A taper roller bearing includes: an inner ring, an outer ring, a plurality of taper rollers, and an annular cage. The cage includes a small-diameter annular portion on one side in a axial direction, a large-diameter annular portion which is positioned on the other side in the axial direction and on a radial outer side of a large flange of the inner ring, and a plurality of column portions which link the small-diameter annular portion and the large-diameter annular portion. The taper roller bearing has a labyrinth structure which suppresses a flow of lubricating oil to the outside of the bearing from the inside of the bearing between the large flange and the large-diameter annular portion.
|
1. A taper roller bearing comprising:
an inner ring that includes a small flange that is positioned on a first side in an axial direction and that protrudes to an outer side in a radial direction, and a large flange that is positioned on a second side in the axial direction and that protrudes to the outer side in the radial direction;
an outer ring that is positioned on the outer side in the radial direction of the inner ring;
a plurality of taper rollers that are positioned between the inner ring and the outer ring; and
an annular cage that holds the plurality of taper rollers at an interval in the circumferential direction,
wherein:
the cage includes a small-diameter annular portion that is positioned on one side of the cage, a large-diameter annular portion that is positioned on an opposite side of the cage and on the outer side in the radial direction of the large flange, and a plurality of column portions that link the small-diameter annular portion and the large-diameter annular portion with each other, and
a labyrinth structure, which suppresses a flow of lubricating oil from inside the taper roller bearing to outside the taper roller bearing, is provided between the large flange and the large-diameter annular portion, the labyrinth structure including an annular enlarged space portion that is disposed axially between a flange surface of the large flange and a radially inward surface of the large-diameter annular portion.
2. The taper roller bearing according to
an inner circumferential surface of the large-diameter annular portion includes a first inner circumferential surface portion and a second inner circumferential surface portion having a diameter larger than a diameter of the first inner circumferential surface portion, and
an outer circumferential surface of the large flange includes a first outer circumferential surface portion opposing to the first inner circumferential surface portion with a fine clearance, and a second outer circumferential surface portion having a diameter that is larger than a diameter of the first outer circumferential surface portion and opposing to the second inner circumferential surface portion with a fine clearance.
3. The taper roller bearing according to
wherein the small-diameter annular portion blocks an annular opening portion formed between the small flange and the outer ring, having fine clearances between the small-diameter annular portion and the small flange and between the small-diameter annular portion and the outer ring, respectively.
4. The taper roller bearing according to
spaces formed between the large-diameter annular portion and the small-diameter annular portion and between the column portions adjacent to each other in the circumferential direction are pockets that hold the taper rollers, and
cut-out portions that are continuous with the pockets are provided on the outer circumferential side of the large-diameter annular portion.
5. The taper roller bearing according to
a depth of an end on the recess portion on an axial side is zero and a bottom surface of the recess portion has a shape of an inclined surface that is inclined as approaching the radial outer side toward the second side.
6. The taper roller bearing according to
the groove having a groove side surface that intersects with the groove longitudinal direction on a first axial side and that is closed on a second axial side.
|
The present invention relates to a taper roller bearing.
A taper roller bearing has a larger load capacity compared to another rolling bearing having the same size and has high rigidity.
The cage 104 includes a small-diameter annular portion 105 on one axial side, a large-diameter annular portion 106 on the other axial side, and a plurality of column portions 107 which link the annular portions 105 and 106 to each other. In addition, a space formed between both of the annular portions 105 and 106 and between the column portions 107 and 107 adjacent to each other in the circumferential direction is a pocket 108 which accommodates the taper roller 103 therein.
In addition, in the taper roller bearing 100, a diameter of an inner circumferential surface of the outer ring 102 widens as approaching the other side from one axial side, and when the taper roller bearing 100 (for example, inner ring 101) rotates, an action (pump action) by which the lubricating oil flows from one axial side to the other side between the outer ring 102 and the inner ring 101 is generated. It is known that, by the pump action which follows the rotation of the taper roller bearing 100, the lubricating oil on the outside of the bearing flows to the inside of the bearing from one axial side, and flows out from the other axial side.
In general, rotation torque of the taper roller bearing tends to increase compared to that of a ball bearing. Torque loss of the taper roller bearing is mainly broadly classified into three including rolling viscosity resistance between raceway rings (the inner ring 101 and the outer ring 102) and the taper roller 103, agitating resistance of the lubricating oil on the inside of the bearing, and sliding friction resistance between the taper roller 103 and a large flange 101b included in the inner ring 101.
As described above, by using the pump action which follows the rotation of the taper roller bearing 100, the oil on the outside of the bearing flows to the inside of the bearing from one axial side and flows out from the other axial side, but when the outflow becomes excessive with respect to the inflow of the lubricating oil, there is a possibility that the inside of the bearing becomes a poor lubrication state. In this case, the sliding friction resistance generated between the taper roller 103 and the inner ring 101 increases.
Here, an object of the present invention is to provide a taper roller bearing which can reduce sliding friction resistance between a taper roller and an inner ring.
According to the present invention, a taper roller bearing including: an inner ring which includes a small flange that is positioned on one side in an axial direction and protrudes to an outer side in a radial direction, and a large flange that is positioned on the other axial side and protrudes to the outer side in the radial direction; an outer ring which is positioned on the outer side in the radial direction of the inner ring; a plurality of taper rollers which are positioned between the inner ring and the outer ring; and an annular cage which holds the plurality of taper rollers at an interval in the circumferential direction, in which the cage includes a small-diameter annular portion which is positioned on one side, a large-diameter annular portion which is disposed on the other side and on the outer side in the radial direction of the large flange, and a plurality of column portions which link the small-diameter annular portion and the large-diameter annular portion to each other, and in which a labyrinth structure which suppresses a flow of lubricating oil to the outside of the taper roller bearing from the inside of the taper roller bearing is provided between the large flange and the large-diameter annular portion.
An inner circumferential surface of the large-diameter annular portion may include a first inner circumferential surface portion and a second inner circumferential surface portion having a diameter larger than a diameter of the first inner circumferential surface portion, and an outer circumferential surface of the large flange may include a first outer circumferential surface portion opposing to the first inner circumferential surface portion with a fine clearance, and a second outer circumferential surface portion having a diameter that is larger than a diameter of the first outer circumferential surface portion and opposing to the second inner circumferential surface portion with a fine clearance.
The small-diameter annular portion may block an annular opening portion formed between the small flange and the outer ring, having fine clearances between the small-diameter annular portion and the small flange and between the small-diameter annular portion and the outer ring, respectively.
Spaces formed between the large-diameter annular portion and the small-diameter annular portion and between the column portions adjacent to each other in the circumferential direction are pockets which holds the taper rollers, and cut-out portions which are continuous to the pockets are provided on the outer circumferential side of the large-diameter annular portion.
According to the present invention, it is possible to suppress the outflow of the lubricating oil from a space between the large flange of the inner ring that is the outflow side of the lubricating oil and the large-diameter annular portion of the cage, and to allow the lubricating oil to remain in the vicinity of the large flange. In addition, it is possible to use the lubricating oil as the lubricating oil between the large flange and the taper roller, and to reduce sliding friction resistance between the large flange and the taper roller.
According to the present invention, by forming the labyrinth structure having a clearance having different steps between the large flange of the inner ring that is the outflow side of the lubricating oil and the large-diameter annular portion of the cage, it is possible to improve a function of suppressing the outflow of the lubricating oil on the inside of the bearing.
According to the present invention, as the annular opening portion which is the inflow side of the lubricating oil is blocked having a fine clearance by the small-diameter annular portion of the cage, it is possible to suppress the inflow of the lubricating oil to the inside of the bearing. Therefore, the outflow increases compared to the inflow of the lubricating oil, there is a possibility that the inside of the bearing becomes a poor lubrication state, but according to the labyrinth structure, it is possible to hold the lubricating oil, and to use the lubricating oil as the lubricating oil between the large flange and the taper roller.
Accordingly, in order to reduce rolling viscosity resistance or agitating resistance, it is possible to reduce sliding friction resistance giving the lubricating oil at a necessary part while suppressing the inflow of the lubricating oil to the inside of the bearing by the small-diameter annular portion.
According to the present invention, at the annular opening portion formed between the large flange of the inner ring that is the outflow side of the lubricating oil and the end portion on the other axial side of the outer ring, on the outer ring side, it is possible to promote the discharge of the lubricating oil on the inside of the bearing by the cut-out portion. Meanwhile, on the inner ring side, as described above, it is possible to allow the lubricating oil to remain in the vicinity of the large flange, and to use the lubricating oil as the lubricating oil between the large flange and the taper roller.
Accordingly, in order to reduce rolling viscosity resistance or agitating resistance, it is possible to reduce sliding friction resistance giving the lubricating oil at a necessary part while promoting the outflow of the lubricating oil on the inside of the bearing by the cut-out portion.
According to the present invention, it is possible to reduce sliding friction resistance between the taper roller and the inner ring, and accordingly, it is possible to reduce energy loss in an apparatus in which the taper roller bearing is used.
[Entire Configuration of Taper Roller Bearing]
The inner ring 2 is an annular member which is formed by using bearing steel or steel for a mechanical structure, and a tapered inner ring raceway surface 2a on which the plurality of taper rollers 4 roll is formed on an outer circumference of the inner ring 2. In addition, the inner ring 2 includes a small flange 5 which protrudes to the radial outer side provided on one axial side (left side in
Similar to the inner ring 2, the outer ring 3 is also an annular member formed by using bearing steel or steel for a mechanical structure, and a tapered outer ring raceway surface 3a which opposes the inner ring raceway surface 2a and on which the plurality of taper rollers 4 roll is formed on an inner circumference of the outer ring 3. The raceway surfaces 2a and 3a are super-finished (finishing processing).
The taper roller 4 is a member formed by using bearing steel, and rolls on the inner ring raceway surface 2a and on the outer ring raceway surface 3a. The taper roller 4 includes a small end surface 4a having a small diameter on one axial side, and a large end surface 4b having a large diameter on the other axial side. The large end surface 4b is super-finished (finishing processing) after slidably coming into contact with a flange surface 7 of the large flange 6. In addition, the flange surface 7 is also super-finished (finishing processing).
In
In
In addition, the cage 10 is positioned with respect to the radial direction as a part thereof (slide contact surfaces 40 and 39) slidably comes into contact with an inner circumferential surface 3b of the outer ring 3. A configuration for this will be described. In
In
Therefore, when the taper roller bearing 1 (inner ring 2 in the embodiment) rotates, an action (pump action) by which the lubricating oil flows from one axial side to the other side in the annular space S formed between the inner ring 2 and the outer ring 3 is generated. By the pump action which follows the rotation of the taper roller bearing 1, the lubricating oil on the outside of the bearing flows into the annular space S (inside of the bearing) between the inner ring 2 and the outer ring 3 from one axial side, and flows out from the other axial side. In other words, the lubricating oil passes through the inside of the bearing. Above, in the taper roller bearing 1 illustrated in
[Regarding Small-diameter Annular Portion 11 of Cage 10]
On the inner circumferential side of the small-diameter annular portion 11, an inner circumferential surface 11b of the small-diameter annular portion 11 opposes an outer circumferential surface 5a of the small flange 5 of the inner ring 2 in the radial direction, the inner circumferential surface 11b and the outer circumferential surface 5a are close to each other, and an annular fine clearance K2 is formed therebetween.
Above, an annular opening portion A1 is formed between the small flange 5 of the inner ring 2 and the end portion 3d on one axial side of the outer ring 3, and the small-diameter annular portion 11 is configured to block the annular opening portion A1 at the fine clearances K1 and K2 between each of the small flange 5 and the end portion 3d of the outer ring 3.
For example, in a case where the inner diameter of the taper roller bearing 1 is 30 to 40 mm and the outer diameter is 70 to 80 mm, the fine clearance K1 on the radial outer side can be 50 to 125 μm, and is 100 μm in the embodiment. In addition, in the taper roller bearing having the dimension, the fine clearance K2 on the radial inner side can be 50 to 125 μm, and is 100 μm in the embodiment. In addition, in the embodiment, a radial dimension partially changes in each of the fine clearances K1 and K2, but the value is a radial dimension, and the clearance is a dimension at a part at which the clearance is the minimum.
As illustrated in the enlarged view on the inner ring 2 side of
The outer circumferential surface 5a of the small flange 5 which radially opposes the inner circumferential surface 11b of the small-diameter annular portion 11 includes a first outer circumferential surface portion 24 which opposes the first inner circumferential surface portion 21 with a fine clearance K2-1, and a second outer circumferential surface portion 25 which opposes the second inner circumferential surface portion 22 with a fine clearance K2-2. The first outer circumferential surface portion 24 has a cylindrical surface around the center line C0 of the taper roller bearing 1, and the second outer circumferential surface portion 25 has an R-surface which is formed in the small flange 5. The first outer circumferential surface portion 24 and the second outer circumferential surface portion 25 are continuous to each other, and a boundary thereof is a virtual surface which is orthogonal to the center line C0 including the annular surface 23. In addition, a diameter d2 of the second outer circumferential surface portion 25 is smaller than a diameter d1 of the first outer circumferential surface portion 24 (d2<d1).
According to the configuration in the small-diameter annular portion 11, the annular opening portion A1 which is the inflow side of the lubricating oil can suppress the inflow of the lubricating oil to the inside of the bearing being blocked by the small-diameter annular portion 11 of the cage 10 with the fine clearances K1 and K2. Furthermore, a labyrinth structure having the annular fine clearances K2-1 and K2-2 which have different steps (different diameters) is formed between the small flange 5 and the small-diameter annular portion 11, and on the inner ring 2 side of the annular opening portion A1, it is possible to more efficiently suppress the inflow of the lubricating oil to the inside of the bearing. As a result, as an amount of lubricating oil decreases on the inside of the bearing, it is possible to reduce rolling viscosity resistance and agitating resistance of the taper roller bearing 1, and a rotation torque of the taper roller bearing 1 is reduced.
In addition, the lubricating oil which passes through the fine clearances K1 and K2 is used for lubricating the taper roller bearing 1. In other words, the fine clearances K1 and K2 allow passage of the lubricating oil, but the inflow of the lubricating oil of which an amount is equal to or greater than an amount necessary for the lubrication to the inside of the bearing is restricted on the inside of the taper roller bearing 1.
In addition, in the embodiment, the diameter d1 of the first outer circumferential surface portion 24 is greater than the diameter D2 of the second inner circumferential surface portion 22 (d1>D2), the fine clearance K2-1 is configured not be seen from one axial side, and it is possible to more efficiently suppress intrusion of the lubricating oil.
As illustrated in
In this case, the diameter D2 of the second inner circumferential surface portion 22 of which the diameter is the minimum on the inner circumferential surface 11b of the small-diameter annular portion 11 (refer to
Here, the outer diameter d7 (maximum value) of the circular portion 9 is determined in accordance with the size of the taper roller bearing 1. For example, in a case where the inner diameter is 30 mm, the outer diameter is 55 mm, and an axial dimension (entire width) is 17 mm, the maximum value of the outer diameter d7 of the circular portion 9 based on the ISO standard is 35 mm. In this case, the diameter D2 of the second inner circumferential surface portion 22 is set to be greater than the outer diameter d7 (35 mm). For example, in a case where the diameter D2 of the second inner circumferential surface portion 22 can be set to be greater than the outer diameter d7 by 1 to 3 millimeters, and the outer diameter d7 of the circular portion 9 is 35 mm, the diameter D2 of the second inner circumferential surface portion 22 can be, for example, 37 mm.
By setting an inner circumferential surface shape of the small-diameter annular portion 11 in this manner, while maintaining the shape of the bearing based on the ISO standard, the taper roller bearing 1 can be provided with the labyrinth structure on the small flange 5 side of the inner ring 2.
In addition, as described above, in order to provide the fine clearance K2 (K2-1 and K2-2) having high dimension accuracy between the small flange 5 and the small-diameter annular portion 11, the finishing processing, such as polishing, is performed with respect to the outer circumferential surface 5a of the small flange 5, and additionally, the cage 10 made of a resin may be molded with high accuracy using a mold.
Otherwise, as another means for providing the fine clearance K2 (K2-1 and K2-2) having high dimension accuracy, the taper roller bearing 1 having the following configuration may be employed.
In other words, a point that the cage 10 made of a resin is molded using a mold is the same, but as illustrated in
Here, when the taper roller bearing 1 (refer to
In other words, as described above, since the radial clearance K0 between the small flange 5 and the small-diameter annular portion 11 is set to be a negative clearance, as illustrated in
Accordingly, it is possible form (automatically form) the labyrinth structure between the small flange 5 and the small-diameter annular portion 11 that is a on the inflow side of the lubricating oil.
In addition, in the aspect illustrated in
In addition, as described in
[Regarding Column Portion 13 of Cage 10]
Here, in
In addition, in the embodiment, as illustrated in
The second virtual taper surface J2 of the embodiment has a diameter which is slightly smaller than that of the first virtual taper surface J1. Therefore, the radial inner surface 17 of the column portion 13 is configured to be provided along the second virtual taper surface J2 which is slightly smaller than the first virtual taper surface J1, and the radial inner surface 17 is positioned further on the radial inner side than a half portion on the outer ring 3 side in the taper roller 4. A radius difference between the first virtual taper surface J1 and the second virtual taper surface J2 can be, for example, in a range of 500 μm to 1000 μm including the maximum value and the minimum value thereof, and the radius difference (minimum value) in the embodiment is 700 μm.
In addition, in the radial inner surface 17, the groove 18 which extends along the longitudinal direction of the column portion 13 is formed. As illustrated in
Meanwhile, the groove 18 does not have a surface which is orthogonal to the groove longitudinal direction on the other axial side, and is open on the other axial side. Specifically speaking, the groove 18 has a shallow part 18e (refer to
Therefore, a sectional shape of the groove 18 is not constant along the groove longitudinal direction and changes in the middle portion 18b on the other axial side. In a region on the other axial side from the middle portion 18b, as the groove 18 becomes shallow, the groove sectional shape becomes smaller. In addition, as illustrated in
According to the configuration in the radial inner surface 17 of the column portion 13, when the taper roller bearing 1 rotates, the taper roller 4 rotates around the center line C1 of itself, and the radial inner surface 17 can scrap the lubricating oil attached to an outer circumferential surface 4c of the taper roller 4 across the entire length in the longitudinal direction of the column portion 13. Therefore, it is possible to reduce rolling viscosity resistance and agitating resistance in the taper roller bearing 1.
Furthermore, in the embodiment, as illustrated in
In addition, as described above, the groove 18 has a part 18e (refer to
In addition, the first virtual taper surface J1 and the second virtual taper surface J2 may match each other. In this case, the radial inner surface 17 can also scrape the lubricating oil attached to the outer circumferential surface 4c of the taper roller 4.
However, as described in the embodiment illustrated in
The reason thereof is that the rigidity (strength) of a radial inner end portion 13a (refer to
Above, in the embodiment, the taper roller 4 can come into contact with the solid part 13b at which the groove 18 in the column portion 13 is not provided, and it is prevented that the groove 18 becomes a weakness from the viewpoint of a strength. In addition, as illustrated in
As described above, in the embodiment, the minimum value of the radius difference between the first virtual taper surface J1 and the second virtual taper surface J2 is 700 μm. This is based on the shape of the groove 18 which is a semicircular shape and the radius thereof which is 500 μm in
A shape on the radial outer side of the column portion 13 will be described. In
[Regarding Large-diameter Annular Portion 12 of Cage 10 (First Thereof)]
As described above, in the taper roller bearing 1 illustrated in
A cut-out portion 15 which is continuous to the pocket 14 is provided on the outer circumferential side of the large-diameter annular portion 12. As illustrated in
Next, a configuration on an inner circumferential side of the large-diameter annular portion 12 will be described. In
For example, in a case where the inner diameter of the taper roller bearing 1 is 30 to 40 mm and the outer diameter is 70 to 80 mm, the fine clearance K3 can be 75 to 125 μm, and is 100 μm in the embodiment. In addition, the radial dimension of the fine clearance K3 may partially change, and the value is a dimension in the radial direction and is a dimension at a part at which the clearance is the minimum.
In addition, the fine clearance K3 may be set to decrease as approaching the other axial side (outside of the bearing), that is, toward the outflow direction of the lubricating oil.
Above, the labyrinth structure which suppresses the flow of the lubricating oil to the outside of the bearing from the inside of the bearing is formed between the large flange 6 and the large-diameter annular portion 12. According to the labyrinth structure, the outflow of the lubricating oil from between the large flange 6 and the large-diameter annular portion 12 can be suppressed, the lubricating oil can remain in the vicinity of the flange surface 7 of the large flange 6. In particular, in the embodiment, in the region on the radial outer side of the flange surface 7 which is the upstream side of the fine clearance K3, an annular enlarged space portion K4 is formed, and the lubricating oil can remain in the annular enlarged space portion K4. In addition, the annular enlarged space portion K4 is made of a region formed between the large flange 6 and the cage 10. In addition, it is possible to use the lubricating oil which remains in the vicinity of the flange surface 7 as the lubricating oil for the lubrication between the flange surface 7 and the large end surface 4b of the taper roller 4, and to reduce sliding friction resistance between the large flange 6 and the taper roller 4.
In addition, as described above, since the cut-out portion 15 which is continuous to the pocket 14 is provided on the outer circumferential side of the large-diameter annular portion 12, in the annular opening portion A2 which is the outflow side of the lubricating oil, on the outer ring 3 side, the discharge of the lubricating oil on the inside of the bearing is promoted. Meanwhile, on the inner ring 2 side, by the labyrinth structure, it is possible to supply the lubricating oil between the flange surface 7 of the large flange 6 and the large end surface 4b of the taper roller 4.
Above, in order to reduce rolling viscosity resistance or agitating resistance, it is possible to reduce the sliding friction resistance by holding the lubricating oil at a necessary part (slide surface between the flange surface 7 and the large end surface 4b) while promoting the outflow of the lubricating oil on the inside of the bearing by the cut-out portion 15.
In addition, in the taper roller bearing 1 of the embodiment, as described above, the small-diameter annular portion 11 of the cage 10 blocks the annular opening portion A1 (refer to
In this manner, as the inflow side (annular opening portion A1) of the lubricating oil is blocked having the fine clearances K1 and K2 by the small-diameter annular portion 11, the inflow of the lubricating oil to the inside of the bearing can be suppressed. Therefore, the amount of outflow increases in the annular opening portion A2 on the axial opposite side with respect to the inflow of the lubricating oil, and there is a possibility that the inside of the bearing becomes a poor lubricating oil state. However, in
Above, in order to reduce rolling viscosity resistance or agitating resistance, it is possible to reduce the sliding friction resistance by giving the lubricating oil at a necessary part while suppressing the inflow of the lubricating oil to the inside of the bearing by the small-diameter annular portion 11.
Here, as described above, since the fine clearance K3 having high dimension accuracy is provided between the large flange 6 of the inner ring 2 and the large-diameter annular portion 12 of the cage 10, the finishing processing, such as polishing, is performed with respect to the outer circumferential surface 6a of the large flange 6, and the cage 10 made of a resin may be molded using a mold with high accuracy.
In addition, as another means for providing the fine clearance K3 having high dimension accuracy, the taper roller bearing 1 having the following configuration may be employed.
In other words, a point that the cage 10 made of a resin is molded using a mold is the same, but as illustrated in
In addition, similar to the technology described by using
In other words, as described above, since the radial clearance K10 between the large flange 6 and the large-diameter annular portion 12 is set to be a negative clearance, as illustrated in
Accordingly, it is possible to form (automatically form) the labyrinth structure between the large flange 6 of the inner ring 2 which is the outflow side of the lubricating oil and the large-diameter annular portion 12 of the cage 10.
In addition, in the embodiment illustrated in
[Modification Example of Large-Diameter Annular Portion 12]
The outer circumferential surface 6a of the large flange 6 which opposes the inner circumferential surface 12a of the large-diameter annular portion 12 in the radial direction includes a first outer circumferential surface portion 29 which opposes the first inner circumferential surface portion 26 having a fine clearance K3-1, and a second outer circumferential surface portion 30 which opposes the second inner circumferential surface portion 27 having a fine clearance K3-2. In addition, a diameter d4 of the second outer circumferential surface portion 30 is greater than a diameter d3 of the first outer circumferential surface portion 29 (d4>d3).
According to the configuration in the above-described large-diameter annular portion 12, it is possible to form the labyrinth structure having clearances (K3-2 and K3-1) having different steps between the large flange 6 which is the outflow side of the lubricating oil and the large-diameter annular portion 12, and to improve a function of suppressing the outflow of the lubricating oil on the inside of the bearing. As a result, similar to the aspect illustrated in
In addition, in the embodiment, the diameter d4 of the second outer circumferential surface portion 30 is greater than the diameter D3 of the first inner circumferential surface portion 26, the fine clearance K3-2 is configured not to be seen from one axial side, and the outflow of the lubricating oil is more efficiently suppressed.
In the embodiment illustrated in
[Regarding Large-diameter Annular Portion 12 of Cage 10 (Second Thereof)]
In addition, in the embodiment, the large-diameter annular portion 12 and the large flange 6 cover the cavity portion 16 from the other axial side. In addition, the fine clearance K3 is formed between the large-diameter annular portion 12 and the large flange 6, and the fine clearance K3 has a function (labyrinth structure) of suppressing the outflow of the lubricating oil as described above. Therefore, all of the cavity portions 16 are covered by the labyrinth structure made by forming the large-diameter annular portion 12, the large flange 6, and the fine clearance K3.
A configuration of the large-diameter annular portion 12 for covering all of the cavity portions 16 in this manner will be described.
Here, the plurality of taper rollers 4 are disposed along the inner ring raceway surface 2a and the outer ring raceway surface 3a, and are positioned to abut against the flange surface 7. Therefore, as illustrated in the enlarged view of
According to the configuration, on the outflow side of the lubricating oil provided in the large-diameter annular portion 12, the axial inner surface 12c of the large-diameter annular portion 12 can cover the cavity portion 16 (a large part thereof) of all of the taper rollers 4 from the axial direction, and can hold the lubricating oil between the axial inner surface 12c and each of the cavity portions 16. In addition, it is possible to use the lubricating oil to be held as the lubricating oil between the flange surface 7 of the large flange 6 and the large end surface 4b of the taper roller 4, and thus, to reduce sliding friction resistance between the large flange 6 and the taper roller 4.
In addition, as described above, on the outer circumferential side of the large-diameter annular portion 12, the cut-out portion 15 which is continuous to the pocket 14 is provided, and thus, it is possible to promote the discharge of the lubricating oil on the inside of the bearing on the outer ring 3 side in the annular opening portion A2 which is the outflow side of the lubricating oil. Meanwhile, on the inner ring 2 side, as described above, the large-diameter annular portion 12 can cover the cavity portion 16 of the large end surface 4b of the taper roller 4 from the axial direction and can hold the lubricating oil. Accordingly, in order to reduce rolling viscosity resistance or agitating resistance, it is possible to reduce sliding friction resistance by holding the lubricating oil at a necessary part (slide surface between the flange surface 7 and the large end surface 4b) while promoting the discharge of the lubricating oil on the inside of the bearing by the cut-out portion 15.
Furthermore, as described above, the labyrinth structure which suppresses the flow of the lubricating oil from the inside of the bearing to the outside of the bearing is provided between the large flange 6 and the large-diameter annular portion 12. Therefore, it is possible to suppress the outflow of the lubricating oil from the space between the large flange 6 and the large-diameter annular portion 12, and to allow the lubricating oil to remain in the annular enlarged space portion K4 which is in the vicinity of the flange surface 7 of the large flange 6. In particular, in the embodiment, as illustrated in
[Regarding Roller Retaining Portions 41 and 42]
In
In
In addition, the first roller retaining portion 41 and the second roller retaining portion 42 are discontinuous to each other, and are provided to be separated from each other in the column portion longitudinal direction.
The first roller retaining portion 41 has a shape of a protruding beam which is a fixed end on the column portion 13 side and on the small-diameter annular portion 11 side, and is a free end on the tip end side in the extending direction which extends in the circumferential direction and in the column portion longitudinal direction. In other words, the first roller retaining portion 41 has a shape of a protruding beam (a shape of a cantilever beam) which is a fixed end being integrated with the column portion 13 at one end 43 in the circumferential direction on the column portion 13 side, and is a free end at another end 45 in the circumferential direction on the other end side in the column portion longitudinal direction while being a fixed end which is integrated with the small-diameter annular portion 11 at one end 44 in the column portion longitudinal direction on the small-diameter annular portion 11 side. Each of the first roller retaining portions 41 is likely to be deformed since the first roller retaining portions 41 have such a shape of a protruding beam, and in particular, have a shape of which a tip portion side in the protruding direction is likely to be bent.
Although not being illustrated, in a case where the first roller retaining portion 41 and the second roller retaining portion 42 are continuous to each other and the first roller retaining portion 41 is not a free end on the other end side in the column portion longitudinal direction, rigidity of the first roller retaining portion 41 increases, and the first roller retaining portion 41 is configured to be unlikely to be deformed.
The second roller retaining portion 42 is provided on the large-diameter annular portion 12 side, and is provided to protrude in the circumferential direction from the column portion 13. The second roller retaining portion 42 is discontinuous to the large-diameter annular portion 12, and has a shape of a cantilever beam that can be deformed independently from the large-diameter annular portion 12. In other words, the second roller retaining portion 42 is a fixed end which is integrated with the column portion 13 at one end 47 in the circumferential direction on the column portion 13 side, and is a free end at the other end 48 in the circumferential direction.
Above, one pair of first roller retaining portions 41 and 41 is provided on both circumferential sides of one pocket 14 on the small-diameter annular portion 11 side, and a pocket width (dimension in the circumferential direction of the pocket 14) on the small-diameter annular portion 11 side becomes smaller than a taper roller width (diameter of the taper roller 4 at corresponding positions) due to the first roller retaining portions 41 and 41.
Similar to this, one pair of second roller retaining portions 42 and 42 is provided on both circumferential sides of one pocket 14 on the large-diameter annular portion 12 side, and a pocket width (dimension in the circumferential direction of the pocket 14) on the large-diameter annular portion 12 side becomes smaller than a taper roller width (diameter of the taper roller 4 at corresponding positions) due to the second roller retaining portions 42 and 42.
Above, the cage 10 can hold the taper roller 4 by preventing the taper roller 4 in the pocket 14 from falling out to the radial outer side. In addition, attachment of the taper roller 4 to the pocket 14 can be performed from the inner circumferential side.
As described above, in order to assemble the taper roller bearing 1, first, as illustrated in
Here, as described above, as the first roller retaining portion 41 has a shape (in particular, a shape by which the tip portion side in the protruding direction is likely to be bent) which is likely to be deformed, the taper roller 4 can easily climb over the small flange 5 pushing (elastically deforming) the first roller retaining portion 41, and the assembly becomes easy.
In the related art, since the column portion functions as a roller retaining portion across the entire length, the rigidity is high, and in a case where the assembly is performed by a similar method, it is necessary to elastically deform the column portion and the small-diameter annular portion. Therefore, the assembly is performed by using a press in the related art. However, in the embodiment, since the first roller retaining portion 41 is easily deformed, the assembly can be performed by a force (manually) of a worker without using a press.
Furthermore, as illustrated in
In addition, although not being illustrated, by allowing the outer ring 3 to approach to the unit of the inner ring 2, the taper roller 4, and the cage 10 which are integrated with each other from the axial direction, and by assembling the outer ring 3 to the unit, the taper roller bearing 1 is configured.
In addition, in the embodiment, the cage 10 includes the second roller retaining portion 42 which is separated in the column portion longitudinal direction other than the first roller retaining portion 41. Therefore, it is possible to reliably prevent the taper roller 4 from falling out from the pocket 14 by the first roller retaining portion 41 and the second roller retaining portion 42. Furthermore, since the first roller retaining portion 41 is separated from the second roller retaining portion 42 in the column portion longitudinal direction, it is possible to prevent the deformation of the first roller retaining portion 41 from being restricted by the second roller retaining portion 42. In other words, it is possible to prevent characteristics that the deformation of the first roller retaining portion 41 is easy from deteriorating.
In addition, the radial outer surface of the second roller retaining portion 42 configures the slide contact surface 39 which is slidable on the inner circumferential surface 3b of the outer ring 3, and accordingly, the slide contact surface 39 can be positioned with respect to the radial direction of the cage 10 together with the slide contact surface 40 on the small-diameter annular portion 11 side.
In addition, in the taper roller bearing 1, as described by using
In this case, the lubricating oil which can intrude the fine clearance K1 (refer to
Furthermore, the lubricating oil which can intrude to the fine clearance K1 and exists on the radial outer side of the column portion 13 flows backward to the small-diameter annular portion 11 side and further flows to the radial outer side of the adjacent column portion 13 climbing over the small-diameter side of the taper roller 4 according to the rotation of the taper roller 4. However, in the embodiment, since the first roller retaining portion 41 includes the arc surface portion 41a which is continuous to the outer circumferential surface 11a of the small-diameter annular portion 11 and is provided along the smooth arc surface, on the radial outer side, it is possible to make it difficult for the flow of the lubricating oil to be generated. In other words, since the surface which opposes the inner circumferential surface 3b of the outer ring 3 having the fine clearance K1 widens being added by the arc surface portion 41a, resistance of the flow of the lubricating oil increases, and it is possible to suppress generation of the backward flow described above.
[Regarding Taper Roller Bearing 1 and Split Mold]
Since the cage 10 is made of a resin, molding is performed by injecting a molten resin to a cavity of the mold and hardening the molten resin. In addition, the manufacturing of the cage 10 is performed by the injection molding. In the embodiment, as illustrated in
In a state where the first mold 51 and the second mold 52 are relatively moved along the center line C2 and are allowed to approach each other, and are further assembled on the inner side of the annular mold 53, the molten resin is injected into the cavity, cooled, and hardened. In addition, by relatively moving the first mold 51 and the second mold 52 along the center line C2 and making the first mold 51 and the second mold 52 separated from each other, the mold of the cage 10 which is a molded article is removed.
In this manner, in order to use the mold that configures the cavity as the two-split molds (51 and 52), when the molds 51 and 52 are separated and removed, it is necessary that the molded article is configured in which a so-called forced extraction is not generated, and the cage 10 of the embodiment is configured in this manner.
Specifically speaking, the cage 10 is configured of the small-diameter annular portion 11, the large-diameter annular portion 12, and the plurality of column portions 13, and the surface of the entire cage including the small-diameter annular portion 11, the large-diameter annular portion 12, and all of the column portions 13, is configured by aggregating a surface viewed from one axial side (refer to
The next surface is included in the surface of the entire cage.
In the small-diameter annular portion 11, the outer circumferential surface 11a, the inner circumferential surface 11b, the axial inner surface 11c, and an axial outer surface 11d are included. In the large-diameter annular portion 12, an outer circumferential surface 12b, the inner circumferential surface 12a, the axial inner surface 12c, and an axial outer surface 12d are included.
In the column portion 13, the radial inner surface 17, a radial outer surface 37, and the side surfaces 13c on both sides are included. In the first roller retaining portion 41 in the column portion 13, the slide contact surface 40 on the small-diameter annular portion 11 side and a rear surface 40a of the slide contact surface 40 are included. In addition, in the second roller retaining portion 42, the slide contact surface 39 on the large-diameter annular portion 12 side, a rear surface 39a of the slide contact surface 39, a surface 40b on one axial side, and a surface 40c on the other axial side.
Here, as illustrated in
Meanwhile, as illustrated in
In
In a case where the groove 18 is not open in the end portion on the other axial side, the inner surface of the part at which the opening is closed is not included in either the surface viewed from one axial side or the surface viewed from the other axial side, the axial movement of one mold (second mold 52) of the first mold 51 and the second mold 52 is inhibited by the part at which the opening is not closed, and the manufacturing of the cage 10 using the half-split mold becomes impossible.
However, according to the configuration of the groove 18 according to the embodiment, each portion of the entire groove 18 is viewed from the other axial side, and the manufacturing of the cage using the half-split mold becomes possible.
In addition, as described above (refer to
However, as illustrated in
Here, as described in the embodiment, as the radial inner surface 17 of the column portion 13 is provided along the second virtual taper surface J2, it is possible to manufacture the cage 10 made of a resin using the half-split molds (51 and 52) while having a function of scraping the lubricating oil of the taper roller 4.
In addition, as described above, in order to flow the lubricating oil in the vicinity of the inner circumferential surface 3b of the outer ring 3 between the pockets 14 and 14 adjacent to each other and weaken agitating resistance of the lubricating oil, the recess portion 33 is formed on the radial outer side of the column portion 13 (refer to
Accordingly, even when the recess portion 33 is formed on the radial outer side of the column portion 13, the molding using the half-split molds (51 and 52) is maintained. In other words, by configuring the recess portion 33 in this manner, the entire recess portion 33 becomes a surface viewed from one axial side (refer to
Above, as the surface of the entire cage is configured by aggregating the surface viewed from one axial side (refer to
In addition, although not being illustrated, the cage 10 of the embodiment illustrated in
The embodiments disclosed above are merely examples in all aspects and are not limited thereto. In other words, the taper roller bearing of the present invention may be another aspect within the range of the present invention not being limited to the aspects illustrated in the drawings.
According to the present invention, it is possible to reduce sliding friction resistance between the taper roller and the inner ring, and accordingly, it is possible to reduce energy loss in an apparatus in which the taper roller bearing is used.
1: TAPER ROLLER BEARING
2: INNER RING
3: OUTER RING
4: TAPER ROLLER
5: SMALL FLANGE
5a: OUTER CIRCUMFERENTIAL SURFACE
6: LARGE FLANGE
6a: OUTER CIRCUMFERENTIAL SURFACE
8: SHAFT
9: CIRCULAR PORTION
10: CAGE
11: SMALL-DIAMETER ANNULAR PORTION
11a: OUTER CIRCUMFERENTIAL SURFACE
11b: INNER CIRCUMFERENTIAL SURFACE
12: LARGE-DIAMETER ANNULAR PORTION
12a: INNER CIRCUMFERENTIAL SURFACE
12c: AXIAL INNER SURFACE
13: COLUMN PORTION
14: POCKET
15: CUT-OUT PORTION
16: CAVITY PORTION
16a: RADIAL OUTER END PORTION
17: RADIAL INNER SURFACE
18: GROOVE
18e: SHALLOW PART
21: FIRST INNER CIRCUMFERENTIAL SURFACE PORTION
22: SECOND INNER CIRCUMFERENTIAL SURFACE PORTION
24: FIRST OUTER CIRCUMFERENTIAL SURFACE PORTION
25: SECOND OUTER CIRCUMFERENTIAL SURFACE PORTION
26: FIRST INNER CIRCUMFERENTIAL SURFACE PORTION
27: SECOND INNER CIRCUMFERENTIAL SURFACE PORTION
29: FIRST OUTER CIRCUMFERENTIAL SURFACE PORTION
30: SECOND OUTER CIRCUMFERENTIAL SURFACE PORTION
33: RECESS PORTION
33a: END
33b: BOTTOM SURFACE
40: SLIDE CONTACT SURFACE
41: FIRST ROLLER RETAINING PORTION
41a: ARC SURFACE PORTION
42: SECOND ROLLER RETAINING PORTION
A1: ANNULAR OPENING PORTION
A2: ANNULAR OPENING PORTION
C1: CENTER LINE
J1: FIRST VIRTUAL TAPER SURFACE
J2: SECOND VIRTUAL TAPER SURFACE
J3: VIRTUAL EXTENDING LINE
K0: RADIAL CLEARANCE
K2-1: FINE CLEARANCE
K2-2: FINE CLEARANCE
K3-1: FINE CLEARANCE
K3-2: FINE CLEARANCE
K10: RADIAL CLEARANCE
Kamamoto, Shigeo, Murata, Junji, Shishihara, Yuki
Patent | Priority | Assignee | Title |
Patent | Priority | Assignee | Title |
1840607, | |||
3477773, | |||
4288129, | Apr 11 1980 | NTN-BOWER CORPORATION | Bearing cage |
4425011, | Jun 07 1982 | MPB Corporation | Polymer cage for a high speed tapered roller bearing |
4462643, | Sep 16 1981 | The Timken Company | Tapered roller bearing cage with spin resisting characteristics |
4664537, | Oct 01 1984 | VEB KOMBINAT WALZLAGER U NORMTEILE, REICHENHANER STRASSE 31 33 - 9022 KARL-MARX-STADT, DDR, GERMAN, A CORP OF GERMANY | Cage for tapered-roller bearing |
4707152, | Feb 22 1986 | FAG Kugelfischer Georg Schafer (KGaA) | Cage for tapered roller bearings |
4728204, | Nov 22 1985 | Riv-Skf Officine Di Villar Perosa S.p.A. | Taper roller bearing, particularly for railway use |
5039231, | Aug 02 1989 | SKF GmbH | Bearing cage |
7955001, | Oct 20 2008 | Amsted Rail Company, Inc. | Tapered roller bearing with improved cage |
8172464, | Nov 09 2006 | NTN Corporation | Tapered roller bearing |
8382380, | Aug 25 2005 | NTN Corporation | Tapered roller bearing |
8480308, | Aug 18 2005 | JTEKT Corporation | Tapered roller bearing, tapered roller bearing apparatus, and automotive pinion shaft supporting apparatus utilizing same tapered roller bearing apparatus |
8596877, | Nov 12 2007 | NTN Corporation | Tapered roller bearing |
8641290, | Feb 19 2004 | JTEKT Corporation | Tapered roller bearing |
8770853, | May 18 2012 | JTEKT Corporation | Split cage for rolling bearing |
8783965, | May 13 2004 | NTN Corporation | Tapered roller bearing |
9039288, | Jul 08 2008 | NSK Ltd | Tapered roller bearing resin cage and tapered roller bearing |
9297419, | Mar 10 2014 | JTEKT Corporation | Tapered roller bearing |
9664230, | Apr 23 2013 | JTEKT Corporation | Taper roller bearing |
20070230852, | |||
20080205813, | |||
20100098369, | |||
20100209036, | |||
20110123142, | |||
20110142389, | |||
20120263405, | |||
20120321237, | |||
20130315522, | |||
20140013603, | |||
20140248018, | |||
20150049971, | |||
20150323008, | |||
20160040716, | |||
20160169285, | |||
AU2010212394, | |||
CN101725634, | |||
CN102089541, | |||
CN203892379, | |||
FR2548297, | |||
JP1085521, | |||
JP2003287033, | |||
JP2005321049, | |||
JP2008002534, | |||
JP2008014335, | |||
JP2008051272, | |||
JP2008051295, | |||
JP2008169995, | |||
JP2008208973, | |||
JP2008249104, | |||
JP2009192069, | |||
JP2009204068, | |||
JP2011226571, | |||
JP2012047250, | |||
JP2013238296, | |||
JP2013242018, | |||
JP2014202284, | |||
JP2014202341, | |||
JP2745160, | |||
JP369823, | |||
JP3751739, | |||
JP4151347, | |||
JP5058956, | |||
JP5429166, | |||
JP55010140, | |||
JP62200019, | |||
WO2014175000, |
Executed on | Assignor | Assignee | Conveyance | Frame | Reel | Doc |
Oct 23 2015 | JTEKT Corporation | (assignment on the face of the patent) | / | |||
Mar 09 2017 | KAMAMOTO, SHIGEO | JTEKT Corporation | ASSIGNMENT OF ASSIGNORS INTEREST SEE DOCUMENT FOR DETAILS | 041847 | /0332 | |
Mar 09 2017 | MURATA, JUNJI | JTEKT Corporation | ASSIGNMENT OF ASSIGNORS INTEREST SEE DOCUMENT FOR DETAILS | 041847 | /0332 | |
Mar 09 2017 | SHISHIHARA, YUKI | JTEKT Corporation | ASSIGNMENT OF ASSIGNORS INTEREST SEE DOCUMENT FOR DETAILS | 041847 | /0332 |
Date | Maintenance Fee Events |
Date | Maintenance Schedule |
Jan 01 2022 | 4 years fee payment window open |
Jul 01 2022 | 6 months grace period start (w surcharge) |
Jan 01 2023 | patent expiry (for year 4) |
Jan 01 2025 | 2 years to revive unintentionally abandoned end. (for year 4) |
Jan 01 2026 | 8 years fee payment window open |
Jul 01 2026 | 6 months grace period start (w surcharge) |
Jan 01 2027 | patent expiry (for year 8) |
Jan 01 2029 | 2 years to revive unintentionally abandoned end. (for year 8) |
Jan 01 2030 | 12 years fee payment window open |
Jul 01 2030 | 6 months grace period start (w surcharge) |
Jan 01 2031 | patent expiry (for year 12) |
Jan 01 2033 | 2 years to revive unintentionally abandoned end. (for year 12) |