capable of measuring the characteristics of a rolling bearing while the outer ring is inclined with respect to the inner ring, and can apply a larger axial load. It was invented to realize a measurable structure.

Of the rolling bearing characteristic measurement support device and rolling bearing characteristic measurement device according to the present invention, the rolling bearing characteristic measurement support device according to claim 1 includes an outer ring having an outer ring raceway on an inner peripheral surface, and an outer peripheral surface. The characteristics of a rolling bearing provided with an inner ring having an inner ring raceway, a plurality of rolling elements provided between the outer ring raceway and the inner ring raceway, and a cage for holding the respective rolling elements are provided. The rolling bearing is supported for measurement.
In particular, in the case of the rolling bearing characteristics measuring support device according to claim 1, the outer ring is held, and a housing capable of transmitting a rotational force to the outer ring is disposed, and the housing is arranged concentrically with the housing. A support shaft for supporting and fixing the inner ring. The housing includes an annular inner housing that fits and fixes the outer ring, and an annular outer housing that is fitted onto the outer peripheral surface of the inner housing. The inner housing and the outer housing are fitted only at the center in the width direction of the outer ring, and the inner housing can be inclined with respect to the outer housing together with the outer ring.
In addition, as a specific structure for positioning the fitting portion at the center in the width direction of the outer ring, for example, as described in claim 2, a part of the outer peripheral surface of the inner housing or the inner periphery of the outer housing A part of the surface is protruded over the entire circumference, and the protruding part and the mating surface are fitted. Alternatively, the outer peripheral surface of the inner housing and the inner peripheral surface of the outer housing are respectively cylindrical surfaces, and a belt-shaped cylindrical member is fitted to any one of these peripheral surfaces, and the cylindrical member is interposed therebetween. The both peripheral surfaces are fitted together. Thus, the fitting portion between the inner housing and the outer housing is the center portion in the width direction of the outer ring.

According to a third aspect of the present invention, there is provided a rolling bearing characteristic device comprising an inclined holding mechanism, a load applying mechanism, and a rotation transmitting mechanism.
Of these, the tilt holding mechanism can hold a state in which the outer ring is quantitatively tilted with respect to the inner ring.
The load applying mechanism applies an axial load to the outer ring.
The rotation transmission mechanism transmits a rotational force to the outer ring.
Then, the outer ring is tilted with respect to the inner ring, and the characteristics generated in the rolling bearing when the outer ring is rotated with an axial load applied to the outer ring are measured.
In particular, in the case of the rolling bearing characteristic measuring device according to claim 3, the inclined holding mechanism is the rolling bearing characteristic measuring support device according to claim 1 or claim 2. In order to incline the outer ring, the outer ring is inclined by inclining the inner housing with respect to the outer housing. The load applying mechanism applies an axial load to the outer ring through the outer housing and the inner housing by applying an axial load to the outer housing. The rotation transmission mechanism rotates the outer ring together with the inner housing and the outer housing.

Further, when measuring with the rolling bearing characteristic measuring device described in claim 3, for example, as described in claim 4, the outer ring is inclined with respect to the inner ring and an axial load is applied to the outer ring. In this state, when the outer ring is rotated, the deflection in the axial direction of the end face of the outer ring or the end face of the inner housing is measured. By measuring this deflection, the actual inclination of the outer ring can be measured.
Furthermore, the load application mechanism described in claim 5 is used as the load application mechanism of the above-described rolling bearing characteristic measurement device. The load applying mechanism includes a load load rod that receives an axial load, and a pressure member that is disposed on the outer diameter side of the load load rod and that contacts the outer housing and applies the axial load to the outer housing. Prepare. Among these, the pressurizing member is rotatably supported via a pair of angular ball bearings with respect to the load rod. As these double ball bearings, it is preferable to use precision ball bearings with high dimensional accuracy. Further, the axial load applied to the load load rod can be applied to the outer housing through the ball bearings and the pressure member. Further, when the outer ring is rotated by the rotation transmission mechanism, the pressure member can be rotated together with the outer housing and the inner housing.

  In the present invention configured as described above, in the case of the invention described in claim 1, the fitting portion between the inner housing and the outer housing is located only in the center in the width direction of the outer ring. It becomes easy to incline with respect to an outer housing. For this reason, the inner housing can be easily inclined with respect to the outer housing without being eccentric. As a result, the state in which the outer ring fitted and fixed to the inner housing is inclined with respect to the inner ring can be easily reproduced. In addition, as described in claim 2, if the outer peripheral surface of the inner housing or a part of the inner peripheral surface of the outer housing is protruded, the structure in which the fitting portion is only the central portion in the width direction of the outer ring is easy. Is obtained.

  Further, according to the invention described in claim 3, the characteristics of the rolling bearing can be measured with the outer ring inclined with respect to the inner ring by the structure described in claim 1 or 2. In addition, as described in claim 4, the inclination of the outer ring can be directly measured by measuring the deflection of the end face of the outer ring or the end face of the inner housing. For example, an indicator such as a dial gauge is installed on the end face of the outer ring or the end face of the inner housing, and the runout of the end face is measured. From the absolute value of the runout and the distance from the bearing center to the measurement position, The actual inclination of the outer ring can be easily checked. Furthermore, as described in claim 5, if the pressure member for applying an axial load is supported by a pair of angular ball bearings with respect to the load load rod, the axial load is applied to the outer ring. It is possible to rotate the outer ring. Further, since the rigidity of the support portion between the pressure member and the load load rod can be increased, it is possible to increase the axial load that can be applied to the rolling bearing. In addition, when the angular ball bearing is a precision ball bearing, the pressure member is prevented from swinging due to rotation, and this pressure member affects the measurement of characteristics of the rolling bearing. Can be prevented.

  1 to 3 show an example of an embodiment of the present invention. A rolling bearing 1, which is an object to be measured in this embodiment, includes an outer ring 3 having an outer ring raceway 2 on an inner peripheral surface, an inner ring 5 having an inner ring raceway 4 on an outer peripheral surface, and the outer ring raceway 2 and the inner ring raceway 4. A plurality of rolling elements 6, 6 provided between the rolling elements 6, 6 are provided. In the case of the present embodiment, a description will be given of a case where a ball bearing having a nominal number 6202 (inner diameter 15 mm, outer diameter 35 mm, width 11 mm) is used as the rolling bearing 1.

  The characteristic measuring device 7 of the rolling bearing 1 of this example measures the characteristics of the rolling bearing 1 in a state where a predetermined inclination angle is applied to the outer ring 3. The characteristic measuring device 7 includes an inclination holding mechanism 8, a load applying mechanism 9, and a rotation transmission mechanism (not shown). Of these, the tilt holding mechanism 8 includes a housing 10 and a support shaft 11, and constitutes a rolling bearing characteristic measurement support device described in the claims. The housing 10 includes an annular inner housing 12 that fits and fixes the outer ring 3, and an annular outer housing 13 that is fitted onto the outer peripheral surface of the inner housing 12. The inner housing 12 and the outer housing 13 are coupled by coupling bolts 14 at a plurality of locations in the circumferential direction (eight locations in the illustrated example).

  That is, as shown in FIG. 2, screw holes 15 are formed at a plurality of locations in the circumferential direction near the inner diameter of the outer housing 13. At the same time, the flange portion 16 formed at the base end portion (the right end portion in FIG. 1) of the inner housing 12 is axially aligned at a position aligned with the screw holes 15 and 15 {FIGS. 1 and 2A. The through-holes 17 penetrating in the left-right direction and the front-back direction in FIG. 2B are respectively formed. As shown in FIG. 1, the inner housing 12 and the outer housing 13 are coupled by inserting the coupling bolts 14 into the through holes 17 and screwing and tightening the threaded bolts 15. Yes.

  The outer ring 3 is fitted and fixed to the inner peripheral surface of the inner housing 12 by an interference fit. Then, in a state where the inner ring portion of the abutting plate 18 is abutted against one end surface (the left end surface in FIG. 1) of the outer ring 3, the outer diameter portion of the abutting plate 18 is placed on the inner housing 12. Further, it is fixed by a plurality of fixing bolts 19, 19. Thus, the outer ring 3 is fitted and fixed to the inner peripheral surface of the inner housing 12, and the outer ring 3 is positioned in the axial direction. With this configuration, the outer ring 3 is held in the housing 10 and the rotational force can be transmitted to the outer ring 3. The housing 10 is driven via, for example, a belt transmission mechanism (not shown) and transmits the rotational force to the outer ring 3.

  On the other hand, the support shaft 11 is arranged concentrically with the housing 10 (only the outer housing 13 when the inner housing 12 is inclined as will be described later), has a stepped columnar shape, and has a small diameter formed at the tip. The inner ring 5 is externally fitted and fixed to the portion 20 while being sandwiched between the spacer 21 and the cap 22. That is, the spacer 21 is formed in an annular shape with an L-shaped cross section, and the outer diameter of the other half in the axial direction (the left half in FIG. 1) is set to the other end of the outer ring 3 (the right end in FIG. 1). ), And the outer diameter of one half in the axial direction (the right half in FIG. 1) is set to a step 24 between the small diameter portion 20 and the large diameter portion 23 in the middle portion of the support shaft 11. It is larger than the outer diameter. The other end surface of the inner ring 5 is brought into contact with one end surface of the spacer 21 in a state where the other end surface of the spacer 21 (the right end surface in FIG. 1) is abutted against the step 24.

  The cap 22 is formed in an annular shape having an L-shaped cross section, and a through hole 25 is formed at the center of one end surface. Further, the outer diameter of the cap 22 is made smaller than the inner diameter of one end portion of the outer ring 3, and the front end surface of the cap 22 is brought into contact with one end surface of the inner ring 5. Then, the inner ring fixing bolt 26 is inserted into the through hole 25, and the tip portion or intermediate portion of the inner ring fixing bolt 26 is formed in the center of the tip portion of the support shaft 11 in the axial direction. 27 is screwed and tightened. As a result, the inner ring 5 is clamped and fixed between the step 24 and the cap 22 via the spacer 21.

  In this example, the inner housing 12 is inclined with respect to the outer housing 13 so that the outer ring 3 fitted and fixed to the inner housing 12 can be inclined. For this purpose, a protruding portion 28 having an outer diameter larger than that of other portions of the outer peripheral surface is formed over the entire circumference at the intermediate portion of the outer peripheral surface excluding the flange portion 16 of the inner housing 12. . The position of the protruding portion 28 in the axial direction is as shown by a chain line a in FIG. 1 in a state where the outer ring 3 is fitted and fixed to the inner housing 12 and the center of the protruding portion 28 in the width direction of the outer ring 3. The center of the width direction is the same. Further, the outer housing 13 is fitted into the protruding portion 28. That is, the inner peripheral surface of the outer housing 13 is a single cylindrical surface except for one end. The cylindrical surface portion is externally fitted to the protruding portion 28. It is preferable that the outer diameter of the protruding portion 28 and the inner diameter of the cylindrical surface of the outer housing 13 are substantially the same, and the fitting portion between the protruding portion 28 and the cylindrical surface is an intermediate fit.

  Further, a flange 29 is formed on the inner peripheral surface of one end portion of the outer housing 13 so as to protrude to the inner diameter side of the cylindrical surface portion and has an inner diameter smaller than the outer diameter of the one end portion of the inner housing 12. Thereby, the fitting direction of the outer housing 13 with respect to the inner housing 12 is restricted. In the state where the outer housing 13 and the inner housing 12 are coupled, the flange 29 is not brought into contact with one end surface of the inner housing 12, and a gap is provided between the flange 29 and the one end surface. Thus, as will be described later, when the inner housing 12 is inclined with respect to the outer housing 13, the end surface of the inner housing 12 is prevented from interfering with the flange portion 29.

  As described above, since the center in the width direction of the protruding portion 28 and the center in the width direction of the outer ring 3 coincide with each other, the fitting portion between the inner housing 12 and the outer housing 13 is the center in the width direction of the outer ring 3. Located in the department. The width of the protruding portion 28 in the axial direction is preferably ¼ or less, more preferably ５ or less of the width dimension of the rolling bearing 1 that is the object to be measured. Further, the outer diameter of the fitting portion (the outer diameter of the protruding portion 28) is preferably 1.5 times or more, more preferably twice or more the outer diameter of the rolling bearing 1. Further, the protrusion amount {(outer diameter of protrusion 28−outer diameter of other part of outer peripheral surface) / 2} of protrusion 28 is preferably 0.5 mm or more, more preferably 1.0 mm or more. . As a result, 0.5 mm (in the portion where the inner peripheral surface of the inner housing 12 and the outer peripheral surface of the outer housing 13 face each other except the fitting portion (both sides of the fitting portion in the axial direction) Or a gap of 1.0 mm or more can be secured. Further, as described above, if the width, outer diameter, and protruding amount of the protruding portion 28 are restricted, the inner housing 12 can be more easily inclined with respect to the outer housing.

  The outer peripheral surface of the inner housing 12 (excluding the flange portion 16) is a single cylindrical surface, and the protruding portion that protrudes radially inward at the central portion in the width direction of the outer ring 3 on the inner peripheral surface of the outer housing 13 is completely formed. It is also possible to form the fitting part by forming it around the circumference. In addition, the outer peripheral surface of the inner housing 12 and the inner peripheral surface of the outer housing 13 are respectively cylindrical surfaces (without forming protrusions), and a belt-like cylindrical member is fitted on either of these peripheral surfaces. In addition, the above-described protruding portion can be constituted by this cylindrical member.

  In the case of this example, in order to incline the inner housing 12 with respect to the outer housing 13, the screw holes 15, 15 are arranged on the same pitch circle P as the screw holes 15, 15 of the outer housing 13. The second screw holes 30, 30 are formed at a plurality of locations deviating from the circumferential direction. In the case of the illustrated example, each of these second screw holes 30 and 30 is formed at three locations, the upper end portion of FIGS. 1 and 2 and the horizontal end portions of FIG. 2B, and the lower end of FIGS. It is not formed in the part. When the inner housing 12 is tilted clockwise in FIGS. 1 and 2A, the second screw located at the upper end of FIGS. A stud 31 is screwed into the hole 30 and the tip of the stud 31 is abutted against the flange portion 16 of the inner housing 12.

  Then, the distance between the other end surface of the outer housing 13 and the flange portion 16 is changed by adjusting the protruding amount of the tip end portion of the stud 31 from the second screw hole 30, and the inner housing 12. Is inclined with respect to the outer housing 13 and the inclination can be adjusted. The amount of protrusion of the stud 31 is adjusted by locking a tool such as a screwdriver in a notch formed on the base end surface of the stud 31 and rotating the stud 31. After the adjustment, among the studs 31 screwed into the second screw hole 30, a lock nut 32 screwed into a portion protruding from the second screw hole 30 to the side opposite to the flange portion 16 is provided. The stud 31 is fixed by tightening.

  When the inner housing 12 and the outer ring 3 are inclined with respect to the outer housing 13, the connecting bolts 14 that connect the inner housing 12 and the outer housing 13 are loosened. Further, a rotation-preventing screw 48 is screwed into a part of the outer peripheral surface of the outer housing 13 to prevent the inner housing 12 and the outer housing 13 from rotating. And the protrusion amount of the front-end | tip part of the said stud 31 is adjusted. When the inner housing 12 is tilted clockwise in FIGS. 1 and 2A, the protruding amount of the tip of the stud 31 screwed into the second screw hole 30 existing in the upper end of FIGS. Adjust. As a result, the inner housing 12 is inclined together with the outer ring 3 in the clockwise direction in FIGS. 1 and 2A around the bearing center of the rolling bearing 1. Note that the center of the inclination is almost the center of the bearing, although there may be some deviation from the center of the bearing due to the internal clearance of the bearing. Therefore, the bearing center includes a shift due to such an internal gap. The same applies to the following.

  When the inner housing 12 and the outer ring 3 are inclined at a desired angle, the connecting bolts 14 are screwed and tightened. As a result, the inner housing 12 and the outer ring 3 are held at a desired angle with respect to the outer housing 13. Since the outer housing 13 and the support shaft 11 are disposed concentrically with each other, the outer ring 3 is held in an inclined state with respect to the inner ring 5 fitted on the support shaft 11 by the predetermined angle. .

Prior to screwing and tightening each of the coupling bolts 14, the protrusions of the tip ends of a pair of studs screwed into both the second screw holes 30, 30 existing at both ends in the horizontal direction in FIG. When the amounts of the studs are adjusted so that the ends of both studs abut against the flange portion 16, when the connecting bolts 14 are screwed and tightened to hold the inner housing 12 in a state inclined at a desired angle. The inner housing 12, together with the outer ring 3, can be prevented from swinging in the direction of rotation about the chain line i passing through the center of the rolling bearing 1 in the width direction. Thereby, the inclination angle of the inner housing 12 can be adjusted more accurately.
Note that the amount of protrusion of the pair of studs from the outer housing 13 is 1/2 of the amount of protrusion of the stud 31 at the upper end of FIG.

  On the other hand, the load applying mechanism 9 applies an axial load to the rolling bearing 1 and is composed of a load load rod 33, a pressure member 34, and a pair of angular ball bearings 35a and 35b. Is done. Of these, the load rod 33 can be displaced in the axial direction by a load device such as an air cylinder (not shown). Further, the load applied by the load device is measured by a load measuring device such as a load cell. The pressure member 34 is disposed concentrically with the load load rod 33 around the tip end portion of the load load rod 33 via the ball bearings 35a and 35b. The pressure member 34 includes a pressure ring 36, a housing 37, and a housing cover 38. As shown in FIG. 3, the pressure ring 36 includes an annular portion 39 and an end surface near the outer diameter of the annular portion 39 {right end surface in FIGS. 1 and 3A) in the axial direction. It comprises a protruding pressure part 40. As shown in FIG. 3B, the pressurizing portion 40 is concentric with the annular portion 39 and has notches 41 and 41 at a plurality of circumferential locations (in the illustrated example, five locations). It is formed in a comb-teeth shape (annular fence shape). In addition, mounting holes 42 and 42 penetrating in the axial direction are formed in the notches 41 and 41 of the circular ring portion 39.

  The pressure ring 36 is fixed to one end face of the housing 37 fitted around the ball bearings 35a, 35b by mounting bolts 43 inserted through the mounting holes 42, 42, respectively. For this purpose, an inner diameter portion of the end surface {the left end surface in FIGS. 1 and 3A) opposite to the one end surface of the pressure ring 36 is projected in the axial direction to form a cylindrical portion 44. The front end surface of the cylindrical portion 44 is brought into contact with a portion near the outer diameter of one end of the ball bearing 35a of one of the ball bearings 35a and 35b (right side in FIG. 1), and the cylindrical portion 44 One end of the housing 37 is externally fitted. In this state, the housing 37 and the pressure ring 36 are coupled by the mounting bolts 43.

  The housing cover 38 has an annular shape and is fixed to the opposite end face of the housing 37 by a plurality of mounting bolts 49, 49, and the inner diameter portion is the other of the ball bearings 35a, 35b (see FIG. 1). The ball bearing 35b on the left side is in contact with a portion near the outer diameter of the opposite end surface. As a result, the ball bearings 35a and 35b are sandwiched between the housing cover 38 and the pressure ring 36. And the said pressurization member 34 which consists of the said pressure ring 36, the housing 37, and the housing cover 38 is fixed to the outer-diameter side of these ball bearings 35a and 35b.

  The ball bearings 35a and 35b are angular-type (or deep-groove type) ball bearings having a back surface combination and imparting contact angles in opposite directions. These ball bearings 35a and 35b are precision ball bearings with high dimensional accuracy. As these ball bearings 35a and 35b, for example, those having an inner diameter of 30 mm, an outer diameter of 62 mm, and a width of 15 mm are used. The ball bearings 35a and 35b are fitted and fixed to the outer peripheral surface of the tip end portion of the load rod 33. In addition, a portion closer to the inner diameter of the opposite end surface of the other ball bearing 35b is brought into contact with the outward flange 45 formed on the outer peripheral surface of the intermediate portion of the load rod 33. In this state, one end surface of one of the ball bearings 35a is flush with the tip surface of the load load rod 33 or slightly protrudes from the tip surface. Then, a portion near the outer diameter of the disk-shaped fixing plate 46 is brought into contact with a portion near the inner diameter of the one end surface of the one ball bearing 35a. The fixing plate 46 is fixed to the tip surface of the load rod 33 by a fixing bolt 47. Therefore, by screwing and tightening the fixing bolt 47, the ball bearings 35a and 35b are fixed between the fixing plate 46 and the outward flange 45 so as not to be displaced in the axial direction.

  The load applying mechanism 9 configured as described above is disposed concentrically with the tilt holding mechanism 8 at a position facing the tilt holding mechanism 8. Then, the front end surface of the pressurizing portion 40 of the pressurizing ring 36 constituting the pressurizing member 34 is brought into contact with a portion closer to the inner diameter of one end surface of the outer housing 13 of the housing 10 constituting the inclined holding mechanism 8. In addition, it is preferable that the position in the radial direction to be contacted in this way is a portion where the flange portion 16 of the inner housing 12 and a portion closer to the inner diameter of the outer housing 13 overlap in the axial direction. That is, it is preferable that the inner housing 12 and the outer housing 13 be connected to each other. Thereby, as will be described later, the axial load applied by the pressure unit 40 can be more smoothly transmitted to the outer ring 3. At this time, there is an adjusting screw 31 for rotating the pressure member 34 to incline the inner housing 12 with the notches 41 and 41 formed at a plurality of locations in the circumferential direction of the pressure ring 36. Align with the part. Thereby, the front end surface of the pressurizing portion 40 can be brought into contact with one end surface of the outer housing 13 without interfering with the adjusting screw 31.

  When measuring the characteristics of the rolling bearing 1 that is the object to be measured, the outer ring 3 constituting the rolling bearing 1 is similarly inclined at a predetermined angle with respect to the inner ring 5 by the tilt holding mechanism 8 as described above. In this state, by driving a load device such as an air cylinder of the load applying mechanism 9 and pushing the load load rod 33 in the axial direction, the ball bearings 35a and 35b and the pressure member 34 are interposed. Then, an axial load is applied to the housing 10 in which the outer ring 3 is fitted and fixed. This axial load is measured by a load measuring device such as a load cell incorporated in the load applying mechanism 9 and adjusted to a predetermined magnitude. Further, since the front end surface of the pressure member 40 of the pressure member 34 is in contact with one end surface of the outer housing 13, the axial load applied as described above is applied to the outer housing 13 and the inner housing. 12 is applied to the outer ring 3 through 12.

  As described above, the outer ring 3 is tilted with respect to the inner ring 5, and the outer ring 3 is rotated by a rotation transmission mechanism (not shown) while an axial load is applied to the outer ring 3. That is, the housing 10 is rotationally driven via, for example, a belt transmission mechanism or the like constituting the rotation transmission mechanism. At this time, the anti-rotation screw 48 screwed into a part of the outer peripheral surface of the outer housing 13 constituting the housing 10 is removed. As a result, the outer ring 3 fitted and fixed to the housing 10 together with the housing 10 is rotationally driven. Further, the outer housing 13 constituting the housing 10 and the pressurizing portion 40 of the pressurizing member 34 constituting the load applying mechanism 9 are in strong contact with each other due to the load of the axial load. The pressure member 34 is also rotated by the rotation. Since the pressure member 34 is rotatably supported by the pair of ball bearings 35 a and 35 b as described above, it smoothly rotates together with the housing 10.

  As described above, since the outer ring 3 that rotates together with the pressure member 34 and the housing 10 is inclined with respect to the inner ring 5 as described above, the outer ring 3 swings in the axial direction by this rotation. The axial runout is measured by bringing a measuring unit of a measuring device such as a dial gauge into contact with the end face of the outer ring 3 or the end face of the inner housing 12 and measuring the runout of the outer ring 3 in the axial direction. For example, the measuring device is installed on one side of the inner housing 12 (right side in FIG. 1), and the measuring unit of the measuring device is brought into contact with any part of one side surface of the inner housing 12. If the housing 10 is rotated in this state, the deflection of the outer ring 3 can be measured. The actual inclination of the outer ring 3 can be easily checked from the absolute value of this deflection and the distance from the bearing center of the rolling bearing 1 to the measurement position. Therefore, it is not necessary to indirectly measure the inclination of the outer ring 3 with an expensive laser micro displacement meter.

  After measuring the inclination of the outer ring 3 as described above, for example, when the outer ring 3 is operated in an inclined state, the behavior of a cage (not shown) incorporated in the rolling bearing 1 or the rolling bearing 1 is measured. It is possible to investigate various characteristics such as life.

  In the case of this example configured as described above, since the fitting portion between the inner housing 12 and the outer housing 13 is located only in the center portion in the width direction of the outer ring 3, the inner housing 12 is connected to the outer housing 13. It becomes easy to incline with respect to it. That is, when the amount of protrusion of the stud 31 screwed into the second screw hole 30 of the outer housing 13 into the inner housing 12 is adjusted and the inner housing 12 is inclined, the inner housing 12 and the outer ring are tilted. 3 inclines around the bearing center of the rolling bearing 1. When the inner housing 12 is inclined in the clockwise direction in FIG. 1, among the lines passing through the bearing center and orthogonal to the axial direction of the rolling bearing 1, the above-mentioned line is centered on the front and back direction line (rotation center line) in FIG. 1. The inner housing 12 is inclined. In this case, the inner housing 12 is inclined with the fitting portion existing on the rotation center line out of the fitting portions between the inner housing 12 and the outer housing 13. In other words, since the fitting portion exists only in the center portion in the width direction of the outer ring 3, any portion of the fitting portion is always present on the rotation center line when tilting.

  In addition, the fitting portions present in the portions other than on the rotation center line tend to be shifted in the axial direction from the central portion in the width direction of the outer ring 3. In this case, at least one of the projecting portion 28 constituting the fitting portion and the inner peripheral surface of the outer housing 13 is elastically deformed to allow the inner housing 12 to be inclined with respect to the outer housing 13. In the case of this example, since the fitting portion exists only in the center portion in the width direction of the outer ring 3, the amount of elastic deformation generated in this way is small. As described above, when the fitting portion between the inner housing 12 and the outer housing 13 is present only at the center in the width direction of the outer ring 3, the inner housing 12 can be easily inclined with respect to the outer housing 13. Further, since the tilt is centered on the rotation center line as described above, the amount of elastic deformation generated in the fitting portion is substantially equal at a symmetrical position with respect to the bearing center. For this reason, the inner housing 12 and the outer housing 13 are not eccentric (the amount is extremely small even if eccentric).

  As a result of acting as described above, the state in which the outer ring 3 fitted and fixed to the inner housing 12 is inclined with respect to the inner ring 5 can be easily and stably reproduced. Further, since the pressing member 34 constituting the load applying mechanism 9 is supported by the pair of angular type or deep groove type ball bearings 35a and 35b with respect to the load load rod 33, an axial load is applied to the outer ring 3. In this state, the outer ring 3 can be rotated. Further, the rigidity of the support portion between the pressing member 34 and the load rod 33 can be sufficiently increased. For this reason, it is possible to increase the axial load that can be applied to the rolling bearing 1. In the case of this example, the ball bearings 35a and 35b are precision ball bearings. Therefore, the pressure member 34 is prevented from swinging due to rotation, and the pressure member 34 is used for the rolling bearing 1. It can prevent the influence on the characteristic measurement.

  In the example of the embodiment described above, the structure for examining the characteristics of the rolling bearing 1 when the outer ring 3 is rotated has been described. However, with the structure described above, the rolling bearing 1 when the inner ring 5 is rotated is described. It is also possible to examine the characteristics of That is, the support shaft 11 that supports the inner ring 5 is rotated to fix the housing 10. Then, with the inner ring 5 being rotated, the characteristics of the rolling bearing 1 such as the behavior of the cage are examined. In the above description, the rolling bearing 1 which is the object to be measured is limited to a predetermined ball bearing. However, the rolling bearing to be measured according to the present invention is installed in a heater or a box for heating. General-purpose ball bearings that are used in various applications, such as being incorporated in a device that stirs the filled gas, are included. Further, not only ball bearings but also roller bearings using rollers as rolling elements are also subject to measurement of the present invention.

Sectional drawing which shows the characteristic measuring apparatus of the rolling bearing of an example of embodiment of this invention. Only the outer housing is shown, (A) is a cross-sectional view, (B) is a view with a part omitted, as viewed from the right side of (A). Only the pressure ring is shown, (A) is a cross-sectional view, (B) is a view as seen from the right side of (A).

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Rolling bearing 2 Outer ring raceway 3 Outer ring 4 Inner ring raceway 5 Inner ring 6 Rolling element 7 Characteristic measuring device 8 Inclination holding mechanism 9 Load applying mechanism 10 Housing 11 Support shaft 12 Inner housing 13 Outer housing 14 Coupling bolt 15 Screw hole 16 Flange 17 Hole 18 Abutting plate 19 Fixing bolt 20 Small diameter part 21 Spacer 22 Cap 23 Large diameter part 24 Step 25 Through hole 26 Inner ring fixing bolt 27 Screw hole 28 Projection part 29 Hook part 30 Second screw hole 31 Stud 32 Lock nut 33 Load rod 34 Pressure member 35a, 35b Ball bearing 36 Pressure ring 37 Housing 38 Housing cover 39 Ring portion 40 Pressure portion 41 Notch 42 Mounting hole 43 Mounting bolt 44 Cylindrical portion 45 Outward flange portion 46 Fixing plate 47 Fixing Bolt 48 Anti-rotation screw 49 Installation bolt

Claims (5)

  An outer ring having an outer ring raceway on the inner peripheral surface, an inner ring having an inner ring raceway on the outer peripheral surface, a plurality of rolling elements provided between the outer ring raceway and the inner ring raceway, and a rolling element A bearing device for measuring the characteristics of a rolling bearing that supports the rolling bearing in order to measure the characteristics of the rolling bearing provided with a retainer that holds the outer ring, and that also provides rotational force to the outer ring. And a support shaft that is arranged concentrically with the housing and supports and fixes the inner ring, and the housing includes an annular inner housing in which the outer ring is fitted and fixed, and an inner housing of the inner housing. It is composed of an annular outer housing that is externally fitted to the outer peripheral surface, and these inner housing and outer housing are fitted only at the center in the width direction of the outer ring, and this inner housing, together with the outer ring, Tiltable and characteristics measured supporting device of a rolling bearing relative to the outer housing of the.   By projecting a part of the outer peripheral surface of the inner housing or a part of the inner peripheral surface of the outer housing over the entire circumference, and fitting the projecting part with the mating surface, the inner housing and the outer housing The support device for measuring characteristics of a rolling bearing according to claim 1, wherein the fitting portion is a central portion in the width direction of the outer ring.   An inclination holding mechanism capable of holding the outer ring quantitatively inclined with respect to the inner ring, a load applying mechanism that applies an axial load to the outer ring, and a rotation transmission mechanism that transmits a rotational force to the outer ring. In addition, the outer ring is inclined with respect to the inner ring, and a characteristic measurement device for a rolling bearing that measures characteristics generated in the rolling bearing when the outer ring is rotated with an axial load applied to the outer ring. The tilt holding mechanism is the rolling bearing characteristic measurement support device according to claim 1 or 2, wherein the outer ring is tilted by tilting the inner housing with respect to the outer housing. The load applying mechanism is configured to apply an axial load to the outer housing through the outer housing and the inner housing. Kigairin to is intended to provide this axial load, the rotation transmission mechanism is characteristic measuring apparatus of the rolling bearing is intended for rotating the outer ring with the inner housing and the outer housing.   Measure the runout in the axial direction of the end face of the outer ring or the end face of the inner housing when the outer ring is rotated while the outer ring is inclined with respect to the inner ring and an axial load is applied to the outer ring. 4. The rolling bearing characteristics measuring device according to claim 3, wherein the actual inclination of the outer ring can be measured. The load applying mechanism includes a load load rod that receives an axial load, and a pressure member that is disposed on the outer diameter side of the load load rod and that contacts the outer housing and applies the axial load to the outer housing. Of these, the pressure member is rotatably supported by a pair of angular type or deep groove type ball bearings with respect to the load load rod, and the axial load applied to the load load rod is reduced. The outer bearing can be applied to the outer housing via the ball bearings and the pressure member, and when the outer ring is rotated by the rotation transmission mechanism, the pressure member can be rotated together with the outer housing and the inner housing. The characteristic measuring apparatus of the rolling bearing according to claim 3 or 4.

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