CN203516458U - Cylindrical roller bearing - Google Patents
Cylindrical roller bearing Download PDFInfo
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- CN203516458U CN203516458U CN201320342542.8U CN201320342542U CN203516458U CN 203516458 U CN203516458 U CN 203516458U CN 201320342542 U CN201320342542 U CN 201320342542U CN 203516458 U CN203516458 U CN 203516458U
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- roller
- roller bearing
- ring raceway
- raceway face
- outer ring
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Abstract
The utility model relates to a cylindrical roller bearing capable of inhibiting the abrasion of a static ring even under the application condition of low rotating speed state. The cylindrical roller bearing (10) provided by the utility model is a full cylindrical roller bearing and is provided with an inner ring (20), an outer ring (30) and cylindrical rollers (40), wherein an inner ring raceway surface (22) is formed on the outer circumferential surface of the inner ring; an outer ring raceway surface (32) is formed on the outer circumferential surface of the outer ring; a plurality of cylindrical rollers are allocated along the circumferential direction and can freely roll between the inner ring raceway surface (22) and the outer ring raceway surface (32), each roller (40) is at least provided with a straight flange part (42) at the axial central part, and the inner ring raceway surface (22) and the outer ring raceway surface (32) are in single circular arc projection shapes.
Description
Technical field
The utility model relates to a kind of roller bearing.
Background technique
In steel-making factory, in order directly to produce continuously slab (slab), steel billet (billet) or this class of round bar from molten steel, there is the product of single section shape and adopt continuous casting process.By slab and the steel billet of continuous casting process moulding, by along its direction of advance, be disposed at its surface and a plurality of deflector rolls of these both sides, the back side are directed and the state carried under by cooling gradually.The deflector roll adopting due to the neck of deflector roll can, because the deflection of deflector roll or the inclination of shell produce inclination, therefore, use self-aligning roller bearing as deflector roll bearing with inner ring and the outer ring of bearing conventionally.
Yet because deflector roll uses under the utmost point slow-speed of revolution with bearing, so oiling agent is difficult for being introduced between bearing ring and rolling element, be difficult for forming oil film.In addition, can not avoid water to infiltrate bearing inside from Environmental Conditions, so likely cause lubricating status poor, can wear and tear because of Metal Contact.Particularly, in self-aligning roller bearing, differential sliding increases, wear extent increases, and likely causes peeling off or ftracture (crack damage).
As the countermeasure that reduces the wearing and tearing of self-aligning roller bearing, proposition has at the top layer of bearing ring formation carbonitrided case, make the retained austenite amount of this carbonitrided case more than 10 volume %, the scheme (for example, patent documentation 1) of surface hardness more than Rockwell hardness HRC58.
In addition, also proposed to add two carbamide compounds at the lubricating base oil of the lubricant composition for lubricating bearings, and added the scheme (for example, patent documentation 2) of polymeric compound and succinic acid and/or succinic acid derivative.According to this, form, can in rotary area and/or sliding area, maintain thicker lubricant film, can prevent the defects such as burn-back, reduce the damage of bearing.
In addition, also proposed, at the outer diametric plane of the outer ring of self-aligning roller bearing, crowning is set, withdrawing surplus (for example, patent documentation 3) has been set between outer ring and shell.According to this, form, when bearing bears load, there is resiliently deformable in outer ring, the pressure of contact surface of outer ring and roller surface is uniformly distributed, so can suppress uneven distribution.
Technical paper formerly
Patent documentation
Patent documentation 1: TOHKEMY 2000-246410 communique
Patent documentation 2: TOHKEMY 2003-073682 communique
Patent documentation 1: TOHKEMY 2003-343554 communique
Model utility content
The problem that model utility will solve
Yet, in the technology of above-mentioned patent documentation 1, used a large amount of alloying elements, and then need to carry out carbonitriding, so likely cause the manufacture cost of bearing ring to increase.
In addition,, in the technology of patent documentation 2, when causing a large amount of water to immerse bearing inside due to surrounding environment, likely make effect very limited.
In addition, in the technology of patent documentation 3, likely occur that the contact length of embedding part shortens, occur that outer ring is with respect to phenomenons such as toppling over of shell, so this countermeasure also belongs to not enough.
The utility model is to propose in view of above-mentioned problem, even if its object is to provide a kind of not roller bearing of the wearing and tearing of rotating ring that also can suppress use under low speed state in the situation that.
Solve the means of problem
Above-mentioned purpose of the present utility model can realize by following proposal.
(1) roller bearing, is characterized in that, it is a kind of full-complement cylinder roller bearing, has: inner ring, and its outer circumferential face is formed with inner ring raceway face; Outer ring, inner circumferential surface is formed with outer ring raceway face; And cylindrical roller, it along the circumferential direction disposes a plurality of, can be between above-mentioned inner ring raceway face and above-mentioned outer ring raceway face Free-rolling, above-mentioned cylindrical roller at least has straight flange portion at axial central part, above-mentioned inner ring raceway face and above-mentioned outer ring raceway face are all single circular arc convex.
(2) roller bearing according to (1), is characterized in that, when establishing the maximum diameter of above-mentioned cylindrical roller, is the axial dimension of Dw, above-mentioned cylindrical roller while being L, meets relation 1.6≤L/Dw≤3.0.
(3) according to the roller bearing (1) or (2) described, it is characterized in that,
When establishing the maximum diameter of above-mentioned cylindrical roller, be the radial dimension of the section of Dw, above-mentioned roller bearing while being H, meet relation 0.55≤Dw/H≤0.65.
(4) according to the roller bearing described in any one in (1)～(3), it is characterized in that, above-mentioned cylindrical roller has the lug boss that is formed at the above-mentioned straight flange portion of axial central part and is formed at the axial both sides of above-mentioned straight flange portion,
When establish the maximum diameter of above-mentioned cylindrical roller be Dw, above-mentioned lug boss from above-mentioned straight flange portion when the drop amount of above-mentioned cylindrical roller axial end portion is C, meet relation 0.0003≤C/Dw≤0.0050.
(5) according to the roller bearing described in any one in (1)～(4), it is characterized in that, when establish the maximum diameter of above-mentioned cylindrical roller be Dw, above-mentioned outer ring raceway face from its axial end portion when the drop amount of the axial central part of above-mentioned outer ring raceway face is A, meet relation 0.0015≤A/Dw≤0.0310.
(6) according to the roller bearing described in any one in (1)～(5), it is characterized in that, when establish the maximum diameter of above-mentioned cylindrical roller be Dw, above-mentioned inner ring raceway face from its axial end portion when the drop amount of the axial central part of above-mentioned inner ring raceway face is B, meet relation 0.0020≤B/Dw≤0.0550.
(7) according to the roller bearing described in any one in (1)～(6), it is characterized in that, when the axial end portion of establishing from above-mentioned outer ring raceway face is A towards the drop amount of the axial central part of above-mentioned outer ring raceway face, from the axial end portion of above-mentioned inner ring raceway face when the drop amount of the axial central part of above-mentioned inner ring raceway face is B, A < B.
(8) according to the roller bearing described in any one in (1)～(7), it is characterized in that, the surface roughness of above-mentioned cylindrical roller is less than the surface roughness of above-mentioned inner ring raceway face and above-mentioned outer ring raceway face.
(9) according to the roller bearing described in any one in (1)～(3), it is characterized in that, above-mentioned cylindrical roller has above-mentioned straight flange portion on axially whole.
The effect of model utility
According to the utility model, even if a kind of not roller bearing of the wearing and tearing of rotating ring that also can suppress use under the slow-speed of revolution in the situation that is provided.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of the roller bearing of a mode of execution of the present utility model.
Fig. 2 (a) is the partial enlarged drawing of outer ring of the roller bearing of Fig. 1, and Fig. 2 (b) is the partial enlarged drawing of inner ring of the roller bearing of Fig. 1.
Fig. 3 is the curve synoptic diagram of the maximized surface pressure of roller and the relation of roller slenderness ratio.
Fig. 4 is the curve synoptic diagram of the relation of the maximized surface pressure of roller and the ratio of roller maximum diameter and section height.
Fig. 5 is the curve synoptic diagram of relation of the ratio of the maximized surface pressure of roller and the drop amount A of outer ring raceway face and roller maximum diameter.
Fig. 6 is the curve synoptic diagram of relation of the ratio of the maximized surface pressure of roller and the drop amount B of inner ring raceway face and roller maximum diameter.
Fig. 7 is the partial enlarged drawing of the shape of the roller that uses of the roller bearing for explanatory drawing 1.
Fig. 8 is the maximized surface pressure of roller and the curve synoptic diagram of the relation of the ratio of protruding drop amount C and roller maximum diameter.
Fig. 9 is the schematic diagram of the self-aligning roller bearing of comparative example.
Figure 10 is the curve synoptic diagram of outer ring wear extent of embodiment's roller bearing.
Figure 11 is the curve synoptic diagram of outer ring wear extent of the self-aligning roller bearing of comparative example.
Symbol description
10 roller bearings
20 inner rings
22 inner ring raceway faces
30 outer rings
32 outer ring raceway faces
40 rollers
Embodiment
With Fig. 1～Fig. 8, the roller bearing of a mode of execution of the present utility model is described below.
As shown in Figure 1, the roller bearing 10 of present embodiment is a kind of full dress rolling bearing without retainer, has: inner ring 20, and its outer circumferential face is formed with inner ring raceway face 22; Outer ring 30, its axial two ends are formed with flange 34,34, and inner circumferential surface is formed with outer ring raceway face 32; With roller 40, it along the circumferential direction disposes a plurality of, can be between inner ring raceway face 22 and outer ring raceway face 32 Free-rolling.The rolling surface of roller 40 has and forms the straight flange portion 42 of cylindrical shape and form protruding curved lug boss 44 from the axial end of the axial two side direction rollers 40 of straight flange portion.By this lug boss 44, make roller bearing 10 there is aligning.The material of roller bearing 10 is so long as hardenable steel, such as can be by making such as Bearing Steel, steel for carburizing.The lubricating grease that roller bearing 10 passes through to fill prearranging quatity is and lubricated, and the inside of roller bearing 10 becomes confined space by Sealing 50,50, is therefore that lubricating grease is difficult for the structure of being discharged to outside.
According to the roller bearing 10 of present embodiment, supporting the neck 3 for the deflector roll 1 of the continuous casting equipment of shaping slab or steel billet, this neck 3 can be rotated freely with respect to shell 5.When slab passes through deflector roll 1, roller bearing 10 is bearing sizable load, but in the present embodiment, because roller bearing 10 is for completely filling mode, thereby load capacity increase, so can suppress the reduction in the life-span of roller bearing 10.
Yet, although roller bearing has advantages of that differential sliding is less conventionally, but, there is the inclination with respect to bearing ring in the inclination once the deflection because of deflector roll 1 or shell 5, the surface pressure of the end of roller and contacting part bearing ring (particularly as not the outer ring of rotating ring) just likely becomes excessive.But the utility model designer finds, the various sizes by suitable regulation roller bearing and shape etc., can suppress the excessive of surface pressure, can significantly reduce wear.
In addition, conventionally, when the rotation of roller bearing, the sense of rotation of roller bearing and the sense of rotation of roller are likely inconsistent, and the running shaft that likely occurs roller is toppled over and the situation of deflection occurred towards circumferencial direction.Particularly, the in the situation that of full-complement cylinder roller bearing, between roller, easily come in contact, therefore deflection problem can occur.Roller 40 has straight flange portion 42 at axial central part in the present embodiment.By such roller with straight flange portion 42 40, compare with the whole roller axially with convex shape, can suppress the generation of deflection, can improve the precision of the surface roughness of rolling surface (straight flange portion 42).
At this, in the present embodiment, when establishing the maximum diameter (diameter of straight flange portion 42 of roller 40.Hereinafter referred to as roller diameter) be the axial dimension (hereinafter referred to as roller length) of Dw, roller 40 when the L, by the slenderness ratio (L/Dw) of regulation roller, suppress the surface pressure of the end of roller 40 and contacting part bearing ring.The slenderness ratio of roller (L/Dw) is shown in Fig. 3 with the relation of the maximized surface pressure of roller 40 and contacting part bearing ring.As shown in Figure 3, when roller slenderness ratio (L/Dw) becomes large, roller 40 becomes large with the area of contact of bearing ring, the expanded range of bearing pressure, so the surface pressure of the end of roller 40 diminishes.The effect that surface pressure reduces is roughly saturated when L/Dw=1.6.In addition, when L/Dw > 3.0, the difficulty of processing of roller 40 increases, and then the thickness of flange is not enough, is difficult to guarantee the intensity of flange.Therefore, in the utility model, by roller slenderness ratio (L/Dw) regulation, be, 1.6≤L/Dw≤3.0.Roller slenderness ratio (L/Dw) is 2.0≤L/Dw≤2.8 more preferably.
In addition, in the present embodiment, when the section height of roller bearing 10 (radial dimension) is H, the ratio (Dw/H) by regulation roller diameter Dw with section height H, can further suppress the surface pressure with the end of the roller 40 of the contacting part of bearing ring.Roller diameter Dw is shown in Fig. 4 with the relation of the ratio (Dw/H) of section height H and the maximized surface pressure of roller 40.As shown in Figure 4, along with the increase of roller diameter Dw, the surface pressure of roller 40 reduces, and therefore can reduce the pressure of contact surface of roller 40 and bearing ring.The effect that surface pressure reduces is o'clock more effective in Dw/H >=0.55.In addition,, during Dw/H > 0.65, the wall thickness of bearing ring is excessively thin, processing difficulties.Therefore, roller diameter Dw and section height H are preferably and meet 0.55≤Dw/H≤0.65.
And then in the present embodiment, the inner ring raceway face 22 of inner ring 20 and the outer ring raceway face 32 of outer ring 30 are all and have single circular arc convex.According to this structure, lug boss is set, when axially central part arranges par, compares with the axial end portion at inner ring raceway face 22 and outer ring raceway face 32, can suppress the sharply rising of the surface pressure of roller 40 ends.
As shown in Figure 2 (a) shows, in the present embodiment, drop amount (the difference of height of the axial central part of outer ring raceway face 32 and the axial end portion of outer ring raceway face 32 of (that is, the joint of withdrawing portion 33 and outer ring raceway face 32) from the axial central part of outer ring raceway face 32 to axial end portion.Below, also referred to as outer ring drop amount) with A, represent.And the ratio (A/Dw) of regulation roller diameter Dw and outer ring drop amount A.Roller diameter Dw is shown in Fig. 5 with the relation of the ratio (A/Dw) of outer ring drop amount A and the maximized surface pressure of roller 40.As shown in Figure 5, along with the increase of A/Dw, that is, along with the increase of outer ring drop amount A, the maximized surface pressure of roller 40 reduces.The effect that surface pressure reduces is to meet A/Dw >=0.0015 o'clock more effective.But, although along with the increase of outer ring drop amount A no longer produces edge loading, can make on the contrary the surface pressure of the axial central part of outer ring raceway face 32 increase, and make the processing (grinding, superfinish) of the axial end portion of outer ring raceway face 32 become difficult.Therefore, be made as A/Dw≤0.0310.More preferably be made as 0.0020≤A/Dw≤0.0150.The surface pressure that just can further suppress thus the end of the roller 40 in the contacting part with outer ring 30.
In addition, as shown in Fig. 2 (b), in the present embodiment, drop amount (the axial central part of inner ring raceway face 22 and the difference of height of axial end portion from the axial central part of inner ring raceway face 22 to axial end portion.Below, also referred to as inner ring drop amount) with B, represent.And, by roller diameter Dw, be 0.0020≤B/Dw≤0.0550 with ratio (B/Dw) regulation of inner ring drop amount B.Roller diameter Dw is shown in Fig. 6 with the relation of the ratio (B/Dw) of inner ring drop amount B and the maximized surface pressure of roller 40.As shown in Figure 6, along with the increase of B/Dw, that is, along with the increase of inner ring drop amount B, the maximized surface pressure of roller 40 reduces.The effect that surface pressure reduces is to meet B/Dw >=0.0020 o'clock more effective.But although along with the increase of inner ring drop amount B no longer produces edge loading, different from the outer ring 30 that is always subject to edge loading effect, the in the situation that of inner ring 20, the roller 40 that produces edge loading is limited, affects less.In addition,, along with the increase of inner ring drop amount B, also there is the problem of roller 40 easy deflections.In addition, along with the increase of inner ring drop amount B, the surface pressure of the axial central part of inner ring raceway face 22 increases, and makes the processing (grinding, superfinish) of the axial end portion of inner ring raceway face 22 become difficult.Therefore, be made as B/Dw≤0.0550.More preferably be made as 0.0030≤B/Dw≤0.0260.The surface pressure that just can further suppress thus the end of the roller 40 in the contacting part with inner ring 20.
In addition, in the present embodiment, outer ring drop amount A and inner ring drop amount B meet A < B.In continuous casting equipment, when the slab of excessive temperature passes through, there is thermal expansion in deflector roll 1, and therefore, the roller bearing 10 being arranged on axle box needs to use the inner ring 20 of not establishing flange that the elongation of deflector roll 1 is discharged towards axial outside.Because in outer ring, 30 axial two end part are formed with flange 34,34, therefore, even when inner ring 20 is moved vertically, the relative position relation of outer ring 30 and roller 40 does not change yet.But, because inner ring 20 and the relative position relation of roller 40 change, so, follow this variation, the distribution of surface pressure is also moved vertically.If the R of the convex shape of inner ring 20 is larger, the area of contact of roller 40 and inner ring raceway face 22 becomes large, so, after inner ring 20 is mobile vertically, inner ring 20 will depart from the rolling surface of roller 40 with the surface of contact of roller 40, thereby likely produces edge loading.In the present embodiment, by setting A < B, can make the area of contact of roller 40 and inner ring raceway face 22 narrow down, therefore, even in the situation that deflector roll 1 extends, inner ring 20 has been moved vertically, the pressure that also can reduce the contact surface of roller 40 and inner ring raceway face 22, can suppress the generation of edge loading.
In addition, in the present embodiment, as shown in Figure 7, in roller 40, from being formed at the straight flange portion 42 of axial central part to the drop amount (protruding drop amount) of axial end portion, be made as C.And, by roller diameter Dw, be 0.0003≤C/Dw≤0.0050 with ratio (C/Dw) regulation of protruding drop amount C.Roller diameter Dw is shown in Fig. 8 with the ratio of roller projection drop amount C and the relation of roller maximized surface pressure.As shown in Figure 8, along with the increase of C/Dw, that is, along with the increase of the protruding drop amount C of roller 40, the maximized surface pressure of roller 40 reduces.The effect that surface pressure reduces is o'clock more effective in satisfied 0.0005≤C/Dw≤0.0030.But, although along with the increase of protruding drop amount C no longer produces edge loading, can make on the contrary the surface pressure of the axial central part of inner ring raceway face 22 and outer ring raceway face 32 increase.In addition,, when protruding drop amount C is larger, it is difficult that the processing of lug boss 4 (grinding, superfinish) becomes, and therefore, is preferably C/Dw≤0.0050.
In addition, in the present embodiment, the surface roughness of the rolling surface of roller 40 is less than the surface roughness of inner ring raceway face 22 and outer ring raceway face 32.As mentioned above, because continuous casting equipment is with utmost point slow-speed of revolution running, between parts, be difficult for forming oil film.Particularly in the situation that full-complement cylinder roller bearing 10 is as in the embodiment described in compared the more difficult formation oil film of roller 40 contacting part each other between the roller 40 contacting with rolling and bearing ring.Now, because the surface roughness of the rolling surface of roller 40 is less, roller 40 contacting part each other more easily forms oil film, therefore can prevent the damage of roller 40.On the other hand, even if reduce the surface roughness of outer ring raceway face 32 and inner ring raceway face 22, but there is this fact of Metal Contact, can not change.Therefore,, even if increase a little the surface roughness of outer ring raceway face 32 and inner ring raceway face 22, can not produce a very large impact the life-span yet.Therefore, in the present embodiment, by making the surface roughness of the rolling surface of roller 40 be less than the surface roughness of inner ring raceway face 22 and outer ring raceway face 32, can reduce the damage of the roller 40 causing due to roller 40 contact each other, the life-span that can improve roller bearing 10.
Like this, according to the roller bearing 10 of present embodiment, make roller maximum dimension D w, roller length L, the section height H of roller bearing 10, outer ring drop amount A, inner ring drop amount B, and protruding drop amount C meets following relation: 1.6≤L/Dw≤3.0, 0.55≤Dw/H≤0.65, 0.0015≤A/Dw≤0.0310, 0.0020≤B/Dw≤0.0550, A < B, and 0.0003≤C/Dw≤0.0050, and the surface roughness that makes the rolling surface of roller 40 is less than the surface roughness of inner ring raceway face 22 and outer ring raceway face 32, can obtain excellent in abrasion resistance thus, the roller bearing that life-span is improved.
In addition, the utility model is not limited to above-mentioned mode of execution, can carry out suitable change and improvement etc.The roller bearing of above-mentioned mode of execution is the deflector roll bearing using in continuous casting process, and outer ring is rotating ring not, and inner ring is driving ring, but also can adopt inner ring, is the structure that rotating ring, outer ring are not driving ring.In addition, roller 40 can be also straight flange portion integrally formed cylindrical roller vertically.According to such roller, not only can further suppress the generation of deflection, and can further improve the precision of the surface roughness of roller surface.In addition,, according to the difference of purposes, cylindrical roller 40 also can be set to biserial or more than three row, also retainer can be set.In addition, in the above-described embodiment, in outer ring, 30 axial two ends are formed with flange 34,34, but according to the difference of specification purposes or condition, also can only in axial one end of outer ring, form flange.
In addition, for prevent to deflector roll install, the skew of roller during dismounting bearing, also can on outer ring 30 or inner ring 20, arrange and stop inclined to one side parts.In addition, the convex shape of outer ring 30 and inner ring 20, in increasing as far as possible the scope of outer ring drop amount A and inner ring drop amount B, according to the difference of use, can be also convex shape or the logarithm convex shape with a plurality of circular shapes, the convex shape with straight flange shape.
Embodiment
In order to confirm effect of the present utility model, use according to the embodiment of roller bearing of the present utility model with according to the comparative example of self-aligning roller bearing in the past and test.
As embodiment, used the roller bearing 10 of full dress roller type as shown in Figure 1.The condition of embodiment's roller bearing 10 is as follows.
< embodiment >
Outer ring outside dimension: Φ 210mm
Inner ring internal diameter size: Φ 140mm
Assembling width dimensions: 69mm
Roller diameter Dw: Φ 21mm(Dw/H=0.6)
Roller length L:44mm(L/Dw=2.10)
Outer ring drop amount A:0.063mm(A/Dw=0.0030)
Inner ring drop amount B:0.084mm(B/Dw=0.0040)
Projection drop amount C:0.015(C/Dw=0.0007)
Material: bearing ring, roller are SUJ2
Surface hardness: HRC60～64
Arithmetic average roughness: Internal and external cycle roller surface 0.16Ra, roller rolling surface 0.10Ra
Dynamic load rating: 525kN(is identical with the self-aligning roller bearing 100 of comparative example)
In addition, as a comparative example, used the self-aligning roller bearing 100 shown in Fig. 9.The condition of the self-aligning roller bearing 100 of comparative example is as follows.
< comparative example >
Nominal numbering: 24028CE4
Outer ring outside dimension: Φ 210mm
Inner ring internal diameter size: Φ 140mm
Assembling width dimensions: 69mm
Material: bearing ring, roller are SUJ2
Surface hardness: HRC60～64
Arithmetic average roughness: Internal and external cycle roller surface 0.16Ra, roller rolling surface 0.10Ra(is identical with embodiment's roller bearing 10)
Dynamic load rating: 525kN
Wherein, the material of embodiment's roller bearing 10 and the self-aligning roller bearing 100 of comparative example, is to make with identical melting feeding quantity, identical material shape.Materials'use with electric furnace melt, after double refining, with continuous casting equipment cast and rolling and material.In addition, the amount of leaving a blank (clearance) adopting in the bearing case of testing installation and axle and actual rolling mill matches, and outer ring, inner ring all adopt Spielpassung.In addition, the rolling surface of the roller of embodiment's roller bearing 10 and the self-aligning roller bearing 100 of comparative example and roller surface be all by superfinish, makes the rolling surface of Internal and external cycle roller surface and roller have respectively the surface roughness of 0.16Ra, 0.10Ra.
The test conditions of embodiment's roller bearing 10 and the self-aligning roller bearing 100 of comparative example is as follows.
[test conditions]
Load: Fr=210kN(P/Cr=0.40)
Rotating speed: 10rpm
Lubricated: lubricating grease Emalube L(TM trade mark) (Japanese Xietong Grease Co., Ltd)
Lubricated amount: 30% of bearing space volume
Test period: 720h
Water injection rate to bearing inside: 15cc/day
Axle tilt angle: 15 ' (=0.25 °)
Elongate axis amount: 10mm
Before test, to the conduct of embodiment and comparative example not the surface configuration of the outer ring of rotating ring all measure in advance.After test period finishes, disassemble bearing, remeasure the surface configuration of outer ring, the wear extent after validation test.Result is shown in Figure 10 and Figure 11.
The outer ring 30 of the roller bearing 10 of the embodiment shown in Figure 10 is compared with the self-aligning roller bearing 100 of the comparative example shown in Figure 11, and the wear extent within the scope of whole roller contact length is reduced to 1/10 left and right.Therefore can confirm: roller bearing of the present utility model has been realized as the repressed effect of wearing and tearing of the outer ring of rotating ring not.
Claims (9)
1. a roller bearing, is characterized in that, described roller bearing is full-complement cylinder roller bearing, has:
Inner ring, the outer circumferential face of described inner ring is formed with inner ring raceway face;
Outer ring, the inner peripheral surface of described outer ring is formed with outer ring raceway face; With
Cylindrical roller, described cylindrical roller along the circumferential direction disposes a plurality of, can be between described inner ring raceway face and described outer ring raceway face Free-rolling,
Described cylindrical roller at least has straight flange portion at axial central part,
Described inner ring raceway face and described outer ring raceway face are all single circular arc convex.
2. roller bearing according to claim 1, is characterized in that,
When establishing the maximum diameter of described cylindrical roller, be the axial dimension of Dw, described cylindrical roller while being L, described roller bearing meets relation 1.6≤L/Dw≤3.0.
3. roller bearing according to claim 1 and 2, is characterized in that,
When establishing the maximum diameter of described cylindrical roller, be the radial dimension of the section of Dw, described roller bearing while being H, described roller bearing meets relation 0.55≤Dw/H≤0.65.
4. roller bearing according to claim 1 and 2, is characterized in that,
Described cylindrical roller has the lug boss that is formed at the described straight flange portion of axial central part and is formed at the axial both sides of described straight flange portion,
When establish the maximum diameter of described cylindrical roller be Dw, described lug boss from described straight flange portion when the drop amount of the axial end portion of described cylindrical roller is C, described roller bearing meets relation 0.0003≤C/Dw≤0.0050.
5. roller bearing according to claim 1 and 2, is characterized in that,
When establish the maximum diameter of described cylindrical roller be the axial end portion from described outer ring raceway face of Dw, described outer ring raceway face when the drop amount of the axial central part of described outer ring raceway face is A, described roller bearing meets 0.0015≤A/Dw≤0.0310.
6. roller bearing according to claim 1 and 2, is characterized in that,
When establish the maximum diameter of described cylindrical roller be the axial end portion from described inner ring raceway face of Dw, described inner ring raceway face when the drop amount of the axial central part of described inner ring raceway face is B, described roller bearing meets 0.0020≤B/Dw≤0.0550.
7. roller bearing according to claim 1 and 2, is characterized in that,
When establish from the axial end portion of described outer ring raceway face towards the drop amount of the axial central part of described outer ring raceway face, be A, from the axial end portion of described inner ring raceway face when the drop amount of the axial central part of described inner ring raceway face is B, A<B.
8. roller bearing according to claim 1 and 2, is characterized in that,
The surface roughness of described cylindrical roller is less than the surface roughness of described inner ring raceway face and the surface roughness of described outer ring raceway face.
9. roller bearing according to claim 1 and 2, is characterized in that,
Described cylindrical roller has described straight flange portion on axially whole.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013-017575 | 2013-01-31 | ||
| JP2013017575 | 2013-01-31 | ||
| JP2013-096392 | 2013-05-01 | ||
| JP2013096392 | 2013-05-01 |
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| CN203516458U true CN203516458U (en) | 2014-04-02 |
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| CN201320342542.8U Expired - Fee Related CN203516458U (en) | 2013-01-31 | 2013-06-14 | Cylindrical roller bearing |
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| CN (1) | CN203516458U (en) |
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| CN110494664A (en) * | 2017-04-12 | 2019-11-22 | 日本精工株式会社 | Tapered roller bearing |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6472671B2 (en) * | 2015-01-28 | 2019-02-20 | Ntn株式会社 | Tapered roller bearing |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5874623U (en) * | 1981-11-13 | 1983-05-20 | トヨタ自動車株式会社 | roller bearing |
| JPH0198712A (en) * | 1987-10-07 | 1989-04-17 | Koyo Seiko Co Ltd | Cylindrical roller bearing |
| JPH07293557A (en) * | 1994-04-27 | 1995-11-07 | Nippon Seiko Kk | Rotation support device for planetary gear |
| JP2002235753A (en) * | 2001-02-09 | 2002-08-23 | Ntn Corp | Shell-type roller bearing |
| JP2003042148A (en) * | 2001-07-27 | 2003-02-13 | Nsk Ltd | Rolling bearing |
| JP4718781B2 (en) * | 2003-02-28 | 2011-07-06 | Ｎｔｎ株式会社 | Transmission components and tapered roller bearings |
| WO2004092603A1 (en) * | 2003-04-16 | 2004-10-28 | Nsk Ltd. | Roller bearing for belt-type stepless speed changer |
| JP2005106107A (en) * | 2003-09-29 | 2005-04-21 | Koyo Seiko Co Ltd | Roller bearing |
| JP4364610B2 (en) * | 2003-11-25 | 2009-11-18 | Ｎｔｎ株式会社 | Roller bearing |
| JP2006226357A (en) * | 2005-02-16 | 2006-08-31 | Ntn Corp | Roller bearing |
| JP2007107554A (en) * | 2005-10-11 | 2007-04-26 | Ntn Corp | Rolling bearing |
| JP2010196861A (en) * | 2009-02-27 | 2010-09-09 | Nsk Ltd | Roll bearing |
| JP2013002567A (en) * | 2011-06-17 | 2013-01-07 | Ntn Corp | Cylindrical roller bearing |
-
2013
- 2013-06-14 CN CN201320342542.8U patent/CN203516458U/en not_active Expired - Fee Related
- 2013-09-27 JP JP2013201709A patent/JP2014231902A/en active Pending
-
2017
- 2017-11-06 JP JP2017214133A patent/JP6512264B2/en active Active
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109153061A (en) * | 2016-05-23 | 2019-01-04 | Ntn株式会社 | The manufacturing method of bearing washer |
| CN110114586A (en) * | 2016-12-26 | 2019-08-09 | Ntn株式会社 | Thrust roller bearing and thrust roller bearing rail ring |
| CN110494664A (en) * | 2017-04-12 | 2019-11-22 | 日本精工株式会社 | Tapered roller bearing |
| CN110017325A (en) * | 2017-12-20 | 2019-07-16 | 斯凯孚公司 | Particularly for the mixing roller bearing of coolant compressor |
| CN110017325B (en) * | 2017-12-20 | 2023-01-10 | 斯凯孚公司 | Hybrid roller bearing, in particular for a refrigerant compressor |
| CN110319114A (en) * | 2018-03-30 | 2019-10-11 | 比亚迪股份有限公司 | Oscillation bearing and wearable device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2014231902A (en) | 2014-12-11 |
| JP6512264B2 (en) | 2019-05-15 |
| JP2018021678A (en) | 2018-02-08 |
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