JP4956995B2 - Bearing support device - Google Patents

Description

  The present invention relates to a bearing support device that supports a rotating shaft such as in a transmission, and more particularly to a bearing supporting device that facilitates a vibration suppression design against vibrations generated on the rotating shaft.

  For example, a rolling bearing is used to rotatably support a rotating shaft in a vehicle transmission. In general, a rolling bearing includes an outer ring that is press-fitted into a bearing support body such as a transmission transmission case, an inner ring that is concentrically positioned on the inner peripheral side of the outer ring, and a rotation shaft that is inserted into the inner peripheral surface, and an inner ring. It is comprised by the rolling element interposed between the outer ring | wheels, and the holder | retainer holding a rolling element.

  In ordinary bearings, the inner ring and rotating shaft of the bearing and the contact surface between the outer ring and the bearing support are fitted with an interference fit, an intermediate fit, a clearance fit, etc. It has a circular cross section. Here, when vibration is generated on the rotating shaft supported by the bearing, they are transmitted to the rotating support via the bearing. In order to reduce this vibration, in the rolling bearing disclosed in Patent Document 1, a synthetic resin sleeve having protrusions and the like is inserted and fixed on the inner peripheral surface of the inner ring of the rolling bearing, and the vibration is absorbed by the sleeve. The vibration transmitted to the bearing support is reduced. Further, Patent Document 2 discloses a technique for absorbing vibration by inserting damping means in a portion where deformation energy excited by a bearing is most concentrated and reducing vibration transmitted to the bearing support. ing.

Japanese Utility Model Publication No. 63-80328 JP 2000-224802 A

  By the way, as described above, in a normal bearing, each contact surface has a circular cross section. However, strictly speaking, it is generally not a perfect circle, and it is generally a circle due to pressing by a meshing reaction force or deformation due to temperature change. The fit is maintained on the circumference in a biased load distribution state. In such a state, for example, when vibration generated at a gear meshing portion or the like is transmitted to the rotating shaft, the vibration is intensively transmitted from the portion where the biased load is applied to the rotating support. The generation of such a biased load distribution is governed by various other force generation conditions such as the roundness of the rotating shaft and the material, and thus cannot be easily grasped. For this reason, the load distribution cannot be set arbitrarily, and it is difficult to design a free vibration control from the viewpoint of vibration control. In Patent Documents 1 and 2, vibrations can be reduced, but it is impossible to set a load distribution. In such a case, for example, the vibration generated in the meshing portion of the gear may be intensively transmitted to the part that is weak against the vibration of the bearing support via the rotating shaft and the bearing, and the transmission of the vibration is increased. There was also a risk that the vibration and noise of the bearing support would be increased. There is also a bearing support device that absorbs vibration by sandwiching a vibration damping material between the inner ring and the rotating shaft and between the outer ring and the bearing support. However, when the load is concentrated on a certain part, the vibration damping material is sufficient. There was a problem that the effect of can not be obtained.

  The present invention has been made against the background of the above circumstances, and the object of the present invention is to support a bearing that facilitates vibration damping design by dispersing or placing the load applied to the bearing at an arbitrary position. To provide an apparatus.

To achieve the above object, the gist of the invention according to claim 1 is that (a) an outer ring fitted on the bearing support, and an inner ring on the inner circumference side of the outer ring is concentrically rotated on the inner circumference surface. In a bearing support device comprising an inner ring into which a shaft is fitted, and a rolling element interposed between the outer ring and the inner ring, and rotatably supporting the rotating shaft, (b) the bearing support and the the one and the other of the outer ring has an axial thickness, is provided respectively engaging protrusion and engaging groove for receiving a load fitted in a state of surface contact with each other in a tight fit state, ( c) On one and the other of the rotating shaft and the inner ring, there are an engagement convex portion and an engagement groove having a thickness in the axial direction and fitted in a state of being in surface contact with each other and receiving a load. Each is provided .

  According to a second aspect of the present invention, there is provided the bearing support device according to the first aspect, wherein the engaging convex portion is at least one of the outer ring so as to protrude radially from the outer peripheral surface of the outer ring. The bearing support body is provided with an engaging groove that is fitted into the engaging convex portion, and is provided at a projecting position.

  According to a third aspect of the present invention, in the bearing support device according to the second aspect, the engagement convex portion is fitted into a key groove provided on the outer peripheral surface of the outer ring. It is composed of keys.

According to a fourth aspect of the present invention, there is provided a bearing support device according to the second aspect, wherein a space is formed between the front end surface of the engagement convex portion and the engagement groove. It is characterized by.

The gist of the invention according to claim 5 is that in the bearing support device according to claim 2 , a damping material is sandwiched between the outer ring and the bearing support. Features.

  According to a sixth aspect of the present invention, in the bearing support device according to the first aspect, the engaging convex portion protrudes from the outer ring in a direction parallel to the axis. In addition, the bearing support body is characterized in that an engagement groove to be fitted to the engagement convex portion is formed in parallel with the shaft center.

According to a seventh aspect of the present invention, there is provided the bearing support device according to the sixth aspect , wherein the engaging convex portion has a rotating shaft that protrudes in a radial direction from an outer peripheral surface of the rotating shaft. The inner ring is provided with an engaging groove fitted to the engaging convex portion.

According to the bearing support device of the first aspect of the present invention, one and the other of the outer ring and the bearing support have an axial thickness and are fitted in a state of surface contact with each other in an interference fit state. Since the engagement protrusions and engagement grooves that receive the load are provided, the contact area between the outer ring and the bearing support is increased, so the load per unit area is reduced and the magnitude of vibration transmitted Vibration is suppressed by reducing. Further, by suitably providing the engagement convex portion and the engagement groove, the load distribution can be distributed substantially uniformly or set at an arbitrary position. As described above, since the load distribution can be arbitrarily set, it is easy to control the vibration affected by the load distribution. Further, one and the other of the rotating shaft and the inner ring are respectively provided with an engaging convex portion and an engaging groove having a thickness in the axial direction and fitted in a state of being in surface contact with each other and receiving a load. Therefore, it is possible to disperse the distribution of the load applied to the inner ring or to set it at an arbitrary place by adjusting the formation position and shape of the engagement convex part and the engagement groove as appropriate. This makes it easy to design vibration suppression.

  According to the bearing support device of the invention according to claim 2, the engaging convex portion protrudes from the outer peripheral surface of the outer ring in the radial direction so as to protrude from at least one place on the outer ring, and to the bearing support body. Is provided with an engagement groove to be fitted to the engagement convex portion. For example, when a plurality of engagement convex portions and engagement grooves are provided uniformly in the circumferential direction, not only the contact area for receiving a load increases. The load distribution can be distributed substantially evenly. As a result, the vibration is evenly transmitted to the bearing support, and the vibration damping design is facilitated. In addition, when the engagement convex portion and the engagement groove are provided at arbitrary locations on the circumference, the portion that receives the vibration of the bearing support can be arbitrarily set, and the vibration damping design becomes easy.

  According to the bearing supporting device of the invention according to claim 3, the engaging convex portion may be constituted by a key fitted in a key groove provided on the outer peripheral surface of the outer ring. The same effect can be obtained. Further, the engaging convex portion can be easily configured by the key.

  According to the bearing support device of the invention according to claim 4, when the space is formed between the front end surface of the engagement convex portion and the engagement groove, deformation occurs due to temperature change or load. However, since the surface that receives the load is not concentrated, fluctuations in the load distribution can be suppressed. This facilitates vibration suppression design for vibration transmission.

  According to the bearing support device of the invention of claim 5, vibrations can be absorbed by the damping material being sandwiched between the outer ring and the bearing support. In particular, when the engagement protrusions and the engagement grooves are arranged at equal angular intervals on the circumference, the load is distributed substantially uniformly on the circumference, so that vibration is transmitted to the entire damping material and vibration suppression. The effect of the material can be improved.

  Further, according to the bearing support device of the invention of claim 6, the engaging convex portion protrudes from the outer ring so as to protrude in parallel with the shaft center, and the bearing support body has the engaging convex portion on the engaging convex portion. By forming the engagement groove to be fitted, the contact area between the outer ring and the bearing support can be increased, and the load per unit area is reduced, so the magnitude of vibration transmitted is reduced. Vibration is suppressed. Moreover, the part which receives the vibration of a bearing support body can be arbitrarily set by providing an engaging convex part and an engaging groove in arbitrary places.

Further, according to the bearing support device of the invention of claim 7 , the engaging convex portion protrudes from at least one portion of the rotating shaft so as to protrude radially from the outer peripheral surface of the rotating shaft, and is provided on the inner ring. Is provided with an engaging groove that fits into the engaging convex part. For example, when a plurality of engaging convex parts and engaging grooves are provided at equal angular intervals in the circumferential direction, the load distribution is substantially uniform. Can be dispersed. As a result, the vibration is evenly transmitted to the inner ring, and the vibration damping design is facilitated. Moreover, since the load applied to each rolling element is disperse | distributed substantially uniformly, rolling resistance can also be suppressed. Furthermore, for example, by arranging the engaging protrusion and the engaging groove at a position corresponding to the periodic load distribution with respect to the shaft whose load changes periodically, such as a shaft with a cam, vibration damping design is facilitated. Become.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a configuration diagram illustrating a support device for a ball bearing 10 to which the present invention is applied. The ball bearing 10 is fitted into a fitting hole 14 formed in a mission case 12 (hereinafter referred to as a case 12), which is a non-rotating member such as a transmission, for example, by press-fitting, The shaft 16 is rotatably supported. The ball bearing 10 includes an annular outer race 18 fitted to the case 12, an annular inner race 20 that is concentrically positioned on the inner peripheral side of the outer race 18, and rotatably supports the shaft 16, and the outer race 18 and the inner race 20. And a plurality of balls 22 interposed therebetween, and a retainer (not shown) that rotatably supports the balls 22. The ball bearing 10 of this embodiment corresponds to the bearing of the present invention, the mission case 12 corresponds to the bearing support, the shaft 16 corresponds to the rotating shaft, and the outer race 18 corresponds to the outer ring. The inner race 20 corresponds to the inner ring, and the ball 22 corresponds to the rolling element.

  The outer race 18 is an annular member, and is fitted in a non-rotatable state in a tight-fitting state by press-fitting into a fitting hole 14 formed in the case 12. On the outer peripheral surface of the outer race 18, a plurality of engaging projections 24 projecting in the radial direction and having a thickness equivalent to that of the outer race 18 in the axial direction are provided in splines at equal angular intervals. On the other hand, in the fitting hole 14 of the case 12, an engaging groove 26 is formed at a position corresponding to the engaging protrusion 24, and they are fitted so as not to rotate relative to each other in an interference fit state. In addition, the engagement protrusion 24 of a present Example respond | corresponds to the engagement convex part of this invention, and the engagement ditch | groove 26 respond | corresponds to an engagement groove | channel.

  Here, since the engagement protrusion 24 of the outer race 18 and the engagement concave groove 26 of the case 12 are provided, and the outer race 18 and the case 12 are engaged in a surface contact state, the area receiving the mutual load is increased. Yes. In addition, the outer race 18 and the case 12 are fitted together in an interference fit state. In particular, the contact surface between the engagement protrusion 24 and the engagement groove 26 is likely to receive a mutual load when the rotating shaft is driven. It has become. Note that the direction of the load is generated in a direction perpendicular to the surfaces in contact with each other.

  The inner race 20 is an annular member, and is concentrically located on the inner peripheral side of the outer race 18, and the shaft 16 is fitted into the inner peripheral surface thereof in a tight-fitting state, and the shaft 16 is rotatably supported. ing. Further, a plurality of balls 22 are interposed between the outer race 18 and the inner race 20 at equal angular intervals by a retainer (not shown), and the balls 22 are rotatably supported.

  In the ball bearing 10 configured as described above, for example, when vibration generated from a meshing portion of a gear (not shown) in the transmission is transmitted to the shaft 16, the vibration is transmitted to the case 12 via the ball bearing 10. At this time, the stronger the load applied to the case 12 from the outer race 18 due to the interference fit, the greater the influence of vibration transmitted to the case 12, but the engagement protrusions 24 and the engagement grooves 26 are equally spaced at equal angular intervals. Provided, and the respective loads are distributed substantially uniformly in the circumferential direction. Thereby, the transmission of vibration is distributed substantially uniformly in the circumferential direction of the case 12.

  As described above, according to the present embodiment, one and the other of the case 12 and the outer race 18 are each provided with the engaging protrusion 24 and the engaging groove 26 that are engaged with each other in a surface contact state and receive a load. Thus, the contact area where the outer race 18 and the case 12 exert a force on each other is increased. Further, the load distribution can be arbitrarily set by suitably providing the engagement protrusion 24 and the engagement groove 26. Thereby, since the load transmitted from the shaft 16 to the case 12 can be set, the vibration suppression design for vibration transmission is facilitated. In particular, when the positions of the engagement protrusions 24 and the engagement grooves 26 are evenly distributed in the circumferential direction, the load applied to the case 12 is dispersed, and for example, strong vibration is locally generated at a portion that is relatively weak against vibration of the case 12. Bad effects such as transmission are prevented. Further, since a load is applied perpendicularly to the contact surfaces of the case 12 and the outer race 18, the direction in which the load is applied can be changed by changing the shapes of the engagement protrusion 24 and the engagement groove 26.

  Next, another embodiment of the present invention will be described. In the following description, the same reference numerals are given to portions common to the above-described embodiment, and the description is omitted.

  FIG. 2 is a configuration diagram illustrating a support device for a ball bearing 30 according to another embodiment of the present invention. When the ball bearing 30 is compared with the ball bearing 10 of the above-described embodiment, the outer protrusion of the outer race 32 is provided with the engagement protrusion 24 at an arbitrary position, and the engagement groove 26 of the case 12 is also the engagement protrusion 24. It is formed in the position which can be engaged with. Other configurations are the same as those of the ball bearing 10. In addition, the ball bearing 30 of a present Example respond | corresponds to the bearing of this invention, and the outer race 32 respond | corresponds to an outer ring | wheel.

  The ball bearing 30 configured as described above has a structure in which a load is relatively concentrated by an interference fit at a place where the engagement protrusion 24 and the engagement groove 26 are provided during driving. Yes. Thereby, when vibration is transmitted to the shaft 16, the vibration is intensively transmitted to the portion of the case 12 where the engaging groove 26 is formed.

  As described above, according to the above-described embodiment, by providing the engagement protrusion 24 and the engagement groove 26 at arbitrary locations on the circumference, it is possible to arbitrarily set the portion where the load is applied. This makes it easier for vibration to be transmitted to a portion to which a load is applied. For example, an engagement protrusion 24 is provided in the vicinity of a portion resistant to vibration of the case 12 to enable vibration suppression design such that vibration is easily transmitted.

  FIG. 3 is a configuration diagram illustrating a support device for a ball bearing 40 according to still another embodiment of the present invention. The ball bearing 40 protrudes in the radial direction on the outer peripheral surface of the shaft 42, and a plurality of engagement protrusions 46 having a thickness equivalent to the inner race 44 in the axial direction are provided in splines at equal angular intervals. On the other hand, in the fitting hole 48 of the inner race 44, an engaging groove 50 is formed at a position corresponding to the engaging protrusion 46, and they are fitted so as not to rotate relative to each other. The ball bearing 40 of the present embodiment corresponds to the bearing of the present invention, the shaft 42 corresponds to the rotating shaft, the inner race 44 corresponds to the inner ring, and the engagement protrusion 46 is the engagement protrusion. The engaging concave groove 50 corresponds to the engaging groove.

  Here, since the engagement protrusion 46 of the shaft 42 and the engagement groove 50 of the inner race 44 are provided, and the shaft 42 and the inner race 44 are engaged in a surface contact state, the area receiving the mutual load increases. Has been. Further, the shaft 42 and the inner race 44 are fitted with each other in an interference fit state, and in particular, the contact surfaces of the engagement protrusion 46 and the engagement groove 50 are easily subjected to a load.

  In the ball bearing 40 configured as described above, when vibration is transmitted to the shaft 42, the vibration is transmitted to the case 12 via the ball bearing 40. At this time, since the engaging protrusions 46 and the engaging grooves 50 are provided at equal angular intervals, the load generated on the shaft 42 and the inner race 44 is distributed substantially evenly in the circumferential direction.

  As described above, according to the above-described embodiment, the engagement protrusion 46 and the engagement groove 50 that receive the load by engaging with each other in the surface contact state are provided on one and the other of the shaft 42 and the inner race 44, respectively. As a result, the contact area in which the shaft 42 and the inner race 44 exert forces on each other can be increased, and the load applied per unit area is reduced, so that the magnitude of the transmitted vibration is reduced and the vibration is suppressed. Is done. Further, by suitably providing the engagement protrusion 46 and the engagement groove 50, the distribution of the load applied from the shaft 42 to the inner race 44 can be dispersed. The risk of being intensively transmitted to a part of is suppressed. In addition, since a load is applied substantially evenly on the circumference of the inner race 44, the balls 22 are equally loaded, and the balls 22 are smoothly rotated, so that rolling resistance can be reduced.

  FIG. 4 is a configuration diagram illustrating a support device for a ball bearing 60 according to still another embodiment of the present invention. When the ball bearing 60 is compared with the ball bearing 40 described above, the engagement protrusion 46 is provided at an arbitrary position on the outer peripheral surface of the shaft 62, and the engagement groove 50 of the inner race 64 is also engaged with the engagement protrusion 46. It is formed at a position where it can be combined. Other configurations are the same as those of the ball bearing 40. The ball bearing 60 of this embodiment corresponds to the bearing of the present invention, the shaft 62 corresponds to the rotating shaft, and the inner race 64 corresponds to the inner ring.

  In the ball bearing 60 configured as described above, when the shaft 62 is, for example, a cam-equipped shaft or a non-straight shaft, the load applied to the inner race 64 periodically changes depending on the shape and rotation angle of the shaft 62. Here, by providing the engagement protrusion 46 and the engagement groove 50 at a position corresponding to the change in the load, the load distribution can be arbitrarily set.

  As described above, according to the above-described embodiment, the load distribution can be arbitrarily set by providing the engagement protrusion 46 and the engagement groove 50 at an arbitrary position corresponding to the change of the load. Vibration design is easy.

  FIG. 5 is a configuration diagram illustrating a support device for a ball bearing 70 according to still another embodiment of the present invention. In the ball bearing 70, the outer race 18 and the case 12 are provided with the engagement protrusion 24 and the engagement groove 26, and the shaft 42 and the inner race 44 are provided with the engagement protrusion 46 and the engagement groove 50, respectively. Thereby, each effect of the above-mentioned ball bearings 10 and 40 can be obtained. Note that the ball bearing 70 of the present embodiment corresponds to the bearing of the present invention.

  FIG. 6 is a configuration diagram illustrating a support device for a ball bearing 80 according to still another embodiment of the present invention. The ball bearing 80 is obtained by sandwiching a damping material 82 between the case 12 and the outer race 18 of the ball bearing 70 described above. The ball bearing 80 can obtain the same effect as the ball bearing 70 because the load applied to the case 12 is uniformly distributed in the same manner as the ball bearing 70 described above. In addition, since the load is dispersed, the effect of the damping material 82 can be sufficiently obtained, so that the vibration is effectively absorbed by the damping material 82 and the vibration is suppressed.

  7 and 8 are conceptual diagrams of the outer race in which protrusions are provided in the axial direction in order to further increase the contact area between the outer race and the transmission case. In FIG. 7 and FIG. 8, constituent members such as an inner race and rolling elements are omitted. In the outer race 90 of FIG. 7, an engaging protrusion 92 in which the engaging protrusion 24 is extended in the axial direction protrudes in parallel with the axial center, and the engaging protrusion 92 of the outer race 90 is formed in a transmission case (not shown). The engaging projection 92 is fitted into the engaging groove having the same shape. Further, in the outer race 100 of FIG. 8, a plurality of cylindrical engagement protrusions 102 protrude from one end surface of the outer race 100 in parallel with the shaft center, and the plurality of engagement protrusions 102 are not illustrated. It fits into an engaging groove having the same shape as the engaging protrusion 102 formed on the case. By fitting these engagement protrusions 92 and 102 to the mission case, the area where the outer races 90 and 100 are in surface contact with the transmission case is increased.

  Thus, according to the above-described embodiment, by providing the engagement protrusions 92 and 102 on the outer races 90 and 100, the contact area between the outer races 90 and 100 and the transmission case is increased, and the load applied to the transmission case is dispersed. Therefore, vibration is reduced. Further, by disposing the engaging protrusions 92 and 102 at arbitrary positions, it is possible to arbitrarily operate the load applied to the mission case.

  FIG. 9 is a configuration diagram illustrating a support device for a ball bearing 110 according to still another embodiment of the present invention. A keyway is formed in each of the outer race 112 and the mission case 12 of the ball bearing 110, and a key 116 is fitted in each keyway. The key 116 forms an engaging projection, increases the contact area between the outer race 112 and the transmission case 114, and allows the load to be manipulated by the arrangement of the key 116. In addition, the ball bearing 110 of a present Example respond | corresponds to the bearing of this invention.

  As described above, according to the above-described embodiment, the ball bearing 110 also functions as an engaging protrusion even by the key 116. Therefore, the same effect as the above-described engaging protrusion 24 is produced, and the protrusion is provided relatively easily. be able to.

  FIG. 10 is a configuration diagram illustrating a support device for a ball bearing 120 according to still another embodiment of the present invention. Spaces 122 are respectively formed between the front end surface of the engagement protrusion 24 of the outer race 18 and the engagement groove 26 of the case 12. Thus, by forming the space 122, it is possible to prevent the surface receiving the load from being concentrated even when deformation occurs due to a temperature change or a load. The ball bearing 120 of this embodiment corresponds to the bearing of the present invention.

  As mentioned above, although the Example of this invention was described in detail based on drawing, this invention is applied also in another aspect.

  For example, the engaging protrusions 24 and 46 of the above-described embodiment have a substantially trapezoidal shape, but the shape of the engaging protrusion such as a triangular shape can be freely changed based on the vibration damping design of the transmission. it can. In general, the load is generated perpendicular to the surfaces in contact with each other, and therefore the direction of the load can be manipulated by changing the shapes of the engagement protrusions 24 and 46.

  Further, in the above-described embodiment, in the ball bearing 10, the outer race 18 is provided with the convex engagement protrusion 24 and the case 12 has the concave engagement groove, but the outer race 18 has the concave engagement groove. A concave groove may be formed, and the case 12 may be provided with a convex engagement protrusion. Similarly, in the ball bearing 40, a convex engagement protrusion 46 is provided on the shaft 42 and a concave engagement groove 50 is formed in the inner race 44, but a concave engagement groove is formed on the shaft 42. It is also possible to form the inner race 44 with a convex engagement protrusion.

  Further, the number and arrangement positions of the engagement protrusions 24 and 46 in the above-described embodiment can be freely provided based on the vibration damping design of the transmission. Even if the number of the engaging protrusions 24 and 46 is one, a sufficient effect can be obtained if the purpose of the vibration damping design is met.

  The bearings of the above-described embodiments are all ball bearings, but the present invention can also be applied to other bearings such as needle bearings whose rolling elements are rollers. In addition, the present invention is applicable to a sliding bearing, such as providing a protrusion on the back metal or providing a protrusion on an outer ring or an inner ring of an air bearing or a magnetic bearing.

  In the above-described embodiment, the bearing of the present invention is applied to the rotating shaft in the transmission, and the transmission case 12 is applied as a bearing support body. The present invention can be applied to other apparatuses as long as the apparatus includes a shaft.

  In the above-described embodiment, for example, the ball bearing 40 is provided with the engaging projections 46 at equal angular intervals between the inner race 44 and the shaft 42, but the outer race 32 is further provided like the ball bearing 30. The engagement protrusion 24 may be provided at an arbitrary position between the case 12 and the case 12. That is, a bearing support device suitable for the vibration damping design can be configured by freely combining the above-described embodiments such as the vibration damping material 82 and the space 122 according to the vibration damping design.

  Further, in the above-described embodiment, in the ball bearing 80, the vibration damping material 82 is inserted between the outer race 18 and the case 12, but the vibration damping material 82 is not inserted in the engaging projection 24 portion. It is also possible to change the arrangement position of the damping material 82 freely. Further, the vibration damping material may be inserted between the shaft and the inner race.

  In the above-described embodiment, the outer race 90 is provided with one engagement protrusion 92, and the outer race 100 is provided with two engagement protrusions 102. The number of these protrusions depends on the damping design. The position and shape provided can be freely changed and implemented.

  The above description is only an embodiment, and the present invention can be implemented in variously modified and improved forms based on the knowledge of those skilled in the art.

It is a block diagram explaining the support apparatus of the ball bearing to which this invention was applied. It is another block diagram explaining the support apparatus of the ball bearing to which this invention was applied. FIG. 5 is still another configuration diagram illustrating a ball bearing support device to which the present invention is applied. FIG. 5 is still another configuration diagram illustrating a ball bearing support device to which the present invention is applied. FIG. 5 is still another configuration diagram illustrating a ball bearing support device to which the present invention is applied. FIG. 5 is still another configuration diagram illustrating a ball bearing support device to which the present invention is applied. It is a conceptual diagram of the outer race to which the present invention is applied. It is a conceptual diagram of the outer race to which the present invention is applied. FIG. 5 is still another configuration diagram illustrating a ball bearing support device to which the present invention is applied. FIG. 5 is still another configuration diagram illustrating a ball bearing support device to which the present invention is applied.

Explanation of symbols

10, 30, 40, 60, 70, 80, 110, 120: Ball bearing (bearing) 12: Mission case (bearing support) 16: Shaft (rotating shaft) 18, 32, 90, 100, 112: Outer race (outer ring) 20, 44, 64: Inner race (inner ring) 22: Ball (rolling element) 24, 46, 92, 102: Engagement protrusion (engagement protrusion) 26, 50: Engagement groove (engagement groove) 82 : Damping material 116: Key 122: Space

Claims (7)

An outer ring fitted to the bearing support, an inner ring located concentrically on the inner circumferential side of the outer ring and having a rotation shaft fitted on the inner circumferential surface, and a rolling element interposed between the outer ring and the inner ring. A bearing support device for rotatably supporting the rotating shaft,
On one and the other of the bearing support and the outer ring, there are an engagement convex portion and an engagement groove having a thickness in the axial direction and fitted in a state of being in surface contact with each other and receiving a load. Provided , and
One and the other of the rotating shaft and the inner ring are provided with an engaging convex portion and an engaging groove, which have an axial thickness and are fitted in a state of being in surface contact with each other and receiving a load. A bearing support device characterized by that .   The engaging convex portion protrudes from at least one portion of the outer ring so as to protrude in the radial direction from the outer peripheral surface of the outer ring, and the bearing support body is engaged with the engaging convex portion. The bearing support device according to claim 1, wherein a groove is provided.   The bearing support device according to claim 2, wherein the engagement convex portion is constituted by a key fitted in a key groove provided on an outer peripheral surface of the outer ring.   The bearing support device according to claim 2, wherein a space is formed between a front end surface of the engagement convex portion and the engagement groove.   The bearing support device according to claim 2, wherein a damping material is sandwiched between the outer ring and the bearing support.   The engaging convex portion protrudes from the outer ring so as to protrude in a direction parallel to the shaft center, and the bearing support body has an engaging groove fitted to the engaging convex portion. The bearing support device according to claim 1, wherein the bearing support device is formed in parallel. The engaging convex portion protrudes from at least one portion of the rotating shaft so as to protrude radially from the outer peripheral surface of the rotating shaft, and the inner ring is engaged with the engaging convex portion. The bearing support device according to claim 6 , further comprising a groove.

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