CN104791289A - Integral shaft-connect type fan clutch bearing - Google Patents
Integral shaft-connect type fan clutch bearing Download PDFInfo
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- CN104791289A CN104791289A CN201510188095.9A CN201510188095A CN104791289A CN 104791289 A CN104791289 A CN 104791289A CN 201510188095 A CN201510188095 A CN 201510188095A CN 104791289 A CN104791289 A CN 104791289A
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Abstract
The invention discloses an integral shaft-connect type fan clutch bearing. The bearing adopts a row of rollers and double-row steel balls, the double-row steel balls adopt an angular contact structure in a geometric form, the bearing comprises a bearing outer ring, a mandrel, a steel ball holder, a roller holder and a seal ring, wherein channels and a raceway are machined on the bearing outer ring and used for bearing the rolling elements and guiding the rotation of rolling elements, the rolling elements comprise the steel balls and the cylindrical rollers, the mandrel is inserted into the bearing outer ring in the axial direction, inner channels are machined on the outer diameter of the mandrel and used for bearing the steel balls and guiding the rotation of the steel balls, an inner raceway is further machined on the outer diameter of the mandrel and used for bearing the cylindrical rollers, the steel ball holder is arranged between the bearing outer ring and the mandrel and makes the steel balls distributed in the channels at equal intervals, the roller holder adopts a design of a cylinder-shaped structure and a spring collar structure, a spring collar is assembled on the bearing outer ring in a matched mode to prevent the cylindrical rollers from springing out in the axial direction, and the sealing ring is installed in a seal groove formed in the end of the bearing outer ring in a pressed mode and remains still with the bearing outer ring.
Description
Technical field
The present invention relates to integral shaft and connect formula fan clutch bearing, belong to the bearings with rolling contact field for rotary motion.
Background technique
Bearing structure of the prior art as shown in Figure 1, mandrel 1 is multiple stage stage structure, comprise the screw thread M20 shown in reference character 11 in accompanying drawing 1, diameter is the first step 12 of 30mm, diameter is the second step 13 of 40mm, diameter is the large external diameter 15 in end of 51mm, and diameter is the large external diameter 14 of 80mm.
Bearing working condition is generally:
1, operating temperature-40 DEG C--180 DEG C;
2, the weight of clutch and load are: 1600N
3, fan weight is 170N
4, axial force is 1500N
5, bearing rated speed: 2600 r.p.m
According to the shape assumption diagram of bearing and shaft strength and working condition, to bearing structure and stressedly to analyze, this bearing structure is one direction stair-step structure, Dimensions is larger, mandrel length is long, and left end provided with fan and clutch are cantilever structure, bears larger radial load and thrust load, due to by effects such as gravity center eccentrics during use, there is balanced dynamic load scarcely.The stress of bearing is cantilever structure, and bearing left end (front end) bears larger load.
Usually the structure adopted in prior art is a fan shaft adopts a set of radial short cylindrical roller bearing and a set of double-row angular contact bal bearing, such as model is respectively NU2208 and 5306, form the bearing unit of NU2208+5306+ axle, wherein NU2208 substantial radial load, 5306 double-row angular contact bal bearings mainly bear a small amount of radial load and larger thrust load.
The boundary dimension of two kinds of bearings and volume move constant load:
NU2208 internal diameter d=40mm outer diameter D=80mm thickness C=23mm
Rated static load Cor=58000N
5306 internal diameter d=30 outer diameter D=72 thickness C=30.2
Rated static load Cor=40500N
Prior art middle (center) bearing is open architecture, needs to lubricate especially and Seal Design bearing during work.There is the larger difficulties such as dismounting in bearing of the prior art in regular maintenance, maintenance etc.
Summary of the invention
The present invention is intended to carry out integrated optimal design to bearing unit of the prior art, and then increases bearing capacity and the reliability of shaft connecting bearing, and simplifies assembly technology.
To achieve these goals, the application provides a kind of integral shaft to connect formula fan clutch bearing, and this bearing adopts row roller and a Double-row ball, Double-row ball geometric format adopts angle contacting structure, and this bearing comprises:
Bearing outer ring, this bearing outer ring is processed with raceway groove and raceway, for carrying the rotation with orienting roll kinetoplast; Described rolling element comprises steel ball and cylindrical roller;
Mandrel, this mandrel axially inserts bearing outer ring, outside diameter of mandrel is processed with interior raceway groove, for carrying and guide the rotation of steel ball; Outside diameter of mandrel is also processed with interior raceway, for carrying cylindrical roller;
Ball retainer, this ball retainer is arranged between bearing outer ring and mandrel, and steel ball is equidistantly distributed in raceway groove;
Roller cage, this roller cage adopts tubular construction to add the structural design of check ring, and the cooperation of this check ring is assemblied on bearing outer ring, prevents cylindrical roller from scurrying out vertically;
Seal ring, sealing circle press-fits in the seal groove of bearing outer ring end, keeps static with bearing outer ring.
Wherein, described bearing outer ring is also processed with annular groove and raceway grinding undercut, in annular groove, is equipped with snap ring, the external diameter of described bearing outer ring is assemblied in bearing support or a few bore, plays benchmark effect, when bearing operation, outer ring maintains static, and bears the power that mandrel transmission comes.
Described mandrel being processed with several steps, for assembling belt pulley and/or clutch, realizing the transmission of torque.
The ditch heart on described mandrel between adjacent two interior raceway grooves is apart from being 15.05 ± 0.02mm, and the ditch heart distance on described bearing outer ring between adjacent two raceway grooves is 15.5 ± 0.02mm.
Described steel ball material is GCr15 high-quality high-carbon-chromium bearing steel, and steel ball adopts the structure of double row angular contact steel ball, and steel ball size is 13.494mm(that is 17/32 inch), often row 8 steel balls, wrapping angle is 25 °, and two row steel balls arrange back-to-back.
Described ball retainer material is for strengthening nylon+25% glass fibre.
Described cylindrical roller material is GCr15 high-quality high-carbon-chromium bearing steel, and the raceway on cylindrical roller and mandrel and bearing outer ring is linear contact lay, and the chamfering of cylindrical roller is designed with cavetto transition processing with its external diameter transition portion, makes cylindrical roller with convexity.
Described roller cage makes cylindrical roller equidistantly be distributed in raceway and guides cylindrical roller to move in a circle along raceway, and roller cage material is for strengthening nylon+25% glass fibre.
Described check ring adopts domatic opening and both sides groove angle is inconsistent, and the side that during installation, groove angle is less is introduced into the circlip groove be arranged on bearing outer ring, and during taking-up, the less side of groove angle is finally ejected.
The described width dimensions on roller cage two end ring limit coordinates with the width dimensions of the raceway grinding undercut of bearing outer ring, and make roller cage when touching grinding undercut rib, the external diameter of roller still contacts outer ring raceway effectively.
The framework material of described seal ring is OCr18NI9Ti stainless steel, sealing material is fluorine rubber, seal ring adopt dual lip configuration and lips all with mandrel interference fit, the magnitude of interference of outer lip is greater than the magnitude of interference of inner lip, cavity zone is formed, for preserving the lubricant oil oozed out between outer lip and inner lip.
The process of pressing and bending has been carried out in the middle part of the skeleton of described seal ring, seal ring press-fits in the seal groove of bearing outer ring, keep geo-stationary with outer ring, the radial dimension of seal groove is less than seal ring outside dimension, and the width of seal groove is greater than the external width of seal ring.
Compared with prior art, the application reduces the load that bearing bears, add the life-span of bearing, adopt the structure of double row angular contact steel ball, compare with single-row steel ball, it is strong that double row angular contact steel ball structure possesses bearing capacity, rotating accuracy is high, and circular runout is little, and strength is more balanced, larger thrust load and radial load can be born simultaneously, and possess the features such as axial float is little.
Accompanying drawing explanation
Fig. 1 is the structural representation of the bearing of prior art.
Fig. 2 is the overall schematic that integral shaft of the present invention connects formula fan clutch bearing.
Fig. 3 is the structural representation that integral shaft of the present invention connects the bearing outer ring of formula fan clutch bearing.
Fig. 4 is the structural representation that integral shaft of the present invention connects the mandrel of formula fan clutch bearing.
Fig. 5 is the structural representation that integral shaft of the present invention connects the ball retainer of formula fan clutch bearing.
Fig. 6 is the structural representation that integral shaft of the present invention connects the cylindrical roller of formula fan clutch bearing.
Fig. 7 is the structural representation that integral shaft of the present invention connects the roller cage of formula fan clutch bearing.
Fig. 8 is the structural representation that integral shaft of the present invention connects the check ring of formula fan clutch bearing.
Fig. 9 is the structural representation that integral shaft of the present invention connects the seal ring of formula fan clutch bearing.
Figure 10 is the right part partial enlarged drawing that integral shaft of the present invention connects formula fan clutch bearing.
Embodiment
Below in conjunction with Figure of description, be clearly and completely described the technological scheme in the present invention, obviously, described embodiment is only a part of embodiment of the present invention, instead of whole embodiments.Based on the embodiment in the present invention, those of ordinary skill in the art, not making the every other embodiment obtained under creative work prerequisite, belong to the scope of protection of the invention.Accompanying drawing, only for exemplary illustration, can not be interpreted as the restriction to this patent.To those skilled in the art, in accompanying drawing, some known features and explanation thereof may be omitted is understandable.
As shown in Figure 2, the invention provides a kind of integral shaft and connect formula fan clutch bearing, this bearing adopts row roller and a Double-row ball, Double-row ball geometric format adopts angle contacting structure, and this bearing comprises:
Bearing outer ring 20, as shown in Figure 3, this bearing outer ring 20 is processed with raceway groove 31 and raceway 32, for carrying the rotation with orienting roll kinetoplast; Described rolling element comprises steel ball 25 and cylindrical roller 24, as shown in Figure 2;
Mandrel 21, this mandrel 21 axially inserts bearing outer ring 20, as shown in Figure 4, the external diameter of mandrel 21 is processed with interior raceway groove 41, for carrying and guide the rotation of steel ball 25; The external diameter of mandrel 21 is also processed with interior raceway 42, for carrying cylindrical roller 24;
Ball retainer 22, as shown in figs. 2 and 10, this ball retainer 22 is arranged between bearing outer ring 20 and mandrel 21, makes steel ball 25 equidistantly be distributed in raceway groove 31;
Roller cage 23, as shown in Fig. 2, Fig. 7, Fig. 8 and Figure 10, this roller cage 23 adopts tubular construction to add the structural design of check ring 80, and the cooperation of this check ring 80 is assemblied on bearing outer ring, prevents cylindrical roller 24 from scurrying out vertically;
Seal ring 27, sealing circle 27 press-fits (see figure 3) in the seal groove 35 of bearing outer ring end, keeps static with bearing outer ring.The structure of seal ring 27 as shown in Figure 9, will be described in further detail below.
As shown in Figure 3, described bearing outer ring 20 is also processed with circlip groove 33 and the auxiliary slot such as raceway grinding undercut 34 and seal groove 35, annular groove; Seal groove 35 is used for fitting tight circle 27, seals; Be equipped with snap ring 26(in annular groove and see accompanying drawing 2 and 10), play a part to keep off set of rollers; Raceway grinding undercut 34 is technology groove, plays transitional function, avoids emery wheel oscillating process to interfere the damage affecting raceway machining accuracy and emery wheel during processing raceway 32.The external diameter of described bearing outer ring 20 is assemblied in bearing support or a few bore (attached not shown), and play benchmark effect, when bearing operation, outer ring maintains static, and bears the power that mandrel 21 transmission is come.Bearing outer ring 20 is also processed with circlip groove 33, for the check ring 80 shown in erection drawing 8, will be described in further detail later.
As Fig. 4, described core, is processed with several steps 43,44 on 21, for assembling belt pulley and/or clutch, realize the transmission of torque.Mandrel 21 is processed with interior raceway groove 41, for carrying, guiding the rotation of steel ball; The position of outside diameter of mandrel's carrier roller, is called interior raceway 42.Mandrel 21 outside dimension forms fit dimension with seal ring lip size, ensures that the existing seal action of seal ring again can flexible rotating.
As Fig. 4, the ditch heart of mandrel 21 is 15.05 ± 0.02mm apart from (distance between the center line that namely raceway groove 41 is respective in two), as Fig. 3, the ditch heart of bearing outer ring 20 is apart from the distance between the L(center line that is two raceway grooves 31 are respective) be 15.5 ± 0.02mm, the ditch heart of bearing outer ring 20 is apart from L 15.5-15.05=0.45 poorer than the ditch heart distance of mandrel 21, this size makes the steel ball group of bearing produce the wrapping angle of 25 ° (in Fig. 10 according to the general custom of engineering drawing by geometrical relationship and calculating, only the wrapping angle of two groups of steel balls is labeled as the wrapping angle of 2 times 50 ° of the wrapping angle of 25 °, the wrapping angle of single group steel ball is 25 °).Here wrapping angle is defined as perpendicular to the radial plane of bearing axis and by the angle of making a concerted effort between nominal line of action of bearing outer ring to steel ball transmitting force.
The material of described steel ball is GCr15 high-quality high-carbon-chromium bearing steel, and steel ball adopts the structure of double row angular contact steel ball, and steel ball size is 13.494mm, often row 8 steel balls, and wrapping angle is 25 °, and two row steel balls arrange back-to-back.Steel ball group mainly bears axial and united load; Steel ball material is GCr15, and high-quality high-carbon-chromium bearing steel adopts vacuum outgas smelting technique, greatly reduces the oxygen content in material and objectionable impurities constituent content, adds the fatigue life of steel ball.
As Fig. 5, ball retainer 22 makes steel ball equidistantly be distributed in raceway, and steel ball so both can have been made to bear uniform load, steel ball can be avoided again to occur too to concentrate in rotation process and produce loose ball and then produce the trend that is separated with Internal and external cycle of steel ball; Ball retainer also plays the effect of friction and the heating of avoiding producing between steel ball, avoids the reduction in efficiency of bearing and the life-span caused thus.Ball retainer material is that PA66+GF25% (strengthening nylon+25% glass fibre) constitutes solid cage, this solid cage has compared with while high structural strength, lighter in weight, can make bearing like this under high speed conditions, the centrifugal force of effective reduction retainer, thus reduce the load that bearing bears, increase the life-span of bearing.Steel ball adopts the structure of double row angular contact steel ball, and compare with single-row steel ball, it is strong that double row angular contact steel ball structure possesses bearing capacity, rotating accuracy is high, and circular runout is little, and strength is more balanced, larger thrust load and radial load can be born simultaneously, and possess the features such as axial float is little.
Bearing adopts double row angular contact ball and a row roller structure, and design bearing steel ball size S used Φ 13.494, often row 8 steel balls, wrapping angle is 25 °, and two row steel balls arrange back-to-back.The design of double row angular contact ball takies less axial space, can bear radial load and the axial load acting on both direction, its energy restrictive axes or displacement of shell bi-directional axial, wrapping angle is about 25 degree, the Bearing configuration that rigidity is higher can be provided, and can tilting moment be born.It is main radial and axial joint load and moment load that double row angular contact structure can bear larger radial load, the axial displacement of two aspects of restrictive axes.Two arrange the structure arranged back-to-back, have better rigidity.Compared with single-row angular contact ball bearing, double-row angular contact bal bearing has better rigidity, can bear tilting moment.Bearing is Nonseparation.Be specially adapted to the application of high rigid requirements.Allow to there is tilt angle between the inside and outside circle of bearing of this structure, and the fatigue of bearing need not be worried.
Described cylindrical roller material is GCr15 high-quality high-carbon-chromium bearing steel, and the raceway on cylindrical roller and mandrel and bearing outer ring is linear contact lay, and the chamfering of cylindrical roller is designed with cavetto transition processing with its external diameter transition portion, makes cylindrical roller with convexity.As shown in Figure 6, cylindrical roller material is GCr15, and high-quality high-carbon-chromium bearing steel adopts vacuum outgas smelting technique, greatly reduces the oxygen content in material and objectionable impurities constituent content, adds the fatigue life of cylindrical roller.Cylindrical roller and mandrel and outer ring raceway face are linear contact lay, considerably increase roller face area like this, and then improve the bearing capacity of roller.Fig. 6 middle and upper part is the schematic appearance of cylindrical roller, bottom is the enlarged diagram of the chamfering Y part of cylindrical roller, as shown in the figure, larger cavetto transition processing is designed with its external diameter transition portion 61 place in the chamfering Y part of roller, make roller with certain convexity, produce stress when such design can avoid the same mandrel of rolling element, outer ring raceway to contact to concentrate, avoid the fatigue ruption of roller and raceway, strengthen the life-span of bearing.
As shown in Figure 7, described roller cage 23 makes cylindrical roller 24 equidistantly be distributed in raceway and guides cylindrical roller to move in a circle along raceway, and roller cage material is for strengthening nylon+25% glass fibre.Pocket hole 71 in roller cage 23 forms Spielpassung with cylindrical roller 24, and roller freely can rotate in pocket hole, can not depart from pocket hole again simultaneously, roller is equidistantly distributed in raceway, roller can be made like this to bear uniform load.Different from the effect of ball retainer a bit, roller cage possesses leading role, and set of rollers is moved in a circle along raceway, prevents roller from deflecting in raceway, causes the serious consequences such as roller locking.Roller cage also plays the effect of avoiding producing friction and heating between roller, thus avoids the reduction in efficiency of bearing and the life-span caused thus.Roller cage material PA66+GF25% (strengthening nylon+25% glass fibre) constitutes solid cage, this solid cage has compared with while high structural strength, lighter in weight, can make bearing like this under high speed conditions, the centrifugal force of effective reduction retainer, thus reduce the load that bearing bears, increase the life-span of bearing.
As shown in FIG. 7 and 8, roller cage 23 adopts tubular construction to add the structural design of check ring (Fig. 8).Tubular retainer possesses simple for structure, easily carries out shaping operation, and inspection is convenient, and is conducive to realizing automatically assembling roller, and it is convenient to have disassemble or assemble, and without features such as destructivenesses.In Fig. 7, left side is the front projection view of tubular retainer, and the right side is the left side projection view of tubular retainer.Can clearly be found out by Fig. 7, tubular retainer is evenly provided with multiple pocket hole 71 on perisporium.Tubular retainer coordinates the check ring (Fig. 8) be assemblied on bearing outer ring, can effectively prevent the axis of roller from scurrying out, and improves stable, the Security of a whole set of bearing.Check ring 80 (Fig. 8) adopts domatic opening and both sides groove angle is inconsistent, and the groove angle of the less side of groove angle 81 is less than the larger side 82 of groove angle.During installation, the less side 81 of groove angle is introduced into circlip groove 33(Fig. 3), during taking-up, the less side 81 of groove angle is finally ejected.Such design is not only easy to check ring 80 to press-fit in the circlip groove 33 of outer ring, simultaneously when set of rollers goes wrong, uses Circlip tongs to be easy to too take out.The application of check ring effectively can increase the effective area of contact of roller cage with it, slows down the wearing and tearing of retainer, and then adds the life-span of bearing.Even if wearing and tearing has appearred completely in retainer, back-up ring still can block roller, avoids it axially to scurry out.In addition, when roller cage two end ring hem width degree dimensional fits outer ring raceway grinding undercut width dimensions makes roller cage touch grinding undercut rib, the external diameter of roller still contacts outer ring raceway effectively.Below what time be that butterfly becomes not available for retainer.To sum up, harsh for Environmental Conditions, operating mode is complicated and the higher stability of requirement and Security situation is more applicable, and it is comparatively economical.
As shown in Figure 9, skeleton 91 material of described seal ring 27 is OCr18NI9Ti stainless steel, and it has good mechanical property, and oxidation resistance is strong, and has good affinity with nonmetallic material; Sealing material 92 is fluorine rubber, in stable condition under the condition of-20 ° to 120 °, and has stronger wear-resisting property.Seal ring 27 adopt dual lip configuration and lips all with mandrel 21 interference fit, dual lip configuration comprises outer lip 94 and inner lip 95, the magnitude of interference of outer lip 94 is greater than the magnitude of interference of inner lip 95, forms cavity zone 96 between outer lip 94 and inner lip 95, for preserving the lubricant oil oozed out.The magnitude of interference of outer lip 94 is comparatively large, is conducive to like this stoping the foreign object such as foreign matter, dust to enter the working surface destroying bearing; The magnitude of interference of inner lip 95 is smaller, is conducive to oozing out of Bearing inner lubricant grease trace like this, plays the effect of lubrication and seal part; Cavity and the cavity zone 96 of certain space is formed between interior outer lip, the design of this structure can be used to preserve the micro lubricating grease oozed out, these greases have the effect of lubrication outer lip, effectively can slow down the wearing and tearing of lip, are unlikely to again the too much outside being seeped into bearing simultaneously; Grease in cavity also possesses prevention foreign matter and enters Bearing inner effect.
Carried out the process of pressing and bending in the middle part of the skeleton 91 of described seal ring 27, dogleg section 93 as shown in Figure 9.This deformation process, effectively enhances the intensity of skeleton.Seal ring 27 press-fits in the seal groove 35 of bearing outer ring 20 (as shown in Figure 3), keeps geo-stationary with bearing outer ring 20, and the radial dimension of seal groove 35 is less than the outside dimension of seal ring 27, takes radial interference fit, makes seal ring and outer ring keep static; The width of seal groove 35 is greater than the external width of seal ring 27, and the fluorine rubber that radial fit can be produced distortion is placed in seal groove completely, avoids the generation of the flaws such as raw flange.
Connect formula fan clutch bearing to the integral shaft shown in Fig. 2 below and carry out analytical calculation, the integral shaft in Fig. 2 connects formula fan clutch bearing and comprises the left end roller 24 of bearing front end and the double row angular contact steel ball 25 of bearing rear end.
When the roller 24 stressed Fa=3743N of bearing front end (Dynamic factor by K=2.5 select get), the dynamic load rating of the every row roller of bearing is 79570N, and bearing life and Calculation of Reliability are analyzed as follows:
A. the mathematic(al) expectation of left end roller is:
1. L
10: the life-span of 90% reliability lower bearing
The reliability correction factor of bearing is 1 under 90% reliability
L
10=(C/P)
10/3× 10
6/ (60 × n) hour
=（79570/3743)
10/3×1000000/（60×2600）
=170597 hours
Wherein: n: bearing working rotating speed (r.p.m)
C: bearing dynamic load rating (N)
P: bearing Equivalent Dynamic Load (N)
2. L
1m: the life-span of 99% reliability lower bearing is:
Bearing reliability correction factor is 0.25 under 99%99% reliability
L
1m=L
10* 0.25=170597*0.25=42649 hour
3. L
0.05m:the life-span of 99.95% reliability lower bearing is:
L
0.05m=L
10* 0.077
=170597*0.077=13135 hour
From calculating, when reliability up to 99.95% time, the life-span of bearing roller end can reach 13135 hours, can meet the requirements of life and reliability.
B. steel ball end life-span computational analysis: right-hand member is double row angular contact spherical structure, bearing dynamic load rating Cr is 52570N, calculation bearing radial load Fb=1718N, this calculating take roller as fulcrum, utilize lever principle to calculate gained, Dynamic factor calculates by 2.5, and axial load is 1500N.
Equivalent load is P=0.67*1718+1.41*1500=3266N
Wherein 1718 be steel ball bear radial load, 0.67 is equivalent load correction factor; 1500 is axial loads that steel ball bears, and 1.41 is equivalent load correction factors.
A) L
10: the life-span of 90% reliability lower bearing
Be 1 during bearing reliability correction factor 90%
L
10=10
6 /(60×n)（Cr/ P）
3
=10
6 /(60×2600)（52570/ 3266）
3
=26732 hours
Wherein: n: bearing working rotating speed (r.p.m)
From computational analysis, in this kind of scheme, the roller step bearing rating life is 170597 hours, and the life-span when reliability is 99% is 42649 hours; The steel ball end rating life is 26732 hours.
In sum, be embodiment of the present invention content, and obviously embodiments of the present invention are not limited in this, it can according to different application environment, utilizes of the present inventionly functionally to realize corresponding demand.
Claims (10)
1. integral shaft connects a formula fan clutch bearing, and this bearing adopts row roller and a Double-row ball, Double-row ball geometric format adopts angle contacting structure, it is characterized in that, this bearing comprises:
Bearing outer ring, this bearing outer ring is processed with raceway groove and raceway, for carrying the rotation with orienting roll kinetoplast; Described rolling element comprises steel ball and cylindrical roller;
Mandrel, this mandrel axially inserts bearing outer ring, outside diameter of mandrel is processed with interior raceway groove, for carrying and guide the rotation of steel ball; Outside diameter of mandrel is also processed with interior raceway, for carrying cylindrical roller;
Ball retainer, this ball retainer is arranged between bearing outer ring and mandrel, and steel ball is equidistantly distributed in raceway groove;
Roller cage, this roller cage adopts tubular construction to add the structural design of check ring, and the cooperation of this check ring is assemblied on bearing outer ring, prevents cylindrical roller from scurrying out vertically;
Seal ring, sealing circle press-fits in the seal groove of bearing outer ring end, keeps static with bearing outer ring.
2. integral shaft according to claim 1 connects formula fan clutch bearing, it is characterized in that, described bearing outer ring is also processed with annular groove and raceway grinding undercut, snap ring is equipped with in annular groove, the external diameter of described bearing outer ring is assemblied in bearing support or a few bore, plays benchmark effect, when bearing operation, outer ring maintains static, and bears the power that mandrel transmission comes.
3. integral shaft according to claim 2 connects formula fan clutch bearing, it is characterized in that, described mandrel is processed with several steps, for assembling belt pulley and/or clutch, realizes the transmission of torque; The ditch heart on described mandrel between adjacent two interior raceway grooves is apart from being 15.05 ± 0.02mm, and the ditch heart distance on described bearing outer ring between adjacent two raceway grooves is 15.5 ± 0.02mm.
4. integral shaft according to claim 3 connects formula fan clutch bearing, it is characterized in that, described steel ball material is GCr15 high-quality high-carbon-chromium bearing steel, steel ball adopts the structure of double row angular contact steel ball, steel ball size is 13.494mm, often row 8 steel balls, wrapping angle is 25 °, and two row steel balls arrange back-to-back.
5. integral shaft according to claim 4 connects formula fan clutch bearing, it is characterized in that, described ball retainer material is for strengthening nylon+25% glass fibre.
6. integral shaft according to claim 5 connects formula fan clutch bearing, it is characterized in that, described cylindrical roller material is GCr15 high-quality high-carbon-chromium bearing steel, interior raceway on cylindrical roller and mandrel and the raceway on bearing outer ring are linear contact lay, the chamfering of cylindrical roller is designed with cavetto transition processing with its external diameter transition portion, makes cylindrical roller with convexity.
7. integral shaft according to claim 6 connects formula fan clutch bearing, it is characterized in that, described roller cage makes cylindrical roller equidistantly be distributed in raceway and guides cylindrical roller to move in a circle along raceway, and roller cage material is for strengthening nylon+25% glass fibre.
8. integral shaft according to claim 1 connects formula fan clutch bearing, it is characterized in that, described check ring adopts domatic opening and both sides groove angle is inconsistent, the side that during installation, groove angle is less is introduced into the circlip groove be arranged on bearing outer ring, and during taking-up, the less side of groove angle is finally ejected.
9. integral shaft according to claim 1 connects formula fan clutch bearing, it is characterized in that, the framework material of described seal ring is OCr18NI9Ti stainless steel, sealing material is fluorine rubber, seal ring adopt dual lip configuration and lips all with mandrel interference fit, the magnitude of interference of outer lip is greater than the magnitude of interference of inner lip, forms cavity zone between outer lip and inner lip, for preserving the lubricant oil oozed out.
10. integral shaft according to claim 9 connects formula fan clutch bearing, it is characterized in that, the process of pressing and bending has been carried out in the middle part of the skeleton of described seal ring, seal ring press-fits in the seal groove of bearing outer ring, geo-stationary is kept with outer ring, the radial dimension of seal groove is less than seal ring outside dimension, and the width of seal groove is greater than the external width of seal ring.
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| CN201510188095.9A CN104791289B (en) | 2015-04-21 | 2015-04-21 | A kind of integral shaft connects formula fan clutch bearing |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105673681A (en) * | 2016-04-12 | 2016-06-15 | 宁波市镇海银球轴承有限公司 | Novel connected bearing |
| CN107989818A (en) * | 2017-11-29 | 2018-05-04 | 河南科技大学 | A kind of W2B types water pump shaft connecting bearings and its durability analysis method |
| CN110513391A (en) * | 2019-08-29 | 2019-11-29 | 宁波市镇海银球轴承有限公司 | The two sides for having O-ring to pre-tighten seals double outer rings long axis two-row ball bearing |
| CN115492858A (en) * | 2022-09-29 | 2022-12-20 | 临清市海滨轴承制造有限公司 | High-speed precise heavy-duty bearing combined type rolling body |
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| CN202673433U (en) * | 2012-05-21 | 2013-01-16 | 龙口市汽车风扇离合器厂 | Integral type housing electromagnetic fan clutch |
| CN202883084U (en) * | 2012-10-23 | 2013-04-17 | 龙口市汽车风扇离合器厂 | Water pump electromagnetism fan clutch assembly |
| CN103790950A (en) * | 2012-10-31 | 2014-05-14 | 瓦房店福斯特轴承科技开发有限公司 | Double-row variable combined bearing |
| CN203641071U (en) * | 2013-10-22 | 2014-06-11 | 浙江省新昌新轴实业有限公司 | Double-row annular-contact water pump shaft coupling bearing with external spline on shaft |
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| CN2150340Y (en) * | 1993-03-31 | 1993-12-22 | 张晶 | Fan clutch for water-cooling system of engine |
| CN101852247A (en) * | 2009-03-25 | 2010-10-06 | Skf公司 | Be used in particular for the double-row conical bearing of supporting wind power generation set rotor shaft |
| CN201475158U (en) * | 2009-07-27 | 2010-05-19 | 杭州华星轴承有限公司 | Clutch bearing of automobile silicone oil fan |
| CN202673433U (en) * | 2012-05-21 | 2013-01-16 | 龙口市汽车风扇离合器厂 | Integral type housing electromagnetic fan clutch |
| CN202883084U (en) * | 2012-10-23 | 2013-04-17 | 龙口市汽车风扇离合器厂 | Water pump electromagnetism fan clutch assembly |
| CN103790950A (en) * | 2012-10-31 | 2014-05-14 | 瓦房店福斯特轴承科技开发有限公司 | Double-row variable combined bearing |
| CN203641071U (en) * | 2013-10-22 | 2014-06-11 | 浙江省新昌新轴实业有限公司 | Double-row annular-contact water pump shaft coupling bearing with external spline on shaft |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105673681A (en) * | 2016-04-12 | 2016-06-15 | 宁波市镇海银球轴承有限公司 | Novel connected bearing |
| CN107989818A (en) * | 2017-11-29 | 2018-05-04 | 河南科技大学 | A kind of W2B types water pump shaft connecting bearings and its durability analysis method |
| CN110513391A (en) * | 2019-08-29 | 2019-11-29 | 宁波市镇海银球轴承有限公司 | The two sides for having O-ring to pre-tighten seals double outer rings long axis two-row ball bearing |
| CN115492858A (en) * | 2022-09-29 | 2022-12-20 | 临清市海滨轴承制造有限公司 | High-speed precise heavy-duty bearing combined type rolling body |
| CN115492858B (en) * | 2022-09-29 | 2023-04-18 | 临清市海滨轴承制造有限公司 | High-speed precise heavy-duty bearing combined rolling body |
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| Publication number | Publication date |
|---|---|
| CN104791289B (en) | 2016-01-20 |
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Address after: The Haihe River Road Pizhou city Jiangsu province 221300 Xuzhou City Economic Development Zone Xuzhou Deyuan Auto Parts Manufacturing Co. Ltd Patentee after: Xuzhou Youli Tongchuang Polytron Technologies Inc Address before: The Haihe River Road Pizhou city Jiangsu province 221300 Xuzhou City Economic Development Zone Xuzhou Deyuan Auto Parts Manufacturing Co. Ltd Patentee before: Xuzhou De Yuan auto parts and components Manufacturing Co., Ltd |
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Effective date of registration: 20171220 Address after: 410215 Changsha economic and Technological Development Zone, Changsha, Hunan Province, No. 1, No. 31, No. 31 industrial city, 3 Building Patentee after: Changsha Youli Electric Drive System Co. Ltd. Address before: The Haihe River Road Pizhou city Jiangsu province 221300 Xuzhou City Economic Development Zone Xuzhou Deyuan Auto Parts Manufacturing Co. Ltd Patentee before: Xuzhou Youli Tongchuang Polytron Technologies Inc |