CN104879379A - Integral coupled fan clutch bearing - Google Patents
Integral coupled fan clutch bearing Download PDFInfo
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- CN104879379A CN104879379A CN201510188102.5A CN201510188102A CN104879379A CN 104879379 A CN104879379 A CN 104879379A CN 201510188102 A CN201510188102 A CN 201510188102A CN 104879379 A CN104879379 A CN 104879379A
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Abstract
The invention discloses an integral coupled fan clutch bearing, a main body structure of which is also applicable to a coupled bearing of an automobile water pump. The bearing comprises double-row rollers and single-row steel balls, and comprises an bearing outer ring, a mandrel, a steel ball retainer, a roller retainer and a seal ring, wherein a groove and a roller path are formed in the bearing outer ring for bearing rolling elements and guiding the rotation of the rolling elements, the rolling elements comprise steel balls and cylindrical rollers, the mandrel is axially inserted into the bearing outer ring, an inner groove is formed in the outer diameter of the mandrel and is used for bearing the steel balls and guiding rotation of the steel balls, an inner roller path is formed in the outer diameter of the mandrel and is used for bearing the cylindrical rollers, the steel ball retainer is arranged between the bearing outer ring and the mandrel, and is used for enabling the steel balls to be evenly distributed in the groove at intervals, the roller retainer adopts the structural design of a barrel-shaped structure and a spring collar, the spring collar is assembled on the bearing outer ring in a matching manner for preventing the cylindrical rollers from jumping out along the axial direction, and the seal ring is pressed into a seal groove in the end part of the bearing outer ring and keeps the stationary state 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 agent structure is equally applicable to auto pump shaft connecting bearing, and this bearing adopts biserial roller and single-row steel ball, single-row steel ball geometric format adopts angle contacting structure, for bearing thrust load; Biserial roller is used for bearing radial load; 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 single-row steel ball is arranged in the neutral position of biserial roller, and biserial roller is arranged as at each row in the left side of single-row steel ball and right side.
Described bearing outer ring is also processed with annular groove and raceway grinding undercut, is equipped with snap ring in annular groove, the external diameter of described bearing outer ring is assemblied in bearing support or a few bore, play benchmark effect, when bearing operation, outer ring maintains static, and bears the power that mandrel transmission comes.
Interior raceway groove in raceway groove on described bearing outer ring and outside diameter of mandrel is peach-shaped ditch, and the position of raceway groove and interior raceway groove is corresponding, and when bearing outer ring and mandrel have been assembled, raceway groove and interior raceway groove make the steel ball of bearing produce the wrapping angle of 25 °.
Described mandrel being processed with several steps, for assembling belt pulley and/or clutch, realizing the transmission of torque.
Described steel ball material is GCr15 high-quality high-carbon-chromium bearing steel, and steel ball adopts the structure of single-row angle contacting steel ball, and steel ball size is 13.494mm(that is 17/32 inch), single-row 8 steel balls, wrapping angle is 25 °.
Described ball retainer material is for strengthening nylon+25% glass fibre.
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.
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 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 effectively increases bearing capacity and the unfailing performance of shaft connecting bearing, makes bearing have better rigidity, reduces the load that bearing bears, add the life-span of bearing, improves stable, the Security of a whole set of bearing.
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.
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 biserial roller and single-row steel ball, single-row steel ball geometric format adopts angle contacting structure, for bearing thrust load; Biserial roller is used for bearing radial load, 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 42,422, for carrying cylindrical roller 24;
Ball retainer 22, as shown in Figure 2, 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 and Fig. 8, 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 2, described single-row steel ball 25 is arranged in the neutral position of biserial roller 24,244, and biserial roller 24,244 is arranged as at each row in the left side of single-row steel ball 25 and right side.
As shown in Figure 3, described bearing outer ring 20 is also processed with circlip groove 33 and raceway grinding undercut 34 and the auxiliary slot such as seal groove 35 and annular groove; Seal groove 35 is used for fitting tight circle 27, seals; Be equipped with snap ring 26,266(in annular groove and see accompanying drawing 2), 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 mandrel 21 being processed with several steps 43,44, for assembling belt pulley and/or clutch, realizing 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 42,422.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.Interior raceway groove 41 on raceway groove 31 on described bearing outer ring 20 and the external diameter of mandrel 21 is peach-shaped ditch, the position of raceway groove 31 and interior raceway groove 41 is corresponding, when bearing outer ring 20 and mandrel 21 have been assembled, raceway groove 31 and interior raceway groove 41 have made the steel ball 25 of bearing produce the wrapping angle of 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 single-row angle contacting steel ball, and steel ball size is 13.494mm, and single-row 8 steel balls, wrapping angle is 25 °.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 avoiding producing friction and heating 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.
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.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.Interior raceway on cylindrical roller and mandrel and the raceway on bearing outer ring 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, and 244 to be equidistantly distributed in raceway and to guide 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 80 (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 groove angle of 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 single-row angle contacting steel ball 25 between biserial roller 24,244 and biserial roller.
When the stressed Fa=3743N of roller (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 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
=（79570/3751)
10/3×1000000/（60*2600）
=169388 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:
Be 0.25 during bearing reliability correction factor 99%
L
1m=L
10* 0.25=169388*0.25=42347 hour
3. L
0.05m:the life-span of 99.95% reliability lower bearing is:
L
0.05m=L
10* 0.077=169388*0.077=13042 hour
From calculating, when reliability up to 99.95% time, the life-span of bearing roller end can reach 13042 hours, can meet the requirements of life and reliability.
B. steel ball end life-span computational analysis: be single-row angular contact ball structure between biserial roller, in view of domestic at present, temporary gear shaper without theoretical foundation is calculated for the life and reliability of 4 angular contact ball bearings when bearing pure thrust load, therefore we are with reference to the correlation technique analysis of Japanese NSK company, when thrust load that bearing bears is 1500N, the mathematic(al) expectation of steel ball end is:
1. .L
10: the life-span of 90% reliability lower bearing
Bearing reliability correction factor is 1 under 90% reliability
L
10=10
6 /(60×n) ×（Ca/ Fa）
3
=10
6 /(60×n) ×[2.37tanα(1-0.333sinα) Cr/ Fa]
3
=41249 hours
Wherein: n: bearing working rotating speed (r.p.m)
Ca: bearing shaft is to dynamic load rating (N)
Fa: bearing axial load (N)
Cr: the radial dynamic load rating (N) of bearing
2.37tan α (1-0.333sin α) is radial Dynamic factor, for only by axial force situation, (steel ball force in radial is very little by the force simplified of steel ball herein, can ignore) stressed for steel ball resolve into normal direction stressed after conversion, α is wrapping angle.
2. .L
1: the life-span of 99% reliability lower bearing is:
Bearing reliability correction factor is 0.25 under 99% reliability
L
1=L
10* 0.25=41249*0.25=10312 hour
From computational analysis, in this scheme of the present invention, the roller step bearing rating life is 169388 hours (see the L that preceding step a calculates
10), the life-span when reliability is 99% is 42347 hours (see the L that preceding step a calculates
1m); Mathematic(al) expectation under 99% reliability situation in steel ball end life-span is 10312 hours, reaches desired life requirements.
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, it is characterized in that, this bearing adopts biserial roller and single-row steel ball, single-row steel ball geometric format adopts angle contacting structure, for bearing thrust load; Biserial roller is used for bearing radial load; 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 single-row steel ball is arranged in the neutral position of biserial roller, and biserial roller is arranged as at each row in the left side of single-row steel ball and right side.
3. integral shaft according to claim 2 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.
4. integral shaft according to claim 3 connects formula fan clutch bearing, it is characterized in that, interior raceway groove in raceway groove on described bearing outer ring and outside diameter of mandrel is peach-shaped ditch, the position of raceway groove and interior raceway groove is corresponding, when bearing outer ring and mandrel have been assembled, raceway groove and interior raceway groove have made the steel ball of bearing produce the wrapping angle of 25 °.
5. integral shaft according to claim 4 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.
6. integral shaft according to claim 5 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 single-row angle contacting steel ball, steel ball size is 13.494mm, and single-row 8 steel balls, wrapping angle is 25 °.
7. integral shaft according to claim 6 connects formula fan clutch bearing, it is characterized in that, described ball retainer material is for strengthening nylon+25% glass fibre; 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; 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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| CN201510188102.5A CN104879379B (en) | 2015-04-21 | 2015-04-21 | A kind of integral shaft connects formula fan clutch bearing |
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| CN201510188102.5A CN104879379B (en) | 2015-04-21 | 2015-04-21 | A kind of integral shaft connects formula fan clutch bearing |
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Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106438730A (en) * | 2016-11-10 | 2017-02-22 | 广东历宏机械有限公司 | Gluing flange for automatic edge bander |
| CN107086705A (en) * | 2017-05-27 | 2017-08-22 | 杭州驰创机械有限公司 | A kind of brushless, permanently high-speed electric expreess locomotive of use integral 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 |
| CN108009342A (en) * | 2017-11-29 | 2018-05-08 | 河南科技大学 | A kind of W2R types shaft connecting bearing and its load distributional analysis method |
| CN108009342B (en) * | 2017-11-29 | 2019-08-16 | 河南科技大学 | A kind of W2R type shaft connecting bearing and its load distributional analysis method |
| CN108167218A (en) * | 2017-12-26 | 2018-06-15 | 新昌县江北轴承有限公司 | A kind of dust-proof double-row angular contact bal bearing of water pump high load |
| US10837488B2 (en) | 2018-07-24 | 2020-11-17 | Roller Bearing Company Of America, Inc. | Roller bearing assembly for use in a fracking pump crank shaft |
| CN108930719A (en) * | 2018-08-21 | 2018-12-04 | 无锡诚石轴承有限公司 | A kind of precision bearing of gardens seeder |
| CN112610596A (en) * | 2020-12-14 | 2021-04-06 | 人本股份有限公司 | Water pump 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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| CN104879379B (en) | 2016-02-24 |
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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 |