CN115600343A - Multi-wedge-groove radial sliding bearing and design method thereof - Google Patents

Multi-wedge-groove radial sliding bearing and design method thereof Download PDF

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CN115600343A
CN115600343A CN202211399347.9A CN202211399347A CN115600343A CN 115600343 A CN115600343 A CN 115600343A CN 202211399347 A CN202211399347 A CN 202211399347A CN 115600343 A CN115600343 A CN 115600343A
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wedge
bearing
sliding bearing
radial sliding
diameter
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张琳
谭鑫
顾延东
刘本庆
程金武
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Huayu Pierboge Pump Technology Co ltd
Yangzhou University
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Huayu Pierboge Pump Technology Co ltd
Yangzhou University
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    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational design
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • 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
    • F16C37/00—Cooling of bearings
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
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Abstract

The invention provides a design method of a multi-wedge groove radial sliding bearing and the multi-wedge groove radial sliding bearing designed by the method, wherein the inner diameter D of the bearing is adjusted in the direction of reducing the diameter 1 Or at the same time increasing the bearing inner diameter D 1 Tolerance class IT 1 Or, adjusting the journal diameter D in the direction of increasing diameter 3 Or at the same time increase the journal diameter D 3 Tolerance class IT 3 The fit clearance between the radial sliding bearing and the shaft neck is reduced, so that the radial sliding bearing can stably support the shaft neck and prevent the shaft system from vibrating; the actual bearing bore diameter obtained by working is D' 1 Diameter ofThe inner wall surface of the sliding bearing is provided with a plurality of spiral wedge-shaped grooves, and the maximum clearance between each spiral wedge-shaped groove and the shaft neck is provided with an arc-shaped groove, so that enough lubricating oil is provided for the radial sliding bearing and the shaft neck friction pair, the radial sliding bearing and the shaft neck friction pair are well lubricated, effectively cooled, absorbed and reduced in load, and the transmission performance of a shaft system is finally improved.

Description

Multi-wedge-groove radial sliding bearing and design method thereof
Technical Field
The invention belongs to the technical field of sliding bearings, and particularly relates to a design method of a multi-wedge groove radial sliding bearing and the multi-wedge groove radial sliding bearing.
Background
The radial sliding bearing is a dynamic pressure bearing which bears the radial load of the shaft neck under the sliding friction, when the shaft neck rotates, a dynamic pressure oil film is formed in a fit clearance between the inner surface of the radial sliding bearing and the outer surface of the shaft neck to balance the radial load of the shaft neck, the inner surface of the radial sliding bearing and the outer surface of the shaft neck are separated by lubricating oil and do not directly contact with each other, the surface abrasion of the inner surface of the radial sliding bearing and the outer surface of the shaft neck is greatly reduced, the friction loss is reduced, the transmission efficiency is improved, the lubricating oil can also cool a friction heat generating point to avoid overheating failure, and the radial sliding bearing is safe and reliable.
The fit clearance between the radial sliding bearing and the journal is an important design parameter which influences the working performance of the radial sliding bearing, the reliability of the whole transmission shafting is directly influenced, if the fit clearance is too small, the lubrication is poor, the friction loss is overlarge, the heat dissipation performance is poor, and the bearing locking and the high-temperature failure are easy to occur; if the fit clearance is too large, a dynamic pressure oil film is limited, the bearing capacity is insufficient, shafting vibration is easy to occur, particularly, under the working conditions of starting, stopping and overload, the radial sliding bearing and the shaft neck are easy to generate surface contact, surface abrasion is caused, the fit clearance is changed, the fit design is deviated, and finally shafting vibration is caused, so that the transmission efficiency is influenced. Therefore, the fit clearance between the radial sliding bearing and the shaft neck needs to be optimally designed, the radial sliding bearing is guaranteed to stably support the shaft neck, good lubrication between the radial sliding bearing and the shaft neck is achieved, and effective cooling is conducted on high heat generated by friction.
Disclosure of Invention
In view of the above, the present invention provides a method for designing a multi-wedge groove radial sliding bearing and a multi-wedge groove radial sliding bearing by optimally designing a radial sliding bearing, so as to ensure stable support of a journal, achieve good lubrication, and perform effective cooling.
In order to achieve the purpose, the invention adopts the following technical scheme:
a method for designing radial slide bearing with multiple wedge grooves features that the radial slide bearing is in clearance fit with axle journal and the internal diameter of said radial slide bearing is D 1 The outer diameter of the bearing is D 2 Bearing length L 1 Journal diameter of D 3 Wherein the method comprises the following steps:
s1: adjusting the inner diameter D of the bearing in the direction of decreasing diameter 1 While maintaining the bearing inner diameter D 1 Tolerance class IT 1 Without changing or increasing the bearing inner diameter D 1 Tolerance class IT of 1 (ii) a Alternatively, the first and second liquid crystal display panels may be,
adjusting the diameter D of the journal in the direction of increasing diameter 3 While maintaining the journal diameter D 3 Tolerance class IT 3 Constant or increasing journal diameter D 3 Tolerance class IT 3 ；
S2: processing to obtain the bearing inner diameter of D' 1 And D 'as the actual bearing inner diameter' 1 The inner wall surface of the radial sliding bearing is provided with a plurality of spiral wedge-shaped grooves which are arranged in parallel with the bearing axis of the radial sliding bearing;
s3: and arc-shaped grooves are arranged at the maximum gap between each spiral wedge-shaped groove and the shaft neck, and the arc-shaped grooves are arranged in parallel with the bearing axis of the radial sliding bearing.
Further, in step S2, the actual bearing inner diameter of the radial sliding bearing is D' 1 Determining the spiral wedge-shaped groove for the basis, wherein the molded line of the spiral wedge-shaped groove is formed by intersecting two equiangular spiral lines which are drawn oppositely, and the inner diameter of the actual bearing is D' 1 The radial sliding bearing's internal face offer a plurality of spiral wedge grooves include:
s21: selecting the wrap angle coefficient C of the spiral wedge-shaped groove α1 The coefficient of wrap angle C α1 Is calculated by the following formula,
Figure BDA0003934369750000021
wherein n is the number of the spiral wedge-shaped grooves;
according to the wrap angle coefficient C α1 Determining the wrap angle alpha of a helical wedge-shaped groove 1 The angle of wrap α 1 Is calculated by the following formula,
α 1 ＝2·π·C α1
wherein the wrap angle alpha of the spiral wedge-shaped groove 1 The unit of (b) is rad;
s22: actual bearing inner diameter of the radial sliding bearing is D' 1 Determining the initial inner radial R of the helical wedge-shaped groove 1 ＝D′ 1 2; determining n molded line initial position points P of molded lines of the spiral wedge-shaped grooves on the inner wall surface of the radial sliding bearing according to the number n of the spiral wedge-shaped grooves 1 、P 2 、…、P n-1 、P n And determining 2n profiles S 1 、S 2 、…、S 2n-1 、S 2n Respectively corresponding 2n inner radial gradients beta 1 、β 2 、…、β 2n-1 、β 2n Wherein beta is 1 ＝β 2 ＝…＝β 2n-1 ＝β 2n ；
According to the initial inner radial R 1 And inner radial inclination beta 1 、β 2 、…、β 2n-1 、β 2n The equation of the profile defining the spiral wedge groove is as follows,
r m ＝R 1 ·β m θ
wherein r is m Is a molded line S m Inner sagittal diameter of, beta m Is a molded line S m M =1,2, 2n-1,2n; theta is the azimuth angle in rad, and the interval is [0, alpha ] 1 ]；
S23: according to the wrap angle alpha of the spiral wedge-shaped groove 1 Sum line initial position point P 1 、P 2 、…、P n-1 、P n And the equation of the profile r m ＝R 1 ·β m θ The actual bearing bore diameter is D' 1 The inner wall surface of the radial sliding bearing is processed with n spiral wedge-shaped grooves.
Further, the sectional depth h of the arc-shaped groove in step S3 is calculated by the following formula,
Figure BDA0003934369750000031
wherein, C 1 Is the section depth coefficient of the arc-shaped groove;
the section width b of the arc-shaped groove is calculated by the following formula,
Figure BDA0003934369750000032
wherein, C 2 Is the section width coefficient of the arc-shaped groove.
Further, the spiral wedge-shaped groove is equal to the radial sliding bearing in length along the axial direction; the arc-shaped groove is equal to the spiral wedge-shaped groove in length along the axial direction.
Further, the profile S 1 Inner radial inclination beta 1 Preferably, it is
Figure BDA0003934369750000033
Further, the section depth coefficient C of the arc-shaped groove 1 Preferably 0 < C 1 ≤0.5。
Further, the arc-shaped grooveCoefficient of section width C 2 Preferably 0 < C 2 ≤3。
Furthermore, the number n of the spiral wedge-shaped grooves is preferably more than or equal to 2 and less than or equal to 6.
The invention also provides a multi-wedge groove radial sliding bearing which is in clearance fit with the shaft neck and is designed by adopting the design method of the multi-wedge groove radial sliding bearing, the inner wall surface of the multi-wedge groove radial sliding bearing is provided with a plurality of spiral wedge grooves, and the maximum clearance between each spiral wedge groove and the shaft neck is provided with an arc-shaped groove.
Compared with the prior art, the invention has the following beneficial effects: the invention provides a design method of a multi-wedge-groove radial sliding bearing and the multi-wedge-groove radial sliding bearing designed by the method by optimally designing the radial sliding bearing, on one hand, the inner diameter D of the bearing is adjusted in the direction of reducing the diameter 1 While maintaining the bearing inner diameter D 1 Tolerance class IT of 1 Without changing or increasing the bearing inner diameter D 1 Tolerance class IT 1 Or adjusting the diameter D of the journal in the direction of increasing diameter 3 While maintaining the journal diameter D 3 Tolerance class IT 3 Constant or increasing journal diameter D 3 Tolerance class IT 3 The fit clearance between the radial sliding bearing and the shaft neck is reduced, so that the radial sliding bearing can stably support the shaft neck and prevent the shaft system from vibrating; on the other hand, the actual bearing bore diameter obtained by working is D' 1 Radial slide bearing's internal face set up a plurality of spiral wedge grooves to further set up the arc wall in the maximum clearance department of every spiral wedge groove and journal, spiral wedge groove and arc wall constitute the fuel feeding wedge groove together, provide sufficient lubricating oil for radial slide bearing and journal friction is vice, not only realize carrying out good lubrication to radial slide bearing and journal friction is vice, can also carry out effective cooling to the friction high fever that radial slide bearing and journal friction are vice to produce, and the lubricating oil in a plurality of fuel feeding wedge grooves that constitute still has the effect of inhaling, it is even to make the journal atress, further avoid taking place shafting vibration, from this finally improve the axle and shakeThe transmission performance of the train. Therefore, the design method of the multi-wedge groove radial sliding bearing and the multi-wedge groove radial sliding bearing designed by the method have the excellent performances of stable shafting, good lubrication and effective cooling.
Drawings
FIG. 1 is a schematic view of a radial slide bearing and journal engagement;
FIG. 2 shows that the bearing inner diameter is substantially D' 1 The structure of the radial sliding bearing is schematically shown;
FIG. 3 is a schematic cross-sectional view of a multi-groove radial sliding bearing according to the present invention;
FIG. 4 is a schematic cross-sectional view of the arcuate slot of FIG. 3;
FIG. 5 is a cross-sectional structure diagram of a three-wedge groove radial sliding bearing of the present invention;
fig. 6 is a three-dimensional structure diagram of the radial sliding bearing with three wedge grooves of the invention.
The reference numerals are explained below:
1. radial sliding bearing
1-1 spiral wedge-shaped groove
1-2 arc groove
2. Axle journal
Detailed Description
The following detailed description of the present invention is provided with reference to the accompanying drawings, and it should be understood that the following detailed description is only illustrative and not restrictive of the scope of the present invention.
The invention provides a design method of a multi-wedge groove radial sliding bearing by optimally designing the radial sliding bearing, so that the multi-wedge groove radial sliding bearing designed by the method has excellent performances of stable shafting, good lubrication and effective cooling, as shown in figures 1-4, the known radial sliding bearing 1 is in clearance fit with a shaft neck 2, and the bearing inner diameter of the radial sliding bearing 1 is D 1 The radial plain bearing 1 has a bearing outer diameter D 2 The radial sliding bearing 1 has a bearing length L 1 Journal diameter of D 3 The method comprises the following steps:
s1: adjusting the inner diameter D of the bearing in the direction of decreasing diameter 1 While maintaining the bearing inner diameter D 1 Tolerance class IT 1 Without changing or increasing the bearing inner diameter D 1 Tolerance class IT of 1 (ii) a Alternatively, the first and second electrodes may be,
adjusting the diameter D of the journal in the direction of increasing diameter 3 While maintaining the journal diameter D 3 Tolerance class IT 3 Constant or increasing journal diameter D 3 Tolerance class IT 3 ；
S2: processing to obtain the bearing inner diameter of D' 1 And the actual bearing inner diameter is D' 1 The inner wall surface of the radial sliding bearing 1 is provided with a plurality of spiral wedge-shaped grooves 1-1, and the spiral wedge-shaped grooves 1-1 are arranged in parallel with the bearing axis of the radial sliding bearing 1;
s3: and arc-shaped grooves 1-2 are arranged at the maximum clearance between each spiral wedge-shaped groove 1-1 and the shaft neck 2, the arc-shaped grooves 1-2 are arranged in parallel with the bearing axis of the radial sliding bearing 1, understandably, the number of the arc-shaped grooves 1-2 is equal to that of the spiral wedge-shaped grooves 1-1, the arc-shaped grooves 1-2 and the spiral wedge-shaped grooves 1-1 are in one-to-one correspondence to form a plurality of oil supply wedge grooves, and the number of the oil supply wedge grooves is also equal to that of the spiral wedge-shaped grooves 1-1. Optionally, the helical wedge groove 1-1 is axially as long as the radial sliding bearing 1, and has a length L 1 (ii) a The arc-shaped groove 1-2 is equal to the spiral wedge-shaped groove 1-1 in length along the axial direction and has a length L 1 。
In the method for designing a multi-wedge-groove radial sliding bearing of the present invention, on the one hand, the inner diameter D of the bearing of the radial sliding bearing 1 is adjusted in the direction of decreasing the diameter 1 While maintaining the bearing inner diameter D 1 Tolerance class IT 1 Constant or increasing the bearing inner diameter D 1 Tolerance class IT of 1 Or adjusting the diameter D of the journal in the direction of increasing diameter 3 While maintaining the journal diameter D 3 Tolerance class IT 3 Constant or increasing journal diameter D 3 Tolerance class IT 3 To reduce the fit clearance of the radial sliding bearing 1 and the shaft journal 2; on the other hand, the actual bearing inner diameter obtained by working is D' 1 The inner wall surface of the radial sliding bearing 1 is provided with a plurality of spiral wedge-shaped grooves 1-1, and further an arc-shaped groove 1-2 is arranged at the maximum clearance between each spiral wedge-shaped groove 1-1 and the journal 2, the spiral wedge-shaped grooves 1-1 and the arc-shaped grooves 1-2 form an oil supply wedge groove, so that enough lubricating oil is provided for a friction pair of the radial sliding bearing 1 and the journal 2, and finally the multi-wedge-groove radial sliding bearing is designed by the method, has a smaller fit clearance with the journal 2, can realize that the radial sliding bearing 1 stably supports the journal 2, and can prevent shafting vibration; meanwhile, the plurality of oil supply wedge grooves can provide enough lubricating oil, insufficient oil supply caused by reduced fit clearance is avoided, good lubrication can be realized for the friction pair of the radial sliding bearing 1 and the shaft neck 2, strong heat dissipation can be further realized for the friction high heat generated by the friction pair of the radial sliding bearing 1 and the shaft neck 2, effective cooling of the friction pair of the radial sliding bearing 1 and the shaft neck 2 is realized, the lubricating oil in the plurality of oil supply wedge grooves also has the vibration absorption effect, the shaft neck 2 can be uniformly stressed, shafting vibration is further avoided, and therefore the transmission performance of the shafting is finally improved.
Further, as shown in fig. 3, in step S2, the actual bearing inner diameter of radial sliding bearing 1 is D' 1 Determining a spiral wedge-shaped groove 1-1 for the basis, wherein the molded line of the spiral wedge-shaped groove 1-1 is formed by intersecting two equiangular spiral lines which are drawn oppositely, and the inner diameter of the actual bearing is D' 1 The inner wall surface of the radial sliding bearing 1 is provided with a plurality of spiral wedge-shaped grooves 1-1, which comprise:
s21: selecting the wrap angle coefficient C of the spiral wedge-shaped groove 1-1 α1 The coefficient of wrap angle C α1 Is calculated by the following formula,
Figure BDA0003934369750000051
wherein n is the number of the spiral wedge-shaped grooves 1-1, and the value range of n which is more than or equal to 2,n is preferably that n is more than or equal to 2 and less than or equal to 6;
according to the wrap angle coefficient C α1 Determining the wrap angle alpha of the spiral wedge-shaped groove 1-1 1 The wrap angle α 1 Calculated by the following formula，
α 1 ＝2·π·C α1
Wherein, the wrap angle alpha of the spiral wedge-shaped groove 1-1 1 Unit of (d) is rad;
s22: the actual bearing inner diameter of radial sliding bearing 1 is D' 1 Determining the initial inner radial R of the spiral wedge-shaped groove 1-1 1 The initial inner radial diameter R 1 ＝D′ 1 2; determining n molded line initial position points P of the molded line of the spiral wedge-shaped groove 1-1 on the inner wall surface of the radial sliding bearing 1 according to the number n of the spiral wedge-shaped grooves 1-1 1 、P 2 、…、P n-1 、P n And determining 2n profiles S 1 、S 2 、…、S 2n-1 、S 2n Respectively corresponding 2n inner radial gradients beta 1 、β 2 、…、β 2n-1 、β 2n Wherein beta is 1 ＝β 2 ＝…β 2n-1 ＝β 2n ，β 1 Preferably in a range of values
Figure BDA0003934369750000061
According to the initial inner radial R 1 And inner radial inclination beta 1 、β 2 、…、β 2n-1 、β 2n The profile equation for determining the helical wedge groove 1-1 is as follows,
r m ＝R 1 ·β m θ
wherein r is m Is a molded line S m Inner sagittal diameter of, beta m Is a molded line S m M =1,2,.., 2n-1,2n; theta is the azimuth angle in rad, and the interval is [0, alpha ] 1 ]；
S23: according to the wrap angle alpha of the spiral wedge-shaped groove 1-1 1 Sum line initial position point P 1 、P 2 、…、P n-1 、P n And the equation of the profile r m ＝R 1 ·β m θ A molded line of the spiral wedge groove 1-1 was drawn, and the actual bearing inner diameter was D' 1 The radial sliding bearing 1 of (1) is provided with n spiral wedge grooves 1-1, it being understood that n spirals are providedThe wedge-shaped grooves 1-1 are uniformly distributed along the circumferential direction. That is, 2n molded lines S constituting molded lines of n spiral wedge grooves 1-1 1 、S 2 、…、S 2n-1 、S 2n Are equiangular spiral lines, the molded line of each spiral wedge-shaped groove 1-1 is formed by intersecting two oppositely drawn equiangular spiral lines, as shown in fig. 3, the molded line of 1 spiral wedge-shaped groove 1-1 is formed between the initial position points of each adjacent molded line, and the initial position points P of n molded lines 1 、P 2 、…、P n-1 、P n Finally, forming the molded line with n spiral wedge-shaped grooves 1-1: from the initial position point P of the profile 1 Initially, profile line S 1 At the molded line initial position point P 1 As a starting point, a profile S 2 At the molded line initial position point P 2 Two substantially equiangular helical profiles S as starting point 1 And S 2 Relative plotting until intersecting to form line initial position point P 1 And P 2 The molded line of the 1 st spiral wedge-shaped groove 1-1 is formed between the two grooves; repeating the above steps until the molded line initial position point P is used n End, profile S 2n-1 At the molded line initial position point P n As a starting point, a profile S 2n At the initial position point P of the molded line 1 Two substantially equiangular helical profiles S as starting point 2n-1 And S 2n Relative drawing till intersecting to finally form the initial position point P at the adjacent molded line n And P 1 The molded line of the nth spiral wedge-shaped groove 1-1 is formed between the two wedge-shaped grooves.
Further, as shown in FIG. 4, the sectional depth h of the arc-shaped groove 1-2 in step S3 is calculated by the following formula,
Figure BDA0003934369750000062
wherein, C 1 Is the section depth coefficient, C, of the arc-shaped groove 1-2 1 Preferably, the value range of (A) is 0 < C 1 ≤0.5；
The section width b of the arc-shaped groove 1-2 is calculated by the following formula,
Figure BDA0003934369750000063
wherein, C 2 Is the section width coefficient, C, of the arc-shaped groove 1-2 2 Preferably, the value range of (A) is 0 < C 2 Less than or equal to 3. Alternatively, the arcuate slots 1-2 are preferably circular arc slots.
The invention also provides a multi-wedge groove radial sliding bearing which is designed by adopting the design method of the multi-wedge groove radial sliding bearing and is in clearance fit with the shaft neck 2, and has excellent performances of stable shaft system, good lubrication and effective cooling, the inner wall surface of the multi-wedge groove radial sliding bearing is provided with a plurality of spiral wedge grooves 1-1, and the maximum clearance between each spiral wedge groove 1-1 and the shaft neck 2 is provided with an arc-shaped groove 1-2.
Specifically, as shown in fig. 5 to 6, the structural schematic view of the present invention, in which the multi-wedge radial sliding bearing is a triple-wedge radial sliding bearing, is illustrated. As is known, the radial sliding bearing 1 is in clearance fit with the shaft journal 2, and the bearing inner diameter D of the radial sliding bearing 1 1 =10mm, bearing inner diameter D 1 With a lower deviation EI =0.02mm and a bearing inner diameter D 1 Upper deviation ES =0.056mm, bearing inner diameter D 1 Tolerance class IT 1 For IT9, the bearing outer diameter D of the radial sliding bearing 1 2 =12mm, bearing length L of radial plain bearing 1 1 =40mm, journal diameter D 3 =10mm, journal diameter D 3 Lower deviation ei = -0.013mm, journal diameter D 3 Upper deviation es = -0.004mm, journal diameter D 3 Tolerance class IT 3 Is IT6. The following explains the design method of the above-mentioned multi-wedge groove radial sliding bearing of the present invention by taking a three-wedge groove radial sliding bearing as an example.
In step S1, the inner diameter D of the bearing is adjusted in the direction of decreasing diameter 1 The lower deviation EI, the inner diameter D of the bearing 1 Is adjusted from 0.02mm to 0mm, where the bearing inner diameter D is selected to be maintained 1 Tolerance class IT 1 IT9 is constant, IT9=0.036mm, at which point the bearing inner diameter D is 1 Upper deviation ES = EI + IT9=0mm +0.036mm =0.036mm; alternatively, the first and second electrodes may be,
adjusting the diameter of the journal in the direction of increasing diameterDiameter D 3 Upper deviation es of the journal diameter D 3 Is adjusted from-0.004 mm to-0.002 mm, where the selected diameter D of the journal is maintained 3 Tolerance class IT 3 IT6 was unchanged, IT6=0.009mm, at which point the journal diameter D 3 Lower deviation ei = es-IT6= -0.002mm-0.009mm = -0.011mm. The above adjustment always maintains the clearance fit between the radial sliding bearing 1 and the journal 2.
In step S2, the actual bearing bore diameter D 'is obtained by machining' 1 =10.036mm, as actual bearing inner diameter D 'of radial sliding bearing 1' 1 Determining spiral wedge-shaped grooves 1-1 based on 10.036mm, and determining the actual bearing inner diameter D' 1 The inner wall surface of the radial sliding bearing 1 of =10.036mm is provided with a plurality of spiral wedge grooves 1-1 arranged in parallel to the bearing axis of the radial sliding bearing 1.
In step S21, the number n =3 of the spiral wedge-shaped grooves 1-1 is selected, and the wrap angle coefficient C of the spiral wedge-shaped grooves 1-1 is selected at the moment α1 ＝1/(2·n)＝1/6；
According to the wrap angle coefficient C α1 Determining the wrap angle alpha of the spiral wedge-shaped groove 1-1 1 ＝2·π·C α1 ＝(π/3)rad。
In step S22, the actual bearing inner diameter D 'of radial sliding bearing 1 is determined' 1 =10.036mm initial inner radial R of spiral wedge groove 1-1 1 The initial inner radial diameter R 1 ＝D′ 1 2=5.018mm; determining 3 molded line initial position points P of the molded line of the spiral wedge-shaped groove 1-1 on the inner wall surface of the radial sliding bearing 1 according to the number n =3 of the spiral wedge-shaped grooves 1-1 1 、P 2 、P 3 And determining 6 profiles S 1 、S 2 、S 3 、S 4 、S 5 、S 6 Respectively corresponding 6 inner radial gradients beta 1 、β 2 、β 3 、β 4 、β 5 、β 6 ，β 1 Preferably in a range of values
Figure BDA0003934369750000081
Value of beta 1 ＝β 2 ＝β 3 ＝β 4 ＝β 5 ＝β 6 ＝1.02；
According to the initial inner radial R 1 And inner radial inclination beta 1 、β 2 、…、β 2n-1 、β 2n The profile equation for determining the helical wedge groove 1-1 is as follows,
r m ＝5.018mm·1.02 θ
wherein r is m Is a molded line S m Inner sagittal diameter of, beta m Is a molded line S m M =1,2,3,4,5,6; theta is the azimuth angle in rad, and the interval is [0, [ pi ]/3]；
In step S23, the wrap angle α according to the spiral wedge groove 1-1 1 Sum line initial position point P 1 、P 2 、P 3 And equation of line r m ＝5.018mm·1.02 θ A molded line of the spiral wedge groove 1-1 was drawn, and the actual bearing inner diameter was D' 1 The inner wall surface of the radial sliding bearing 1 is evenly processed with 3 spiral wedge-shaped grooves 1-1 along the circumferential direction, the spiral wedge-shaped grooves 1-1 are equal to the radial sliding bearing 1 along the axial direction, and the length is L 1 =40mm. In particular, 6 profiles S of the profiles forming 3 helical wedge grooves 1-1 1 、S 2 、S 3 、S 4 、S 5 、S 6 Are equiangular spiral lines, the molded line of each spiral wedge-shaped groove 1-1 is formed by intersecting two oppositely drawn equiangular spiral lines, as shown in fig. 5, 1 molded line of the spiral wedge-shaped groove 1-1 is formed between the initial position points of each adjacent molded line, and 3 initial position points P of the molded line 1 、P 2 、P 3 Finally, the molded line with 3 spiral wedge-shaped grooves 1-1 is formed: from the initial position point P of the profile 1 Initially, profile line S 1 At the molded line initial position point P 1 As a starting point, a profile S 2 At the molded line initial position point P 2 Two substantially equiangular helical profiles S as starting point 1 And S 2 Relative plotting until intersecting to form line initial position point P 1 And P 2 The molded line of the 1 st spiral wedge-shaped groove 1-1 is formed between the two wedge-shaped grooves; then the initial position point P of the molded line 2 Line S 3 At the molded line initial position point P 2 As a starting point, a profile S 4 By molded lineStarting point P 3 Two substantially equiangular helical profiles S as starting point 3 And S 4 Relative plotting until intersecting to form line initial position point P 2 And P 3 The molded line of the 2 nd spiral wedge-shaped groove 1-1 is formed between the two wedge-shaped grooves; finally, the molded line initial position point P is used 3 End, profile line S 5 At the molded line initial position point P 3 As a starting point, a profile S 6 At the molded line initial position point P 1 Two substantially equiangular helical profiles S as starting point 5 And S 6 Relative drawing till intersecting to finally form the initial position point P at the adjacent molded line 3 And P 1 The molded line of the 3 rd spiral wedge-shaped groove 1-1 is formed.
In step S3, an arc-shaped groove 1-2 which is parallel to the bearing axis of the radial sliding bearing 1 is further arranged at the maximum gap between each spiral wedge-shaped groove 1-1 and the shaft neck 2, the arc-shaped groove 1-2 is an arc groove, and the section depth coefficient C of the arc-shaped groove 1-2 is taken as a value 1 =0.4, cross-sectional depth of arc-shaped groove 1-2
Figure BDA0003934369750000082
The cross section width coefficient C of the arc-shaped groove 1-2 is taken as a value 2 =2, cross-sectional width of arc-shaped groove 1-2
Figure BDA0003934369750000083
The arc-shaped groove 1-2 is equal to the spiral wedge-shaped groove 1-1 in length along the axial direction and has a length L 1 And the number of the arc-shaped grooves 1-2 corresponding to the number of the spiral wedge-shaped grooves 1-1 is 3, and the arc-shaped grooves 1-2 and the spiral wedge-shaped grooves 1-1 are in one-to-one correspondence to form 3 oil supply wedge grooves.
Through steps S1 to S3, a three-wedge radial plain bearing as shown in fig. 5 to 6 can be designed. Through CFD simulation calculation, compared with the radial sliding bearing before optimized design, the three-wedge groove radial sliding bearing designed by the multi-wedge groove radial sliding bearing design method has the advantages that the mechanical wear rate is reduced by 27%, the friction loss power is reduced by 13%, the heat generated by friction is reduced by 20%, the purposes of stable shafting, good lubrication and effective cooling are realized, and the transmission performance of the shafting is finally improved.
The above description is only a preferred embodiment of the present invention, but the scope of the present invention is not limited thereto. It should be understood that various changes, substitutions and alterations can be made herein without departing from the spirit and scope of the invention as defined by the appended claims.

Claims (9)

1. A method for designing radial slide bearing with multiple wedge grooves features that the radial slide bearing is in clearance fit with axle journal and the internal diameter of said radial slide bearing is D 1 The outer diameter of the bearing is D 2 Bearing length L 1 Journal diameter of D 3 The method is characterized by comprising the following steps:
s1: adjusting the inner diameter D of the bearing in the direction of decreasing diameter 1 While maintaining the bearing inner diameter D 1 Tolerance class IT 1 Without changing or increasing the bearing inner diameter D 1 Tolerance class IT 1 (ii) a Alternatively, the first and second electrodes may be,
adjusting the diameter D of the journal in the direction of increasing diameter 3 While maintaining the journal diameter D 3 Tolerance class IT 3 Constant or increasing journal diameter D 3 Tolerance class IT 3 ；
S2: processing to obtain the bearing inner diameter of D' 1 And D 'as the actual bearing inner diameter' 1 The inner wall surface of the radial sliding bearing is provided with a plurality of spiral wedge-shaped grooves which are arranged in parallel with the bearing axis of the radial sliding bearing;
s3: and arc-shaped grooves are arranged at the maximum clearance between each spiral wedge-shaped groove and the shaft neck, and the arc-shaped grooves are arranged in parallel with the bearing axis of the radial sliding bearing.
2. The method of designing a multi-groove radial sliding bearing according to claim 1, wherein the actual bearing inner diameter of the radial sliding bearing is D 'in step S2' 1 Determining the spiral wedge-shaped groove for the basis, wherein the molded line of the spiral wedge-shaped groove is composed of two equiangular spiral lines which are drawn oppositelyAnd the inner diameter of the actual bearing is D' 1 The radial sliding bearing's internal face offer a plurality of spiral wedge grooves include:
s21: selecting wrap angle coefficient C of the spiral wedge-shaped groove α1 The coefficient of wrap angle C α1 Is calculated by the following formula,
Figure FDA0003934369740000011
wherein n is the number of the spiral wedge-shaped grooves;
according to the wrap angle coefficient C α1 Determining the wrap angle alpha of a helical wedge-shaped groove 1 The angle of wrap α 1 Is calculated by the following formula,
α 1 ＝2·π·C α1
wherein the wrap angle alpha of the spiral wedge-shaped groove 1 Unit of (d) is rad;
s22: d 'is the actual bearing inner diameter of the radial sliding bearing' 1 Determining the initial inner radius R of the helical wedge groove 1 ＝D′ 1 2; determining n molded line initial position points P of molded lines of the spiral wedge-shaped grooves on the inner wall surface of the radial sliding bearing according to the number n of the spiral wedge-shaped grooves 1 、P 2 、…、P n-1 、P n And determining 2n profiles S 1 、S 2 、…、S 2n-1 、S 2n Respectively corresponding 2n inner radial gradients beta 1 、β 2 、…、β 2n-1 、β 2n In which beta is 1 ＝β 2 ＝…＝β 2n-1 ＝β 2n ；
According to the initial inner radial R 1 And inner radial inclination beta 1 、β 2 、…、β 2n-1 、β 2n The equation of the profile defining the spiral wedge groove is as follows,
r m ＝R 1 ·β m θ
wherein r is m Is a molded line S m Inner sagittal diameter of, beta m Is a molded line S m M =1,2,., 2n-1,2n; theta is the azimuth angle in rad, and the interval is [0, alpha ] 1 ]；
S23: according to the wrap angle alpha of the spiral wedge-shaped groove 1 And the molded line initial position point P 1 、P 2 、…、P n-1 、P n And equation of line r m ＝R 1 ·β m θ The actual bearing bore diameter is D' 1 The inner wall surface of the radial sliding bearing is processed with n spiral wedge-shaped grooves.
3. The method of claim 2, wherein the depth h of the arc-shaped groove is calculated in step S3 by the following formula,
Figure FDA0003934369740000021
wherein, C 1 Is the section depth coefficient of the arc-shaped groove;
the section width b of the arc-shaped groove is calculated by the following formula,
Figure FDA0003934369740000022
wherein, C 2 Is the section width coefficient of the arc-shaped groove.
4. A method of designing a multi-groove radial sliding bearing according to claim 3, wherein the helical wedge grooves are axially as long as the radial sliding bearing; the arc-shaped groove is equal to the spiral wedge-shaped groove in length along the axial direction.
5. Method for designing a multi-groove radial plain bearing according to claim 3, characterized in that the profile S 1 Inner radial inclination beta 1 Preferably, it is
Figure FDA0003934369740000023
6. A method of designing a multi-groove radial sliding bearing according to claim 3, wherein the coefficient of cross-sectional depth C of the arc-shaped groove 1 Preferably 0 < C 1 ≤0.5。
7. A method of designing a multi-groove radial sliding bearing according to claim 3, wherein the cross-sectional width coefficient C of the arc-shaped groove 2 Preferably 0 < C 2 ≤3。
8. A method according to claim 3, wherein the number n of said spiral tapered grooves is preferably 2-6.
9. A multi-wedge groove radial sliding bearing is in clearance fit with a shaft neck, and is characterized in that the multi-wedge groove radial sliding bearing is designed by the design method of the multi-wedge groove radial sliding bearing according to any one of claims 1 to 8, a plurality of spiral wedge grooves are formed in the inner wall surface of the multi-wedge groove radial sliding bearing, and an arc-shaped groove is formed in the maximum clearance between each spiral wedge groove and the shaft neck.
CN202211399347.9A 2022-11-09 2022-11-09 Multi-wedge-groove radial sliding bearing and design method thereof Pending CN115600343A (en)

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Application Number Priority Date Filing Date Title
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