CN116644611A - Design method of hub bearing flange riveting structure and spin riveting tool design method - Google Patents
Design method of hub bearing flange riveting structure and spin riveting tool design method Download PDFInfo
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Abstract
The application relates to the technical field of hub bearing design, and particularly discloses a hub bearing flange riveting structure design method which comprises the following steps: s1, determining the boundary size of a riveting structure according to requirements; s2, calculating the maximum axial force F born by the hub bearing according to the vehicle parameters a The method comprises the steps of carrying out a first treatment on the surface of the S3, applying F which is more than or equal to 2 times on the hub bearing with the non-riveted structure a The axial clamping force F of the small inner ring on the hub bearing under the non-riveted structure is obtained 3 The method comprises the steps of carrying out a first treatment on the surface of the S4, through the axial displacement M 3 To formulate the riveting parameters of the spin riveting equipment to obtain the axial displacement M 3 Is a riveted structure. The spin riveting tool design method comprises the following steps: according to the size after rivetingExternal diameter size of riveting position before inner ring rivetingAnd bore sizeAccording toAndand determining the size of the riveting tool. The scheme is used for solving the problem that the prior hub bearing flange riveting structure has loosening of spin riveting pretension or the phenomenon that the hub bearing is loose or a channel heats and fails in advance due to excessive spin riveting pretension.
Description
Technical Field
The application relates to the technical field of hub bearing design, in particular to a hub bearing flange riveting structure design method and a spin riveting tool design method.
Background
Along with the increasing competition of the automobile market, the requirements of a host factory on energy conservation, reliability, light weight and cost of automobile rotating parts are higher and higher, and the third-generation hub bearing is particularly favored by the market as a key rotating part of the whole automobile chassis. The third-generation hub bearing assembly with the riveting structure integrates the inner ring, the outer ring, the rolling body, the retainer and the sealing piece and has the pre-tightening function, and the hub bearing assembly is not connected by a lock nut. In recent years, some famous bearing enterprises at home and abroad successively develop hub bearing units with riveted structures, and because the core spin riveting design process technology is not mastered, a large number of trial-produced parts are required to carry out test verification in a new product development stage, the project development period is prolonged, and manpower and material resources are occupied; meanwhile, the quality of the produced third-generation hub bearing unit is unstable, and the following problems occur: the spin riveting working plane is unstable in one-step molding, cannot meet the requirements of clients, and can be finished only by secondary machining; spin riveting pretension loosens, and the hub bearing generates looseness in the later stage of use; the spin riveting is excessive in pretightening, and the channel of the hub bearing is seriously heated in the use process, so that the phenomenon of early failure occurs. Up to now, no design method for a hub bearing riveting structure exists in the prior art, therefore, the application provides a design method for a hub bearing flange riveting structure to solve the problems and fill the technical blank in the field.
Disclosure of Invention
The application aims to provide a design method of a hub bearing flange riveting structure, which aims to solve the problem that the hub bearing is loose or a channel is heated to fail in advance due to loosening of spin riveting or excessive spin riveting of the existing hub bearing flange riveting structure.
In order to achieve the above purpose, the application adopts the following technical scheme:
the design method of the hub bearing flange riveting structure comprises the following steps:
s1, determining the maximum value of the outer diameter dimension of the riveted structure after riveting according to requirementsMinimum value of the bore size->And minimum value M of plane width of riveted structure min ；
S2, calculating the maximum axial force F born by a spin riveting side channel of the hub bearing according to the vehicle body parameters of the vehicle applying the hub bearing a ；
S3, applying F which is more than or equal to 2 times on the hub bearing with the non-riveted structure a The axial clamping force F of the small inner ring on the hub bearing under the non-riveted structure is obtained 3 ；
S4, through the axial displacement M 3 To formulate the riveting parameters of the spin riveting equipment to obtain the axial displacement M 3 Is riveted with the structure, the outside diameter of the riveted structure isThe inner hole size is +.>And the plane width dimension of the riveting structure is M 1 。
Principle of the schemeThe advantages are that: in the scheme, when the hub bearing flange riveting structure is designed, the hub bearing with the non-riveting structure simulates 2 times F a The lower axial clamping force F is used for obtaining the displacement M of the small inner ring under the axial clamping force F 3 The method comprises the steps of carrying out a first treatment on the surface of the By setting the axial clamping force F to a maximum axial force F not less than 2 times a Ensuring that the axial clamping force is not too small or too loose; the spin riveting equipment ensures that the small inner ring achieves the same displacement M after spin riveting 3 When the axial clamping force F applied to the small inner ring by the riveting structure is equal to the axial clamping force F, the situation that the axial clamping force F is too small to loosen is avoided, and the situation that the axial clamping force is too large to cause the heating of a channel to fail in advance is avoided.
In addition, in the prior hub bearing with the riveting structure, after the hub bearing is manufactured, firstly detecting the withdrawal force of the riveting structure of the hub bearing, generally adopting (5-10) tons of axial force to act on the riveting structure, and taking the change value of the axial play as a judgment standard to detect whether the riveting structure can meet the requirement for the first time; the service condition of the hub bearing is verified by taking the bearing life tester and adopting an axial and radial loading mode, but the service life test of the hub bearing takes longer time and generally takes more than 300 hours; when the design of the hub bearing does not reach the standard, the size of the riveting structure of the hub bearing needs to be modified again, and the hub bearing is manufactured again for service life verification, so that the development time of the hub bearing is very long. In the scheme, the maximum axial force F applied to the spin-rivet side channel a As the reference force of the axial clamping force of the riveting structure, the hub bearing with the non-riveting structure can quickly know the axial clamping force of the locking nut to the small inner ring by installing the locking nut on the shaft, so that the same axial displacement M is equivalently obtained 3 The axial clamping force is considered immediately before the hub bearing riveting structure is manufactured, so that the designed and processed hub bearing is higher in reliability, safety and service life, and the hub bearing designed and processed by the method is verified to be basically capable of ensuring that one-time development is successful without multiple size adjustment and multiple size adjustment of the hub bearingAnd the service life of the secondary bearing is tested, so that the development period of the product is greatly shortened, and the design cost is reduced.
Preferably, as a modification, in step S4, if the size range of the riveting structure does not meet the S1 requirement, then adjusting F and repeating step S3 and/or adjusting the riveting parameters until the requirements of step S3 and step S1 are met.
Preferably, in step S2, a maximum axial force W of the hub bearing is calculated from the vehicle body parameters of the vehicle to which the hub bearing is applied t And maximum radial force W r Then according to the maximum axial force W t And maximum radial force W r Calculating the maximum axial force F born by the spin riveting side channel of the hub bearing a 。
Preferably, as an improvement, the maximum axial force W of the hub bearing t And maximum radial force W r The relationship of (2) is as follows:
W r ＝f w ·(W/2+G·W·H/T)
W t ＝G·W r
w: axle load; t: wheel tread; h: the gravity center is high under the full load of the vehicle; r: wheel rolling radius;
W r : radial road surface reaction force; w (W) t : axial road surface reaction force; f (f) w : impact coefficient; g: vehicle cornering acceleration design maximum.
Preferably, as a modification, according to the maximum axial force W t And maximum radial force W r Calculating the maximum axial force F born by the spin riveting side channel of the hub bearing a The following are provided:
F a ＝e·W t
F a : maximum axial load of the spin-rivet side channel; e: the axial force coefficient is derived and is determined by radial force, contact angle and play.
Preferably, as a modification, the hub bearing is subjected to a maximum axial force F on the spin-rivet side channel a Also has the following formula:
F a ＝e·W t ＝F r /2Y+W t
F r ＝|a/L×W r +R/L×W t |
F r : maximum radial load of the spin-rivet side channel; a: the distance from the intersection point of the connecting line of the action point of the steel ball on the non-spin riveting side and the central axis of the hub bearing to the center of the wheel; l: the span of two rows of steel balls; the contact angle of the steel ball on the hub bearing is 35 degrees, and then the value of Y is 0.66; and when the contact angle of the steel ball is 40 degrees, the value of Y is 0.57.
Preferably, as an improvement, the method further comprises step S5: maximum axial force W based on hub bearing t Maximum radial force W r According to the design specification of the bearing, the rolling body diameter and the minimum wall thickness of the small inner ring of the hub bearing are determined, the minimum wall thickness d of the small inner ring is more than or equal to 4mm, and the specific requirements for the rolling body diameter are as follows:
for the hub bearing adopting the steel balls for the rolling bodies, the requirement of M is met Ditch 1 ≥1.2·D w1 Wherein M is Ditch 1 D is the distance between the side end face of the small inner ring close to the riveting structure and the center of the channel w1 The diameter of the steel ball;
for a hub bearing with rollers for rolling bodies, the requirement of M is met Ditch 2 ≥0.45·D w2 Wherein M is Ditch 2 D, the minimum distance between the side end face of the small inner ring close to the riveting structure and the groove is D w2 The diameter of the roller is large.
The beneficial effects are that: in the prior art, the spin riveting equipment generates plastic deformation on the flange of the inner ring of the hub with larger riveting force to form a riveting structure, the riveting structure is finally formed according to the shape of the rivet head of the riveting tool, and the maximum riveting pressure of the spin riveting equipment reaches 18 tons once in the process, so that a channel close to the riveting side of the hub bearing generates slight plastic deformation at a rolling body contact point, and meanwhile, the roundness of the channel is damaged, thereby reducing the rotation precision of the hub bearing and enabling the hub bearing to generate NVH noise at low frequency. Under the covering of engine booming noise, the traditional fuel oil vehicle can not be identified by the human ear when a user drives in the vehicle, but can identify low-frequency abnormal sound of buzzing when driving a new energy electric vehicle. According to the scheme, through the dimensional design of the upper channel and the rolling body of the inner structure of the hub bearing, the hub bearing with the riveting structure has lower vibration value, higher rotation precision and longer service life, the problem caused by determining the position of the roller path by using experience in the traditional method is avoided, and the design of the hub bearing is more reasonable.
Preferably, as an improvement, in the step S3, a hub bearing with a non-riveted structure is mounted on the shaft, a lock nut is mounted on the small inner ring side, the lock nut pushes the small inner ring to apply an axial clamping force F, and during screwing of the lock nut, an axial displacement of the small inner ring and a torque N of the lock nut are recorded, wherein a relationship between the torque N and the axial clamping force F is as follows:
N＝μ·F·D
n: torque of the lock nut; mu: the friction coefficient is 0.18-0.19; f: an axial clamping force; d: the lock nut has a nominal diameter.
The beneficial effects are that: the axial clamping force of the hub bearing with the non-riveted structure is calculated more simply and conveniently by adopting the scheme.
The application also provides a spin riveting tool design method, which needs to adopt the design method of the hub bearing flange riveting structure to obtain the external diameter size of the riveted structure after riveting as followsThe inner hole size is +.>And the plane width dimension of the riveting structure is M 1 The method also comprises the following steps:
step A, according to the outside diameter of the riveted structure after riveting, the outside diameter isThe inner hole size is +.>And the plane width dimension of the riveting structure is M 1 Determining the outer diameter of the riveting position before the inner ring is riveted>And the inner hole size of the riveting position before the inner ring is riveted +.>
Step B, according toAnd->Determining the outer diameter of the end part of the convex column inserted into the inner ring on the riveting tool>The inclination angle alpha of the outer periphery of the convex column and the minor diameter of the root of the convex column>Large diameter of convex column root +.>
Preferably, in the step B, in the step A, as a modificationAnd->After the dimensioning, if the dimension of the spin-rivet cannot be satisfied +.>M min And the axial clamping force F, adjusting +.>Alpha and chamfer R of the root of the convex column 1 The dimension after spin riveting is enabled to be +>M 1 Reaching an optimal value.
By adopting the spin riveting tool design method, the design of the spin riveting tool is simpler and faster, and the probability of one-time qualified forming of the spin riveting working plane of the hub bearing is greatly improved.
Drawings
FIG. 1 shows the boundary dimensions of a rivet structure according to an embodiment of the present applicationAnd M min Is a schematic diagram of (a).
FIG. 2 shows a displacement M of a hub bearing mounting lock nut prior to staking in accordance with an embodiment of the present application 3 Schematic structural diagram during test.
FIG. 3 shows the size of the riveting structure according to the first embodiment of the present applicationAnd M 1 Is a schematic diagram of (a).
Fig. 4 is a schematic diagram of a size mark of a hub bearing according to a second embodiment of the present application.
Fig. 5 is a schematic diagram of a cross section of a channel of a hub bearing employing steel balls at a spin-rivet end for rolling bodies according to a second embodiment of the present application.
Fig. 6 is a schematic diagram of a cross section of a channel of a hub bearing employing tapered rollers for rolling elements at a spin-rivet end according to a second embodiment of the present application.
FIG. 7 is a schematic illustration of the dimensions of the inner race of a hub bearing prior to staking in accordance with a third embodiment of the present application.
Fig. 8 is a schematic dimensional diagram of a riveting tool according to a third embodiment of the application.
Detailed Description
The following is a further detailed description of the embodiments:
reference numerals in the drawings of the specification include: an inner ring 1 with a riveting structure, a small inner ring 2 and a spin riveting tool 3.
An embodiment substantially as shown in figures 1 to 3 of the accompanying drawings.
Referring to fig. 1, the design method of the hub bearing flange riveting structure comprises the following steps:
s1, determining the maximum value of the outer diameter size of the riveted structure after riveting according to the installation size requirement of a customerMinimum value of the bore size->And minimum value M of plane width of riveted structure min (i.e., the size of the rivet structure shown in FIG. 1);
s2, calculating the maximum axial force W of the hub bearing according to the vehicle body parameters of the vehicle applying the hub bearing t And maximum radial force W r The method is characterized by comprising the following steps:
W r ＝f w ·(W/2+G·W·H/T)；
W t ＝G·W r ；
w: axle load/N; t: wheel track/mm; h: the height/mm of the gravity center of the vehicle under full load; r: wheel rolling radius/mm;
W r : radial road reaction force/N; w (W) t : axial road surface reaction force/N; f (f) w : the impact coefficient is 1-1.5 according to the road spectrum working condition; the corresponding road spectrum conditions comprise a good road surface, a bumpy road surface, a cobble surface, a convex-concave road surface and a deceleration strip road surface, and the different road surfaces have different values, specifically: good road surface value 1, bumpy road surface value 1.1, cobble road surface value 1.3, convex-concave road surface value 1.5 and deceleration strip road surface 1.2; g: vehicle cornering acceleration design maximum.
Then according to the maximum axial force W t And maximum radial force W r Calculating the maximum axial force F of the spin riveting side channel of the hub bearing under 0.8 times of turning acceleration a And maximum radial force F r The method is characterized by comprising the following steps:
F r ＝|a/L×W r +R/L×W t |；
F a ＝e·W t ＝F r /2Y+W t ；
F r : maximum radial load/N of the spin-rivet side channel; f (F) a : maximum axial load/N of the spin-rivet side channel; a: the distance/mm from the intersection point of the connecting line of the action point of the steel ball on the non-spin riveting side and the central axis of the hub bearing to the center of the wheel; l: the span of the two rows of steel balls is/mm; e: deriving an axial force coefficient, which is determined by radial force, contact angle and play; the contact angle of the steel ball on the hub bearing is 35 degrees, and then the value of Y is 0.66; and when the contact angle of the steel ball is 40 degrees, the value of Y is 0.57.
S3, applying F which is more than or equal to 2 times on the hub bearing with the non-riveted structure a The axial clamping force F of the small inner ring on the hub bearing under the non-riveted structure is obtained 3 ；
The method comprises the following steps: the hub bearing before riveting, which is produced in the same batch, is taken, the hub bearing is arranged on a shaft, a lock nut is arranged on the side of a small inner ring (as shown in figure 2), the lock nut props against the small inner ring to apply an axial clamping force F, and in the screwing process of the lock nut, the axial displacement of the small inner ring and the torque N of the lock nut are recorded, and the relation between the torque N and the axial clamping force F is as follows:
N＝μ·F·D；
n: torque/Nmm of the lock nut; mu: the friction coefficient is 0.18-0.19; f: axial clamping force/N; d: the lock nut nominal diameter/mm.
S4, through the axial displacement M 3 To formulate the riveting parameters of the spin riveting equipment to obtain the axial displacement M 3 Is riveted with the structure, the outside diameter of the riveted structure isThe inner hole size is +.>And the plane width dimension of the riveting structure is M 1 (i.e., the size of the rivet structure shown in FIG. 3); and if the size range of the riveting structure does not meet the requirement of S1, adjusting F and repeating the step S3 and/or adjusting riveting parameters until the requirements of the step S3 and the step S1 are met.
By adopting the design method of the hub bearing flange riveting structure, the situation that the hub bearing riveting structure is loose in pretightening or excessive in pretightening can not occur after the hub bearing riveting structure is formed is ensured, the one-time development success rate of the hub bearing riveting structure is improved, the product development period is shortened, and the cost is reduced; the reliability, the safety and the service life of the hub bearing are improved, raw material consumption is reduced, and the energy-saving effect is achieved.
Example two
With reference to fig. 4 to 6, the second embodiment is further improved on the basis of the first embodiment, and specifically further includes the following steps:
step S5: the hub bearing appearance structure is designed based on customer requirements and wheel end peripheral installation space, and the hub bearing appearance size can be completely determined on the premise of giving the knuckle threaded hole position, the inner hole diameter, the knuckle installation surface-rim installation surface distance, the rim installation bolt position, the inner hole diameter, the brake disc matching inner hole, the driving shaft spline length, the locking center nut size and the wheel speed sensor installation position.
With reference to fig. 4, the external dimensions include: the outer diameter A of the outer flange, the position size (1) of the threaded hole of the outer flange, the position size (2) of the threaded hole or the bolt of the inner flange, the spin riveting outer diameter B of the inner flange, the mounting outer diameter C of the inner flange, the inner hole D, the distance E between the inner flange and the outer flange, the total height F of the hub bearing and the total height G of the outer ring.
Maximum axial force W based on hub bearing t Maximum radial force W r The external structure of the hub bearing constructs the internal dimension of the hub bearing according to the design specification of the double-row angular contact bearing, and the internal dimension of the hub bearing comprises the diameter D of the rolling bodies w The rolling element rolling device comprises a rolling element number (3), a retainer structure (4), a sealing ring structure, a sealing ring position (5), a rolling path center distance L of two rows of rolling elements, a rolling path position M and a minimum wall thickness d of a small inner ring.
The hub bearing has the advantages that the total height limits the center distance L of the roller path and the dimension M of the position of the roller path, and on the premise of meeting the design space of a sealing structure, the smaller the M value is, the better the bearing capacity of the bearing is. M is calculated from the following formula,
M＝(G-L)/2；
in order to eliminate the shaping deformation of the roller path in the spin riveting process, the minimum wall thickness d of the small inner ring is more than or equal to 4mm, and meanwhile, the specific requirements for determining the diameter of the rolling body are as follows:
with reference to FIG. 5, for a hub bearing with steel balls for the rolling elements, the requirement satisfies M Ditch 1 ≥1.2·D w1 Wherein M is Ditch 1 D is the distance between the side end face of the small inner ring close to the riveting structure and the center of the channel w1 The diameter of the steel ball is/mm;
referring to fig. 6, the hub bearing using tapered rollers for the rolling elements is required to satisfy M Ditch 2 ≥0.45·D w2 Wherein M is Ditch 2 D, the minimum distance between the side end face of the small inner ring close to the riveting structure and the groove is D w2 Is the roller big diameter/mm.
Example III
Referring to fig. 7 and 8, a third embodiment provides a spin riveting tool design method, in which the design method of the hub bearing flange riveting structure according to the first embodiment is required to obtain a riveted structure with an outer diameter ofThe inner hole size is +.>And the plane width dimension of the riveting structure is M 1 In obtaining->And M 1 After sizing, the following steps are performed:
step A, according to the outside diameter of the riveted structure after riveting, the outside diameter isThe inner hole size is +.>And the plane width dimension of the riveting structure is M 1 Determining the outer diameter of the riveting position before the inner ring is riveted>And the inner hole size of the riveting position before the inner ring is riveted +.>The specific relation is as follows:
step B, according toAnd->Determining the outer diameter of the end part of the convex column inserted into the inner ring on the riveting tool>The inclination angle alpha of the outer periphery of the convex column and the minor diameter of the root of the convex column>Large diameter of convex column root +.>The specific relation is as follows:
is subject to->M 1 Size changes, in this example +.>Wherein delta takes a value of 6mm;
the inclination angle alpha of the periphery of the convex column takes the value of 15-30 degrees;
chamfering R of the root of the convex column 1 The value is R4-R5.
In step B, in step AAnd->After the size is determined, if the size obtained by spin riveting cannot meet the requirementM min And the axial clamping force F, adjusting +.>Alpha and R 1 The dimension after spin riveting is enabled to be +>M 1 Reaching an optimal value.
In addition, in the embodiment, the material of the spin riveting tool is Cr12MoV, and the hardness is controlled between 61HRC and 65HRC by adopting low-temperature tempering after high-temperature quenching.
In the prior art, the one-step forming of the spin riveting working plane is unstable and is mainly characterized in that the requirement that the width of the spin riveting plane is more than or equal to 3mm cannot be met (the spin riveting plane is M in figure 2 1 Position), the flatness of the spin riveting plane is not more than 0.05mm, the runout of the spin riveting plane is not more than 0.05mm, and the roughness of the spin riveting plane is not metThe degree Ra is less than or equal to 0.32, and surface defects such as burrs, bulges, dents and the like can occur on the spin riveting plane, so that the product quality is affected; the embodiment makes the design of the spin riveting tool simpler and faster, and by the spin riveting tool/R 1 The determination of alpha solves the problem that the width of the spin-rivet plane does not reach the standard by aiming at ∈>The alpha is determined, so that the problems of flatness, runout, roughness, burrs and the like of the spin riveting plane are solved, and the once qualified forming probability of the spin riveting working plane of the hub bearing is greatly improved.
The foregoing is merely exemplary of the present application, and specific technical solutions and/or features that are well known in the art have not been described in detail herein. It should be noted that, for those skilled in the art, several variations and modifications can be made without departing from the technical solution of the present application, and these should also be regarded as the protection scope of the present application, which does not affect the effect of the implementation of the present application and the practical applicability of the patent. The protection scope of the present application is subject to the content of the claims, and the description of the specific embodiments and the like in the specification can be used for explaining the content of the claims.
Claims (10)
1. The design method of the hub bearing flange riveting structure is characterized by comprising the following steps of:
s1, determining the maximum value of the outer diameter dimension of the riveted structure after riveting according to requirementsMinimum value of the bore size->And minimum value M of plane width of riveted structure min ；
S2, according to a vehicle body parameter meter applying the hub bearingCalculating the maximum axial force F born by the spin riveting side channel of the hub bearing a ；
S3, applying F which is more than or equal to 2 times on the hub bearing with the non-riveted structure a The axial clamping force F of the small inner ring on the hub bearing under the non-riveted structure is obtained 3 ；
S4, through the axial displacement M 3 To formulate the riveting parameters of the spin riveting equipment to obtain the axial displacement M 3 Is riveted with the structure, the outside diameter of the riveted structure isThe inner hole size is +.>And the plane width dimension of the riveting structure is M 1 。
2. The method according to claim 1, wherein in step S4, if the size range of the rivet structure does not meet the S1 requirement, then F is adjusted and step S3 and/or the rivet parameters are repeated until the requirements of step S3 and step S1 are met.
3. The method according to claim 1, wherein in step S2, the maximum axial force W of the hub bearing is calculated according to the vehicle body parameters of the vehicle to which the hub bearing is applied t And maximum radial force W r Then according to the maximum axial force W t And maximum radial force W r Calculating the maximum axial force F born by the spin riveting side channel of the hub bearing a 。
4. A hub bearing flange riveting structure design method as claimed in claim 3, characterized in that the maximum axial force W of the hub bearing t And maximum radial force W r The relationship of (2) is as follows:
W r ＝f w ·(W/2+G·W·H/T)
W t ＝G·W r
w: axle load; t: wheel tread; h: the gravity center is high under the full load of the vehicle; r: wheel rolling radius;
W r : radial road surface reaction force; w (W) t : axial road surface reaction force; f (f) w : impact coefficient; g: vehicle cornering acceleration design maximum.
5. The method of claim 4, wherein the maximum axial force W is used to design the hub bearing flange rivet structure t And maximum radial force W r Calculating the maximum axial force F born by the spin riveting side channel of the hub bearing a The following are provided:
F a ＝e·W t
F a : maximum axial load of the spin-rivet side channel; e: the axial force coefficient is derived and is determined by radial force, contact angle and play.
6. The method for designing a rivet structure of a hub bearing flange as set forth in claim 5, characterized in that said hub bearing rivet side channel receives a maximum axial force F a Also has the following formula:
F a ＝e·W t ＝F r /2Y+W t
F r ＝|a/L×W r +R/L×W t |
F r : maximum radial load of the spin-rivet side channel; a: the distance from the intersection point of the connecting line of the action point of the steel ball on the non-spin riveting side and the central axis of the hub bearing to the center of the wheel; l: the span of two rows of steel balls; the contact angle of the steel ball on the hub bearing is 35 degrees, and then the value of Y is 0.66; and when the contact angle of the steel ball is 40 degrees, the value of Y is 0.57.
7. The hub bearing flange riveting structure design method as claimed in claim 4, further comprising step S5: maximum axial force W based on hub bearing t Maximum radial force W r The appearance structure of the hub bearing determines the hub bearing according to the design specification of the bearingThe diameter of the rolling body and the minimum wall thickness of the small inner ring are equal to or larger than 4mm, and the specific requirements of the diameter of the rolling body are as follows:
for the hub bearing adopting the steel balls for the rolling bodies, the requirement of M is met Ditch 1 ≥1.2·D w1 Wherein M is Ditch 1 D is the distance between the side end face of the small inner ring close to the riveting structure and the center of the channel w1 The diameter of the steel ball;
for a hub bearing with rollers for rolling bodies, the requirement of M is met Ditch 2 ≥0.45·D w2 Wherein M is Ditch 2 D, the minimum distance between the side end face of the small inner ring close to the riveting structure and the groove is D w2 The diameter of the roller is large.
8. The method according to claim 1, wherein in the step S3, the hub bearing of the non-riveted structure is mounted on the shaft, a lock nut is mounted on the small inner ring side, the lock nut pushes the small inner ring to apply the axial clamping force F, and during the screwing process of the lock nut, the axial displacement of the small inner ring and the torque N of the lock nut are recorded, and the relationship between the torque N and the axial clamping force F is as follows:
N＝μ·F·D
n: torque of the lock nut; mu: the friction coefficient is 0.18-0.19; f: an axial clamping force; d: the lock nut has a nominal diameter.
9. A spin riveting tool design method, characterized in that the design method of the hub bearing flange riveting structure according to any one of claims 1-8 is adopted to obtain the external diameter size of the riveted structure after rivetingThe inner hole size is +.>And the plane width dimension of the riveting structure is M 1 The method also comprises the following steps:
step A, according to the outer part of the riveted structure after rivetingThe diameter size isThe inner hole size is +.>And the plane width dimension of the riveting structure is M 1 Determining the outer diameter of the riveting position before the inner ring is riveted>And the inner hole size of the riveting position before the inner ring is riveted +.>
Step B, according toAnd->Determining the outer diameter of the end part of the convex column inserted into the inner ring on the riveting tool>The inclination angle alpha of the outer periphery of the convex column and the minor diameter of the root of the convex column>Large diameter of convex column root +.>
10. The spin rivet tool design method of claim 9, wherein in step B, in step aAnd->After the dimensioning, if the dimension of the spin-rivet cannot be satisfied +.>M min And the axial clamping force F, adjusting +.>Alpha and chamfer R of the root of the convex column 1 The dimension after spin riveting is enabled to be +>M 1 Reaching an optimal value.
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116972070A (en) * | 2023-08-31 | 2023-10-31 | 重庆长江轴承股份有限公司 | Three-row ball hub bearing for new energy automobile |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116972070A (en) * | 2023-08-31 | 2023-10-31 | 重庆长江轴承股份有限公司 | Three-row ball hub bearing for new energy automobile |
| CN116972070B (en) * | 2023-08-31 | 2024-05-14 | 重庆长江轴承股份有限公司 | Three-row ball hub bearing for new energy automobile |
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