CN206439303U - A kind of not rounded contacts locus of points rolling bearing - Google Patents
A kind of not rounded contacts locus of points rolling bearing Download PDFInfo
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- CN206439303U CN206439303U CN201621158092.7U CN201621158092U CN206439303U CN 206439303 U CN206439303 U CN 206439303U CN 201621158092 U CN201621158092 U CN 201621158092U CN 206439303 U CN206439303 U CN 206439303U
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Abstract
Locus of points rolling bearing is contacted the utility model discloses a kind of not rounded.Including bearing outer ring, bearing inner race, flexible retainer, rolling element and lubricant, bearing outer ring inside curve shape is that quadravalence or six ranks are oval, curve shape is that three ranks or quadravalence are oval on the outside of corresponding bearing inner race, retainer is flexible retainer, rolling element is cylinder rolling element, number is 7 or 10, and cylinder rolling element is scheduled between bearing outer ring and bearing inner race by flexible retainer, and uniform arrangement is installed.The utility model is in the most of time of bearing working, and the composite curve radius that roller is contacted with Internal and external cycle is larger, can realize reduction contact stress, extend contact fatigue life.
Description
Technical field
The utility model is related to a kind of rolling bearing, and locus of points rolling bearing is contacted more particularly, to a kind of not rounded.
Background technology
In rolling bearing, rolling element is in contact with the raceway of the inside and outside circle of bearing.Inside and outside rolling bearing of the prior art
The interior outside of circle is all circular, and the composite curve radius of roller and raceway contact is smaller, and contact stress is big, bearing life
It is short.
Utility model content
In order to solve in background technology, contact stress is big, contact between general circle Internal and external cycle rolling bearing roller and raceway
The problem of fatigue life is short, the purpose of this utility model is the provision of a kind of not rounded contact locus of points rolling bearing, can reduce
The tired contact life of contact stress and increase between rolling element and raceway.
The technical solution adopted in the utility model is：
First, a kind of 3-4 types not rounded contact locus of points rolling bearing：
Including bearing outer ring, bearing inner race, flexible retainer, rolling element and lubricant, the bearing outer ring inside curve
Shape is that quadravalence is oval, and outside curve shape is circular；Curve shape is that three ranks are oval on the outside of the bearing inner race, inside curve
Shape is circular；The retainer is flexible retainer.
Described rolling element is cylinder rolling element, and number is 7, and cylinder rolling element is scheduled on outside bearing by flexible retainer
Between circle and bearing inner race, uniform arrangement is installed.
It is described that flexible to keep frame material be 40CrNiMoA, 30CrMnSi, 42CrMo4, carbon fiber reinforced epoxy resin-based
Composite (CF/EP) and glass fiber reinforced epoxy resin based composites (GF/EP) one of which.
2nd, a kind of 4-6 types not rounded contact locus of points rolling bearing：
Including bearing outer ring, bearing inner race, flexible retainer, rolling element and lubricant, the bearing outer ring inside curve
Shape is that six ranks are oval, and outside curve shape is circular；Curve shape is that quadravalence is oval on the outside of the bearing inner race, inside curve
Shape is circular；The retainer is flexible retainer.
Described rolling element is cylinder rolling element, and number is 10, and cylinder rolling element is scheduled on bearing by flexible retainer
Between outer ring and bearing inner race, uniform arrangement is installed.
It is described that flexible to keep frame material be 40CrNiMoA, 30CrMnSi, 42CrMo4, carbon fiber reinforced epoxy resin-based
Composite (CF/EP) and glass fiber reinforced epoxy resin based composites (GF/EP) one of which.
Curve uses the expression formula of below equation on the outside of described bearing outer ring inside curve and bearing inner race：
In formula：A is the major semiaxis before oval develop, and k is oval eccentricity；
Wherein, the relation of below equation is met on the outside of bearing outer ring inside curve and bearing inner race between curve：
Under the polar coordinate system shown in Fig. 4, in formula, r1Be on the outside of bearing inner race curve to footpath, θ1It is on the outside of bearing inner race
The polar angle of curve, r2It is the radius of cylindrical roller, r3It is bearing outer ring inside curve to footpath, θ3It is bearing outer ring inside curve
Polar angle, u1It was roller with inner ring contact point m common tangent and inner ring to footpath r1Between angle, u2It was roller and outer ring
Contact point n common tangent and outer ring are to footpath r3Between angle.
Described oval eccentricity k scope is 0.04~0.14.
The utility model is made by the way that the shape on the inside of bearing outer ring and on the outside of bearing inner race is designed into high-order elliptical shape
Rolling bearing is in the most of time section of work, and the composite curve radius that roller is contacted with bearing internal external circle becomes big.Specifically may be used
Refer to the direct stress σ contacted between following two partsHCalculation formula.
In formula：The gross pressure for F-act on contact surface；B-initial contact line length；μ1And μ2- it is respectively the He of part 1
The Poisson's ratio of the material of part 2；E1And E2- be respectively part 1 and the material of part 2 modulus of elasticity.ρ1And ρ2- it is respectively first
The radius of curvature of individual part and second part initial contact.
Generally, makeReferred to as synthetic curvature, andReferred to as composite curve radius, wherein positive sign
For outer contacting, negative sign is used for interior contact.Roller can be because ellipse with the contact situation of bearing internal external circle raceway in the utility model
Circle eccentricity value is different and obtains different contact situations, so contact or outer contacting are needed according to curve side in being specifically
The second dervative of journey finds knee of curve for 0 and just can determine that.
Above formula is the calculation formula of contact stress when two parts that Elasticity is provided contact with each other.It is public more than
Formula can be seen that the synthetic curvature of contact stress and two parts at initial contact link between two parts contacted with each other
Radius is relevant.Composite curve radius is bigger, and contact stress is just smaller.Rolling element diameter of the present utility model keeps constant, improves
With the bearing inner race and outer ring radius of curvature of rolling element contact position, so as to improve composite curve radius, thus contact can be reduced should
Power, improves the bearing capacity and service life of rolling bearing.
The utility model has an advantageous effect in that：
The utility model is made by the way that the shape on the inside of bearing outer ring and on the outside of bearing inner race is designed into high-order elliptical shape
Rolling bearing is in the most of time section of work, and the composite curve radius of roller and bearing internal external circle becomes big, with general circle
Internal and external cycle bearing compared to can cause in the most of time of bearing working, the contact stress of roller and bearing internal external circle is small,
Contact fatigue life is long.
Brief description of the drawings
Fig. 1 is the non-round dot contact trace rolling bearing structure schematic diagram of 3-4 types.
Fig. 2 is the non-round dot contact trace rolling bearing structure schematic diagram of 4-6 types.
Fig. 3 is the schematic diagram that n ranks ellipse is developed.
Fig. 4 is the roller and curve on the outside of outer ring inside curve and inner ring of the non-round dot contact trace rolling bearing of 3-4 types
In the position view of a certain operation time.
Fig. 5 is the schematic diagram that the non-round dot contact trace rolling bearing Internal and external cycle of 3-4 types contains a roller.
Fig. 6 is the schematic diagram that the non-round dot contact trace rolling bearing Internal and external cycle of 3-4 types contains two rollers.
Embodiment
The utility model is further described below in conjunction with drawings and examples.
As shown in figure 3, curve is that n ranks are oval on the outside of bearing outer ring inside curve of the present utility model and bearing inner race
Develop.If keeping oval upper certain point D's constant and its polar angle is reduced into integral multiple n (n is the oval song of high-order to footpath r
N=3 in the periodicity of line change, figure), i.e., oval original polar angle θ becomes present n θ, so develops new curve out
It is exactly that n ranks are oval, its pitch curve equation is：
In formula, A is the major semiaxis before oval develop, and k is oval eccentricity.
It is oval for quadravalence on the inside of bearing outer ring for the non-round dot contact trace rolling bearing of 3-4 types, by n=4, in substitution
The curvilinear equation on the inside of outer ring can be obtained by stating formula (1).Similarly, the non-round dot contact trace rolling bearing of 4-6 types can be obtained
Curvilinear equation on the inside of outer ring.Obtaining the non-round dot contact trace rolling bearing of 3-4 types and the non-round dot contact trace rolling of 4-6 types
After the outer ring inside curve equation of bearing, next the principle using cylindrical roller all the time with Internal and external cycle raceway contact (is similar to
Planetary gear and the principle that sun gear is engaged all the time in planetary gear train) ask for curvilinear equation on the outside of corresponding inner ring.
The rolling principle of the utility model bearing is：
As shown in figure 4, being cylindrical roller 14 and the outer ring inside curve 15 of non-round dot contact trace rolling bearing and interior
Position view of the circle outside curve 16 in a certain operation time.O points represent bearing centre in figure, are also that Internal and external cycle high-order is oval
The absolute instantaneous centre of velocity of the center of curve and now Internal and external cycle；M points represent contact of the roller at this moment with curve on the outside of inner ring
Point, is also roller and the absolute instantaneous centre of velocity of outer ring at this moment；N points represent contact point of the roller now with outer ring inside curve,
It is also the absolute instantaneous centre of velocity of roller and inner ring.O, m, n three point on a straight line are understood by Kennedy-Aronhold the-orem.Such as Fig. 4, coordinate pole axis is set up
13, with angle θ1As polar angle, Om is as to footpath r1, then the curvilinear equation on the outside of inner ring can be represented with the two parameters.Similarly,
With angle θ3As polar angle, On is as to footpath r3, then the curvilinear equation on the inside of outer ring can be represented with the two parameters.The half of roller
Footpath r2Represent, be O'm or O'n length in figure.Made roller and curve on the outside of inner ring contact point m common tangent and inner ring
To footpath r1Between angle be u1, roller and outer ring contact point n common tangent and outer ring inside curve were made to footpath r3Between folder
Angle is u2, u is understood by geometrical relationship1=u2.From Differential Geometry：
From geometrical relationship：
r1=r3-2r2sin u1 (4)
To formula (4) both sides while differential, vertical (2) in parallel, formula (3) can be obtained：
So the curvilinear equation on the outside of inner ring is：
In formula：r1It is the curve 16 to footpath on the outside of bearing inner race under the polar coordinate system shown in Fig. 4；
θ1It is the polar angle of curve 16 on the outside of bearing inner race under the polar coordinate system shown in Fig. 4；
r2It is the radius of cylindrical roller 14；
r3Be under the polar coordinate system shown in Fig. 4, bearing outer ring inside curve 15 to footpath；
θ3It is the polar angle of bearing outer ring inside curve 15 under the polar coordinate system shown in Fig. 4；
u1It was roller with inner ring contact point m common tangent and inner ring to footpath r1Between angle；
u2It was roller with outer ring contact point n common tangent and outer ring to footpath r3Between angle.
From formula (6), after it have selected the high-order elliptic equation on the inside of bearing outer ring, you can obtain corresponding inner ring
Outside curvilinear equation.Round dot non-for 3-4 types contacts rolling bearing, and selection n=4, which substitutes into formula (1), can obtain the song on the inside of outer ring
Line equation is：
Formula (7) is substituted into formula (6) can obtain curvilinear equation on the outside of the inner ring of the non-round dot contact trace rolling bearing of 3-4 types.
Curvilinear equation can be obtained by same method on the outside of the inner ring of the non-round dot contact trace roller bearing of 4-6 types.Fig. 1 and Fig. 2 points
It is not the schematic diagram that have chosen the 3-4 types obtained after suitable parameter and the non-round dot contact rolling bearing of 4-6 types.It can be seen that 3-4
The outer ring inside curve period of change of the non-round dot contact trace rolling bearing of type is 4, and the inner ring curvilinear motion cycle is 3, therefore will
This bearing is referred to as 3-4 types.The outer ring inside curve period of change of the non-round dot contact trace rolling bearing of 4-6 types is 6, inner ring curve
Period of change is 4, therefore this bearing is referred to as into 4-6 types.
The uniform bar of roller number is proved on the inside of bearing outer ring and on the outside of inner ring after curvilinear equation, next obtaining
Part.
As shown in figure 5, being the situation that the non-round dot contact trace rolling bearing Internal and external cycle of 3-4 types contains a roller.Assuming that
Under this original state, roller is contacted with outer ring in b points, and roller is contacted with inner ring in a points.Bearing centre is point O.By this mechanism
3-4 type non-circular gear drive structures are analogous to, roller can be considered as to planetary gear, inner ring outside and be considered as sun gear pitch curve, outer ring
Inner side is considered as internal gear pitch curve.When internal gear is motionless, planetary gear and sun gear are moved together.Due to internal tooth pitch curve and too
Sun wheel pitch curve is mechanical periodicity, and the sun gear pitch curve cycle is 3, and the internal gear pitch curve cycle is 4, when sun gear is turned over
After the angle of 2 π/3, the relative position of sun gear and internal gear as original state, simply before planetary gear and sun gear, interior
The contact point of gear ring becomes a' the and b' points shown in Fig. 6.Now one can be installed between 2 points of c, d shown in Fig. 6 again
Gear.By that analogy, after sun gear turns over 2 π (i-1)/3 angle, i-th of gear can be installed.
Next consider after i-th of gear is mounted with, the position of first gear.
Assuming that planetary gear revolution speed is 0, sun gear and internal gear rotate, and obtain switching mechanism.Sun gear and internal tooth
The arc length that wheel pitch curve changes in a cycle should be equal, and sun gear pitch curve can not otherwise closed.Accordingly, internal tooth is worked as
Wheel is turned over after a circle, and sun gear needs to rotate 4/3 circle.In actual application, internal gear is motionless, and sun gear does dead axle and turned
When dynamic, planetary gear will also revolve round the sun while rotation and translation is made around the fixed center of ring gear, and its angle revolved round the sun is exactly
The angle that ring gear is turned in transformation mechanism.Therefore, when the revolution angle of planetary gear is 2 π (returning to original position), sun gear is needed
The angle turned over is 3+4=7 times that (1+4/3) * 2 π is just 2 π/3, because sun gear is to turn over 2 π/3 every time, therefore can
Uniformly to install 7 gears.So can uniform 7 cylindrical rollers for the non-round dot contact trace rolling bearing of 3-4 types.Similarly
It can prove that the non-round dot contact trace rolling bearing of 4-6 types can uniformly install 10 cylindrical rollers.Final installation effect is such as
Shown in Fig. 1 and Fig. 2.
Embodiment of the present utility model is as follows：
Embodiment 1
As shown in figure 1, embodiment 1 is a kind of non-round dot contact trace rolling bearing structure schematic diagram of 3-4 types.Including 3-4
The non-round dot contact trace housing washer (1) of type, the flexible retainer (2) of the non-round dot contact trace rolling bearing of 3-4 types, 3-4
The non-round dot contact trace rolling bearing rolling element (3) of type and the non-round dot contact trace rolling bearing inner ring (4) of 3-4 types.Wherein, outside
The inner shape for enclosing (1) is quadravalence elliptic curve 9, and the outer shape of inner ring (4) is three rank elliptic curves 10.Rolling element (3) is
Cylindrical roller, is distributed in flexible retainer (2).By A=51.7, n=4, k=0.1289, substitute into formula (1) and obtain outer ring
Inside curve equation is：
Above-mentioned curvilinear equation is substituted into formula (6) can obtain curvilinear equation on the outside of inner ring, obtain Internal and external cycle curvilinear equation.Press
Bearing internal external circle raceway is made according to this two curvilinear equations.Then installation process is uniformly arranged according to foregoing cylindrical roller, by 7
Cylindrical roller is uniformly arranged between Internal and external cycle.The design sketch finally given is as schemed shown in (1).
In this example of lower surface analysis, in a work period, bearing connects in most of working time scope rollers with raceway
Touch composite curve radius bigger than the composite curve radius of roller and circular raceway contact.
Outer ring inside curve equation (8) in example one
By arc length formula ds=ρ d θ, formula (8) is substituted into the camber line Zhou Changwei for obtaining the whole curve in outer ring：
Wherein：S is the girth of outer ring inside curve, and ρ is to footpath when polar angle is equal to θ on curve.
If outer ring inside curve is equivalent into a circumference, equivalent radius of a circle R can obtain：
Wherein：R is the radius of the circle equivalent with outer ring inside curve.
After the radius for trying to achieve equivalent circular, each point on curve can further be tried to achieve according to outer ring inside curve equation (8)
Radius of curvature, then obtains radius of curvature in the inside curve of outer ring and is more than the central angle corresponding to radius of equivalent circle, by these models
Central angle in enclosing, which is added, obtains total central angle, calculates total central angle and the integrated curved central angle of one week on the inside of outer ring
The ratio between (i.e. 2 π), can represent that the composite curve radius that roller is contacted with outer race track connects than general roller and circular orbit with the ratio
Tactile composite curve radius wants big probability.
It is 0 first according to the second dervative of curvilinear equation when calculating composite curve radius, finds out the flex point position on curve
Put, thus differentiate contacted in roller and raceway and outer contacting contact range.It can be obtained after calculating, roller is rolled with outer ring
The composite curve radius of road roller and outer ring raceway in the range of the time of contact of 58.3% (being more than 50%) is than general roller
The radius of curvature contacted with circular orbit is big.Similarly, it can calculate and obtain roller with inner ring raceway in 65.4% (being more than 50%)
Time of contact in the composite curve radius of roller and inner ring raceway will than the radius of curvature that general roller is contacted with circular orbit
Greatly, so as to reduce the contact stress between roller and raceway, the working life of bearing is improved.
Embodiment 2
As shown in Fig. 2 embodiment 2 is a kind of non-round dot contact trace rolling bearing structure schematic diagram of 4-6 types.Including 4-6
The non-round dot contact trace housing washer (5) of type, the non-round dot contact trace rolling bearing rolling element (6) of 4-6 types, 4-6 types are non-
Round dot contact trace rolling bearing flexibility retainer (7) and the non-round dot contact trace rolling bearing inner ring (8) of 4-6 types.Wherein, outside
The inner shape for enclosing (5) is six rank elliptic curves 11, and the outer shape of inner ring (8) is quadravalence elliptic curve 12.Rolling element (6) is
Cylindrical roller, is distributed in flexible retainer (7).By A=47.43, n=6, k=0.0729, substitute into formula (1) and obtain outer
Enclosing inside curve equation is：
Above-mentioned outer ring inside curve equation is substituted into formula (6) can obtain curvilinear equation on the outside of inner ring, obtain Internal and external cycle bent
Line equation, bearing internal external circle raceway is made according to this two curvilinear equations.Then installation is uniformly arranged according to foregoing cylindrical roller
Process, 10 cylindrical rollers are uniformly arranged between Internal and external cycle.The design sketch finally given is as schemed shown in (2).
In this example of lower surface analysis, in a work period, bearing connects in most of working time scope rollers with raceway
Touch composite curve radius bigger than the composite curve radius of roller and circular raceway contact.
Outer ring inside curve equation (11) in example two
By arc length formula ds=ρ d θ, formula (11) is substituted into the camber line Zhou Changwei for obtaining the whole curve in outer ring：
Wherein：S is the girth of outer ring inside curve, and ρ is to footpath when polar angle is equal to θ on curve.
If outer ring inside curve is equivalent into a circumference, equivalent radius of a circle R=47.3 can obtain：
After the radius for trying to achieve equivalent circular, each point on curve can further be tried to achieve according to outer ring inside curve equation (11)
Radius of curvature, then finds out radius of curvature in the inside curve of outer ring and is more than the central angle corresponding to radius of equivalent circle, by these models
The central angle enclosed, which is added, obtains total central angle, calculates total central angle and the integrated curved central angle of one week (i.e. 2 on the inside of outer ring
The ratio between π), it can represent that composite curve radius that roller is contacted with outer race track is contacted than general roller with circular orbit with the ratio
Composite curve radius wants big probability.
It is 0 first according to the second dervative of curvilinear equation when calculating composite curve radius, finds out the flex point position on curve
Put, thus differentiate contacted in roller and raceway and outer contacting contact range.It can be obtained after calculating, roller is rolled with outer ring
The composite curve radius of road roller and outer ring raceway in the range of the time of contact of 54.7% (being more than 50%) is than general roller
The radius of curvature contacted with circular orbit is big.Similarly, it can calculate and obtain roller with inner ring raceway in 57.2% (being more than 50%)
Time of contact in the composite curve radius of roller and inner ring raceway will than the radius of curvature that general roller is contacted with circular orbit
Greatly, so as to reduce the contact stress between roller and raceway, the working life of bearing is improved.
Operation principle of the present utility model is：
In general circular scrolling bearing, the composite curve radius of roller and Internal and external cycle raceway contact is smaller, so holds
The contact stress that is easily caused between roller and Internal and external cycle is excessive, reduce the working life of bearing.When oval major axis and round half
When footpath is equal, the relatively round radius of curvature of the radius of curvature of most of point is larger on ellipse.As can be seen here, the utility model is by axle
Hold on the outside of inner ring, be designed on the inside of outer ring high-order elliptical shape can so that bearing work most of moment (on details are shown in
State example calculation) composite curve radius of roller and inside and outside raceway contact is larger, so as to reduce between roller and inside and outside raceway
Contact stress, improves the contact fatigue life of bearing.
Above-mentioned embodiment is used for illustrating the utility model, rather than the utility model is limited,
In spirit and scope of the claims of the present utility model, any modifications and changes made to the utility model all fall
Enter protection domain of the present utility model.
Claims (8)
1. a kind of not rounded contacts locus of points rolling bearing, including bearing outer ring, bearing inner race, flexible retainer, rolling element and profit
Lubrication prescription, it is characterised in that：The bearing outer ring inside curve shape is that quadravalence is oval, and outside curve shape is circular；The axle
It is that three ranks are oval to hold curve shape on the outside of inner ring, and inside curve shape is circular；The retainer is flexible retainer.
2. a kind of not rounded contact locus of points rolling bearing according to claim 1, it is characterised in that：Described rolling element is
Cylinder rolling element, number is 7, and cylinder rolling element is scheduled between bearing outer ring and bearing inner race uniform cloth by flexible retainer
Put installation.
3. a kind of not rounded contact locus of points rolling bearing according to claim 1, it is characterised in that：Described flexible holding
Frame material is 40CrNiMoA, 30CrMnSi, 42CrMo4, carbon fiber reinforced epoxy resin-based composite (CF/EP) and glass
Fiber reinforced epoxy resin based composites (GF/EP) one of which.
4. a kind of not rounded contacts locus of points rolling bearing, including bearing outer ring, bearing inner race, flexible retainer, rolling element and profit
Lubrication prescription, it is characterised in that：The bearing outer ring inside curve shape is that six ranks are oval, and outside curve shape is circular；The axle
It is that quadravalence is oval to hold curve shape on the outside of inner ring, and inside curve shape is circular；The retainer is flexible retainer.
5. a kind of not rounded contact locus of points rolling bearing according to claim 4, it is characterised in that：Described rolling element is
Cylinder rolling element, number is 10, and cylinder rolling element is scheduled between bearing outer ring and bearing inner race uniformly by flexible retainer
Arrangement is installed.
6. a kind of not rounded contact locus of points rolling bearing according to claim 4, it is characterised in that：Described flexible holding
Frame material is 40CrNiMoA, 30CrMnSi, 42CrMo4, carbon fiber reinforced epoxy resin-based composite (CF/EP) and glass
Fiber reinforced epoxy resin based composites (GF/EP) one of which.
7. locus of points rolling bearing is contacted according to a kind of any described not rounded of claim 1-6, it is characterised in that：Described axle
Curve uses the expression formula of below equation on the outside of bearing outer-ring inside curve and bearing inner race：
In formula, A is the major semiaxis before oval develop, and k is oval eccentricity；
Wherein, the relation of below equation is met on the outside of bearing outer ring inside curve and bearing inner race between curve：
In formula, r1Be on the outside of bearing inner race curve to footpath, θ1It is the polar angle of curve on the outside of bearing inner race, r2It is cylindrical roller
Radius, r3It is bearing outer ring inside curve to footpath, θ3It is the polar angle of bearing outer ring inside curve, u1It was that roller connects with inner ring
Contact m common tangent and inner ring are to footpath r1Between angle, u2It was roller with outer ring contact point n common tangent and outer ring to footpath
r3Between angle.
8. a kind of not rounded contact locus of points rolling bearing according to claim 7, it is characterised in that：It is described it is oval from
Heart rate k scope is 0.04~0.14.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621158092.7U CN206439303U (en) | 2016-10-25 | 2016-10-25 | A kind of not rounded contacts locus of points rolling bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621158092.7U CN206439303U (en) | 2016-10-25 | 2016-10-25 | A kind of not rounded contacts locus of points rolling bearing |
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| Publication Number | Publication Date |
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| CN206439303U true CN206439303U (en) | 2017-08-25 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201621158092.7U Withdrawn - After Issue CN206439303U (en) | 2016-10-25 | 2016-10-25 | A kind of not rounded contacts locus of points rolling bearing |
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| CN (1) | CN206439303U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106402149A (en) * | 2016-10-25 | 2017-02-15 | 浙江大学 | Noncircular contact point path rolling bearing |
-
2016
- 2016-10-25 CN CN201621158092.7U patent/CN206439303U/en not_active Withdrawn - After Issue
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106402149A (en) * | 2016-10-25 | 2017-02-15 | 浙江大学 | Noncircular contact point path rolling bearing |
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| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20170825 Effective date of abandoning: 20190118 |