JP2005299887A - Cylindrical roller bearing and rotation supporting device with lubricating device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To achieve a sufficient speedup of a spindle internally fitted and supported by a cylindrical roller bearing 3a. <P>SOLUTION: While an inward flange part 20 is provided to the inner peripheral surface of one end of an outer ring 4a, a compression spring 21 and a spacer 22 are arranged between the inside surface of the inward flange part 20 and one end surface of a plurality of cylindrical rollers 6. By pressing one end surface of each cylindrical roller 6 based on elasticity of the compression spring 21, the other end surface of each cylindrical roller 6 is brought into contact with the inside surface of a first outward flange part 9. The one end surface of each cylindrical roller 6 which is a part to which lubricating oil is hard to be supplied during operation is prevented from coming into contact with the inside surface of a second outward flange part 10. By employing this construction, the above subject is attained. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The cylindrical roller bearing and the rotation support device with a lubrication device of the present invention are used for supporting a shaft that rotates at high speed, such as a main shaft of a machine tool.

  In recent years, in order to improve the machining efficiency and machining accuracy of a machine tool, the speed and rigidity of the spindle of the machine tool have been increased. Along with this, a fixed-position preload combination angular contact ball bearing is used as a bearing to support the tip end portion of this spindle, and a single-row cylindrical roller bearing is used as a bearing to support the base end portion. Tend to. Among these, as a conventional structure of a portion that supports the main shaft by a single-row cylindrical roller bearing that is an object of the present invention, for example, a structure described in Patent Document 1 is known. FIG. 5 shows an example of a conventional structure in which the basic structure is the same as that described in Patent Document 1.

  A main shaft 2 is rotatably supported by a cylindrical roller bearing 3 inside the housing 1. The cylindrical roller bearing 3 includes an outer ring 4, an inner ring 5, and a plurality of cylindrical rollers 6. Out of these, the outer ring 4 has a cylindrical outer ring raceway 7 on the inner peripheral surface. The inner ring 5 has a cylindrical inner ring raceway 8 at an intermediate portion in the axial direction of the outer peripheral surface (left and right direction in FIG. 5), and first and second outward flanges 9 at both ends of the outer peripheral surface. 10 are provided over the entire circumference so as to protrude outward in the radial direction. Further, each cylindrical roller 6 is provided between the outer ring raceway 7 and the inner ring raceway 8 so as to be able to roll while being held by a cage 11. During operation, the inner side surfaces of the first and second outward flanges 9 and 10 respectively guide both end surfaces of the cylindrical rollers 6, and the cylindrical rollers 6 are excessively skewed (of the cylindrical rollers 6). Prevent rotation axis from tilting with respect to revolution axis).

  In such a cylindrical roller bearing 3, the outer ring 4 is fitted and supported on the housing 1, and the inner ring 5 is fitted and supported on the main shaft 2. Further, in this state, the outer ring 4 is positioned in the axial direction by abutting the end face of the outer ring 4 in the axial direction against the step surface 12 provided on the inner peripheral surface of the housing 1. At the same time, the inner ring 5 is sandwiched between a pair of inner ring spacers 13 and 14 that are externally fitted and fixed to the main shaft 2, thereby positioning the inner ring 5 in the axial direction.

  In addition, a nozzle member 15 having a T-shaped cross section is provided in a part of the housing 1 in the vicinity of the portion where the cylindrical roller bearing 3 is fitted in the axial direction, and the housing 1 is disposed in the radial direction (the vertical direction in FIG. ) Is provided in a state of penetrating. And the front end side (lower end side of FIG. 5) part of this nozzle member 15 is arrange | positioned in the side of the said cylindrical roller bearing 3 (right side of FIG. 5). A lubricating oil passage 16 is provided inside the nozzle member 15. Then, the upstream end (the upper end in FIG. 5) of the lubricating oil passage 16 is connected to a supply source of lubricating oil (oil air or oil mist) through an inner passage of a supply pipe 17 provided in the housing 1. ing. At the same time, the downstream end (lower end in FIG. 5) of the lubricating oil passage 16 is communicated to the outside through a nozzle hole 18 provided at the tip of the nozzle member 15.

  Further, a downstream end (left end in FIG. 5) opening of the nozzle hole 18 is formed in a bearing internal space 19 in which the plurality of cylindrical rollers 6 are installed between the inner peripheral surface of the outer ring 4 and the outer peripheral surface of the inner ring 5. On one side (on the side where the first outward flange 9 is provided in the axial direction and on the right side of FIG. 5), in the case of the illustrated example, specifically, the outer peripheral surface of the first outward flange 9 And the inner peripheral surface of the retainer 11). Thus, the lubricating oil fed into the lubricating oil passage 16 from the supply source through the inner passage of the supply pipe 17 is ejected from the nozzle hole 18 toward the opening on one side of the bearing internal space 19. The lubricating oil can be freely supplied into the bearing internal space 19. Further, during the operation of the machine tool, the lubricating oil supplied into the bearing inner space 19 in this way is used for lubrication of the rolling contact portion and the sliding contact portion existing in the bearing inner space 19, and thus centrifugal force is applied. To move radially outward. Then, after reaching the inner peripheral surface of the outer ring 4, the outer ring 4 is discharged to the outside through both end openings of the bearing inner space 19. During the operation of the machine tool, such supply and discharge of the lubricating oil are performed continuously or intermittently.

  However, as described above, in the case of the conventional structure shown in FIG. 5, the lubricating oil is supplied to the bearing inner space 19 only through the opening on one side of the bearing inner space 19. For this reason, the inner surface of the second outward flange 10 and one end surface of each cylindrical roller 6 (FIG. 5), which are present on the refueling side, that is, on the other side of the bearing internal space 19 (left side in FIG. 5). It is difficult for the lubricant to reach the sliding contact portion with the left end surface of Accordingly, the seizure resistance of the slidable contact portion is lowered, and the presence of the slidable contact portion causes the high speed of the main shaft 2 to be hindered. On the other hand, if the lubricating oil is supplied to the bearing internal space 19 from both sides of the bearing internal space 19, both end faces of the rollers 6 and the first and second outward flanges 9, 10 are provided. Lubricating oil can be easily delivered to the sliding contact portions with the inner surface of each of the sliding contact portions, and the seizure resistance of each sliding contact portion can be increased.

  However, if the lubricating oil is supplied through the openings on both sides of the bearing internal space 19 as described above, the amount of lubricating oil supplied to the bearing internal space 19 becomes too large. On the other hand, the cylindrical roller bearing 3 for supporting the main shaft 2 is in a state in which the radial gap during operation is negative over the entire circumference in order to prevent the above-described skew (the radial load is applied to all the cylindrical rollers 6). In a state where the Therefore, if the supply amount of the lubricating oil to the bearing internal space 19 becomes excessive as described above, the stirring resistance and temperature rise of the lubricating oil increase, resulting in an increase in the rotational resistance of the cylindrical roller bearing 3 and This is not preferable because it may lead to a decrease in life. Further, in the case where the lubricating oil is supplied from both sides of the bearing internal space 19 as described above, equipment (the nozzle member 15 and the like) for supplying the lubricating oil is arranged on both sides of the cylindrical roller bearing 3 in the axial direction. Therefore, there is a disadvantage that the installation space and cost of this equipment increase.

Japanese Patent Laid-Open No. 2004-3577

  In the cylindrical roller bearing and the rotation support device with a lubrication device according to the present invention, the inner side surface of the second outward flange portion present on the side opposite to the oil supply during operation is in contact with the end surfaces of the plurality of cylindrical rollers in view of the above-described circumstances. The invention was invented to realize a structure that prevents the occurrence of the failure and facilitates speeding up.

Of the cylindrical roller bearing and the rotation support device with a lubricating device according to the present invention, the cylindrical roller bearing described in claim 1 includes an outer ring, an inner ring, and a plurality of cylindrical rollers.
Of these, the outer ring has a cylindrical outer ring raceway on the inner peripheral surface.
The inner ring has a cylindrical inner ring raceway in the axially intermediate portion of the outer peripheral surface, and the first and second outward flanges at both axial ends of the outer peripheral surface, respectively, radially outward. It is provided over the entire circumference in a protruding state.
The plurality of cylindrical rollers are provided between the outer ring raceway and the inner ring raceway so as to roll freely.

  In particular, the cylindrical roller bearing described in claim 1 has an inward flange portion at an end portion on the side facing the second outward flange portion with respect to the radial direction among the axial end portions of the inner peripheral surface of the outer ring. It is provided over the entire circumference in a state protruding inward in the direction. At the same time, an elastic member is provided between the inner side surfaces of the inward flanges facing each other and one end surfaces of the cylindrical rollers. At least in use, the other end surface of each cylindrical roller is brought into contact with the inner surface of the first outward flange by pressing one end surface of each cylindrical roller based on the elasticity of the elastic member. I have to.

According to a third aspect of the present invention, there is provided a rotation support device with a lubrication device comprising an outer ring, an inner ring, a plurality of cylindrical rollers, and a lubrication device.
Of these, the outer ring has a cylindrical outer ring raceway on the inner peripheral surface, and is fitted and supported in the housing in a state in which it is positioned in the axial direction.
The inner ring has a cylindrical inner ring raceway in the axially intermediate portion of the outer peripheral surface, and the first and second outward flanges at both axial ends of the outer peripheral surface, respectively, radially outward. It is provided over the entire circumference in a projecting state, and is externally supported on the rotary shaft in a state in which it is positioned in the axial direction.
The plurality of cylindrical rollers are provided between the outer ring raceway and the inner ring raceway so as to roll freely.
Further, the lubricating device is provided in the bearing inner space where the cylindrical rollers are installed between the inner peripheral surface of the outer ring and the outer peripheral surface of the inner ring, on the first outward flange side of the bearing inner space. Lubricating oil is supplied from the opening.

  In particular, in the rotation support device with a lubrication device according to claim 3, at the end portion on the side facing the second outward flange portion in the radial direction among the axial end portions of the inner peripheral surface of the outer ring. An inward flange is provided over the entire circumference so as to protrude radially inward. At the same time, an elastic member is provided between the inner side surfaces of the inward flanges facing each other and one end surfaces of the cylindrical rollers. Then, by pressing one end face of each cylindrical roller (directly or via a spacer) based on the elasticity of the elastic member, the other end face of each cylindrical roller is brought into contact with the inner side face of the first outward flange portion. Is in contact with

  On the other hand, in the rotation support device with a lubrication device according to claim 4, the end of the axially opposite ends of the inner peripheral surface of the outer ring on the side facing the second outward flange portion with respect to the radial direction. An inward flange portion is provided over the entire circumference so as to protrude radially inward. At the same time, the axial distance between the inner surface of the second outward flange portion facing each other and the one end surface of each cylindrical roller is set to be equal to the inner surface of the inner flange portion facing each other and one of the cylindrical rollers. It is larger than the axial distance between the end faces.

  According to the cylindrical roller bearing and the rotational support device with a lubrication device of the present invention configured as described above, the second outwardly facing flange portion that is present on the anti-oil supply side and is hard to reach the lubricant during operation. It can prevent that an inner surface and the one end surface of each cylindrical roller contact. That is, in the case of the present invention, one end surface of each cylindrical roller is guided by the elastic member or the side surface of the spacer (Claims 1 and 3) or the inner side surface of the inward flange (Claim 4). For this reason, it can prevent that the one end surface of each said cylindrical roller contacts the inner surface of said 2nd outward collar part. Therefore, when increasing the speed of the rotating shaft supported by the cylindrical roller bearing, it is necessary to consider the seizure resistance when the one end surface of each cylindrical roller and the inner side surface of the second outward flange portion contact each other. Absent.

In the case of the present invention, the contact portion between one end surface of each cylindrical roller and the side surface (Claims 1 and 3) of the elastic member or spacer or the inner side surface (Claim 4) of the inward flange portion is: Each of them exists on the side opposite to the oil supply side of the bearing internal space. However, since each of these contact portions exists at the radially outer end portion of the bearing inner space, a sufficient amount of lubricating oil can be supplied during operation. That is, the lubricating oil supplied to the bearing internal space during operation moves radially outward by centrifugal force and then moves toward both axial ends of the bearing internal space. Accordingly, a sufficient amount of each of the cylindrical roller and the contact portion between the elastic member or the side surface of the spacer (Claims 1 and 3) or the inner side surface of the inward flange (Claim 4) is sufficient. Lubricating oil can be supplied.
On the other hand, in the case of the present invention, the other end surface of each cylindrical roller is guided by the inner side surface of the first outward flange portion. However, since the contact portion between the other end surface of each cylindrical roller and the inner side surface of the first outward flange is on the oil supply side of the bearing internal space, a sufficient amount of lubricating oil can be supplied.

  Therefore, in the case of the present invention, it is possible to sufficiently secure the seizure resistance of the contact portions between the both end faces of the cylindrical rollers and the guide surfaces. As a result, it is possible to sufficiently contribute to speeding up the rotating shaft supported by the cylindrical roller bearing.

When the cylindrical roller bearing described in claim 1 is implemented, preferably, as described in claim 2, a guide inclined surface is provided on the outer peripheral surface of the first outward flange, and the guide inclined surface is provided as an inner ring. Inclination is performed in a direction in which the diameter decreases as the distance from the raceway increases, and the end portion on the small-diameter side is projected outward in the axial direction from the end surface of the outer ring.
Moreover, when implementing the rotation support apparatus with a lubrication device described in claims 3 to 4, preferably, as described in claim 5, the outer peripheral surface of the first outward flange portion is separated from the inner ring raceway. A guide inclined surface that is inclined in a direction of decreasing the diameter is provided, and a small-diameter side end portion of the guide inclined surface is projected outward in the axial direction from the end surface of the outer ring. In addition, the lubrication device includes a nozzle hole that ejects lubricating oil toward a portion of the guide inclined surface that protrudes outward in the axial direction from the end surface of the outer ring.

  If each configuration as described above is employed, the lubricating oil discharged from the nozzle hole adheres to the guide inclined surface during operation. The lubricating oil adhering to the guide inclined surface in this way is sent to the large diameter side of the guide inclined surface along the guide inclined surface due to the balance between the centrifugal force accompanying rotation and the surface tension of the self, Supplied in the space. Thus, the operation of supplying the lubricating oil along the guide inclined surface into the bearing internal space is efficiently performed without being obstructed by the air curtain formed in the opening portions at both ends of the cylindrical roller bearing during high-speed rotation. Therefore, the lubricating oil ejected from the nozzle hole can be efficiently supplied into the bearing internal space.

  FIG. 1 shows a first embodiment of the present invention corresponding to claims 1 and 3. The feature of this embodiment is the structure of the outer ring 4a constituting the cylindrical roller bearing 3a and the point that a predetermined member is assembled between the outer ring 4a and the plurality of cylindrical rollers 6. The structure and operation of other parts are almost the same as those of the conventional structure shown in FIG. For this reason, the same parts are denoted by the same reference numerals, and redundant description is omitted or simplified. Hereinafter, the characteristic parts of this embodiment and parts different from the conventional structure will be mainly described.

  In the case of the present embodiment, among the axial end portions of the inner peripheral surface of the outer ring 4a, the inward flange portion 20 is located at the end portion (left end portion in FIG. 1) facing the second outward flange portion 10 in the radial direction. Are provided over the entire circumference in a state of projecting radially inward. At the same time, a compression spring 21 such as a disc spring or the like is generally rectangular in cross section between the inner side surface of the inward flange portion 20 and the one end surface (left end surface in FIG. 1) of each cylindrical roller 6 facing each other. Are provided in order from the inward flange portion 20 side. Then, by pressing one end surface of each cylindrical roller 6 through the spacer 22 based on the elasticity of the compression spring 21, the other end surface (right end surface in FIG. 1) of each cylindrical roller 6 is It is made to contact the inner surface of the 1st outward eaves part 9. FIG. In other words, by bringing the other end surface of each cylindrical roller 6 into contact with the inner surface of the first outward flange 9 in this way, one end surface of each of the cylindrical rollers 6 and the inside of the second outward flange 10 Prevents contact with the side. In the case of this embodiment, during operation, the side surface of the spacer 22 (the right side surface in FIG. 1) and the inner side surface of the first outward flange 9 are respectively opposite to both end surfaces of the cylindrical rollers 6. It becomes a guide surface. In the case of the present embodiment, the elasticity of the compression spring is adjusted (slightly so that the frictional force acting on the contact portion between the both end faces of each cylindrical roller 6 and each guide surface does not become excessive. )doing.

  As described above, according to the cylindrical roller bearing and the rotation support device with a lubrication apparatus of the present embodiment, the lubrication oil is difficult to reach during operation due to the presence of the bearing inner space 19 on the anti-oil supply side (left side in FIG. 1). It is possible to prevent the inner surface of the second outward flange portion 10 that is a part from contacting one end surface of each cylindrical roller 6. Therefore, in the case of the present embodiment, when increasing the speed of the main shaft (not shown) fitted in the inner ring 5 constituting the cylindrical roller bearing 3a, the one end surface of each cylindrical roller 6 and the second outward direction are used. It is not necessary to consider the seizure resistance when the inner surface of the collar portion 10 comes into contact.

  In the case of this embodiment, the contact portion between the one end surface of each cylindrical roller 6 and the side surface of the spacer 22 exists on the oil refueling side of the bearing internal space 19. However, since each of these contact portions exists at the radially outer end portion of the bearing inner space 19, a sufficient amount of lubricating oil can be supplied during operation. That is, the lubricating oil supplied to the bearing inner space 19 during operation moves radially outward by centrifugal force and then moves toward both axial ends of the bearing inner space 19. Therefore, a sufficient amount of lubricating oil can be supplied to the contact portion between the one end surface of each cylindrical roller 6 and the side surface of the spacer 22. Further, the contact portion between the other end surface of each cylindrical roller 6 and the inner side surface of the first outward flange 9 is on the oil supply side (right side in FIG. 1) of the bearing internal space 19. For this reason, a sufficient amount of lubricating oil can be supplied to each of these contact portions. Therefore, in the case of the present embodiment, the seizure resistance of the contact portion between the both end faces of each cylindrical roller 6 and each guide face can be sufficiently secured. As a result, the main shaft supported by the cylindrical roller bearing 3a can sufficiently contribute to speeding up.

  Next, FIG. 2 shows Embodiment 2 of the present invention corresponding to claims 1, 2, 3, and 5. In the case of the present embodiment, the guide inclined surface 23 is provided on the outer peripheral surface of the first outward flange 9a. The guide inclined surface 23 is inclined in a direction in which the diameter decreases as the distance from the inner ring raceway 8 increases, and the small diameter side end portion (the right end portion in FIG. 2) projects outward in the axial direction from the end surface of the outer ring 4a. Yes. Further, in the assembled state shown in the drawing, the outer half of the guide inclined surface 23 in the axial direction is made to enter the inside of the nozzle member 15a in the radial direction. Then, the nozzle hole 18 is formed by making the downstream end opening (lower end in FIG. 2) of the nozzle hole 18 provided at the tip of the nozzle member 15a face the outer peripheral surface of the outer half of the guide inclined surface 23. Therefore, the lubricating oil can be discharged toward the outer peripheral surface of the outer half.

  In the case of this embodiment, during operation, the lubricating oil discharged from the nozzle hole 18 adheres to the guide inclined surface 23. The lubricating oil adhering to the guide inclined surface 23 in this way is on the large diameter side of the guide inclined surface 23 along the guide inclined surface 23 (FIG. 2) due to the balance between the centrifugal force accompanying rotation and the surface tension of itself. To the left side) and supplied into the bearing internal space 19. That is, the centrifugal force exerts a force directed outward in the radial direction on the lubricating oil, but the lubricating oil also receives a force to remain attached to the inclined guide surface 23 due to surface tension. Then, due to the balance between these two forces, the lubricating oil adhering to the guide inclined surface 23 is sent to the large diameter side of the guide inclined surface 17 while adhering to the guide inclined surface 17, and the bearing internal space 19 is supplied. Thus, the operation of supplying the lubricating oil into the bearing internal space 19 along the guide inclined surface 23 is efficiently prevented without being obstructed by the air curtains formed at both end openings of the cylindrical roller bearing 3b during high-speed rotation. Done. In the present embodiment, the nozzle hole 18 is inclined toward the large diameter side of the guide inclined surface 23. Therefore, the lubricating oil discharged from the nozzle hole 18 tends to move toward the large diameter side of the guide inclined surface 17 depending on the discharge momentum. Therefore, in the case of the present embodiment, the lubricating oil discharged from the nozzle hole 18 can be efficiently supplied into the bearing inner space 19.

  In the case of this embodiment, in order to allow the lubricating oil to move efficiently along the guide inclined surface 23 when supplying the lubricating oil into the bearing internal space 19 as described above, The surface roughness of the guide inclined surface and the inclination angle θ with respect to the central axis are regulated. Specifically, the surface roughness is set to 0.8 μmRa or less, and the inclination angle θ is set to about 5 degrees. The inclination angle θ is preferably at least 3 degrees (θ ≧ 3 degrees). However, if the inclination angle θ is too large, the thickness dimension of the inner ring 5a in the radial direction (vertical direction in FIG. 1) becomes too large, and the pitch circle diameter of the cylindrical roller bearing 3b cannot be reduced. Therefore, the maximum value of the inclination angle θ is preferably set to a value that does not cause such inconvenience (for example, about 30 degrees).

  In the illustrated example, an inclined surface similar to the guide inclined surface 23 is also provided on the outer peripheral surface of the second outward flange portion 10a. However, when carrying out the present invention, the outer peripheral surface of the second outward flange portion 10a may be the same cylindrical surface as in the case of the first embodiment described above. In the case of this embodiment, the inner peripheral surface of the inner ring 5a is a tapered surface (conical concave surface) in accordance with the shape of the outer peripheral surface of a main shaft (not shown) on which the inner ring 5a is to be fitted. The structure and operation of the other parts are the same as those of the first embodiment shown in FIG.

  Next, FIG. 3 shows Embodiment 3 of the present invention corresponding to claim 4. The feature of this embodiment is that the structure of the outer ring 4b constituting the cylindrical roller bearing 3c and the position where the cylindrical roller bearing 3c is assembled to the housing 1 and the main shaft (not shown) are regulated. The structure and operation of other parts are almost the same as those of the conventional structure shown in FIG. For this reason, the same parts are denoted by the same reference numerals, and redundant description is omitted or simplified. Hereinafter, the characteristic parts of this embodiment and parts different from the conventional structure will be mainly described.

In the case of the present embodiment, the inward flange portion 20a at the end portion (left end portion in FIG. 3) on the side facing the second outward flange portion 10 in the radial direction among the axial end portions of the inner peripheral surface of the outer ring 4b. Are provided over the entire circumference in a state protruding inward in the radial direction. The outer ring 4b is fitted and fixed to the housing 1 and the inner ring 5 is fitted and fixed to the main shaft, and the inner surface of the second outwardly facing flange portion 10 and the plurality of cylindrical rollers 6 facing each other. the axial distance L ₂ between the end surface is greater than the axial distance L ₃ between the inner surface and one end surface of each cylindrical roller 6 of the inward flange portion 20a opposed to each other (L _2> L ₃ ) Furthermore, in the case of the present embodiment, the axial distance L ₁ between the inner surface of the first outward flange 9 facing each other and the other end surface of each cylindrical roller 6 is substantially equal to the axial distance. (L ₁ ≈L ₃ ). And by adopting such a configuration, the inner side surface of the inwardly facing flange portion 20a and the inner side surface of the first outwardly facing flange portion 9 are used as guide surfaces with respect to both end surfaces of the respective cylindrical rollers 6, and The inner side surface of the second outward flange portion 10 and the one end surface of each cylindrical roller 6 are prevented from contacting each other. The axial dimensions L ₁ and L ₃ are restricted to such a size that excessive skew does not occur in the cylindrical rollers 6.

  As described above, also in the case of the cylindrical roller bearing and the rotation support device with a lubrication apparatus of the present embodiment, the lubrication oil is difficult to reach during operation due to the presence of the bearing inner space 19 on the anti-oil supply side (left side in FIG. 3). It is possible to prevent the inner surface of the second outward flange portion 10 that is a part from contacting one end surface of each cylindrical roller 6. Therefore, also in the case of the present embodiment, when the speed of the main shaft fitted in the inner ring 5 constituting the cylindrical roller bearing 3c is increased, one end face of each cylindrical roller 6 and the inner side of the second outward flange 10 There is no need to consider the seizure resistance when the side contacts.

  In the case of this embodiment, when the one end surface of each cylindrical roller 6 and the inner side surface of the inward flange portion 20a are in contact with each other, these contact portions are present on the oil refueling side of the bearing inner space 19. To do. However, since each of these contact portions exists at the radially outer end portion of the bearing inner space 19, a sufficient amount of lubricating oil can be supplied during operation. That is, the lubricating oil supplied to the bearing inner space 19 during operation moves radially outward by centrifugal force and then moves toward both axial ends of the bearing inner space 19. Therefore, a sufficient amount of lubricating oil can be supplied to the contact portion between the one end surface of each cylindrical roller 6 and the inner surface of the inward flange portion 20a. Further, when the other end surface of each cylindrical roller 6 and the inner side surface of the first outward flange 9 are in contact with each other, these contact portions are on the oil supply side of the bearing internal space 19 (right side in FIG. 3). Exists. For this reason, a sufficient amount of lubricating oil can be supplied to each of these contact portions. Therefore, in the case of the present embodiment, it is possible to sufficiently secure the seizure resistance of the contact portion between the both end faces of the cylindrical rollers 6 and the guide surfaces. As a result, the main shaft supported by the cylindrical roller bearing 3c can sufficiently contribute to speeding up.

  Next, FIG. 4 shows Embodiment 4 of the present invention corresponding to claims 4 to 5. Also in the case of the present embodiment, the guide inclined surface 23 is provided on the outer peripheral surface of the first outward flange 9a constituting the inner ring 5a of the cylindrical roller bearing 3d, as in the case of the second embodiment shown in FIG. At the same time, the downstream end opening of the nozzle hole 18 is opposed to the guide inclined surface 23 to improve the efficiency of supplying the lubricating oil to the bearing internal space 19. The structure and operation of the other parts are the same as in the case of the third embodiment shown in FIG.

FIG. 2 is a half sectional view showing Example 1 of the present invention. The figure similar to FIG. 1 which shows Example 2 similarly. The same figure as FIG. 1 which shows Example 3 similarly. The figure similar to FIG. 1 which shows Example 4 similarly. The fragmentary sectional view which shows one example of the conventional structure.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Housing 2 Main shaft 3, 3a-3d Cylindrical roller bearing 4, 4a, 4b Outer ring 5, 5a Inner ring 6 Cylindrical roller 7 Outer ring raceway 8 Inner ring raceway 9, 9a First outward flange part 10, 10a Second outward flange part 11 Cage 12 Step surface 13 Inner ring spacer 14 Inner ring spacer 15, 15a Nozzle member 16 Lubricating oil passage 17 Supply pipe 18 Nozzle hole 19 Bearing inner space 20, 20a Inward flange 21 Compression spring 22 Spacer 23 Guide inclined surface

Claims (5)

  An outer ring having a cylindrical outer ring raceway on the inner peripheral surface, and a cylindrical inner ring raceway in the axially intermediate portion of the outer peripheral surface, and the first and second outward flanges at both axial ends of the outer peripheral surface A cylindrical roller provided with an inner ring that is provided over the entire circumference in a state in which each portion protrudes radially outward, and a plurality of cylindrical rollers that are provided between the outer ring raceway and the inner ring raceway so as to be capable of rolling. In the bearing, in the state of projecting inward inward in the radial direction at the end opposite to the second outward facing with respect to the radial direction among the axial ends of the inner peripheral surface of the outer ring. An elastic member is provided over the entire circumference and provided between an inner surface of the inwardly facing flange portion and one end surface of each cylindrical roller facing each other, and at least in use, each cylindrical roller is based on the elasticity of the elastic member. The other end surface of each cylindrical roller is Cylindrical roller bearing, characterized in that was set to be brought into contact with the inner surface of the flange portion.   A guide inclined surface is provided on the outer peripheral surface of the first outward flange, and the guide inclined surface is inclined in a direction in which the diameter decreases as the distance from the inner ring raceway increases, and the end portion on the small diameter side is more than the end surface of the outer ring. The cylindrical roller bearing according to claim 1, which protrudes outward in the axial direction.   It has a cylindrical outer ring raceway on the inner peripheral surface, and has an outer ring fitted and supported in the housing in an axially positioned state, and a cylindrical inner ring raceway in the axial middle portion of the outer peripheral surface, First and second outward flanges are provided at both ends in the axial direction of the outer peripheral surface over the entire circumference in a state of projecting outward in the radial direction, and rotated in an axially positioned state. An inner ring externally supported on a shaft, a plurality of cylindrical rollers rotatably provided between the outer ring raceway and the inner ring raceway, and the inner ring between the outer ring and the outer ring surface of the inner ring. In a rotation support device with a lubrication device comprising a lubrication device for supplying lubricating oil from the opening on the first outward flange side of the bearing internal space in the bearing internal space where each cylindrical roller is installed, Of the both ends in the axial direction of the inner peripheral surface of the outer ring, facing the second outward flange with respect to the radial direction An inward flange is provided at the end on the side so as to protrude inward in the radial direction, and an elastic member is provided between the inner surface of the inward flange facing each other and one end surface of each cylindrical roller. The other end surface of each cylindrical roller is brought into contact with the inner surface of the first outward flange by pressing one end surface of each cylindrical roller based on the elasticity of the elastic member. A rotation support device with a lubrication device.   It has a cylindrical outer ring raceway on the inner peripheral surface, and has an outer ring fitted and supported in the housing in an axially positioned state, and a cylindrical inner ring raceway in the axial middle portion of the outer peripheral surface, First and second outward flanges are provided at both ends in the axial direction of the outer peripheral surface over the entire circumference in a state of projecting outward in the radial direction, and rotated in an axially positioned state. An inner ring externally supported on a shaft, a plurality of cylindrical rollers rotatably provided between the outer ring raceway and the inner ring raceway, and the inner ring between the outer ring and the outer ring surface of the inner ring. In a rotation support device with a lubrication device comprising a lubrication device for supplying lubricating oil from the opening on the first outward flange side of the bearing internal space in the bearing internal space where each cylindrical roller is installed, Of the both ends in the axial direction of the inner peripheral surface of the outer ring, facing the second outward flange with respect to the radial direction An inward flange is provided at the end on the side so as to protrude radially inward, and between the inner surface of the second outward flange facing each other and one end surface of each cylindrical roller. The rotational support device with a lubrication device is characterized in that the axial distance is larger than the axial distance between the inner surface of the inwardly facing flange portion and the one end surface of each cylindrical roller. A guide inclined surface is provided on the outer peripheral surface of the first outward flange, and the guide inclined surface is inclined in a direction in which the diameter decreases as the distance from the inner ring raceway increases. It protrudes to an axial direction outer side, and the lubricating device is provided with the nozzle hole which ejects lubricating oil toward the part which protruded on the axial direction outer side rather than the end surface of the said outer ring | wheel among the said guide inclined surfaces. The rotation support device with a lubrication device according to any one of 4.

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