CN102239339B - Rolling bearing having optimized outer race - Google Patents
Rolling bearing having optimized outer race Download PDFInfo
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- CN102239339B CN102239339B CN200980148844.8A CN200980148844A CN102239339B CN 102239339 B CN102239339 B CN 102239339B CN 200980148844 A CN200980148844 A CN 200980148844A CN 102239339 B CN102239339 B CN 102239339B
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- inner ring
- rolling element
- groove
- element raceway
- axial
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- 238000005096 rolling process Methods 0.000 title claims abstract description 150
- 241000397426 Centroberyx lineatus Species 0.000 claims description 3
- 241000222712 Kinetoplastida Species 0.000 claims description 2
- 238000009434 installation Methods 0.000 abstract 1
- 241001131688 Coracias garrulus Species 0.000 description 24
- 239000000463 material Substances 0.000 description 4
- 230000008602 contraction Effects 0.000 description 3
- 238000001816 cooling Methods 0.000 description 3
- 230000002349 favourable effect Effects 0.000 description 3
- 239000008041 oiling agent Substances 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000019771 cognition Effects 0.000 description 2
- 238000005520 cutting process Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000007665 sagging Methods 0.000 description 2
- 238000004904 shortening Methods 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 208000034189 Sclerosis Diseases 0.000 description 1
- 230000000994 depressogenic effect Effects 0.000 description 1
- 230000002045 lasting effect Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000002791 soaking Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
- F16C19/26—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with a single row of rollers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/583—Details of specific parts of races
- F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/583—Details of specific parts of races
- F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
- F16C2240/50—Crowning, e.g. crowning height or crowning radius
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
- Support Of The Bearing (AREA)
Abstract
The invention relates to a rolling bearing (1), comprising rolling elements (4) and an outer race (2), wherein an outer shell (12a, 12b) of the outer race (2) comprises two circumferential grooves (10, 11) axially spaced at least by the amount of the axial extent of the rolling elements (4), and wherein a first part of the outer shell (12b) axially between the two grooves (10, 11) is radially retracted relative to a second part of the outer shell (12b) axially outside of the grooves (10, 11), and wherein the outer race comprises a substantially constant thickness in the area of the first part of the outer shell (12a). In order to provide a simple rolling bearing that is inexpensive to produce and fits in a standard installation space, the invention proposes that the ratio for each groove between a radial wall thickness (B) of said groove and an axial wall thickness (A) of said groove is in the range from 0.5 to 1.5, wherein the radial wall thickness (B) corresponds to the smallest radial wall thickness of the outer race, and wherein the axial wall thickness (A) corresponds to the smallest axial distance of the groove from an adjacent end face (14, 15) of the outer race.
Description
Technical field
The present invention relates to a kind of rolling bearing, this rolling bearing comprises rolling element and outer ring, wherein, the shell surface of outer ring has two annular grooves, these grooves are at least spaced apart with the axially extended amount of rolling element in the axial direction, and wherein, shell surface in the axial direction the first portion's opposite shell face between two grooves in the axial direction the second portion outside groove bounce back diametrically, and wherein, outer ring has the thickness of substantial constant in the region of the first portion of shell surface.This rolling bearing is for example adapted for the floating bearing that is used as main shaft supporting in lathe.
Background technique
The main shaft of quick rotation like this or motor driving or external drive supports by rigid bearing and floating bearing.At this, the anti-relative torsion of main shaft ground is connected with the inner ring of rigid bearing or floating bearing, and anti-relative torsion ground, the outer ring of this bearing is connected with housing.
Typically, angular contact ball bearing is used as rigid bearing and roller bearing is used as floating bearing.At this, roller bearing has following task as floating bearing, that is, when the relatively cooling housing of main shaft that is for example in operation has higher temperature, the different longitudinal tensile strain in the axial direction being determined by heat of compensation main shaft and housing.
Because machining accuracy has been proposed to very high requirement in lathe, so that roller bearing is adjusted into is conventionally zero-lash.In the poor situation of high-temperature between hot main shaft and cooling housing, then roller bearing can be diametrically because the different expansion of bearer ring compresses.
By the known a kind of roller bearing of prior art, this roller bearing does not rely on temperature has realized operation zero-lash and that do not compress.
By the known a kind of roller bearing of DE 965 671, the radial internal clearance of this roller bearing can regulate as follows in installment state, that is, outer ring has depressed part radially in addition.Yet, in the rolling bearing of DE 965 671 disadvantageously, outer ring is when adjusting radial internal clearance and when by rolling element load diametrically, changed the geometrical shape of outer ring in the region of rolling element raceway, and overarch in particular, this is on contacting and have negative impact with rolling between rolling element at rolling element raceway.At rolling element raceway, contact minimizing with the rolling between rolling element, this causes the reduction of bearing value.
By the known a kind of roller bearing of DE 10 2,004 035 387 B4, its outer ring has the groove that is bathtub shape on shell surface, and wherein, two axial end regions of groove are compared the region of the axial centre of groove and deepened more consumingly.For the bearing without radial internal clearance is provided, according to the instruction of DE 10 2,004 035 387 B4, do following suggestion, that is, extending axially of the outer ring forming by this way selects to be greater than extending axially of inner ring.In particular, according to preferred embodiment, extending axially of outer ring should be axially extended 1.5 to 3.5 times or 2 to 3 times of inner ring.The shape of obviously, extending according to this especially essential large axial arrangement of the outer ring of DE 10 2,004 035 387 B1 is disadvantageous in practice.
Summary of the invention
Task of the present invention based on, rolling bearing simply a kind of and that manufacture is at low cost provided, this rolling bearing has little extending axially, and this rolling bearing does not rely on running temperature and realizes operation zero-lash and that do not compress simultaneously.
This task solves by the rolling bearing of the feature according to independent claims.It is as a result of following rolling bearing, this rolling bearing comprises rolling element and outer ring, wherein, the shell surface of outer ring has two annular grooves, these grooves are at least spaced apart with the axially extended amount of rolling element in the axial direction, and wherein, the first portion between two grooves in the axial direction of shell surface bounces back diametrically with respect to the second portion outside groove in the axial direction of shell surface, and wherein, outer ring has the thickness of substantial constant in the region of the first portion of shell surface, it is characterized in that, ratio for each groove between the radial thickness of groove and the axial wall thickness of groove is in 0.5 to 1.5 scope, wherein, smallest radial wall thickness in groove conforms to described radial thickness with outer ring, and wherein, described axial wall thickness conforms to the minimum axial direction spacing of the adjacent face of the relative outer ring of groove.
Radially pliable and tough outer ring has been realized in the radially region of retraction being in the axial direction between two grooves by groove and cylinder blanket face.In particular, can be by the outwards pushing diametrically of the region of the first portion of shell surface.The mode that the region of the first portion by shell surface has constant thickness is guaranteed as follows,, while moving radially in this region, does not carry out the variation of the geometrical shape in this region that is.Thus, the rolling element raceway being inverted mutually diametrically with the first portion of shell surface has desired shape in addition.Thus, have resilient pliable and tough outer ring in other words diametrically, thereby the rolling element raceway of outer ring can be sunk diametrically in definite load according to rolling bearing of the present invention, wherein, yet rolling element raceway does not lose its original shape at this.
The present invention is based on following cognition, that is, the radial thickness by the groove to axial specific ratio of wall thickness realizes for below former thereby rolling bearing that relative prior art is favourable.
Applicable as follows in principle, that is, the outer ring of the type is implemented widelyr in the axial direction, and the radially ductility of this outer ring can be larger.Therefore, DE 10 2,004 035 387 B4 intend to design as far as possible axially wider outer ring.Yet, the present invention is based on following thought, that is, provide a kind of rolling bearing, this rolling bearing has the optimum state about radially ductility and the needed axial arrangement space of outer ring.For this reason, groove designs as follows,, first realizes the little axial arrangement space of outer ring that is.Compare the solution of DE 10 2,004 035 387 B4, axially wall thickness is reduced with respect to radial thickness.In the situation of given radial thickness, in order to arrive definite radially suppleness, axial wall thickness (on that is to say axially, be in the region outside groove, that is, the second portion of shell surface) less according to the present invention.Thus, needed axial arrangement space is less.For example make thus to become as follows possibility, that is, conventional standard outer ring is provided with according to groove of the present invention and therebetween radial contraction.Secondly, yet provide in addition sufficient radial flexibility, so that for example use in the main shaft bearing of pre-pressing, to compensate the different radial expansions of main shaft and housing at this place.
Radial thickness to axial wall thickness according to ratio of the present invention, cause equally the advantage in the manufacture of outer ring, this outer ring can for example, consist of the conventional material for this outer ring (roller bearing steel) in addition.Because this wall thickness ratio is in the scope of value 1 left and right, so for example compare by the DE 10 2,004 035 387 known outer rings of B4, this outer ring can be more simply and sclerosis more reliably, because the corresponding wall of groove is about the same cooling soon.
According to a kind of mode of execution, for each groove, the radial thickness to axial ratio of wall thickness is in 0.6 to 1.3 scope, preferably in 0.7 to 1.2 scope, further preferably in 0.9 to 1.1 scope.
According to a kind of mode of execution, the extending axially in axially extended 10% to 20% the scope that is in outer ring of each groove, preferably in axially extended 12.5% to 17.5% the scope of outer ring.
According to a kind of mode of execution, extending axially with axially extended 45% to 55% of outer ring of the first portion of shell surface conforms to.
According to a kind of mode of execution, groove is spaced apart with the axially extended amount of rolling element.Accordingly, realized special joint space-efficient solution.If the first portion of the diametrically opposed shell surface of rolling element raceway is positioned on the shell face of inside of outer ring, guarantee in addition as follows, that is, although rolling element raceway has radially ductility, remain its geometrical shape.
According to another kind of mode of execution, on the rolling element raceway that rolling element is inverted diametrically mutually in the first portion with shell surface, roll.Thus, rolling element raceway is in the region by two recess defining in the axial direction.At this, rolling element raceway is distributed on the internal valve of outer ring.
According to another kind of mode of execution, one or two groove have take the shape of the letter U, V-shaped, rectangle or be the cross-sectional profiles of swallow-tail form.Self-evidently, other shape or combination are thus feasible equally.At this, the cross-sectional profiles of groove is preferably about the spin axis Rotational Symmetry of outer ring.
According to another kind of mode of execution, the cross-sectional profiles of two grooves or axially extended value equate.Because outer ring is symmetrical about the plane mirror picture perpendicular to outer ring spin axis.
According to another kind of mode of execution, the diameter of the first portion of shell surface is in 98% to 99.99% the scope of diameter of second portion of shell surface, preferably in 99.9% to 99.95% scope.
According to another kind of mode of execution, one or two groove has 1% to 5% the degree of depth of diameter of the second portion of shell surface, preferably has 2% to 4% the degree of depth.
According to another kind of mode of execution, rolling bearing comprises that it extends axially the inner ring substantially conforming to extending axially of outer ring.Preferably, this inner ring is standard inner ring, and it adapts to normal structure space.Extending axially preferably of rolling bearing conforms to axially extended 45% to 55% of rolling bearing or inner ring or outer ring.
According to another kind of mode of execution, rolling bearing comprises the inner ring with at least one edge.Preferably, this inner ring has two for the edge of axial lead rolling element.Because outer ring does not have edge, so this rolling bearing is floating bearing.Preferably, according to rolling bearing of the present invention, compressed in advance.
According to another kind of mode of execution, this rolling bearing comprises the inner ring with cone shape hole, and can be open on the corresponding shaft shoulder thus.
According to another kind of mode of execution, this rolling bearing has the inner ring that comprises inner ring rolling element raceway, this inner ring rolling element raceway is between two edges with each inner ring for the surface of contact of contact roller kinetoplast end face in the axial direction about inner ring spin axis, wherein, this inner ring has the grooving circularizing about inner ring spin axis between at least one edge and inner ring rolling element raceway, and wherein, the width that is located at two parts in the region between surface of contact of at least one grooving conforms to the 15%-30% of the spacing of two surface of contact.Thus, this grooving extends through the 15%-30% of the distance between two surface of contact in two surface of contact.The width of grooving and the spacing of surface of contact are parallel to raceway and measure in the cross section that comprises inner ring spin axis.In such cross section, two surface of contact are parallel to each other all the time.Thus, in the inner ring of roller bearing, the width of grooving conforms to extending axially of grooving.In addition, this inner ring can consist of the conventional material of the inner ring for the type, for example, roller bearing steel, consist of.
At this, this mode of execution based on following cognition, that is, by having realized the reduction of the width of inner ring rolling element raceway according to grooving of the present invention, and then has been realized the reduction of the bearing value of the rolling bearing that comprises inner ring.Yet in contrast to current viewpoint, the grooving of so selecting is greatly favourable in definite application, because the advantage forming by this grooving has been offset these shortcomings.
So, by this grooving, formed corresponding larger oiling agent hiding-place.Thus, at inner ring place, adjusted obviously better lubrication circumstances.Especially clearly, by grooving between two surface of contact, through the spacing of two surface of contact 15% to 30% preferably through 20% to 25% according to extension of the present invention, very good lubriation material is carried becomes possibility.In addition, formed oiling agent hiding-place causes as follows that in the location of edge the best of surface of contact at edge is lubricated, that is, lubriation material is delivered to the surface of contact at edge by the end face of rolling element.
In addition, the shortening producing of the inner ring rolling element raceway by inner ring draws the less friction between rolling element and inner ring, and then is in operation and generates less frictional heat.This advantage realizes especially consumingly in particular in the rolling bearing of quick rotation.
In addition, the present invention utilizes as follows, that is, and especially rolling element outwards pushing significantly due to centrifugal force when high rotating speed.Although first this grooving shows as the corresponding shortening of the width of rolling element raceway, it causes the nominal reduction of bearing capacity equally.Yet due to centrifugal force, the contact force between rolling element and inner ring rolling element raceway reduces, thereby make the reduction less generation effectively of bearing capacity.Thus, rotating speed is higher, less by the nominal reduction of the bearing capacity causing according to variation of the present invention of the rolling element raceway at inner ring and the contact geometry shape between rolling element.
According to a kind of preferred implementation of rolling bearing, this rolling bearing comprises the inner ring with grooving, and the width that is located at two parts in the region between surface of contact of at least one grooving conforms to the 20%-25% of the spacing of two surface of contact.
Preferred embodiment a kind of according to rolling bearing, this rolling bearing comprises the inner ring with grooving, this inner ring has the grooving circularizing about the spin axis of inner ring between each edge and inner ring rolling element raceway, wherein, the width that is located at two parts in the region between surface of contact of each grooving conforms to the 15%-30% of the spacing of two surface of contact, preferably conforms to the 20%-25% of the spacing of two surface of contact.
Preferred embodiment a kind of according to rolling bearing, this rolling bearing comprises the inner ring with grooving, described grooving by sinking, the contraction of groove or inner ring rolling element raceway forms.Self-evidently, grooving equally can be otherwise or the combination by mentioned form form.Preferably, this grooving spin axis about inner ring as inner ring rolling element raceway and two surface of contact is symmetrically configured to.Grooving only can be risen by adjacent surface of contact and extend upward in the side of another (that is to say opposed) surface of contact.Thus, the overall width of grooving conforms to the width of the part between surface of contact of grooving.Yet may be considered that equally, grooving extends in addition equally in the opposite direction.Thus, about adjacent surface of contact, form sagging.In principle, the degree of depth of grooving can be selected on arbitrary dimension ground.Even when not increased by the increase of cutting groove depth while soaking face, yet the increase of oiling agent hiding-place is favourable.
Preferred embodiment a kind of according to rolling bearing, this rolling bearing comprises the inner ring with grooving, inner ring rolling element raceway is embodied as and is protruding spherical.Thus, this inner ring has protruding shape in the region of inner ring rolling element raceway.Preferably, inner ring rolling element raceway is configured to be spheroidal, that is to say in comprising the sectional drawing of inner ring spin axis, and inner ring rolling element raceway has constant curvature.The inner ring rolling element raceway of relatively flat, the diameter at two axial end portion places of inner ring rolling element raceway reduces for this reason.Another kind of mode of execution according to rolling bearing, this rolling bearing comprises the inner ring with grooving, inner ring rolling element raceway is punctured into about inner ring rolling element raceway at 0.0025% of the diameter in the middle of axially of inner ring rolling element raceway the axial end portion place of inner ring rolling element raceway, be preferably 0.005% to 0.0125%, more preferably 0.01%.In the inner ring of roller bearing, the diameter of the inner ring rolling element raceway of this inner ring in the middle of is axially 80mm, and the diameter of inner ring rolling element raceway at axial end portion place for example reduces by 8 μ m, 0.01% of 80mm.The advantage of protruding spherical inner ring rolling element raceway is, seamed edge sideslip
appear in service being minimized.
According to another kind of mode of execution, this rolling bearing is roller bearing.It can be for example single-row roller bearing.This roller bearing for example can be used as main shaft supporting part.
Accompanying drawing explanation
Below, embodiments of the invention are described with reference to accompanying drawing, this:
Fig. 1 illustrates the schematic sectional drawing of the first embodiment of the present invention;
Fig. 2 illustrates the schematic sectional drawing of the second embodiment of the present invention;
Fig. 3 illustrates the schematic sectional drawing of inner ring;
Fig. 4 illustrates the schematic sectional drawing of inner ring;
Fig. 5 illustrates the schematic sectional drawing of the third embodiment of the present invention;
Fig. 6 illustrates the schematic sectional drawing of the fourth embodiment of the present invention; And
Fig. 7 illustrates the schematic sectional drawing by means of the main shaft supporting according to rolling bearing of the present invention.
Embodiment
Fig. 1 illustrate according to the first embodiment according to rolling bearing 1 of the present invention.This rolling bearing 1 is roller bearing, and comprises the outer ring 2 with rolling element raceway 3, and rolling element 4 rolls on rolling element raceway 3.In addition, rolling element 4 is in the upper rolling of rolling element raceway 5 (inner ring rolling element raceway 5) of inner ring 6.Inner ring has for guiding in the axial direction the edge 7,8 of rolling element 4.On periphery, rolling element keeps by retainer 9 compartment of terrains.Inner ring has cone shape internal valve 13.
Outer ring has two grooves 10,11, and these two grooves are distributed on periphery on shell surface 12a, the 12b of outer ring 2.This shell surface has the 12a of first portion being in the axial direction between two grooves 10,11, and is presented axially in the second portion 12b outside groove 10,11 towards both sides.The 12a of first portion slightly bounces back diametrically, that is to say that the diameter D1 of shell surface in the 12a of first portion region is less than the diameter D2 of shell surface in second portion 12b region.This outer ring is supported in unshowned housing diametrically by the second portion 12b of shell surface.In contrast, the 12a of first portion of shell surface need not be as being resisted against in housing.
Groove 10,11 has the cross-sectional profiles taking the shape of the letter U.Groove 10,11 is directly connected to respectively the location of the rolling element raceway 3 that rolling element 4 rolls in the axial direction thereon.
Each groove has axial wall thickness A and radial thickness B.Axially wall thickness A correspondingly conforms to the short axial spacing between the adjacent end face 14,15 of groove 10,11 and outer ring.Radial thickness B correspondingly conforms to the minimum radial thickness of outer ring in corresponding groove 10,11.In this embodiment, radial thickness B to axial the ratio of wall thickness A be approximately 0.7.
Fig. 2 illustrate according to the second embodiment according to rolling bearing 1 of the present invention.As relative the first embodiment's basic distinction, outer ring has with two grooves 10,11 that are the cross-sectional profiles of swallow-tail form.In this embodiment, radial thickness B to axial the ratio of wall thickness A be approximately 0.8.
Fig. 3 illustrates for the inner ring 6 using according to rolling bearing of the present invention.In the cutting plane of spin axis 19 that comprises inner ring 6, expressed the sectional drawing of inner ring 6.Can recognize inner ring rolling element raceway 5, this inner ring rolling element raceway is parallel to spin axis 19 and distributes.Two surface of contact 20,21 at two edges 7,8 surround inner ring rolling element raceway 5 in the axial direction.Two surface of contact 20,21 distribute in parallel with each other and perpendicular to rolling element raceway 5 ground and perpendicular to spin axis 19 ground.Relate to the inner ring 6 for roller bearing.
Between edge 7,8 and inner ring rolling element raceway 5, there is respectively grooving 22,23.The width of grooving 22,23 is with ' a ' or ' b ' mark, and the axially extended size in the region of grooving between two surface of contact 20,21 has been described.Two groovings 22,23 only extend in the region between two surface of contact 20,21 in the axial direction in the axial direction.The mark of width ' a ' or ' b ' and two surface of contact 20,21 conforms to about 20% of the spacing of ' c '.Two groovings 22,23 are directly connected to respectively on surface of contact 20,21 in the axial direction.By surface of contact 20,21 to the transition of grooving 22,23 and the transition between grooving 22,23 and inner ring rolling element raceway 5, by radius 24, carry out rounding.
The endoporus of inner ring 6 has cone shape internal valve 13.
Fig. 4 illustrates for the inner ring 6 using according to rolling bearing of the present invention.Substantially, this inner ring 6 conforms to the embodiment according to Fig. 3.Yet in contrast, inner ring rolling element raceway 5 be embodied as protruding spherical and there is protruding shape.
With the point of maximum dimension D am, be positioned at the axial centre of inner ring antifriction-bearing raceway 5.Two that set out thus axially on diameter reduce, that is to say correspondingly retraction diametrically of inner ring rolling element raceway 5.This lasting contraction correspondingly has minimum diameter Dae at the axial end portion place of inner ring rolling element raceway 5.
In this example, Dam=80mm and Dae=79.992mm.
Fig. 5 illustrates the schematic sectional drawing of the third embodiment of the present invention.Fig. 5 illustrates rolling bearing 1, i.e. roller bearing, and this rolling bearing comprises inner ring 6 and outer ring 2, wherein, outer ring 2 is for example configured to according to the embodiment according to Fig. 1.
Show again half of sectional drawing of the spin axis 19 that comprises inner ring 6.This inner ring 6 conforms to the embodiment according to Fig. 4.
This roller bearing is the roller bearing with columniform rolling element 4, and these rolling elements roll between the rolling element raceway 3 of inner ring rolling element raceway 5 and outer ring 2.Outer ring 2 is embodied as unskirted, thereby obtains floating bearing.
Fig. 6 illustrates rolling bearing 1, and this rolling bearing comprises the inner ring 6 that is embodied as sagging grooving 22,23 with two.In the region of grooving 22,23 between two surface of contact, have and extend axially ' a ' or ' b ', wherein, this extends width is in other words only the whole part for width in other words that extends axially of grooving.Grooving 22,23 has respectively and extends axially ' x ' in the axial direction outside surface of contact.
Fig. 7 illustrates the main shaft 16 of lathe, and this main shaft is on the one hand by angular contact ball bearing 17 and on the other hand by for example, supporting according to roller bearing 18 of the present invention (according to Fig. 1 embodiment).
Reference numerals list
1 rolling bearing
2 outer rings
3 rolling element raceways
4 rolling elements
The rolling element raceway of 5 inner rings (inner ring rolling element raceway)
6 inner rings
7 edges
8 edges
9 retainers
10 grooves
11 grooves
12a shell surface (first portion)
12b shell surface (second portion)
13 internal valves
14 end faces
15 end faces
16 main shafts
17 angular contact ball bearings
18 roller bearings
19 spin axiss
20 surface of contact
21 surface of contact
22 groovings
23 groovings
24 radiuses
Claims (17)
1. roller bearing, described roller bearing comprises columniform rolling element (4) and outer ring (2), wherein, shell surface (the 12a of described outer ring (2), 12b) there are two annular grooves (10, 11), described groove is at least spaced apart with the axially extended amount of described rolling element (4) in the axial direction, and wherein, described shell surface in the axial direction at two described grooves (10, 11) first portion between (12a) with respect to described shell surface in the axial direction at described groove (10, 11) second portion outside (12b) bounces back diametrically, and wherein, described outer ring (2) has the thickness of substantial constant in the region of the described first portion (12a) of described shell surface, it is characterized in that, for each groove (10, 11), this groove (10, 11) radial thickness (B) and this groove (10, 11) ratio between axial wall thickness (A) is in 0.5 to 1.5 scope, wherein, described radial thickness (B) and described outer ring (2) are at described groove (10, 11) inner minimum radial thickness conforms to, and wherein, described axial wall thickness (A) and described groove (10, 11) arrive the adjacent end face (14 of described outer ring (2), 15) minimum axial spacing conforms to, and, described roller bearing has inner ring, described inner ring comprises inner ring rolling element raceway, described inner ring rolling element raceway is presented axially between two edges with each the described inner ring for the surface of contact of contact roller kinetoplast end face about the spin axis of described inner ring, wherein, described inner ring has the grooving circularizing about the spin axis of described inner ring between at least one edge and described inner ring rolling element raceway, and wherein, described at least one, the width that is located at two parts in the region between described surface of contact of grooving conforms to the 15%-30% of the spacing of two described surface of contact.
2. roller bearing according to claim 1, is characterized in that, for each groove (10,11), radial thickness (B) the to axial ratio of wall thickness (A) is in 0.6 to 1.3 scope.
3. roller bearing according to claim 2, is characterized in that, for each groove (10,11), radial thickness (B) the to axial ratio of wall thickness (A) is in 0.7 to 1.2 scope.
4. roller bearing according to claim 3, is characterized in that, for each groove (10,11), radial thickness (B) the to axial ratio of wall thickness (A) is in 0.9 to 1.1 scope.
5. roller bearing according to claim 1 and 2, is characterized in that, the extending axially in axially extended 10% to 20% the scope that is in described outer ring (2) of each groove (10,11).
6. roller bearing according to claim 5, is characterized in that, the extending axially in axially extended 12.5% to 17.5% the scope that is in described outer ring (2) of each groove (10,11).
7. roller bearing according to claim 1, is characterized in that, extending axially of the first portion of described shell surface (12a) and axially extended 45% to 55% conforming to of described outer ring (2).
8. roller bearing according to claim 1, is characterized in that, described groove (10,11) is spaced apart with the axially extended amount of described rolling element (4) in the axial direction.
9. roller bearing according to claim 1, is characterized in that, one or two groove (10,11) has cross-sectional profiles that take the shape of the letter U, V-shaped, rectangle or that be swallow-tail form.
10. roller bearing according to claim 1, is characterized in that, the diameter of the described first portion (12a) of described shell surface is in 98% to 99.99% the scope of diameter of second portion (12b) of described shell surface.
11. roller bearings according to claim 10, is characterized in that, the diameter of the described first portion (12a) of described shell surface is in 99.9% to 99.95% the scope of diameter of second portion (12b) of described shell surface.
12. roller bearings according to claim 1, is characterized in that, 1% to 5% of the diameter of the described second portion (12b) that the degree of depth of one or two groove (10,11) is described shell surface.
13. roller bearings according to claim 12, is characterized in that, 2% to 4% of the diameter of the described second portion (12b) that the degree of depth of one or two groove (10,11) is described shell surface.
14. roller bearings according to claim 1, is characterized in that, extending axially substantially of described inner ring conforms to extending axially of described outer ring (2).
15. roller bearings according to claim 1, it is characterized in that, described inner ring rolling element raceway is punctured into described inner ring rolling element raceway (2) at 0.0025% to 0.015% of the diameter at the axial middle part of described inner ring rolling element raceway the axial end portion place of described inner ring rolling element raceway.
16. roller bearings according to claim 15, it is characterized in that, described inner ring rolling element raceway is punctured into described inner ring rolling element raceway (2) at 0.005% to 0.0125% of the diameter at the axial middle part of described inner ring rolling element raceway the axial end portion place of described inner ring rolling element raceway.
17. roller bearings according to claim 16, it is characterized in that, described inner ring rolling element raceway is punctured into described inner ring rolling element raceway (2) at 0.01% of the diameter at the axial middle part of described inner ring rolling element raceway the axial end portion place of described inner ring rolling element raceway.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102008060480 | 2008-12-05 | ||
| DE102008060480.1 | 2008-12-05 | ||
| DE102009053375.3 | 2009-11-14 | ||
| DE102009053375A DE102009053375A1 (en) | 2008-12-05 | 2009-11-14 | Rolling bearings with optimized outer ring |
| PCT/DE2009/001719 WO2010063281A1 (en) | 2008-12-05 | 2009-12-02 | Rolling bearing having optimized outer race |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102239339A CN102239339A (en) | 2011-11-09 |
| CN102239339B true CN102239339B (en) | 2014-03-26 |
Family
ID=42145848
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200980148844.8A Active CN102239339B (en) | 2008-12-05 | 2009-12-02 | Rolling bearing having optimized outer race |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP2010133560A (en) |
| CN (1) | CN102239339B (en) |
| DE (1) | DE102009053375A1 (en) |
| WO (1) | WO2010063281A1 (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5654798B2 (en) * | 2010-07-30 | 2015-01-14 | 住友重機械工業株式会社 | Roller retainer and swinging intermeshing gear device |
| DE102011080818B4 (en) * | 2011-08-11 | 2013-09-19 | Aktiebolaget Skf | Method for producing a rolling bearing cage of high stability |
| JP6144665B2 (en) * | 2014-12-04 | 2017-06-07 | 本田技研工業株式会社 | One-way clutch and vehicle power transmission device |
| DE102015204435A1 (en) * | 2015-03-12 | 2016-09-15 | Aktiebolaget Skf | Bearing rings with coordinated axial stiffness |
| CN105114449A (en) * | 2015-07-24 | 2015-12-02 | 山东凯美瑞轴承科技有限公司 | Floating deflection mixing bearing for electric main shaft |
| CN105156467A (en) * | 2015-10-12 | 2015-12-16 | 山东凯美瑞轴承科技有限公司 | Double-row floating displacement hybrid bearing for electric spindle |
| DE102015118674A1 (en) * | 2015-10-30 | 2017-05-04 | Bernd Bösinger | Method for producing a precision spindle for machining |
| DE102017113457B4 (en) * | 2017-06-20 | 2022-03-17 | Schaeffler Technologies AG & Co. KG | Steering head bearing arrangement for a bicycle for the rotatable mounting of a steering shaft |
| JP2022106105A (en) * | 2021-01-06 | 2022-07-19 | Ntn株式会社 | Cross roller bearing |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3512856A (en) * | 1968-09-25 | 1970-05-19 | North American Rockwell | Low stress bearing |
| US3588205A (en) * | 1969-08-27 | 1971-06-28 | Us Navy | Rolling contact bearing design which reduces bearing generated noise and fretting corrosion |
| DE102004035387A1 (en) * | 2004-07-21 | 2006-03-16 | Ab Skf | Cylindrical roller bearing for machine tool manufacturing, has outer ring whose casing exhibits groove, which is deepened in area of trough inflection points, where plane area of groove is axially extended equal to that of roller body |
| CN101187399A (en) * | 2003-09-30 | 2008-05-28 | Ntn株式会社 | Cylindrical roller bearing |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE965671C (en) | 1954-05-27 | 1957-06-13 | Rudolf Spieth | Cylindrical roller bearing in which at least one race is designed as an elastic member |
| JP2007051702A (en) * | 2005-08-18 | 2007-03-01 | Jtekt Corp | Tapered roller bearing and vehicular pinion shaft supporting device using the same |
-
2009
- 2009-11-14 DE DE102009053375A patent/DE102009053375A1/en not_active Ceased
- 2009-11-30 JP JP2009272328A patent/JP2010133560A/en active Pending
- 2009-12-02 CN CN200980148844.8A patent/CN102239339B/en active Active
- 2009-12-02 WO PCT/DE2009/001719 patent/WO2010063281A1/en active Application Filing
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3512856A (en) * | 1968-09-25 | 1970-05-19 | North American Rockwell | Low stress bearing |
| US3588205A (en) * | 1969-08-27 | 1971-06-28 | Us Navy | Rolling contact bearing design which reduces bearing generated noise and fretting corrosion |
| CN101187399A (en) * | 2003-09-30 | 2008-05-28 | Ntn株式会社 | Cylindrical roller bearing |
| DE102004035387A1 (en) * | 2004-07-21 | 2006-03-16 | Ab Skf | Cylindrical roller bearing for machine tool manufacturing, has outer ring whose casing exhibits groove, which is deepened in area of trough inflection points, where plane area of groove is axially extended equal to that of roller body |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2010063281A1 (en) | 2010-06-10 |
| JP2010133560A (en) | 2010-06-17 |
| DE102009053375A1 (en) | 2010-06-10 |
| CN102239339A (en) | 2011-11-09 |
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