A method for designing a multi-wedge groove radial sliding bearing and a multi-wedge groove radial sliding bearing

Abstract

This invention provides a design method for a multi-wedge groove radial sliding bearing and the multi-wedge groove radial sliding bearing designed by this method. By adjusting the lower deviation EI of the bearing inner diameter D1 in the direction of decreasing diameter, or simultaneously increasing the tolerance grade IT1 of the bearing inner diameter D1, or by adjusting the upper deviation es of the journal diameter D3 in the direction of increasing diameter, or simultaneously increasing the tolerance grade IT3 of the journal diameter D3, the clearance between the radial sliding bearing and the journal is reduced, thereby achieving stable support of the journal by the radial sliding bearing and preventing shaft vibration. By creating multiple helical wedge grooves on the inner wall of the radial sliding bearing with an actual bearing inner diameter of D′1, and creating an arc-shaped groove at the maximum clearance between each helical wedge groove and the journal, sufficient lubricating oil is provided for the friction pair between the radial sliding bearing and the journal. This achieves good lubrication, effective cooling, and vibration absorption and load reduction for the friction pair between the radial sliding bearing and the journal, ultimately improving the transmission performance of the shaft system.

Description

Technical Field

[0001] This invention belongs to the field of sliding bearing technology, and particularly relates to a design method for a multi-wedge groove radial sliding bearing and the multi-wedge groove radial sliding bearing. Background Technology

[0002] Radial sliding bearings are hydrodynamic bearings that bear radial loads on the journal under sliding friction. When the journal rotates, the fit clearance between the inner surface of the radial sliding bearing and the outer surface of the journal forms a hydrodynamic oil film to balance the radial load on the journal. The inner surface of the radial sliding bearing and the outer surface of the journal are separated by the lubricating oil and do not come into direct contact, which greatly reduces surface wear on the inner surface of the radial sliding bearing and the outer surface of the journal, reduces friction loss, and improves transmission efficiency. Moreover, the lubricating oil can also cool down the heat-generating points of friction, preventing overheating failure. Therefore, radial sliding bearings are widely used in defense, power, chemical, aerospace, and transportation industries, such as in pumps, propellers, and water turbines.

[0003] The clearance between the radial sliding bearing and the journal is a crucial design parameter affecting the bearing's performance and directly impacts the reliability of the entire transmission shaft system. If the clearance is too small, lubrication will be poor, friction losses will be excessive, and heat dissipation will be inadequate, leading to bearing seizure and high-temperature failure. Conversely, if the clearance is too large, the hydrodynamic oil film will be limited, resulting in insufficient load-bearing capacity and increased shaft vibration, especially during start-up, shutdown, and overload conditions. In these situations, the radial sliding bearing and journal are more prone to surface contact, causing surface wear, altering the clearance, deviating from the design, and ultimately triggering shaft vibration, thus affecting transmission efficiency. Therefore, it is necessary to optimize the clearance between the radial sliding bearing and the journal to ensure stable support from the bearing, good lubrication, and effective cooling of the heat generated by friction. Summary of the Invention

[0004] In view of this, the present invention aims to provide a design method and a multi-wedge groove radial sliding bearing by optimizing the design of the radial sliding bearing, so as to ensure stable support for the journal, achieve good lubrication, and provide effective cooling.

[0005] To achieve the above objectives, the present invention adopts the following technical solution:

[0006] A design method for a multi-wedge groove radial sliding bearing, wherein the radial sliding bearing and the journal are clearance fit, the bearing inner diameter is D1, the bearing outer diameter is D2, the bearing length is L1, and the journal diameter is D3, wherein the method includes the following steps:

[0007] S1: Adjust the lower deviation EI of the bearing inner diameter D1 in the direction of decreasing diameter, while keeping the tolerance grade IT1 of the bearing inner diameter D1 unchanged or increasing the tolerance grade IT1 of the bearing inner diameter D1; or,

[0008] Adjust the upper deviation es of journal diameter D3 in the direction of increasing diameter, while keeping the tolerance grade IT3 of journal diameter D3 unchanged or increasing the tolerance grade IT3 of journal diameter D3.

[0009] S2: A radial sliding bearing with an actual inner diameter of D′1 is obtained by machining, and multiple spiral wedge grooves are opened on the inner wall surface of the radial sliding bearing with an actual inner diameter of D′1. The spiral wedge grooves are arranged parallel to the bearing axis of the radial sliding bearing.

[0010] S3: An arc-shaped groove is opened at the maximum gap between each spiral wedge groove and the journal, and the arc-shaped groove is set parallel to the bearing axis of the radial sliding bearing.

[0011] Further, in step S2, the spiral wedge groove is determined based on the actual bearing inner diameter D′1 of the radial sliding bearing. The profile of the spiral wedge groove is formed by the intersection of two opposing equiangular spiral lines. The step of opening multiple spiral wedge grooves on the inner wall surface of the radial sliding bearing with an actual bearing inner diameter of D′1 includes:

[0012] S21: Select the wrap angle coefficient C of the spiral wedge groove. α1 The wrap angle coefficient C α1 It is calculated using the following formula.

[0013]

[0014] Where n is the number of spiral wedge grooves;

[0015] According to the wrap angle coefficient C α1 The wrap angle α1 of the spiral wedge groove is determined, and the wrap angle α1 is calculated using the following formula.

[0016] α1=2·π·C α1

[0017] The unit of the wrap angle α1 of the spiral wedge groove is rad;

[0018] S22: Determine the initial inner diameter R1 of the helical wedge groove as D′1 based on the actual inner diameter of the radial sliding bearing; determine the initial position points P1, P2, ..., P on the inner wall surface of the radial sliding bearing based on the number n of helical wedge grooves. n-1 P n And determine 2n profiles S1, S2, ..., S 2n-1 S 2nThe corresponding 2n interior radius inclinations β1, β2, ..., β 2n-1 β 2n , where β1=β2=…=β 2n-1 =β 2n ;

[0019] Based on the initial inner diameter R1 and the inner diameter inclination β1, β2, ..., β 2n-1 β 2n The profile equation for the helical wedge groove is determined as follows:

[0020] r m =R1·β m θ

[0021] Where, r m For the S-shaped line m The inner diameter, β m For the S-shaped line m The inclination of the inner radius vector, m = 1, 2, ..., 2n-1, 2n; θ is the azimuth angle, in rad, in the interval [0, α1];

[0022] S23: Based on the wrap angle α1 of the spiral wedge groove and the initial position points P1, P2, ..., P of the profile... n-1 P n and the curve equation r m =R1·β m θ n spiral wedge grooves are machined on the inner wall surface of a radial sliding bearing with an actual bearing inner diameter of D′1.

[0023] Furthermore, the cross-sectional depth h of the arc-shaped groove in step S3 is calculated using the following formula:

[0024]

[0025] Where C1 is the section depth coefficient of the arc groove;

[0026] The cross-sectional width b of the arc-shaped groove is calculated using the following formula.

[0027]

[0028] Where C2 is the cross-sectional width coefficient of the arc groove.

[0029] Furthermore, the spiral wedge groove is the same length as the radial sliding bearing along the axial direction; the arc-shaped groove is the same length as the spiral wedge groove along the axial direction.

[0030] Furthermore, the inclination β1 of the inner diameter of the profile S1 is preferably...

[0031] Furthermore, the cross-sectional depth coefficient C1 of the arc-shaped groove is preferably 0 < C1 ≤ 0.5.

[0032] Furthermore, the cross-sectional width coefficient C2 of the arc-shaped groove is preferably 0 < C2 ≤ 3.

[0033] Furthermore, the number n of the spiral wedge grooves is preferably 2≤n≤6.

[0034] The present invention also provides a multi-wedge groove radial sliding bearing, which has a clearance fit with the journal. The multi-wedge groove radial sliding bearing is designed using the multi-wedge groove radial sliding bearing design method described above. The inner wall surface of the multi-wedge groove radial sliding bearing is provided with a plurality of helical wedge grooves, and an arc groove is provided at the maximum clearance between each helical wedge groove and the journal.

[0035] Compared with the prior art, the present invention has the following beneficial effects: The present invention provides a design method for a multi-wedge groove radial sliding bearing and a multi-wedge groove radial sliding bearing designed by the method through optimized design of radial sliding bearings. On the one hand, by adjusting the lower deviation EI of the bearing inner diameter D1 in the direction of decreasing diameter, while keeping the tolerance grade IT1 of the bearing inner diameter D1 unchanged or increasing the tolerance grade IT1 of the bearing inner diameter D1, or by adjusting the upper deviation es of the journal diameter D3 in the direction of increasing diameter, while keeping the tolerance grade IT3 of the journal diameter D3 unchanged or increasing the tolerance grade IT3 of the journal diameter D3, the fitting clearance between the radial sliding bearing and the journal is reduced, so as to realize the radial sliding bearing's fit clearance with the journal. The design provides stable support and prevents shaft vibration. Furthermore, by creating multiple helical wedge grooves on the inner wall of a radial sliding bearing with an actual inner diameter of D′1, and further creating an arc-shaped groove at the maximum clearance between each helical wedge groove and the journal, the helical wedge grooves and arc-shaped grooves together form an oil supply wedge groove. This provides sufficient lubricating oil to the friction pair between the radial sliding bearing and the journal, achieving not only good lubrication but also effective cooling of the high frictional heat generated by the friction pair. Moreover, the lubricating oil in the multiple oil supply wedge grooves also has a vibration-absorbing effect, ensuring uniform stress on the journal and further preventing shaft vibration, thereby ultimately improving the transmission performance of the shaft system. Therefore, the multi-wedge groove radial sliding bearing design method of this application and the multi-wedge groove radial sliding bearing designed by this method possess excellent performance characteristics, including shaft stability, good lubrication, and effective cooling. Attached Figure Description

[0036] Figure 1 This is a schematic diagram of the fit between the radial sliding bearing and the journal;

[0037] Figure 2 This is a schematic diagram of a radial sliding bearing with an actual inner diameter of D′1.

[0038] Figure 3 This is a schematic diagram of the cross-sectional structure of the multi-wedge groove radial sliding bearing of the present invention;

[0039] Figure 4 yes Figure 3 Schematic diagram of the cross-sectional structure of the arc-shaped groove;

[0040] Figure 5 This is a schematic diagram of the cross-sectional structure of the three-wedge groove radial sliding bearing of the present invention;

[0041] Figure 6 This is a three-dimensional structural schematic diagram of the three-wedge groove radial sliding bearing of the present invention.

[0042] The annotations in the attached figures are explained as follows:

[0043] 1 Radial sliding bearing

[0044] 1-1 Spiral wedge groove

[0045] 1-2 Arc-shaped groove

[0046] 2 journals Detailed Implementation

[0047] The specific embodiments of the present invention will be further described in detail below with reference to the accompanying drawings. Obviously, the following embodiments are only used to illustrate the present invention and are not intended to limit the scope of protection of the present invention.

[0048] This invention provides a design method for multi-wedge groove radial sliding bearings through optimized design. The multi-wedge groove radial sliding bearings designed using this method exhibit excellent performance in terms of shaft stability, good lubrication, and effective cooling. Figure 1-4 As shown, the radial sliding bearing 1 and the journal 2 are known to have a clearance fit. The inner diameter of the radial sliding bearing 1 is D1, the outer diameter of the radial sliding bearing 1 is D2, the length of the radial sliding bearing 1 is L1, and the journal diameter is D3. The method includes the following steps:

[0049] S1: Adjust the lower deviation EI of the bearing inner diameter D1 in the direction of decreasing diameter, while keeping the tolerance grade IT1 of the bearing inner diameter D1 unchanged or increasing the tolerance grade IT1 of the bearing inner diameter D1; or,

[0050] Adjust the upper deviation es of journal diameter D3 in the direction of increasing diameter, while keeping the tolerance grade IT3 of journal diameter D3 unchanged or increasing the tolerance grade IT3 of journal diameter D3.

[0051] S2: A radial sliding bearing 1 with an actual inner diameter of D′1 is obtained by machining, and multiple spiral wedge grooves 1-1 are opened on the inner wall surface of the radial sliding bearing 1 with an actual inner diameter of D′1. The spiral wedge grooves 1-1 are set parallel to the bearing axis of the radial sliding bearing 1.

[0052] S3: An arc-shaped groove 1-2 is formed at the maximum clearance between each helical wedge groove 1-1 and the journal 2. The arc-shaped groove 1-2 is arranged parallel to the bearing axis of the radial sliding bearing 1. It can be understood that the number of arc-shaped grooves 1-2 is equal to the number of helical wedge grooves 1-1. The arc-shaped grooves 1-2 and the helical wedge grooves 1-1 correspond one-to-one to form multiple oil supply wedge grooves, and the number of oil supply wedge grooves is also equal to the number of helical wedge grooves 1-1. Optionally, the helical wedge groove 1-1 is axially the same length as the radial sliding bearing 1, with a length of L1; the arc-shaped groove 1-2 is axially the same length as the helical wedge groove 1-1, with a length of L1.

[0053] The multi-wedge groove radial sliding bearing design method of the present invention reduces the fit clearance between the radial sliding bearing 1 and the journal 2 by adjusting the lower deviation EI of the bearing inner diameter D1 in the direction of decreasing diameter, while keeping the tolerance grade IT1 of the bearing inner diameter D1 unchanged or increasing the tolerance grade IT1, or by adjusting the upper deviation es of the journal diameter D3 in the direction of increasing diameter, while keeping the tolerance grade IT3 of the journal diameter D3 unchanged or increasing the tolerance grade IT3. Furthermore, it reduces the fit clearance between the radial sliding bearing 1 and the journal 2 by opening multiple helical wedge grooves 1-1 on the inner wall surface of the radial sliding bearing 1 with an actual bearing inner diameter of D′1, and further opening an arc groove 1-2 at the maximum clearance between each helical wedge groove 1-1 and the journal 2. The helical wedge grooves 1-1 and the arc grooves 1-2 together constitute... The oil supply wedge grooves provide sufficient lubricating oil to the friction pair between the radial sliding bearing 1 and the journal 2. This method ultimately designs a multi-wedge groove radial sliding bearing with a small clearance to the journal 2, enabling stable support of the journal 2 by the radial sliding bearing 1 and preventing shaft vibration. Simultaneously, the multiple oil supply wedge grooves provide sufficient lubricating oil, avoiding insufficient oil supply caused by the reduced clearance. This not only ensures good lubrication of the friction pair between the radial sliding bearing 1 and the journal 2 but also effectively dissipates the high frictional heat generated by the friction pair, achieving effective cooling. Furthermore, the lubricating oil in the multiple oil supply wedge grooves also has a vibration-absorbing effect, ensuring uniform stress on the journal 2 and further preventing shaft vibration, thereby ultimately improving the transmission performance of the shaft system.

[0054] Furthermore, such as Figure 3As shown, in step S2, the spiral wedge groove 1-1 is determined based on the actual bearing inner diameter D′1 of the radial sliding bearing 1. The profile of the spiral wedge groove 1-1 is formed by the intersection of two opposing equal-angle spiral lines. The step of opening multiple spiral wedge grooves 1-1 on the inner wall surface of the radial sliding bearing 1 with an actual bearing inner diameter D′1 includes:

[0055] S21: Select the wrap angle coefficient C of the spiral wedge groove 1-1. α1 The wrap angle coefficient C α1 It is calculated using the following formula.

[0056]

[0057] Wherein, n is the number of spiral wedge grooves 1-1, n≥2, and the preferred value range of n is 2≤n≤6;

[0058] According to the wrap angle coefficient C α1 The wrap angle α1 of the spiral wedge groove 1-1 is determined, and the wrap angle α1 is calculated by the following formula.

[0059] α1=2·π·C α1

[0060] The unit of the wrap angle α1 of the spiral wedge groove 1-1 is rad;

[0061] S22: Determine the initial inner diameter R1 of the helical wedge groove 1-1 based on the actual bearing inner diameter D′1 of the radial sliding bearing 1, wherein the initial inner diameter R1 = D′1 / 2; determine the n initial position points P1, P2, ..., P on the inner wall surface of the radial sliding bearing 1 based on the number n of the helical wedge grooves 1-1. n-1 P n And determine 2n profiles S1, S2, ..., S 2n-1 S 2n The corresponding 2n interior radius inclinations β1, β2, ..., β 2n-1 β 2n , where β1=β2=…β 2n-1 =β 2n The preferred range of values ​​for β1 is...

[0062] Based on the initial inner diameter R1 and the inner diameter inclination β1, β2, ..., β 2n-1 β 2n The profile equation for the spiral wedge groove 1-1 is determined as follows:

[0063] r m =R1·β m θ

[0064] Where, r m For the S-shaped line m The inner diameter, β m For the S-shaped line m The inclination of the inner radius vector, m = 1, 2, ..., 2n-1, 2n; θ is the azimuth angle, in rad, in the interval [0, α1];

[0065] S23: Based on the wrap angle α1 of the spiral wedge groove 1-1 and the initial position points P1, P2, ..., P of the profile... n-1 P n and the curve equation r m =R1·β m θ Draw the profile of the spiral wedge groove 1-1. Machine n spiral wedge grooves 1-1 on the inner wall of the radial sliding bearing 1 with an actual bearing inner diameter of D′1. It can be understood that the n spiral wedge grooves 1-1 are evenly distributed circumferentially. That is, the 2n profiles S1, S2, ..., S1 that make up the profile of the n spiral wedge grooves 1-1 are... 2n-1 S 2n All are equiangular helices, and the profile of each helical wedge groove 1-1 is formed by the intersection of two oppositely drawn equiangular helices, such as... Figure 3 As shown, a spiral wedge groove 1-1 is formed between each adjacent initial position point of the profile, and there are n initial position points P1, P2, ..., Pn. n-1 P n The final profile consists of n spiral wedge grooves 1-1: Starting from the initial position point P1, profile S1 begins at P1, and profile S2 begins at P2. Two profiles S1 and S2, which are essentially equal-angled spirals, are drawn opposite each other until they intersect, forming the first spiral wedge groove 1-1 between adjacent initial position points P1 and P2. This process is repeated until the profile begins at P1. n End, S-shaped line 2n-1 Using the initial position point P of the profile n Starting from point S, the profile line 2n Starting from the initial position point P1 of the profile, the two profiles S are essentially equal-angled spirals. 2n-1 and S 2n Draw relative to each other until they intersect, finally at the initial position point P of the adjacent profile. n The profile of the nth spiral wedge groove 1-1 is formed between P1 and P1.

[0066] Furthermore, such as Figure 4 As shown, the cross-sectional depth h of the arc groove 1-2 in step S3 is calculated using the following formula:

[0067]

[0068] Wherein, C1 is the cross-sectional depth coefficient of the arc groove 1-2, and the preferred value range of C1 is 0 < C1 ≤ 0.5;

[0069] The cross-sectional width b of the arc groove 1-2 is calculated using the following formula.

[0070]

[0071] Wherein, C2 is the cross-sectional width coefficient of the arc groove 1-2, and the preferred value range of C2 is 0 < C2 ≤ 3. Optionally, the arc groove 1-2 is preferably a circular arc groove.

[0072] The present invention also provides a multi-wedge groove radial sliding bearing designed using the multi-wedge groove radial sliding bearing design method described above. It has a clearance fit with the journal 2 and has excellent performance in terms of shaft stability, 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 an arc groove 1-2 is provided at the maximum clearance between each spiral wedge groove 1-1 and the journal 2.

[0073] Specifically, such as Figure 5-6 The diagram illustrates a schematic of the multi-slot radial sliding bearing of the present invention, which is a three-slot radial sliding bearing. It is known that the radial sliding bearing 1 and the journal 2 have a clearance fit. The bearing inner diameter D1 of the radial sliding bearing 1 is 10 mm, the lower deviation EI of the bearing inner diameter D1 is 0.02 mm, the upper deviation ES of the bearing inner diameter D1 is 0.056 mm, and the tolerance grade IT1 of the bearing inner diameter D1 is IT9. The bearing outer diameter D2 of the radial sliding bearing 1 is 12 mm, the bearing length L1 of the radial sliding bearing 1 is 40 mm, the journal diameter is D3 is 10 mm, the lower deviation ei of the journal diameter D3 is -0.013 mm, the upper deviation es of the journal diameter D3 is -0.004 mm, and the tolerance grade IT3 of the journal diameter D3 is IT6. The design method of the above-mentioned multi-slot radial sliding bearing of the present invention will be described below using a three-slot radial sliding bearing as an example.

[0074] In step S1, the lower deviation EI of the bearing inner diameter D1 is adjusted in the direction of decreasing diameter, from 0.02mm to 0mm. Here, the tolerance grade IT1 of the bearing inner diameter D1 is kept constant at IT9, where IT9 = 0.036mm. At this point, the upper deviation ES of the bearing inner diameter D1 = EI + IT9 = 0mm + 0.036mm = 0.036mm; or...

[0075] Adjust the upper deviation es of the journal diameter D3 in the direction of increasing diameter, from -0.004mm to -0.002mm. Keep the tolerance grade IT3 of the journal diameter D3 unchanged at IT6, where IT6 = 0.009mm. At this point, the lower deviation ei of the journal diameter D3 is ei = es - IT6 = -0.002mm - 0.009mm = -0.011mm. All adjustments must maintain a clearance fit between the radial sliding bearing 1 and the journal 2.

[0076] In step S2, a radial sliding bearing 1 with an actual bearing inner diameter D′1 = 10.036 mm is machined. Based on the actual bearing inner diameter D′1 = 10.036 mm of the radial sliding bearing 1, a spiral wedge groove 1-1 is determined. Multiple spiral wedge grooves 1-1 are opened on the inner wall surface of the radial sliding bearing 1 with an actual bearing inner diameter D′1 = 10.036 mm, which are parallel to the bearing axis of the radial sliding bearing 1.

[0077] In step S21, the number of spiral wedge grooves 1-1 is selected as n=3, and the wrap angle coefficient C of the spiral wedge grooves 1-1 is... α1 =1 / (2·n) =1 / 6;

[0078] According to the wrap angle coefficient C α1 Determine the wrap angle α1 of the spiral wedge groove 1-1 as 2·π·C α1 = (π / 3) rad.

[0079] In step S22, the initial inner diameter R1 of the spiral wedge groove 1-1 is determined based on the actual bearing inner diameter D′1 = 10.036 mm of the radial sliding bearing 1. The initial inner diameter R1 = D′1 / 2 = 5.018 mm. Based on the number of spiral wedge grooves 1-1 (n = 3), the initial positions P1, P2, and P3 of the profile of the spiral wedge groove 1-1 on the inner wall of the radial sliding bearing 1 are determined. The inclinations β1, β2, β3, β4, β5, and β6 corresponding to the six profiles S1, S2, S3, S4, S5, and S6 are also determined. The preferred value range for β1 is... The value β1=β2=β3=β4=β5=β6=1.02;

[0080] Based on the initial inner diameter R1 and the inner diameter inclination β1, β2, ..., β 2n-1 β 2n The profile equation for the spiral wedge groove 1-1 is determined as follows:

[0081] r m =5.018mm·1.02 θ

[0082] Where, r m For the S-shaped linem The inner diameter, β m For the S-shaped line m The inclination of the inner radius vector is m = 1, 2, 3, 4, 5, 6; θ is the azimuth angle in rad, and the interval is [0, π / 3].

[0083] In step S23, based on the wrap angle α1 of the spiral wedge groove 1-1, the initial position points P1, P2, P3 of the profile, and the profile equation r... m =5.018mm·1.02 θ Draw the profile of the spiral wedge groove 1-1. Three spiral wedge grooves 1-1 are uniformly machined circumferentially on the inner wall of the radial sliding bearing 1 with an actual inner diameter of D′1. The spiral wedge grooves 1-1 are axially the same length as the radial sliding bearing 1, with a length of L1 = 40mm. Specifically, the six profiles S1, S2, S3, S4, S5, and S6 that make up the three spiral wedge grooves 1-1 are all equiangular helices. Each spiral wedge groove 1-1 profile is formed by the intersection of two oppositely drawn equiangular helices, such as... Figure 5 As shown, a spiral wedge groove 1-1 is formed between each adjacent initial position point of the profile. The three initial position points P1, P2, and P3 ultimately form three spiral wedge grooves 1-1 in the profile: Starting from the initial position point P1, profile S1 takes the initial position point P1 as its starting point, and profile S2 takes the initial position point P2 as its starting point. The two profiles S1 and S2, which are essentially equal-angled spirals, are drawn relative to each other until they intersect to form the first spiral wedge groove 1-1 between the adjacent initial position points P1 and P2; then, profile S3 takes the initial position point P2 as its starting point, and profile S2 takes the initial position point P2 as its starting point. Starting from point P2, profile S4 begins at the initial position point P3. Two profiles S3 and S4, which are essentially equiangular spirals, are drawn relative to each other until they intersect, forming the second spiral wedge groove 1-1 between adjacent initial position points P2 and P3. Finally, starting from the initial position point P3, profile S5 begins at the initial position point P3, and profile S6 begins at the initial position point P1. Two profiles S5 and S6, which are essentially equiangular spirals, are drawn relative to each other until they intersect, ultimately forming the third spiral wedge groove 1-1 between adjacent initial position points P3 and P1.

[0084] In step S3, an arc-shaped groove 1-2, parallel to the bearing axis of the radial sliding bearing 1, is further formed at the maximum clearance between each helical wedge groove 1-1 and the journal 2. The arc-shaped groove 1-2 is a circular arc groove, and the cross-sectional depth coefficient C1 of the arc-shaped groove 1-2 is taken as 0.4. The cross-sectional width coefficient C2 of the arc groove 1-2 is set to 2, and the cross-sectional width of the arc groove 1-2 is... The arc-shaped groove 1-2 is the same length as the spiral wedge groove 1-1 along the axial direction, with a length of L1 = 40mm. Corresponding to the three spiral wedge grooves 1-1, there are also three arc-shaped grooves 1-2. The arc-shaped grooves 1-2 and the spiral wedge grooves 1-1 correspond one-to-one to form three oil supply wedge grooves.

[0085] Thus, the design can be obtained through steps S1-S3. Figure 5-6 The three-wedge-groove radial sliding bearing shown is an example. CFD simulation calculations show that, compared to the radial sliding bearing before optimization, the three-wedge-groove radial sliding bearing designed using the multi-wedge-groove radial sliding bearing design method of this invention reduces mechanical wear rate by 27%, frictional power loss by 13%, and frictional heat generation by 20%. This achieves the goals of shaft system stability, good lubrication, and effective cooling, ultimately improving the transmission performance of the shaft system.

[0086] The above description is merely a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. It should be noted that all modifications or equivalent substitutions made by those skilled in the art without departing from the spirit and technical concept disclosed in the present invention should be included within the scope of protection of the present invention.

Claims

1. A design method for a multi-wedge groove radial sliding bearing, wherein the radial sliding bearing and the journal are clearance fit, the bearing inner diameter is D1, the bearing outer diameter is D2, the bearing length is L1, and the journal diameter is D3, characterized in that, The method includes the following steps: S1: Adjust the lower deviation EI of the bearing inner diameter D1 in the direction of decreasing diameter, while keeping the tolerance grade IT1 of the bearing inner diameter D1 unchanged or increasing the tolerance grade IT1 of the bearing inner diameter D1; or, Adjust the upper deviation es of journal diameter D3 in the direction of increasing diameter, while keeping the tolerance grade IT3 of journal diameter D3 unchanged or increasing the tolerance grade IT3 of journal diameter D3. S2: A radial sliding bearing with an actual inner diameter of D′1 is obtained by machining, and multiple spiral wedge grooves are opened on the inner wall surface of the radial sliding bearing with an actual inner diameter of D′1. The spiral wedge grooves are arranged parallel to the bearing axis of the radial sliding bearing. S3: An arc-shaped groove is opened at the maximum gap between each spiral wedge groove and the journal, and the arc-shaped groove is set parallel to the bearing axis of the radial sliding bearing.

2. The design method for a multi-wedge groove radial sliding bearing according to claim 1, characterized in that, In step S2, the spiral wedge groove is determined based on the actual bearing inner diameter D′1 of the radial sliding bearing. The profile of the spiral wedge groove is formed by the intersection of two opposing equiangular spiral lines. The process of creating multiple spiral wedge grooves on the inner wall of the radial sliding bearing with an actual bearing inner diameter D′1 includes: S21: Select the wrap angle coefficient C of the spiral wedge groove. α1 The wrap angle coefficient C α1 It is calculated using the following formula. Where n is the number of spiral wedge grooves; According to the wrap angle coefficient C α1 The wrap angle α1 of the spiral wedge groove is determined, and the wrap angle α1 is calculated using the following formula. α1＝2·π·C α1 The unit of the wrap angle α1 of the spiral wedge groove is rad; S22: Determine the initial inner diameter R1 of the helical wedge groove as D′1 based on the actual inner diameter of the radial sliding bearing; determine the initial position points P1, P2, ..., P on the inner wall surface of the radial sliding bearing based on the number n of helical wedge grooves. n-1 P n And determine 2n profiles S1, S2, ..., S 2n-1 S 2n The corresponding 2n interior radius inclinations β1, β2, ..., β 2n-1 β 2n , where β1=β2=…=β 2n-1 =β 2n ; Based on the initial inner diameter R1 and the inner diameter inclination β1, β2, ..., β 2n-1 β 2n The profile equation for the helical wedge groove is determined as follows: r m ＝R1·β m θ Where, r m For the S-shaped line m The inner diameter, β m For the S-shaped line m The inclination of the inner radius vector, m = 1, 2, ..., 2n-1, 2n; θ is the azimuth angle, in rad, in the interval [0, α1]; S23: Based on the wrap angle α1 of the spiral wedge groove and the initial position points P1, P2, ..., P of the profile... n-1 P n and the curve equation r m =R1·β m θ n spiral wedge grooves are machined on the inner wall surface of a radial sliding bearing with an actual bearing inner diameter of D′1.

3. The design method for a multi-wedge groove radial sliding bearing according to claim 2, characterized in that, The cross-sectional depth h of the arc-shaped groove in step S3 is calculated using the following formula. Where C1 is the section depth coefficient of the arc groove; The cross-sectional width b of the arc-shaped groove is calculated using the following formula. Where C2 is the cross-sectional width coefficient of the arc groove.

4. The design method for a multi-wedge groove radial sliding bearing according to claim 3, characterized in that, The spiral wedge groove is the same length as the radial sliding bearing along the axial direction; the arc-shaped groove is the same length as the spiral wedge groove along the axial direction.

5. The design method for a multi-wedge groove radial sliding bearing according to claim 3, characterized in that, The inner diameter inclination β1 of the profile S1 is preferably...

6. The design method for a multi-wedge groove radial sliding bearing according to claim 3, characterized in that, The preferred depth coefficient C1 of the arc-shaped groove is 0 < C1 ≤ 0.

5.

7. The design method for a multi-wedge groove radial sliding bearing according to claim 3, characterized in that, The cross-sectional width coefficient C2 of the arc-shaped groove is preferably 0 < C2 ≤ 3.

8. The design method for a multi-wedge groove radial sliding bearing according to claim 3, characterized in that, The number n of the spiral wedge grooves is preferably 2≤n≤6.

9. A multi-wedge groove radial sliding bearing, with a clearance fit to the journal, characterized in that, The multi-wedge groove radial sliding bearing is designed using the multi-wedge groove radial sliding bearing design method as described in any one of claims 1-8. The inner wall surface of the multi-wedge groove radial sliding bearing is provided with a plurality of spiral wedge grooves, and an arc groove is provided at the maximum gap between each spiral wedge groove and the journal.

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