Center offset type line sliding bearing

Abstract

The application relates to a circular center offset type line sliding bearing and belongs to the technical field of sliding bearing application. The purpose of the application is to solve the problem that the existing fixed type line sliding bearing cannot meet the use requirement of multiple stress directions under the limit use index. The inner circumferential surface of a bearing body is covered by an alloy, the alloy surface is covered by three sections of type lines, the three sections of type lines are arranged along the inner circumferential direction of the bearing body in sequence, the thickness of each section of type line gradually increases along the clockwise direction in sequence, the angle formed by the three sections of type lines along the clockwise direction is alpha, beta and gamma in sequence, alpha is approximately equal to gamma and greater than beta, a rotor is located at the central axis position in the bearing body, and a gap is left between the bearing body and the rotor; and the bearing is used for providing multiple stress directions.

Description

Technical Field

[0001] This invention relates to the structure of sliding bearings and belongs to the field of sliding bearing application technology. Background Technology

[0002] Sliding bearings are widely used in rotating machinery. In high-power, high-speed, single-stage gear transmission devices, sliding bearings are generally used under high-speed and heavy-load conditions. Currently, the maximum allowable linear velocity of fixed-type sliding bearings with a single force direction is 90 m / s, and the maximum allowable specific pressure is 3.5 MPa.

[0003] For certain specific applications, a single-stage gear transmission device must function as both a speed-increasing and speed-reducing device; that is, the external device connected by the high-speed and low-speed gears of the gear transmission device can function as both a driving device and a load-bearing device. In this case, the force angle of the sliding bearing under full load is distributed on both sides along the line connecting the high-speed and low-speed gears. Existing fixed-profile sliding bearings cannot meet the above requirements for multi-direction force application under extreme performance conditions. Summary of the Invention

[0004] The purpose of this invention is to solve the problem that existing fixed profile sliding bearings cannot meet the requirements for use in multiple force directions under extreme performance conditions, and to propose a center-offset profile sliding bearing.

[0005] A center-offset profile sliding bearing, comprising a bearing housing, a rotor, three profile sections, and an alloy;

[0006] The inner circumferential surface of the bearing housing is covered by an alloy, and the alloy surface is covered by three profiles. The three profiles are arranged sequentially along the inner circumferential direction of the bearing housing, and the thickness of each profile gradually increases in the clockwise direction. The angles formed by the three profiles in the clockwise direction are α, β and γ, respectively, where α≈γ>β. The rotor is located at the central axis position of the bearing housing, and a gap is left between the bearing housing and the rotor.

[0007] Based on Formulas 1, 2, and 3, the diameter Φdε of the circle formed by connecting the centers of the three 3-segment profiles, the diameter φd of the inscribed circle formed by the three 3-segment profiles, the rotor diameter φds, and the radius R of the outer circle formed by the three 3-segment profiles are defined.

[0008]

[0009]

[0010]

[0011] The process of obtaining φd, φds, R, and Φdε:

[0012] The bearing body is divided into an upper bearing and a lower bearing along the axis X to the axis -X direction of the split surface of the bearing body. Three profiles are machined on the alloy surface, which are divided by the axis M, the axis -X and the axis N respectively. The outer diameter of the bearing body is φdo, the center of the outer circle is point O, and the diameter of the rotor that mates with the bearing body is φds.

[0013] The angle region α between axis -X and axis M is profile C1, the angle region β between axis M and axis N is profile C2, and the angle region γ between axis -X and axis N is profile C3.

[0014] The center point O1 of the profile C1 is located on the axis -X, the center point O2 of the profile C2 is located on the axis M, and the center point O3 of the profile C3 is located on the axis N.

[0015] The diameter of the circle formed by center points O1, O2, and O3 with center point O as the center is φdε. The profile C1 is formed with center point O1 as the center reference and the profile machining radius R; the profile C2 is formed with center point O2 as the center reference and the profile machining radius R; the profile C3 is formed with center point O3 as the center reference and the profile machining radius R.

[0016] The extension line C1ex of profile C1 extends from the center point O to the axis X direction; the extension line C2ex of profile C2 extends from the axis M to the center point O direction; the extension line C3ex of profile C3 extends from the axis N to the center point O direction, and the distance from the center point O to the end point of the extension line C1ex, the distance to the end point of the extension line C2ex, and the distance to the end point of the extension line C3ex are all λ.

[0017] With center point O as the center and distance λ as the radius, form a three-segment inscribed circle with diameter φd, where φd = 2λ. The bearing body area enclosed by profile C1 is the first load-bearing area, the bearing body area enclosed by profile C2 is the non-load-bearing area, and the bearing body area enclosed by profile C3 is the second load-bearing area. The bearing force in the first load-bearing area is F1, and the bearing force in the second load-bearing area is F3. The angle between axis -X and bearing force F1 is α / 2, the angle between bearing force F1 and axis M is α / 2, the angle between axis -X and bearing force F3 is γ / 2, and the angle between bearing force F1 and axis N is γ / 2.

[0018] The rotor rotates unidirectionally clockwise within the bearing housing. The difference between the inscribed circle φd and the rotor diameter φds is the theoretical bearing diameter clearance (φd-φds). The difference between the machined diameter 2R corresponding to the radius R and the rotor diameter φds is the machined bearing diameter clearance (2R-φds).

[0019] The ratio of the theoretical bearing diameter clearance (φd-φds) to the inscribed circle φds is 0.0015-0.0020, thus yielding Formula 1;

[0020] The formula relationship between the theoretical bearing diameter clearance (φd-φds) and the machined bearing diameter clearance (2R-φds) is Formula 2;

[0021] The formula relationship between the inscribed circle φd of the profile, the machining radius R of the profile, and the diameter φdε of the offset center distribution circle is Formula 3.

[0022] Preferably, the sliding bearing further includes three oil inlet holes and three oil drain chambers;

[0023] The three oil inlets are named the first load-bearing zone oil inlet, the non-load-bearing zone oil inlet, and the second load-bearing zone oil inlet, respectively.

[0024] The three oil drain chambers are named the first load-bearing area oil drain chamber, the non-load-bearing area oil drain chamber, and the second load-bearing area oil drain chamber, respectively.

[0025] Along a clockwise direction, a first bearing area oil inlet hole is machined at the front of the inner surface of the first bearing area profile, and a first bearing area oil drain cavity is machined at the end of the inner surface of the first bearing area profile; a non-bearing area oil inlet hole is machined at the front of the non-bearing area profile, and a non-bearing area oil drain cavity is machined at the end of the non-bearing area profile; a second bearing area oil inlet hole is machined at the front of the second bearing area profile, and a second bearing area oil drain cavity is machined at the end of the second bearing area profile;

[0026] The oil inlet holes in the first load-bearing area, the non-load-bearing area, and the second load-bearing area are all radially arranged and extend from the profile to the outer circumference of the bearing body.

[0027] The first load-bearing area oil drain chamber, the non-load-bearing area oil drain chamber, and the second load-bearing area oil drain chamber all extend axially from one end face of the bearing body to the other end face.

[0028] Preferably, the sliding bearing further includes three oil inlet grooves;

[0029] The three oil inlet tanks are named the first load-bearing area oil inlet tank, the non-load-bearing area oil inlet tank, and the second load-bearing area oil inlet tank, respectively.

[0030] Along a clockwise direction, a first bearing area oil inlet groove is machined on the front part of the inner surface of the first bearing area profile; a non-bearing area oil inlet groove is machined on the front part of the non-bearing area profile; and a second bearing area oil inlet groove is machined on the front part of the second bearing area profile.

[0031] The first bearing area oil inlet groove is connected to the first bearing area oil inlet hole;

[0032] The oil inlet groove in the non-load-bearing area is connected to the oil inlet hole in the non-load-bearing area;

[0033] The oil inlet groove of the second bearing area is connected to the oil inlet hole of the second bearing area.

[0034] Preferably, the sliding bearing further includes three oil outlet grooves;

[0035] The three oil outlet channels are named the first load-bearing area oil outlet channel, the non-load-bearing area oil outlet channel, and the second load-bearing area oil outlet channel, respectively.

[0036] A first bearing area oil outlet groove is machined on the rear part of the inner surface of the first bearing area profile; a non-bearing area oil outlet groove is machined on the rear part of the inner surface of the non-bearing area profile; and a second bearing area oil outlet groove is machined on the rear part of the inner surface of the second bearing area profile.

[0037] The equivalent length of each oil inlet groove along the circumference is greater than the equivalent length of each oil outlet groove along the circumference.

[0038]

[0039] The beneficial effects of this invention are:

[0040] This application provides three profile lines on the inner circumferential surface of the bearing body. The angles formed by the three profile lines are α, β and γ respectively, where α≈γ>β. This allows the bearing to withstand multiple forces. Therefore, this application can be used as both a speed-increasing device and a speed-reducing device, improving its adaptability to the direction of force.

[0041] The maximum linear velocity of the sliding bearing under multiple force directions can be applied up to 95 m / s; the maximum specific pressure of the sliding bearing under multiple force directions can be applied up to 4 MPa; and the maximum temperature of the bearing oil film corresponding to the maximum applied linear velocity and maximum applied specific pressure is relatively low.

[0042] This application divides each oil groove into an inlet groove and an outlet groove, making the circumferential equivalent length of the inlet groove greater than that of the outlet groove. This arrangement allows more lubricating oil to be filled into the inlet groove, and the lubricating oil is supplied to the inner surface of the corresponding bearing area under rotor rotation, resulting in better lubrication between the rotor and the profile. This leads to a higher order of magnitude of dynamic performance parameters of bearing oil film stiffness and oil film damping, thereby improving the stability of the supported rotor operation. Attached Figure Description

[0043] Figure 1 This is a schematic diagram of a center-offset profile sliding bearing.

[0044] Figure 2 A schematic diagram of the machining dimensions for a center-offset profile sliding bearing;

[0045] Figure 3 for Figure 2 A schematic diagram of the radial cross-sectional structure;

[0046] Figure 4This is a schematic diagram of the machining structure of the oil inlet, oil groove, and oil drain chamber in a center-offset profile sliding bearing.

[0047] Figure 5 A three-dimensional structural diagram of a center-offset profile sliding bearing viewed from the left.

[0048] Figure 6 A three-dimensional structural diagram of a center-offset profile sliding bearing viewed from the right.

[0049] Figure 7 A three-dimensional structural diagram of the upper part of the bearing body;

[0050] Figure 8 This is a three-dimensional structural diagram of the lower half of the bearing housing. Detailed Implementation

[0051] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0052] It should be noted that, unless otherwise specified, the embodiments and features described in the present invention can be combined with each other.

[0053] The present invention will be further described below with reference to the accompanying drawings and specific embodiments, but this is not intended to limit the scope of the invention.

[0054] In existing technologies, fixed-profile sliding bearings cannot meet the requirements for use in multiple force directions under extreme operating conditions. To address this technical problem, embodiments of the present invention propose a center-offset profile sliding bearing, thereby meeting the requirements for use in multiple force directions under extreme operating conditions.

[0055] Example 1:

[0056] Reference Figure 1 and Figure 2 In this embodiment, a center-offset profile sliding bearing is provided. The sliding bearing includes a bearing body 1, a rotor 2, three profile sections 3, and an alloy.

[0057] The inner circumferential surface of the bearing body 1 is covered by an alloy, and the alloy surface is covered by three profile lines 3. The three profile lines 3 are arranged sequentially along the inner circumferential direction of the bearing body 1, and the thickness of each profile line 3 gradually increases in the clockwise direction. The angles formed by the three profile lines 3 in the clockwise direction are α, β and γ, respectively, where α≈γ>β. The rotor 2 is located at the central axis position inside the bearing body 1, and a gap 15 is left between the bearing body 1 and the rotor 2.

[0058] According to Formulas 1, 2 and 3, the diameter Φdε of the circle formed by connecting the centers of the three circles of the three profile 3, the diameter φd of the inscribed circle formed by the three profile 3, the rotor diameter φds and the radius R of the outer circle formed by the three profile 3 are defined.

[0059]

[0060]

[0061]

[0062] The process of obtaining φd, φds, R, and Φdε:

[0063] The bearing body 1 is divided into an upper bearing 1-1 and a lower bearing 1-2 along the axis X to the axis -X of the dividing surface in the bearing body 1. Three profiles are machined on the alloy surface, which are divided by the axis M, the axis -X and the axis N respectively. The outer diameter of the bearing body 1 is φdo and the center of the outer circle is point O. The diameter of the rotor that mates with the bearing body 1 is φds.

[0064] The angle region α between axis -X and axis M is profile C1, the angle region β between axis M and axis N is profile C2, and the angle region γ between axis -X and axis N is profile C3.

[0065] The center point O1 of the profile C1 is located on the axis -X, the center point O2 of the profile C2 is located on the axis M, and the center point O3 of the profile C3 is located on the axis N.

[0066] The diameter of the circle formed by center points O1, O2, and O3 with center point O as the center is φdε. The profile C1 is formed with center point O1 as the center reference and the profile machining radius R; the profile C2 is formed with center point O2 as the center reference and the profile machining radius R; the profile C3 is formed with center point O3 as the center reference and the profile machining radius R.

[0067] The extension line C1ex of profile C1 extends from the center point O to the axis X direction; the extension line C2ex of profile C2 extends from the axis M to the center point O direction; the extension line C3ex of profile C3 extends from the axis N to the center point O direction, and the distance from the center point O to the end point of the extension line C1ex, the distance to the end point of the extension line C2ex, and the distance to the end point of the extension line C3ex are all λ.

[0068] With center point O as the center and distance λ as the radius, form a three-segment inscribed circle with diameter φd, where φd = 2λ. The bearing body 1 area enclosed by profile C1 is the first load-bearing area 1, the bearing body 1 area enclosed by profile C2 is the non-load-bearing area 2, and the bearing body 1 area enclosed by profile C3 is the second load-bearing area 3. The bearing force in the first load-bearing area 1 is F1, and the bearing force in the second load-bearing area 3 is F3. The angle between axis -X and bearing force F1 is α / 2, the angle between bearing force F1 and axis M is α / 2, the angle between axis -X and bearing force F3 is γ / 2, and the angle between bearing force F1 and axis N is γ / 2.

[0069] The rotor 2 rotates unidirectionally clockwise within the bearing housing 1. The difference between the inscribed circle φd of the profile and the rotor 2 diameter φds is the theoretical bearing diameter clearance (φd-φds). The difference between the profile machining diameter 2R corresponding to the radius R and the rotor diameter φds is the bearing machining diameter clearance (2R-φds).

[0070] The ratio of the theoretical bearing diameter clearance (φd-φds) to the inscribed circle φds is 0.0015-0.0020, thus yielding Formula 1;

[0071] The formula relationship between the theoretical bearing diameter clearance (φd-φds) and the machined bearing diameter clearance (2R-φds) is Formula 2;

[0072] The formula relationship between the inscribed circle φd of the profile, the machining radius R of the profile, and the diameter φdε of the offset center distribution circle is Formula 3.

[0073] In this embodiment, high-power, high-speed gear transmission devices often use sliding bearings. For certain specific applications, a single-stage gear transmission device is required to function as both a speed-increasing and speed-reducing device; that is, the external device connected to the high-speed and low-speed gears of the gear transmission device can function as both a driving device and a load device. In this case, the force angle of the sliding bearing under full load is distributed along the line connecting the high-speed and low-speed gears on both sides. Existing fixed-profile sliding bearings cannot meet the above-mentioned requirements for multiple force directions under extreme performance conditions.

[0074] This application improves the adaptability of sliding bearings to the direction of force under the above-mentioned usage conditions by optimizing the profile of conventionally designed high-speed, heavy-duty sliding bearings.

[0075] Combined with appendix Figure 1 - Appendix Figure 8As shown. The circular offset profile sliding bearing described in this application consists of two halves: the upper half bearing 1-2 has an upper half bearing alloy 13 cast on it, and the lower half bearing 1-2 has a lower half bearing alloy 14 cast on it. The angle region α between axis -X and axis M is profile C1, corresponding to load-bearing area 1; the angle region β between axis M and axis N is profile C2, corresponding to non-load-bearing area 2; and the angle region γ between axis -X and axis N is profile C3, corresponding to load-bearing area 3.

[0076] The angle region α corresponding to the first load-bearing area 1 is greater than the angle region β corresponding to the non-load-bearing area 2, and the angle region γ corresponding to the second load-bearing area 3 is greater than the angle region β corresponding to the non-load-bearing area 2. Therefore, the first load-bearing area 1 and the second load-bearing area 3 mainly bear the bearing force when the single-stage gear transmission device can be used as both a speed-increasing device and a speed-reducing device in specific situations.

[0077] Under this usage, the bearing forces F1 and F3 are basically mirror images of each other along the axis from -X to X; the angle between the axis -X and the bearing force F1 is α / 2, the angle between the bearing force F1 and the axis M is α / 2; the angle between the axis -X and the bearing force F3 is γ / 2, the angle between the bearing force F1 and the axis N is γ / 2; that is, α≈γ.

[0078] At the initial stage of machining, the outer diameter φdo of the bearing is first machined. Then, using the outer diameter φdo as a reference, the inner diameter of the bearing is rough machined to a size less than the inscribed circle diameter φd of the bearing profile.

[0079] After the rough machining of the bearing inner circle is completed, the oil inlet, oil groove, and oil drain cavity are machined. To ensure that more lubricating oil enters the corresponding profile areas of the three oil grooves, the center lines E, G, and H of the oil inlet holes in the first load-bearing area 1, M, and N are offset by a distance k along axes -X, M, and N, respectively. The center point of the oil groove machining is the intersection of the center point O, the offset diameter φdg of the oil groove machining, and the three offset axes: Os1 for the first load-bearing area 1, Os2 for the non-load-bearing area 2, and Os3 for the second load-bearing area 3. The three oil grooves are machined by setting a machining radius r. After the three oil grooves are machined, the equivalent length a of the oil groove inlet area is greater than or equal to the equivalent length b of the oil groove outlet area. The first load-bearing area oil drain cavity is machined in a rectangle with axis M as the reference, the non-load-bearing area oil drain cavity is machined in a rectangle with axis N as the reference, and the second load-bearing area oil drain cavity is machined with axis X as the reference. All three oil drain cavities extend axially from one end face of the sliding bearing to the other end face.

[0080] After completing the above-mentioned finishing of the outer circle, roughing of the inner circle, machining of the oil inlet hole, machining of the oil groove, and machining of the oil drain cavity, the finishing of the inner circle profile begins.

[0081] Based on the given rotor diameter φds, the bearing profile inscribed circle diameter φd, profile machining radius R, and offset center distribution circle diameter φdε are obtained according to the following formulas 1, 2, and 3.

[0082]

[0083]

[0084]

[0085] By setting the intersection points of the distribution circle with the diameter φdε of the center point O and the axis -X, axis M, and axis N as the machining center points O1, O2, and O3 of the profile C1, the bearing alloy is machined into three profile areas with a machining radius R.

[0086] Lubricating oil enters the bearing through the first load-bearing area inlet 4, the non-load-bearing area inlet 6, and the second load-bearing area inlet 7. After entering the first load-bearing area inlet 4, the lubricating oil fills the first load-bearing area inlet groove and, under the action of the rotor's rotation ω, rotates into the profile C1 that aligns with the rotor diameter. In the gap area between the profile C1 and the non-load-bearing area, due to the offset of the center O1, the lubricating oil swirls from the larger gap area to the smaller gap area, and finally drains out into the first load-bearing area oil drain chamber 9; after entering the non-load-bearing area oil inlet hole 6, the lubricating oil fills the non-load-bearing area oil inlet groove, and under the action of the rotor rotation ω, it swirls into the profile C2 and the rotor diameter. In the gap area between the two sections, due to the offset of the center O2 of profile C2, the lubricating oil swirls from the larger gap area to the smaller gap area, and finally drains out into the non-load-bearing area oil drain chamber 10; after entering the oil inlet 7 of the second load-bearing area, the lubricating oil fills the oil groove of the second load-bearing area, and under the action of the rotor rotation ω, it swirls into the profile C3 and the rotor diameter. Due to the offset of the center O3 of profile C3, the lubricating oil swirls from the larger gap area to the smaller gap area within the bearing, eventually draining out into the second bearing area's oil drain chamber 8. Within the bearing, the lubricating oil swirls from the larger gap area to the smaller gap area. Under the eccentric operation of the rotor, this further increases the wedge-shaped area of ​​the gap between the bearing and the rotor, thereby improving the bearing's specific pressure performance and linear velocity performance. The dynamic performance parameters of the bearing oil film stiffness and oil film damping corresponding to this profile are on the order of magnitude higher, thus improving the stability of the supported rotor operation.

[0087] The necessary condition for the formation of an oil film in a hydrodynamic lubrication sliding bearing is that a converging wedge-shaped region must be formed between the relatively moving rotor and the bearing, and the rotor's motion direction must ensure that the lubricating oil flows in from the larger gap and out from the smaller gap. By using formulas and empirical parameters to define the three-segment profiles C1, C2, and C3 corresponding to the offset centers O1, O2, and O3, compared to conventional sliding bearing structures, the effect of forming a converging wedge-shaped region between the rotor and bearing, as well as the effect of lubricating oil flowing in from the larger gap and out from the smaller gap, are enhanced. Especially under the effect of rotor eccentricity, the wedge-shaped region effect between the bearing and rotor is further increased on the basis of concentricity between the rotor and bearing (center O), thereby improving the bearing's specific pressure performance and linear velocity performance. The dynamic performance parameters of the bearing oil film stiffness and oil film damping corresponding to this profile are on the order of magnitude higher, thus improving the stability of the supported rotor operation.

[0088] The advantages of this bearing design with three curved surfaces are:

[0089] The inner circumferential surface of the bearing consists of three arc surfaces. The force F1 is borne in the first load-bearing area at angle α, and the direction of F1 is the centerline direction of the first load-bearing area (the angle between the axis-X and the bearing force F1 is α / 2, and the angle between the bearing force F1 and the axis M is α / 2). The force F3 is borne in the non-load-bearing area at angle γ, and the direction of F3 is the centerline direction of the non-load-bearing area (the angle between the axis-X and the bearing force F3 is γ / 2, and the angle between the bearing force F1 and the axis N is γ / 2). Therefore, the bearing bears one force in each of the first load-bearing area, the second load-bearing area, and the non-load-bearing area, so the bearing can bear multiple forces.

[0090] In a preferred embodiment, the sliding bearing further includes three oil inlet holes and three oil drain chambers;

[0091] The three oil inlets are named the first load-bearing area oil inlet 4, the non-load-bearing area oil inlet 6, and the second load-bearing area oil inlet 7, respectively.

[0092] The three oil drain chambers are named the first load-bearing area oil drain chamber 9, the non-load-bearing area oil drain chamber 10, and the second load-bearing area oil drain chamber 8, respectively.

[0093] Along a clockwise direction, a first bearing zone oil inlet hole 4 is machined at the front of the inner surface of the first bearing zone type 1 line, and a first bearing zone oil drain cavity 9 is machined at the end of the inner surface of the first bearing zone type 1 line; a non-bearing zone oil inlet hole 6 is machined at the front of the non-bearing zone type 2 line, and a non-bearing zone oil drain cavity 10 is machined at the end of the non-bearing zone type 2 line; a second bearing zone oil inlet hole 7 is machined at the front of the second bearing zone type 3 line, and a second bearing zone oil drain cavity 8 is machined at the end of the second bearing zone type 3 line;

[0094] The first load-bearing area oil inlet 4, the non-load-bearing area oil inlet 6, and the second load-bearing area oil inlet 7 are all radially opened, and all extend from the profile 3 to the outer circumference of the bearing body 1.

[0095] The first load-bearing area oil drain chamber 9, the non-load-bearing area oil drain chamber 10, and the second load-bearing area oil drain chamber 8 all extend axially from one end face of the bearing body 1 to the other end face.

[0096] In a preferred embodiment, the sliding bearing further includes three oil inlet grooves;

[0097] The three oil inlet tanks are named the first load-bearing area oil inlet tank 5-1, the non-load-bearing area oil inlet tank 11-2, and the second load-bearing area oil inlet tank 12-2, respectively.

[0098] Along the clockwise direction, the first bearing area oil inlet groove 5-1 is machined on the front part of the inner surface of the first bearing area type 1 line; the non-bearing area oil inlet groove 11-2 is machined on the front part of the non-bearing area type 2 line; and the second bearing area oil inlet groove 12-2 is machined on the front part of the second bearing area type 3 line.

[0099] The first bearing area oil inlet groove 5-1 is connected to the first bearing area oil inlet hole 4;

[0100] The non-load-bearing zone oil inlet groove 11-2 is connected to the non-load-bearing zone oil inlet hole 6;

[0101] The second bearing area oil inlet groove 12-2 is connected to the second bearing area oil inlet hole 7.

[0102] In a preferred embodiment, the sliding bearing further includes three oil outlet grooves;

[0103] The three oil outlet channels are named the first bearing area oil outlet channel 11-1, the non-bearing area oil outlet channel 12-1, and the second bearing area oil outlet channel 5-2, respectively.

[0104] Oil outlet groove 11-1 of the first bearing area is machined on the rear part of the inner surface of the first bearing area type 1 line; oil outlet groove 12-1 of the non-bearing area is machined on the rear part of the inner surface of the non-bearing area type 2 line; oil outlet groove 5-2 of the second bearing area is machined on the rear part of the inner surface of the second bearing area type 3 line.

[0105] The equivalent length of each oil inlet groove along the circumference is greater than the equivalent length of each oil outlet groove along the circumference.

[0106] In this embodiment, lubricating oil is filled into each oil inlet, and the lubricating oil flowing out from each oil inlet enters the oil groove. As the bearing body 1 rotates clockwise, the lubricating oil in each oil groove flows along the corresponding arc surface 3 to the next oil groove and is discharged from the drain chamber of the next oil groove.

[0107] Preferred implementation method,

[0108] from Figure 4It can be seen that the machining positions of the oil inlet holes are: the center line E of the oil inlet hole in the first bearing area, the center line G of the oil inlet hole in the non-bearing area, and the center line H of the oil inlet hole in the second bearing area are offset by a distance k along the axis -X, axis M, and axis N, respectively; the machining positions of the oil grooves are: the center point of the oil groove machining is taken as the intersection of the center point O, the oil groove machining offset diameter Φdg, and the three offset axes (the center point of the oil groove machining in the first bearing area Os1, the center point of the oil groove machining in the non-bearing area Os2, and the center point of the oil groove machining in the second bearing area Os3), and three oil grooves are machined by setting the machining radius r.

[0109] The movement process of the lubricating oil in this application is as follows:

[0110] The bearing housing and the three curved surfaces remain stationary; only the rotor rotates clockwise. The lubricating oil filling the first load-bearing area oil inlet 4, the non-load-bearing area oil inlet 6, and the second load-bearing area oil inlet 7 is high-pressure oil. Due to its high pressure, the high-pressure lubricating oil enters the corresponding oil inlet groove after entering through the inlet hole. Only a small amount of lubricating oil falls into the outlet groove, or none at all. The high pressure of the lubricating oil, combined with the rotor's clockwise rotation (reaching a maximum linear velocity of 95 m / s), causes the oil in the inlet groove to... The lubricating oil enters the corresponding arc surface and then flows into the oil outlet groove on the corresponding arc surface, and is discharged from the oil drain chamber corresponding to the oil outlet groove. In addition, the purpose of setting an oil drain chamber at the end of each arc surface is: for example, if the lubricating oil temperature entering through the oil inlet is 45 degrees, the lubricating oil temperature may rise to 67 degrees after passing through each arc surface. Therefore, to prevent the lubricating oil at this temperature from continuing to flush the next arc surface, the lubricating oil at this temperature must be discharged in time. Therefore, this application sets an oil drain chamber at the end of each arc surface, which can not only lubricate the arc surface in time, but also quickly discharge the high-temperature lubricating oil.

[0111] In this embodiment, from Figure 4 As can be seen from the data, the equivalent circumferential length of the first bearing area oil inlet groove 5-1, the non-bearing area oil inlet groove 11-2, and the second bearing area oil inlet groove 12-2 is 'a', and the equivalent circumferential length of the second bearing area oil outlet groove 5-2, the first bearing area oil outlet groove 11-1, and the non-bearing area oil outlet groove 12-1 is 'b'.

[0112] In designing the oil inlet and outlet structures, this application makes the circumferential equivalent length of the oil inlet groove greater than the circumferential equivalent length of the oil outlet groove. The purpose is that with a larger circumferential equivalent length of the oil inlet groove, more lubricating oil can be filled in, and more lubricating oil will be provided to the inner surface of the corresponding bearing area during rotation, so that the lubrication between the rotor and the arc surface is better, thereby improving the stability of the rotor operation.

[0113] In this embodiment, from Figure 3As can be seen, an oil drain chamber is set at the end of each arc surface. The purpose of this setting is that after the lubricating oil has finished lubricating a complete arc surface, the high-temperature lubricating oil is discharged from the end of the arc surface.

[0114] While the invention has been described herein with reference to specific embodiments, it should be understood that these embodiments are merely examples of the principles and applications of the invention. Therefore, it should be understood that many modifications can be made to the exemplary embodiments, and other arrangements can be designed without departing from the spirit and scope of the invention as defined by the appended claims. It should be understood that different dependent claims and features described herein can be combined in ways different from those described in the original claims. It is also understood that features described in conjunction with individual embodiments can be used in other described embodiments.

Claims

1. A center-offset profile sliding bearing, characterized in that, The sliding bearing includes a bearing body (1), a rotor (2), three profiles (3), and an alloy; The inner circumferential surface of the bearing body (1) is covered by an alloy, and the alloy surface is covered by three profiles (3). The three profiles (3) are arranged sequentially along the inner circumferential direction of the bearing body (1), and the thickness of each profile (3) gradually increases in the clockwise direction. The angles formed by the three profiles (3) in the clockwise direction are α, β and γ, respectively, where α≈γ>β. The rotor (2) is located at the central axis position inside the bearing body (1), and a gap (15) is left between the bearing body (1) and the rotor (2). According to Formulas 1, 2 and 3, the diameter Φdε of the circle formed by connecting the three centers of the three profiles (3), the diameter φd of the inscribed circle formed by the three profiles (3), the rotor diameter φds and the radius R of the outer circle formed by the three profiles (3) are defined. The process of obtaining φd, φds, R, and Φdε: Along the axis X to the axis-X direction of the dividing surface of the bearing body (1), the bearing body (1) is divided into an upper bearing (1-1) and a lower bearing (1-2). Three profiles are machined on the alloy surface, which are divided by the axis M, the axis-X and the axis N respectively. The outer diameter of the bearing body (1) is φdo, the center of the outer circle is point O, and the diameter of the rotor that mates with the bearing body (1) is φds. The angle region α between axis -X and axis M is profile C1, the angle region β between axis M and axis N is profile C2, and the angle region γ between axis -X and axis N is profile C3. The center point O1 of the profile C1 is located on the axis -X, the center point O2 of the profile C2 is located on the axis M, and the center point O3 of the profile C3 is located on the axis N. The diameter of the circle formed by center points O1, O2, and O3 with center point O as the center is φdε. The profile C1 is formed with center point O1 as the center reference and the profile machining radius R; the profile C2 is formed with center point O2 as the center reference and the profile machining radius R; the profile C3 is formed with center point O3 as the center reference and the profile machining radius R. The extension line C1ex of profile C1 extends from the center point O to the axis X direction; the extension line C2ex of profile C2 extends from the axis M to the center point O direction; the extension line C3ex of profile C3 extends from the axis N to the center point O direction, and the distance from the center point O to the end point of the extension line C1ex, the distance to the end point of the extension line C2ex, and the distance to the end point of the extension line C3ex are all λ. With the center point O as the center and the distance λ as the radius, form a three-segment inscribed circle with diameter φd (3), where φd = 2λ. The bearing body (1) area enclosed by the profile C1 is the first bearing area (1), the bearing body (1) area enclosed by the profile C2 is the non-bearing area (2), and the bearing body (1) area enclosed by the profile C3 is the second bearing area (3). The bearing force in the first bearing area (1) is F1, and the bearing force in the second bearing area (3) is F3. The angle between the axis -X and the bearing force F1 is α / 2, the angle between the bearing force F1 and the axis M is α / 2, the angle between the axis -X and the bearing force F3 is γ / 2, and the angle between the bearing force F1 and the axis N is γ / 2. The rotor (2) rotates clockwise unidirectionally within the bearing housing (1). The difference between the inscribed circle φd of the profile and the rotor (2) diameter φds is the theoretical bearing diameter clearance (φd-φds). The difference between the profile machining diameter 2R corresponding to the radius R and the rotor diameter φds is the bearing machining diameter clearance (2R-φds). The ratio of the theoretical bearing diameter clearance (φd-φds) to the inscribed circle φds is 0.0015-0.0020, thus yielding Formula 1; The formula relationship between the theoretical bearing diameter clearance (φd-φds) and the machined bearing diameter clearance (2R-φds) is Formula 2; The formula relationship between the inscribed circle φd of the profile, the machining radius R of the profile, and the diameter φdε of the offset center distribution circle is Formula 3.

2. The circular offset profile sliding bearing according to claim 1, characterized in that, The sliding bearing also includes three oil inlet holes and three oil drain chambers; The three oil inlets are named the first bearing area oil inlet (4), the non-bearing area oil inlet (6), and the second bearing area oil inlet (7), respectively. The three oil drain chambers are named the first load-bearing area oil drain chamber (9), the non-load-bearing area oil drain chamber (10), and the second load-bearing area oil drain chamber (8), respectively. Along the clockwise direction, a first bearing area oil inlet hole (4) is machined at the front of the inner surface of the first bearing area (1) profile, and a first bearing area oil drain cavity (9) is machined at the end of the inner surface of the first bearing area (1) profile; a non-bearing area oil inlet hole (6) is machined at the front of the non-bearing area (2) profile, and a non-bearing area oil drain cavity (10) is machined at the end of the non-bearing area (2) profile; a second bearing area oil inlet hole (7) is machined at the front of the second bearing area (3) profile, and a second bearing area oil drain cavity (8) is machined at the end of the second bearing area (3) profile; The first bearing area oil inlet (4), the non-bearing area oil inlet (6), and the second bearing area oil inlet (7) are all radially opened and extend from the profile (3) to the outer circumference of the bearing body (1). The first load-bearing area oil drain chamber (9), the non-load-bearing area oil drain chamber (10), and the second load-bearing area oil drain chamber (8) all extend axially from one end face of the bearing body (1) to the other end face.

3. The circular offset profile sliding bearing according to claim 2, characterized in that, The sliding bearing also includes three oil inlet grooves; The three oil inlet grooves are named the first load-bearing area oil inlet groove (5-1), the non-load-bearing area oil inlet groove (11-2), and the second load-bearing area oil inlet groove (12-2), respectively. Along the clockwise direction, the first bearing area oil inlet groove (5-1) is machined at the front of the inner surface of the first bearing area (1) profile; the non-bearing area oil inlet groove (11-2) is machined at the front of the non-bearing area (2) profile; and the second bearing area oil inlet groove (12-2) is machined at the front of the second bearing area (3) profile. The first bearing area oil inlet groove (5-1) is connected to the first bearing area oil inlet hole (4); The oil inlet groove (11-2) in the non-load-bearing area is connected to the oil inlet hole (6) in the non-load-bearing area; The second bearing area oil inlet groove (12-2) is connected to the second bearing area oil inlet hole (7).

4. The center-offset profile sliding bearing according to claim 3, characterized in that, The sliding bearing also includes three oil outlet grooves; The three oil outlet channels are named the first bearing area oil outlet channel (11-1), the non-bearing area oil outlet channel (12-1), and the second bearing area oil outlet channel (5-2), respectively. A first bearing area oil outlet groove (11-1) is machined on the rear part of the inner surface of the first bearing area (1) profile, a non-bearing area oil outlet groove (12-1) is machined on the rear part of the inner surface of the non-bearing area (2) profile, and a second bearing area oil outlet groove (5-2) is machined on the rear part of the inner surface of the second bearing area (3) profile. The equivalent length of each oil inlet groove along the circumference is greater than the equivalent length of each oil outlet groove along the circumference.

5. The circular offset profile sliding bearing according to claim 4, characterized in that,

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