CN109505857B - Design method for lubricating spherical pair grease of automobile spherical hinge - Google Patents
Design method for lubricating spherical pair grease of automobile spherical hinge Download PDFInfo
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- CN109505857B CN109505857B CN201910025179.9A CN201910025179A CN109505857B CN 109505857 B CN109505857 B CN 109505857B CN 201910025179 A CN201910025179 A CN 201910025179A CN 109505857 B CN109505857 B CN 109505857B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C11/00—Pivots; Pivotal connections
- F16C11/04—Pivotal connections
- F16C11/06—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
- F16C11/068—Special features relating to lubrication
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D7/00—Steering linkage; Stub axles or their mountings
- B62D7/18—Steering knuckles; King pins
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Pivots And Pivotal Connections (AREA)
Abstract
The invention provides a design method for grease lubrication of a spherical pair of an automobile spherical hinge, which belongs to the technical field of design and development of automobile spherical hinge products and is used for parameter design at the position of an automobile spherical hinge
b. Determining the root mean square roughness of the spherical surface of the ball head or the spherical surface in the ball pin seat, and c, establishing an engineering calculation formula M of the swing working torque of the spherical pairf＝μ·f·fvG.r; and calculating to obtain the radius r of the ball head. By the grease lubrication design method for the spherical pair of the automobile spherical hinge, the starting torque of the automobile spherical hinge can be determined to be larger than the working torque according to the grease lubrication characteristic (thixotropy), the contact stress of the spherical pair of the automobile spherical hinge is optimized, the lubrication durability of the spherical hinge is improved, and the starting torque of the automobile spherical hinge is reduced.
Description
Technical Field
The invention relates to the technical field of design and development of spherical hinge products, in particular to a design method for grease lubrication of a spherical pair of an automobile spherical hinge.
Background
The structure of the automobile ball joint is shown in fig. 1 and fig. 2, and mainly comprises a ball pin 1, a ball pin seat 2, a ball pin sleeve 3 and lubricating grease 4, wherein the grease lubrication design of the automobile ball joint is related to the starting torque and the endurance reliability of the automobile ball joint.
At present, for the design and development of automobile spherical hinge products, the system design is not carried out from the characteristic of grease lubrication, so that the starting torque of the automobile spherical hinge is larger, and the durability and reliability are reduced. With market competition, the technical requirements on the automobile spherical hinge are higher and higher, and the existing design method cannot meet the requirements.
Disclosure of Invention
The invention provides a design method for grease lubrication of an automobile spherical hinge spherical pair, and aims to solve the problems of the design method for grease lubrication of the automobile spherical hinge spherical pair in the prior art.
The invention is realized by the following steps:
a design method for grease lubrication of an automobile spherical hinge spherical pair is used for parameter design at an automobile spherical hinge, the automobile spherical hinge comprises a spherical pin, a spherical pin seat and spherical pair grease, a ball head spherical surface of the spherical pin and an inner spherical surface of the spherical pin seat form the automobile spherical hinge spherical pair, and the method comprises the following steps:
a. mathematical model for establishing grease lubrication state of spherical pair of automobile spherical hinge according to thickness of lubrication film
In the formula hminIs the minimum nominal oil film thickness, R, between the ball end spherical surface and the inner spherical surface of the ball pin baseq1、Rq2Root mean square roughness, R, of the ball end sphere and the inner sphere of the ball pin seatq＝(1.20～1.25)Ra，RaA surface roughness value that is a surface profile;
b. determining the root mean square roughness of the spherical surface of the ball head or the spherical surface in the ball pin seat, and when lambda is more than or equal to 3, determining the minimum nominal oil film thickness hmin＝1μm；
The root mean square roughness R of the spherical surface of the ball headq1Substitution into
Taking lambda as 3 to obtain the root mean square roughness R of the inner spherical surface of the ball pin seatq2；
Or the root mean square roughness R of the inner spherical surface of the ball pin seatq2Substitution into
Taking lambda as 3 to obtain the root mean square roughness R of the spherical surface of the ball headq1；
c. Engineering calculation formula M for establishing spherical pair swing working torquef＝μ·f·fv·G·r；
In the formula (f)vThe equivalent coefficient takes a value of pi; f is the coefficient of friction of fluid lubrication is 0.01; g is axial force; r is the ball head radius; mu is a correction coefficient;
determining a pendulum working moment MfAnd calculating the ball head radius r after the axial force G.
In an embodiment of the present invention, after the step c, the method further includes the steps of:
d. checking the contact stress intensity sigma of the ball pin seat as F/S;
in the formula, F is an axial limit load, and S is an axial projection area;
if sigma is larger than or equal to sigmabcIncreasing radius r of ball head, where σbcThe compressive strength of the ball pin seat;
if σ < σbcAnd keeping the radius r of the ball head.
In one embodiment of the invention, S ═ tr according to the spherical hinge punch rivet closing law2-π(r*cos(π/6))2。
In one embodiment of the present invention, the axial force G takes the value of 100 kN.
The invention has the beneficial effects that: by the grease lubrication design method for the spherical pair of the automobile spherical hinge, which is provided by the invention, the starting moment of the automobile spherical hinge can be determined to be larger than the working moment according to the grease lubrication characteristics (thixotropy).
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings that are required to be used in the embodiments will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present invention and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained according to the drawings without inventive efforts.
FIG. 1 is a cross-sectional view of an automotive ball joint provided by an embodiment of the present invention;
FIG. 2 is an enlarged view of a portion of area A of FIG. 1;
FIG. 3 is a schematic structural diagram of a ball pin provided by an embodiment of the present invention;
fig. 4 is a cross-sectional view of a ball pin sleeve provided by an embodiment of the present invention.
Icon: 1-ball pin; 2-ball pin seat; 3-ball pin sleeve; 4-lubricating grease.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the technical solutions of the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings of the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, are within the scope of the present invention. Thus, the following detailed description of the embodiments of the present invention, presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, are within the scope of the present invention.
In the description of the present invention, it is to be understood that the terms indicating an orientation or positional relationship are based on the orientation or positional relationship shown in the drawings only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention.
In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In the present invention, unless otherwise expressly stated or limited, the first feature may be present on or under the second feature in direct contact with the first and second feature, or may be present in the first and second feature not in direct contact but in contact with another feature between them. Also, the first feature being above, on or above the second feature includes the first feature being directly above and obliquely above the second feature, or merely means that the first feature is at a higher level than the second feature. A first feature that underlies, and underlies a second feature includes a first feature that is directly under and obliquely under a second feature, or simply means that the first feature is at a lesser level than the second feature.
The design method for grease lubrication of the spherical pair of the automobile spherical hinge is used for parameter design at the position of the automobile spherical hinge, the automobile spherical hinge comprises a spherical pin 1, a spherical pin seat 2 and spherical pair grease, and the spherical surface of a ball head of the spherical pin 1 and the spherical surface in the spherical pin seat 2 form the spherical pair of the automobile spherical hinge, and the method comprises the following steps:
a. mathematical model for establishing grease lubrication state of spherical pair of automobile spherical hinge according to thickness of lubrication film
In the formula hminIs the minimum nominal oil film thickness, R, between the ball end spherical surface and the inner spherical surface of the ball pin base 2q1、Rq2Root mean square roughness, R, of the ball-end sphere and of the sphere in the ball pin seat 2q＝(1.20～1.25)Ra，RaA surface roughness value that is a surface profile;
b. and determining the root mean square roughness of the spherical surface of the ball head or the spherical surface in the ball pin seat 2, and when the lambda is more than or equal to 3, the spherical pair of the automobile spherical hinge can be considered to be in a fluid lubrication state, and the friction property depends on the viscous resistance among the molecules in the lubricating grease 4. According to the definition of the lubrication state: minimum nominal oil film thickness hmin＝1μm；
The root mean square roughness R of the spherical surface of the ball headq1Substitution into
Taking λ ═ 3, the root mean square roughness R of the spherical surface in the ball pin boss 2 was obtainedq2；
Or, the ball pin seat2 root mean square roughness R of inner sphereq2Substitution into
Taking lambda as 3 to obtain the root mean square roughness R of the spherical surface of the ball headq1；
c. Engineering calculation formula M for establishing spherical pair swing working torquef＝μ·f·fv·G·r；
In the formula (f)vThe equivalent coefficient takes a value of pi; f is the coefficient of friction of fluid lubrication, and the internal viscous resistance of the grease 4 is 0.01; g is axial force; r is the ball head radius; mu is a correction coefficient;
wherein f isvIs derived by the following steps:
spherical normal pressure FN＝G*fvWhereas the whole moment acts on the spherical pair by only half of the whole spherical pair, so FNG/r 2 pi r 1/2G pi, so fv＝π。
Determining a pendulum working moment MfAnd calculating to obtain the ball head radius r after the axial force G, wherein the swing working moment can be calculated by using the swing working moment statistical value of 2.0Nm under the working state, and the axial force G is calculated according to the following formula:
before the ball pin sleeve 3 is punched, riveted and closed, the outer diameter is r1After punching and riveting the closed end, the outer diameter of the boundary is r2The axial force-bearing area S' ═ pi (r) in the process of punching, riveting and closing up the ball pin sleeve 31 2-r2 2) Axial force G ═ σsS’。
d. Checking the contact stress intensity sigma of the ball pin seat 2 as F/S;
in the formula, F is an axial limit load, and S is an axial projection area;
if sigma is larger than or equal to sigmabcIncreasing radius r of ball head, where σbcThe compressive strength of the ball pin base 2;
if σ < σbcRetention ofThe radius r of the bulb.
Examples
Referring to fig. 1, a ball pin seat 2 is a POM injection molded part, the roughness Ra of an inner spherical surface model is 0.1 μm, and the roughness Ra of the inner spherical surface of the ball pin seat 2 is 1-2 levels lower than that of the model, so that the roughness Ra of the inner spherical surface of the ball pin seat 2 is reduced by 1-2 levels1＝0.2μm，Rq1＝1.25*0.2＝0.25，hmin＝1μm。
Substitution into
Contour root mean square deviation Rq of sphere of ball pin 12When the thickness is 0.22 mu m, the spherical surface Ra of the ball pin 1 is further obtained2＝Rq2/1.25＝0.17μm。
Engineering calculation formula M for establishing spherical pair swing working torquef＝μ·f·fvG r, oscillating working moment Mf2.0Nm is required, the axial force G being according to G- σsAnd S' calculating.
Wherein the ball pin sleeve 3 adopts 20# steel with sigmas245MPa, and the outer diameter r before punching and riveting closing120mm, outer diameter r of the border after punching and riveting216.43mm, yielding G100 kN. When the ball pin 1 of POM is obtained from the statistical data, the correction coefficient μ is 0.025, and r is calculated to be 25 mm.
Through sigmabcAnd carrying out r value verification, wherein the sigma is F/S. Wherein F is the value of a loading coefficient multiplied by the steering gear rack force, the loading coefficient is 1.5, and the steering gear rack force is 12 kN; s ═ pi r2-π(r*cos(π/6))2The value r is substituted to 25 mm. The compressive strength σ of the POM ball pin socket 2 was calculated to be 36.68MPabcThe pressure was adjusted to 66.67MPa (safety factor: 1.5 in the formula) at 100 MPa/1.5.
According to the comparison σ < σbcThe retention r is 25 mm.
By the grease lubrication design method for the spherical pair of the automobile spherical hinge, which is provided by the invention, the starting moment of the automobile spherical hinge can be determined to be larger than the working moment according to the grease lubrication characteristics (thixotropy).
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (3)
1. A design method for grease lubrication of an automobile spherical hinge spherical pair is used for parameter design at an automobile spherical hinge, the automobile spherical hinge comprises a spherical pin, a spherical pin seat and spherical pair grease, and a ball head spherical surface of the spherical pin and an inner spherical surface of the spherical pin seat form the automobile spherical hinge spherical pair, and is characterized by comprising the following steps:
a. mathematical model for establishing grease lubrication state of spherical pair of automobile spherical hinge according to thickness of lubrication film
Wherein λ is the film thickness ratio, hminIs the minimum nominal oil film thickness, R, between the ball end spherical surface and the inner spherical surface of the ball pin baseq1、Rq2Root mean square roughness, R, of the ball end sphere and the inner sphere of the ball pin seatq＝(1.20～1.25)Ra，RaA surface roughness value that is a surface profile;
b. determining the root mean square roughness of the spherical surface of the ball head or the spherical surface in the ball pin seat, and when lambda is more than or equal to 3, determining the minimum nominal oil film thickness hmin＝1μm；
The root mean square roughness R of the spherical surface of the ball headq1Substitution into
Taking lambda as 3 to obtain the root mean square roughness R of the inner spherical surface of the ball pin seatq2；
Or the root mean square roughness R of the inner spherical surface of the ball pin seatq2Substitution into
Taking lambda as 3 to obtain the root mean square roughness R of the spherical surface of the ball headq1；
c. Engineering calculation formula M for establishing spherical pair swing working torquef＝μ·f·fv·G·r；
In the formula (f)vThe equivalent coefficient takes a value of pi; f is the coefficient of friction of fluid lubrication is 0.01; g is axial force; r is the ball head radius; mu is a correction coefficient;
determining a pendulum working moment MfAnd calculating the ball head radius r after the axial force G.
2. The design method for grease lubrication of spherical pair of spherical hinges for automobile of claim 1, further comprising the following steps after step c:
d. checking the contact stress intensity sigma of the ball pin seat as F/S,
in the formula, F is an axial limit load, and S is an axial projection area;
wherein, according to the law of spherical hinge punching riveting closing-in, the axial projection area S ═ pi r2- π (r*cos( π /6))2；
If sigma is larger than or equal to sigmabcIncreasing radius r of ball head, where σbcThe compressive strength of the ball pin seat;
if σ < σbcAnd keeping the radius r of the ball head.
3. The design method for grease lubrication of the spherical pair of the spherical hinge of the automobile as claimed in claim 1, wherein the axial force G is 100 kN.
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3856423A (en) * | 1973-02-06 | 1974-12-24 | Ishikawa Tekko Kk | Ball joint |
| JP2006162068A (en) * | 2004-12-03 | 2006-06-22 | Minebea Co Ltd | Manufacturing method of self-lubricating plain bearing, self-lubricating plain bearing, bearing element member and self-lubricating spherical plain bearing |
| EP2080922A1 (en) * | 2006-09-11 | 2009-07-22 | NTN Corporation | Steel ball rolling structure and constant velocity universal joint |
| CN105333006A (en) * | 2015-11-27 | 2016-02-17 | 中国航空工业集团公司沈阳飞机设计研究所 | Novel polyhedral sliding and rotary swing combined knuckle bearing design method |
| CN107203668A (en) * | 2017-05-23 | 2017-09-26 | 四川望锦机械有限公司 | A kind of automobile spherical hinge structure design method based on CAE |
| CN207437576U (en) * | 2017-11-09 | 2018-06-01 | 成都望锦汽车部件有限公司 | A kind of automobile spherical hinge structure of staring torque optimization |
-
2019
- 2019-01-11 CN CN201910025179.9A patent/CN109505857B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3856423A (en) * | 1973-02-06 | 1974-12-24 | Ishikawa Tekko Kk | Ball joint |
| JP2006162068A (en) * | 2004-12-03 | 2006-06-22 | Minebea Co Ltd | Manufacturing method of self-lubricating plain bearing, self-lubricating plain bearing, bearing element member and self-lubricating spherical plain bearing |
| EP2080922A1 (en) * | 2006-09-11 | 2009-07-22 | NTN Corporation | Steel ball rolling structure and constant velocity universal joint |
| CN105333006A (en) * | 2015-11-27 | 2016-02-17 | 中国航空工业集团公司沈阳飞机设计研究所 | Novel polyhedral sliding and rotary swing combined knuckle bearing design method |
| CN107203668A (en) * | 2017-05-23 | 2017-09-26 | 四川望锦机械有限公司 | A kind of automobile spherical hinge structure design method based on CAE |
| CN207437576U (en) * | 2017-11-09 | 2018-06-01 | 成都望锦汽车部件有限公司 | A kind of automobile spherical hinge structure of staring torque optimization |
Non-Patent Citations (1)
| Title |
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| 滑动球铰的精度分析及减摩优化;刘良宝等;《航空精密制造技术》;20181231;第54卷(第6期);第28页至第31页 * |
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Address after: The 15 group of Dayi County town of Sha Qu Shun he Cun 611300 Sichuan city of Chengdu province (Industrial Development Zone) Applicant after: Chengdu hope Automobile Parts Co., Ltd. Address before: 611300 Chengdu, Sichuan, Dayi, Pengzhou, Dayi, Sha town, Shun River Village 15 groups (Industrial Development Zone) Applicant before: Chengdu hope Automobile Parts Co., Ltd. |
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