WO2022061707A1 - 动压滑动轴承组件和动压滑动轴承单元 - Google Patents

动压滑动轴承组件和动压滑动轴承单元 Download PDF

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Publication number
WO2022061707A1
WO2022061707A1 PCT/CN2020/117728 CN2020117728W WO2022061707A1 WO 2022061707 A1 WO2022061707 A1 WO 2022061707A1 CN 2020117728 W CN2020117728 W CN 2020117728W WO 2022061707 A1 WO2022061707 A1 WO 2022061707A1
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WIPO (PCT)
Prior art keywords
dynamic pressure
sliding bearing
pressure sliding
peripheral surface
hydraulic medium
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PCT/CN2020/117728
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English (en)
French (fr)
Inventor
韩慧敏
刘际轩
胡林
蓝辛基
夏祥瑞
Original Assignee
舍弗勒技术股份两合公司
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Application filed by 舍弗勒技术股份两合公司 filed Critical 舍弗勒技术股份两合公司
Priority to CN202080103960.4A priority Critical patent/CN116113782A/zh
Priority to PCT/CN2020/117728 priority patent/WO2022061707A1/zh
Publication of WO2022061707A1 publication Critical patent/WO2022061707A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D9/00—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • This application relates to the field of bearings.
  • the present application particularly relates to a dynamic pressure sliding bearing assembly and a dynamic pressure sliding bearing unit.
  • Bearings are key components in the gearboxes of wind turbines. Rolling bearings are mostly used in gearboxes of current wind turbines. Due to the occasional axial load, in the solution using radial bearings such as needle bearings, it is also necessary to additionally provide a thrust bearing at the shaft. Especially due to installation and manufacturing tolerances and deflection of the shaft due to operating loads, rolling bearings with angular adjustment capability are preferably used.
  • Chinese patent application document CN 102792018 B discloses a gearbox for wind turbines, wherein the gearbox has a casing, a gear carrier, a planetary gear shaft held on the gear carrier, and supported on the planetary gear shafts respectively. The planetary gear, and the ring gear and the sun gear meshing with the planetary gear.
  • the individual planet gears are supported on the respective planet gear shafts by means of rolling bearings designed as self-aligning roller bearings.
  • the above objects are achieved on the one hand by a hydrodynamic sliding bearing assembly.
  • the dynamic pressure sliding bearing assembly is arranged to be radially arranged between a first member and a second member that are rotatable relative to each other, so as to be supported between the first member and the second member in a relatively rotatable manner.
  • the first component has an inner peripheral surface for surrounding the second component, wherein a boss is formed on the inner peripheral surface of the first component.
  • the dynamic pressure sliding bearing assembly includes two dynamic pressure sliding bearings, wherein the dynamic pressure sliding bearings can be fixed to the first member in such a concentric and axially aligned manner that the boss portion of the first member is axially accommodated in the dynamic pressure sliding bearing. Between the sliding bearings, the outer peripheral surface of each dynamic pressure sliding bearing and the axial end surfaces that are close to each other are respectively connected and transitioned by arc surfaces.
  • first component and the second component are arranged nesting within each other and rotatable relative to each other about the same axis of rotation.
  • the central axis of the hydrodynamic sliding bearing assembly here coincides with the same rotational axis of the first member and the second member. Accordingly, unless taught otherwise, the terms “radial”, “axial” and “circumferential” refer to the central axis of the hydrodynamic plain bearing assembly.
  • the first component has a substantially annular hole, preferably a central hole, for surrounding the second component.
  • the inner peripheral surface of the first member refers to the inner peripheral surface of the hole, preferably the central hole.
  • the first component can have holes in the form of through holes.
  • the first component can also have holes in the form of blind holes.
  • the first member is a gear or a housing or the like.
  • a boss portion is formed on the inner peripheral surface of the hole of the first component, preferably the central hole, wherein the boss portion projects radially inward from the inner peripheral surface of the central hole.
  • the boss portion is configured as a continuous annular boss.
  • the boss portion is configured discontinuously in the circumferential direction.
  • the second component has a substantially cylindrical outer peripheral surface at least in regions and can be accommodated at least in regions by means of this outer peripheral surface in a bore, preferably a central bore, of the first component.
  • the second component is, for example, a separate shaft element or a shaft part formed on the component.
  • the dynamic pressure sliding bearing assembly includes two dynamic pressure sliding bearings used in pairs, that is, a first dynamic pressure sliding bearing and a second dynamic pressure sliding bearing.
  • the hydrodynamic sliding bearings each have a substantially sleeve-like structure.
  • the two hydrodynamic sliding bearings are fixed to the second member, preferably at the outer peripheral surface of the second member, concentrically and axially aligned with their respective inner peripheral surfaces.
  • the two dynamic pressure sliding bearings respectively achieve a tight fit with the second member through their respective inner peripheral surfaces.
  • the dynamic pressure sliding bearing assembly and the second member are collectively accommodated in the hole of the first member in such a way that the boss portion of the first member can protrude into the two dynamic pressure sliding bearings of the dynamic pressure sliding bearing assembly in the axial clearance between the bearings.
  • the radial gap between the outer peripheral surfaces of the two hydrodynamic sliding bearings and the inner peripheral surface of the first member should be sufficiently small to be able to generate sufficient radial clearance in the hydraulic medium flowing through the radial gaps Dynamic pressure to support the first member.
  • the two axial gaps between the axial end surfaces of the two hydrodynamic sliding bearings that are close to each other and the axial end surface of the boss portion of the first member should be small enough to be able to flow through the axial gaps A dynamic pressure sufficient to support the first member in the axial direction is generated in the hydraulic medium.
  • the hydraulic medium preferably oil
  • the hydraulic medium can be fed into the hydrodynamic plain bearing assembly by means of a pump, for example.
  • the hydraulic medium can flow through the radial gap between the outer peripheral surface of the dynamic pressure sliding bearing and the inner peripheral surface of the first member and through the axial end surfaces of the two dynamic pressure sliding bearings which are close to each other and the convex surface of the first member. Axial clearance between the axial end faces of the platform.
  • the outer peripheral surface of each hydrodynamic sliding bearing and the axial end surfaces that are close to each other are connected and transitioned by arc surfaces respectively.
  • the radially outer circumferential edge of the first dynamic pressure sliding bearing is configured as an arc surface, for example, through arc modification
  • the radially outer circumferential edge of the second dynamic pressure sliding bearing is configured as an arc surface, eg, arc-shaped.
  • the inner peripheral surface of the first member and the two axial end surfaces of the boss portion are also preferably connected and transitioned by an arc surface. Therefore, on the one hand, since the outer peripheral surface of each dynamic pressure sliding bearing and the axial end surfaces that are close to each other are connected and transitioned by arc surfaces, respectively, it is easy to move between the dynamic pressure sliding bearing and the boss portion of the first member in the axial direction.
  • the formation of a hydraulic medium film is beneficial for the dynamic pressure sliding bearing assembly to bear the axial load.
  • the dynamic pressure sliding bearing and the boss portion of the first member can cooperate with each other through the arc surface to realize the self-aligning function, so as to adapt to the actual working conditions as much as possible .
  • the respective outer peripheral surfaces and the axial end surfaces adjacent to each other of the hydrodynamic sliding bearing are hard-coated.
  • the hydrodynamic sliding bearing in particular the above-mentioned surface, can be adapted to the dynamic pressure sliding bearing and the first during the start-stop phase. Dry friction and boundary friction between components. As a result, the wear resistance of the hydrodynamic sliding bearing can be improved.
  • an axially extending hydraulic medium chamber is formed on the outer peripheral surface of the hydrodynamic sliding bearing.
  • one, two, three or more hydraulic medium chambers may be formed at the outer peripheral surface of the hydrodynamic sliding bearing, in particular depending on the radial dimensions of the hydrodynamic sliding bearing.
  • the hydraulic medium chamber is arranged offset from the main support region of the hydrodynamic sliding bearing.
  • two hydraulic medium chambers are provided at the outer peripheral surface of the hydrodynamic sliding bearing.
  • two radially opposite hydraulic medium chambers are provided on the outer peripheral surface of the hydrodynamic sliding bearing. This facilitates the formation of a hydraulic medium film on the entire outer peripheral surface of the hydrodynamic sliding bearing in the axial direction.
  • the hydrodynamic sliding bearing is configured with a hydraulic medium input which communicates from the inner peripheral surface of the hydrodynamic sliding bearing to the hydraulic medium chamber.
  • the hydraulic medium input is designed here as a through hole which penetrates the hydraulic medium chamber of the outer surface of the hydrodynamic sliding bearing and the inner surface of the hydrodynamic sliding bearing.
  • the hydraulic medium feed itself has a simple structure and is easy to manufacture.
  • an input passage for supplying the hydraulic medium to the dynamic pressure sliding bearing assembly, particularly the hydraulic medium input portion can be realized by utilizing the internal structure of the second member.
  • the hydraulic medium passage is simple and reliable, and the hydrodynamic sliding bearing assembly or the hydrodynamic sliding bearing unit can be realized with a simple structure and at a low cost.
  • the hydrodynamic sliding bearing is configured with a hydraulic medium outlet which communicates from the hydraulic medium chamber to mutually adjacent axial end faces of the hydrodynamic sliding bearing.
  • the hydraulic medium outlet is designed here as a pressure relief groove.
  • the hydraulic medium can flow from the hydraulic medium chamber through the hydraulic medium output portion to between the mutually adjacent axial end faces of the hydrodynamic sliding bearing and the axial end face of the boss portion of the first member, thereby forming an axial dynamic pressure bearing Department.
  • a spacer ring is provided between the dynamic pressure sliding bearings in the axial direction, wherein the spacer ring is configured with an annular groove on its outer peripheral surface and a passage connecting the annular groove and the inner peripheral surface of the spacer ring. hole.
  • annular axial projections are formed at the ends of the hydrodynamic sliding bearing which are close to each other, wherein the axial projections are arranged on the radial inner side of the hydrodynamic sliding bearing. area and is provided with a recess that is recessed in the axial direction.
  • the axial projections belonging to the two hydrodynamic sliding bearings used in pairs are combined with each other to substantially replace the spacer ring in the previous embodiment in function.
  • the recesses belonging to the two axial projections can be combined into a through hole that communicates with the hydraulic medium output passage inside the second member. Thereby, the hydraulic medium from the hydraulic medium output portion can flow along the surface of the hydrodynamic sliding bearing to the outer peripheral surface of the axial projection portion.
  • the hydraulic medium at the axial projection can be further discharged through the through hole formed by the combination of the recesses, eg, to a hydraulic medium output passage located inside the second member.
  • a hydraulic medium channel extending in the circumferential direction is also configured on the outer peripheral surface of the hydrodynamic sliding bearing, and the hydraulic medium channel communicates with the hydraulic medium chamber. This facilitates the formation of a hydraulic medium film on the entire outer peripheral surface of the hydrodynamic sliding bearing in the circumferential direction.
  • one, two, three or more hydraulic medium passages may be provided at the outer peripheral surface of the hydrodynamic sliding bearing according to the axial dimension of the hydrodynamic sliding bearing.
  • a hydraulic medium channel is provided at the outer peripheral surface of the hydrodynamic sliding bearing.
  • the two hydrodynamic slide bearings of the hydrodynamic slide bearing assembly are constructed identically.
  • the first hydrodynamic sliding bearing and the second hydrodynamic sliding bearing are designed and produced identically and are mounted opposite to each other in a subsequent step.
  • the two hydrodynamic sliding bearings can be interchanged with each other, which is beneficial to save design costs as well as manufacturing and maintenance costs.
  • the above object can also be achieved by a hydrodynamic sliding bearing unit.
  • the dynamic pressure sliding bearing includes a first member and a second member that are rotatable relative to each other, wherein the first member has an inner peripheral surface for surrounding the second member, wherein a protrusion is configured on the inner peripheral surface of the second member a table portion; and a hydrodynamic sliding bearing assembly constructed according to the above-described embodiment, disposed radially between the first member and the second member.
  • the dynamic pressure sliding bearings of the dynamic pressure sliding bearing assembly are fixed to the second member, preferably the outer peripheral surface thereof, in such a concentric and axially aligned manner that the boss portion of the first member is axially accommodated in the dynamic pressure sliding bearing.
  • a radial dynamic pressure bearing can be formed between the outer peripheral surface of the dynamic pressure sliding bearing and the inner peripheral surface of the first member by means of the hydraulic medium, and the radial dynamic pressure bearing can be formed between the mutually adjacent axial end surfaces of the dynamic pressure sliding bearing and the convex surface of the first member.
  • An axial dynamic pressure support portion is formed between the axial end faces of the platform portion.
  • the boss portion of the first component is formed at an axially intermediate position of the inner peripheral surface of the first component.
  • the first component for example the gear wheel
  • the first component can be designed to be symmetrical in the axial direction, which contributes to increased bearing stability.
  • the two dynamic pressure sliding bearings of the dynamic pressure sliding bearing assembly are allowed to be constructed exactly the same.
  • the two hydrodynamic sliding bearings can be interchanged with each other, which is beneficial to save design costs as well as manufacturing and maintenance costs.
  • the second member is configured with an input passage for supplying hydraulic medium to the hydrodynamic sliding bearing assembly.
  • the hydrodynamic sliding bearing unit can be implemented compactly and at low cost.
  • the second member is configured with an output passage that discharges the hydraulic medium from the hydrodynamic sliding bearing assembly.
  • the dynamic pressure sliding bearing assembly and the dynamic pressure sliding bearing unit according to the present application can be applied in various fields, especially in the field of wind power.
  • the hydrodynamic sliding bearing assembly can, for example, support the planetary gears on the corresponding planetary gear shafts in a relatively rotatable manner in the gearbox of the wind turbine.
  • the hydrodynamic sliding bearing assembly provided herein is constructed as a multifunctional bearing assembly which can simultaneously bear radial load, axial load and overturning moment.
  • the hydrodynamic sliding bearing assembly is simple in structure, easy to install and low in cost.
  • the hydrodynamic sliding bearing assembly can carry occasional axial loads, so no additional thrust bearing is required, which can reduce costs.
  • the mating surfaces of the dynamic pressure sliding bearing and the first member, such as the boss portion of the planetary gear are both configured as arc surfaces.
  • a hydraulic medium film such as an oil film
  • the outer peripheral surface of the hydrodynamic sliding bearing and the axial end face facing the other hydrodynamic sliding bearing, in particular the arc-shaped surface are hard-coated, ie the surface of the hydrodynamic sliding bearing for forming the hydraulic medium film is hard-coated.
  • the surface of the oil film is hard-coated, whereby the hydrodynamic sliding bearing assembly can accommodate dry friction and boundary friction between the hydrodynamic sliding bearing and the first member, such as a planetary gear, during the start-stop phase.
  • FIG. 1 is a schematic axial cross-sectional view of a dynamic pressure sliding bearing unit according to a first embodiment
  • FIG. 2 is a schematic perspective view of a dynamic pressure sliding bearing in the dynamic pressure sliding bearing unit according to FIG. 1 ,
  • FIG. 3 is a schematic perspective view of a spacer in the hydrodynamic sliding bearing unit according to FIG. 1 ,
  • FIG. 4 is a schematic axial cross-sectional view of a dynamic pressure sliding bearing unit according to a second embodiment
  • FIG. 5 is a schematic perspective view of the dynamic pressure sliding bearing in the dynamic pressure sliding bearing unit according to FIG. 4 .
  • FIG. 1 shows a schematic axial cross-sectional view of a hydrodynamic sliding bearing unit according to a first embodiment.
  • the dynamic pressure sliding bearing unit is used in the gearbox of the wind turbine.
  • the hydrodynamic sliding bearing unit includes a first component designed as a planetary gear 10 and a second component designed as a planetary gear shaft 20 .
  • the planetary gear shafts 20 are here fastened to the planet carrier 30 .
  • the dynamic pressure sliding bearing unit also includes a dynamic pressure sliding bearing assembly.
  • the dynamic pressure sliding bearing assembly is radially arranged between the planetary gear 10 and the planetary gear shaft 20 to support the planetary gear 10 on the planetary gear shaft 20 in a relatively rotatable manner.
  • the dynamic pressure sliding bearing assembly includes two dynamic pressure sliding bearings, namely, a first dynamic pressure sliding bearing 40 and a second dynamic pressure sliding bearing 50.
  • the two dynamic pressure sliding bearings 40 and 50 have a substantially sleeve-like structure.
  • the first dynamic pressure sliding bearing 40 and the second dynamic pressure sliding bearing 50 are identically designed and manufactured, so that they can be interchanged with each other, which is beneficial to save design costs and manufacturing and maintenance costs.
  • the first dynamic pressure sliding bearing 40 and the second dynamic pressure sliding bearing 50 are arranged opposite to each other.
  • the first dynamic pressure sliding bearing 40 and the second dynamic pressure sliding bearing 50 are fixed at the outer peripheral surface of the planetary gear shaft 20 concentrically and arranged in the axial direction.
  • the first dynamic pressure sliding bearing 40 and the second dynamic pressure sliding bearing 50 are tightly fitted with the planetary gear shaft 20 .
  • the dynamic pressure sliding bearing assembly further includes a spacer 60 which is axially arranged between the first dynamic pressure sliding bearing 40 and the second dynamic pressure sliding bearing 50 .
  • a spacer 60 which is axially arranged between the first dynamic pressure sliding bearing 40 and the second dynamic pressure sliding bearing 50 .
  • the flange 203 of the planetary gear shaft 20 , the second dynamic pressure sliding bearing 50 , the spacer 60 , the first dynamic pressure sliding bearing 40 and the planetary carrier 30 which are arranged in sequence in the axial direction abut against each other.
  • the planetary gear 10 has a central hole for surrounding the dynamic pressure sliding bearing assembly and the planetary gear shaft 20, and an annular boss portion 101 is configured at the inner peripheral surface of the central hole.
  • the boss portion 101 is arranged at the axial middle of the inner peripheral surface of the center hole.
  • the first dynamic pressure sliding bearing 40 and the second dynamic pressure sliding bearing 50 are accommodated in the center hole of the planetary gear 10 such that the boss portion 101 of the planetary gear 10 protrudes into the first dynamic pressure sliding bearing 40 and the second dynamic pressure sliding bearing 40 and the second dynamic pressure sliding bearing. into the axial gap between the sliding bearings 50 .
  • the spacer ring 60 is located radially inward of the boss portion 101 of the planetary gear 10 .
  • the hydraulic medium is lubricating oil for lubricating various components in the gearbox.
  • oil can flow into the radial gap between the outer peripheral surfaces of the two hydrodynamic sliding bearings 40 , 50 and the inner peripheral surface of the center hole of the planetary gear 10 and form an oil film serving as a hydraulic medium film.
  • a radial dynamic pressure support portion can be formed between the outer peripheral surfaces of the two dynamic pressure sliding bearings 40 and 50 and the inner peripheral surface of the center hole of the planetary gear 10 .
  • Oil can also flow into the two axial gaps between the axial end faces of the two hydrodynamic sliding bearings 40 , 50 that are close to each other and the axial end face of the boss portion 101 of the planetary gear 10 and form a hydraulic medium film. Oil film.
  • the axial dynamic pressure support portion can be formed between the axial end surfaces of the dynamic pressure sliding bearings 40 and 50 which are close to each other and the axial end surface of the boss portion 101 of the planetary gear 10 .
  • the outer peripheral surface of the first dynamic pressure sliding bearing 40 and the axial end surface close to the second dynamic pressure sliding bearing 50 are connected and transitioned by arc surfaces 405 respectively, and the outer peripheral surface of the second dynamic pressure sliding bearing 50
  • the axial end surfaces of the first dynamic pressure sliding bearing 40 are connected and transitioned through arc surfaces 505 respectively.
  • the inner peripheral surface of the planetary gear 10 and the two axial end surfaces of the boss portion 101 are respectively connected and transitioned by arc surfaces.
  • the two dynamic pressure sliding bearings 40 and 50 and the cambered mating surfaces of the boss portion 101 of the planetary gear 10 can coordinate with each other to achieve the self-aligning function, thereby adapting to various practical work. condition.
  • the outer peripheral surface of the first dynamic pressure sliding bearing 40 and the axial end surface adjacent to the second dynamic pressure sliding bearing 50 are hard-coated, and the outer peripheral surface of the second dynamic pressure sliding bearing 50 and the outer peripheral surface adjacent to the first dynamic pressure sliding bearing 50 are hard-coated.
  • the axial end faces of the press sliding bearing 40 are hard-coated.
  • FIGS. 1 to 3 respectively show schematic perspective views of the first dynamic pressure sliding bearing 40 and the spacer 60 in the dynamic pressure sliding bearing unit according to the first embodiment.
  • the flow path of the oil used as hydraulic medium can be seen in particular in conjunction with FIGS. 1 to 3 .
  • hydraulic medium chambers extending in the axial direction namely hydraulic oil chambers 401 and 501 and hydraulic medium passages extending in the circumferential direction, are formed on the outer peripheral surfaces of the respective hydrodynamic sliding bearings 40 and 50 That is, the oil passage 404 .
  • the hydraulic oil chambers 401 and 501 and the oil passage 404 communicate with each other here.
  • two radially opposite hydraulic oil chambers 401 and 501 are respectively provided at the outer peripheral surfaces of the dynamic pressure sliding bearings 40 and 50 , and the shafts at the outer peripheral surfaces of the dynamic pressure sliding bearings 40 and 50 are respectively provided.
  • the oil gallery 404 is arranged to the intermediate position.
  • each of the hydrodynamic sliding bearings 40 , 50 is provided with a hydraulic medium input portion in the form of oil inlet holes 402 , 502 .
  • the oil inlet holes 402 and 502 communicate with the hydraulic oil chambers 401 and 501 from the inner peripheral surfaces of the center holes of the dynamic pressure sliding bearings 40 and 50 .
  • Each hydrodynamic sliding bearing 40 , 50 is also configured with a hydraulic medium output in the form of a pressure relief groove 403 , 503 .
  • the pressure relief grooves 403 , 503 extend from the hydraulic oil chambers 401 , 501 to the axial end faces, especially the arcuate faces 405 , 505 of the hydrodynamic sliding bearings 40 , 50 that are close to each other.
  • the spacer 60 is configured with an annular groove 601 at the outer peripheral surface thereof and a through hole 602 communicating the annular groove 601 and the inner peripheral surface of the spacer 60 .
  • an input passage for supplying oil to the dynamic pressure sliding bearing assembly is constructed inside the planetary gear shaft 20 .
  • the input passage of the planetary gear shaft 20 is connected to the oil inlet holes 402 , 502 of the dynamic pressure sliding bearings 40 , 50 via the oil inlet hole 201 .
  • An output passage for discharging oil from the dynamic pressure sliding bearing assembly is also constructed inside the planetary gear shaft 20 .
  • the through hole 602 of the cage 60 leads to the oil return hole 202 of the output passage of the planetary gear shaft 20 .
  • the oil delivered by the oil pump can enter the hydraulic oil chambers 401 and 501 through the input passage of the planetary gear shaft 20 and the oil inlet holes 402 and 502 of the dynamic pressure sliding bearings 40 and 50 in sequence.
  • Oil can flow from the hydraulic oil chambers 401 , 501 and the oil passages 404 communicating with the hydraulic oil chambers 401 , 501 to the outer peripheral surfaces of the dynamic pressure sliding bearings 40 , 50 .
  • oil can also flow from the hydraulic oil chambers 401, 501 and the pressure relief grooves 403, 503 communicating with the hydraulic oil chambers 401, 501 to the arc surfaces 405, 505 of the two dynamic pressure sliding bearings 40, 50 that are close to each other and the axial direction end face.
  • Oil flowing into the axial gap of the two hydrodynamic sliding bearings 40 , 50 may be collected into the annular groove 601 of the spacer ring 60 , and may be further discharged to the output passage inside the planetary gear shaft 20 through the through hole 602 .
  • FIG. 4 shows a schematic axial cross-sectional view of a hydrodynamic sliding bearing unit according to a second embodiment.
  • the dynamic pressure sliding bearing unit according to the present embodiment is constructed similarly to the dynamic pressure sliding bearing unit according to the first embodiment. Only the differences between the two embodiments are explained below.
  • the dynamic pressure sliding bearing assembly includes two dynamic pressure sliding bearings of the same configuration and oppositely arranged, ie, the first dynamic pressure sliding bearing 70 and the second dynamic pressure sliding bearing 80 .
  • FIG. 5 shows a schematic perspective view of the dynamic pressure sliding bearing 70 in the dynamic pressure sliding bearing unit according to the second embodiment.
  • the first dynamic pressure sliding bearing 70 and the second dynamic pressure sliding bearing 80 are arranged in abutment with each other.
  • Ring-shaped axial projections 706 , 806 are formed at the ends of the hydrodynamic sliding bearings 70 , 80 which abut against each other, wherein the axial projections 706 , 806 are formed at the ends of the dynamic pressure sliding bearings 70 , 80 .
  • the axial protrusion 706 of the first dynamic pressure sliding bearing 70 is provided with a recess 707 recessed in the axial direction.
  • the axial protrusion 806 of the second dynamic pressure sliding bearing 80 is provided with a recess recessed in the axial direction.
  • the axial projections 706 , 806 belonging to the two hydrodynamic sliding bearings 70 , 80 are combined with each other by abutting against each other, thereby substantially replacing the spacer ring 60 in the first embodiment in function.
  • the recesses belonging to the two axial projections 706, 806 may be combined into a through hole communicating to the output passage inside the planetary gear shaft 20.
  • the oil delivered by the oil pump can enter the hydraulic oil chambers 701 and 801 through the input passage of the planetary gear shaft 20 and the oil inlet holes 702 and 802 of the dynamic pressure sliding bearings 70 and 80 in sequence. Oil can flow to the outer peripheral surfaces of the hydrodynamic sliding bearings 70 and 80 from the hydraulic oil chambers 701 and 801 and the oil passages communicating with the hydraulic oil chambers 701 and 801 .
  • oil can also flow from the hydraulic oil chambers 701, 801 and the pressure relief grooves 703, 803 communicating with the hydraulic oil chambers 701, 801 to the arc surfaces at the axial ends of the two dynamic pressure sliding bearings 70, 80 that are close to each other 705 , 805 , and then flow to the outer peripheral surfaces of the axial protrusions 706 , 806 .
  • the oil collected here is further discharged to the output passage inside the planetary gear shaft 20 through the through hole formed by the combination of the recesses of the two axial projections 706 , 806 .
  • the hydrodynamic sliding bearing assembly according to the above-mentioned two embodiments is configured as a multifunctional bearing assembly, which can bear radial load, axial load and overturning moment at the same time.
  • the dynamic pressure sliding bearing assembly has a simple structure, is easy to install and has a low cost.

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Abstract

一种动压滑动轴承组件和动压滑动轴承单元。动压滑动轴承组件用于沿径向布置在可以相对彼此旋转的第一构件(10)和第二构件(20)之间，其中，第一构件(10)具有用于环绕第二构件(20)的内周面，其中，在该内周面处构造有凸台部(101)，其中，动压滑动轴承组件包括两个动压滑动轴承(40、50；70、80)，二者能够如此同心地且沿轴向排列地固定于第二构件(20)，使得凸台部(101)沿轴向容纳在两个动压滑动轴承(40、50；70、80)之间，其中，各个动压滑动轴承(40、50；70、80)的外周面和彼此靠近的轴向端面分别通过弧面(405、505；705、805)连接过渡。

Description

动压滑动轴承组件和动压滑动轴承单元 技术领域
本申请涉及轴承领域。本申请具体地涉及一种动压滑动轴承组件和动压滑动轴承单元。
背景技术
随着海上风电的发展，大兆瓦级风力发电机是未来发展的趋势。同时，为了降低度电成本，对风力发电机的齿轮箱的成本以及运行可靠性有更苛刻的要求。
轴承是风力发电机的齿轮箱中的关键部件。在当前的风力发电机的齿轮箱中大多采用滚动轴承。由于存在偶发的轴向载荷，因此在采用滚针轴承等径向轴承的方案中还需要在轴处附加地设置推力轴承。尤其由于存在安装和制造误差以及由工作载荷引起的轴的挠曲，优选使用具有角度调整能力的滚动轴承。例如，中国专利申请文件CN 102792018 B公开了一种用于风力发电机的齿轮箱，其中，齿轮箱具有壳体、齿轮架、保持在齿轮架上的行星齿轮轴、分别支撑在行星齿轮轴上的行星齿轮、以及与行星齿轮啮合的环形齿轮和中心齿轮。在该方案中，各个行星齿轮借助构造为自调整滚柱轴承的滚动轴承支承在相应的行星齿轮轴上。
然而，一方面，随着风电技术的发展，对轴承的尺寸以及承载能力的要求越来越高。另一方面，如上所述，轴承的运行可靠性也非常重要。若风力发电机的齿轮箱中的滚动轴承失效，将导致大量的维修时间和成本的浪费。
发明内容
因此，本申请的目的在于提供一种轴承组件，该轴承组件具有良好的承载能力并且成本较低。
上述目的在一方面通过一种动压滑动轴承组件实现。该动压滑动轴承组件用于沿径向布置在可以相对彼此旋转的第一构件和第二构件之间，从而以可相对旋转的方式在第一构件和第二构件之间进行支承。在此，第一构件具有用于环绕第二构件的内周面，其中，在第一构件的内周面处构造有凸台部。动压滑动轴承组件包括两个动压滑动轴承，其中，动压滑动轴承可以如此同心地且沿轴向排列地固定于第一构件，使得第一构件的凸台部沿轴向容纳在动压滑动轴承之间，其中，各个动压滑动轴承的外周面和彼此靠近的轴向端面分别通过弧面连接过渡。
在本文的范围内，第一构件和第二构件彼此套设地布置并且可以围绕同一旋转轴线相对彼此旋转。动压滑动轴承组件的中轴线在此与第一构件和第二构件的同一旋转轴线重合。因此，除非有另外的教导，否则术语“径向”、“轴向”以及“周向”均参考动压滑动轴承组件的中轴线。
在此，第一构件具有用于环绕第二构件的基本呈环形的孔、优选中心孔。在本文的范围中，除非有另外的教导，否则第一构件的内周面均指该孔、优选中心孔的内周面。在此，第一构件可以具有通孔形式的孔。备选地，第一构件也可以具有盲孔形式的孔。例如，第一构件是齿轮或壳体等。
特别地，在第一构件的孔、优选中心孔的内周面处构造有凸台部，其中，该凸台部从中心孔的内周面朝向径向内侧伸出。优选地，凸台部构造为连续的环形凸台。备选地，凸台部在周向上非连续地构造。
在此，第二构件至少局部地具有基本呈圆柱形的外周面并且可以借助该外周面至少局部地被容纳在第一构件的孔、优选中心孔中。第二构件例如是独立的轴件或者是构造于零部件上的轴部。
在此，动压滑动轴承组件包括成对使用的两个动压滑动轴承、即第一动压滑动轴承和第二动压滑动轴承。动压滑动轴承分别具有基本呈套筒状的结构。
在完成装配后，两个动压滑动轴承以各自的内周面同心地且沿轴向排列地固定于第二构件、优选固定于第二构件的外周面处。优选地，两个动压滑动轴承分别以各自的内周面实现与第二构件的紧配合。在此，动压滑 动轴承组件和第二构件通过以下方式被共同地容纳在第一构件的孔中，使得第一构件的凸台部能够伸入到动压滑动轴承组件的两个动压滑动轴承之间的轴向间隙中。在这种情况下，在两个动压滑动轴承的外周面和第一构件的内周面之间的径向间隙应当足够小，以能够在流经径向间隙的液压介质中产生足以沿径向支承第一构件的动压。类似地，在两个动压滑动轴承的彼此靠近的轴向端面和第一构件的凸台部的轴向端面之间的两个轴向间隙应当足够小，以能够在流经轴向间隙的液压介质中产生足以沿轴向支承第一构件的动压。
在这种情况下，液压介质、优选油可以在例如泵的作用下被输送到动压滑动轴承组件中。液压介质能够流经在动压滑动轴承的外周面和第一构件的内周面之间的径向间隙并且流经在两个动压滑动轴承的彼此靠近的轴向端面和第一构件的凸台部的轴向端面之间的轴向间隙。由此，在动压滑动轴承组件和第二构件共同地相对第一构件旋转时，能够借助液压介质形成在两个动压滑动轴承和第一构件之间的径向动压支承部并且在两个动压滑动轴承和第一构件的凸台部之间的轴向动压支承部。通过这种设计方案，动压滑动轴承组件既能够承载径向载荷，也能够承载轴向载荷。
根据本文提出的方案，各个动压滑动轴承的外周面和彼此靠近的轴向端面分别通过弧面连接过渡。换言之，在第一动压滑动轴承的靠近第二动压滑动轴承的轴向端部处，第一动压滑动轴承的径向外侧的周向边缘构造为弧面、例如经弧形修型，并且在第二动压滑动轴承的靠近第一动压滑动轴承的轴向端部处，第二动压滑动轴承的径向外侧的周向边缘构造为弧面、例如经弧形修型。相应地，第一构件的内周面和凸台部的两个轴向端面也优选通过弧面连接过渡。由此，在一方面，由于各个动压滑动轴承的外周面和彼此靠近的轴向端面分别通过弧面连接过渡，因此易于沿轴向在动压滑动轴承和第一构件的凸台部之间形成液压介质膜，有利于动压滑动轴承组件承受轴向载荷。在另一方面，当第一构件、例如齿轮存在倾覆力矩时，动压滑动轴承以及第一构件的凸台部可以通过弧面相互配合地实现调心功能，从而尽可能地适配实际工况。
根据一种优选的实施方式，动压滑动轴承的各自的外周面和彼此靠近 的轴向端面经硬化涂层。在此，通过对动压滑动轴承的用于形成液压介质膜、例如油膜的表面进行硬化涂层，可以使动压滑动轴承、尤其上述表面适应在启停阶段中在动压滑动轴承和第一构件之间的干摩擦和边界摩擦。由此可以提高动压滑动轴承的耐磨性能。
根据一种优选的实施方式，在动压滑动轴承的外周面处构造有沿轴向延伸的液压介质腔。可选地，尤其根据动压滑动轴承的径向尺寸，可以在动压滑动轴承的外周面处构造一个、两个、三个或更多液压介质腔。有利地，液压介质腔与动压滑动轴承的主承载区域错开地布置。优选地，在动压滑动轴承的外周面处设置两个液压介质腔。特别优选地，在动压滑动轴承的外周面处设置两个沿径向对置的液压介质腔。由此有利于沿轴向在整个动压滑动轴承的外周面上形成液压介质膜。此外，由于动压滑动轴承的外周面和第一构件的内周面的径向间隙较小，将液压介质腔构造在动压滑动轴承的外周面处有利于液压介质快速充盈至该径向间隙，由此在第一构件和第二构件开始相对彼此旋转时，可以尽可能快速地结束动压滑动轴承和第一构件之间的干摩擦和边界摩擦。
有利地，动压滑动轴承构造有液压介质输入部，液压介质输入部从动压滑动轴承的内周面连通至液压介质腔。优选地，液压介质输入部在此构造为通孔，该通孔贯通动压滑动轴承的外表面的液压介质腔和动压滑动轴承的内表面。由此，液压介质输入部自身结构简单且易于制造。相应地，能够利用第二构件的内部结构实现向动压滑动轴承组件、具体地液压介质输入部提供液压介质的输入通路。由此液压介质通路简单可靠，动压滑动轴承组件或者动压滑动轴承单元可以通过简单的结构实现并且成本较低。
有利地，动压滑动轴承构造有液压介质输出部，液压介质输出部从液压介质腔连通至动压滑动轴承的彼此靠近的轴向端面。优选地，液压介质输出部在此构造为泄压槽。由此，液压介质可以通过液压介质输出部从液压介质腔流至动压滑动轴承的彼此靠近的轴向端面和第一构件的凸台部的轴向端面之间，从而形成轴向动压支承部。
在此，在一个实施方式中，沿轴向在动压滑动轴承之间设置隔圈，其中，隔圈构造有在其外周面处的环形槽以及连通环形槽和隔圈的内周面的 通孔。由此，通过液压介质输出部流至两个动压滑动轴承的轴向间隙中液压介质可以汇集到隔圈的环形槽中，并且可以进一步通过通孔排出到例如位于第二构件内部的液压介质输出通路。
在此，在另一个实施方式中，在动压滑动轴承的彼此靠近的端部处构造有呈环形的轴向凸出部，其中，轴向凸出部布置在动压滑动轴承的径向内侧区域并且设有沿轴向凹陷的凹口。在此，分属于成对使用的两个动压滑动轴承的轴向凸出部彼此组合，以在功能上基本替代上一实施方式中的隔圈。在这种情况下，分属于两个轴向凸出部的凹口可以组合成连通至第二构件内部的液压介质输出通路的通孔。由此，来自液压介质输出部的液压介质可以沿着动压滑动轴承的表面流至轴向凸出部的外周面。在轴向凸出部处的液压介质可以进一步通过由凹口组合形成的通孔排出到例如位于第二构件内部的液压介质输出通路。
有利地，在动压滑动轴承的外周面处还构造有沿周向延伸的液压介质通道，液压介质通道与液压介质腔连通。由此有利于沿周向在整个动压滑动轴承的外周面上形成液压介质膜。可选地，根据动压滑动轴承的轴向尺寸，可以在动压滑动轴承的外周面处设置一个、两个、三个或更多液压介质通道。优选地，在动压滑动轴承的外周面处设置一个液压介质通道。
根据一种优选的实施方式，动压滑动轴承组件的两个动压滑动轴承相同地构造。在此，第一动压滑动轴承和第二动压滑动轴承完全相同地设计与制造，并且在后续的步骤中被相互对置地安装。在这种情况下，两个动压滑动轴承能够实现彼此的互换，这有利于节省设计成本以及制造和维修成本。
上述目的在另一方面还可以通过一种动压滑动轴承单元实现。该动压滑动轴承包括：能够相对彼此旋转的第一构件和第二构件，其中第一构件具有用于环绕第二构件的内周面，其中，在第二构件的内周面处构造有凸台部；以及沿径向布置在第一构件和第二构件之间的、根据上述实施方式构造的动压滑动轴承组件。在此，动压滑动轴承组件的动压滑动轴承如此同心地且沿轴向排列地固定于第二构件、优选其外周面处，使得第一构件的凸台部沿轴向容纳在动压滑动轴承之间，其中，第一构件的内周面和凸 台部的两个轴向端面分别通过弧面连接过渡，并且，各个动压滑动轴承的外周面和彼此靠近的轴向端面分别通过弧面连接过渡。
由此可以借助液压介质在动压滑动轴承的外周面和第一构件的内周面之间形成径向动压支承部并且在动压滑动轴承的彼此靠近的轴向端面和第一构件的凸台部的轴向端面之间形成轴向动压支承部。此外，由此当第一构件、例如齿轮存在倾覆力矩时，动压滑动轴承以及第一构件的凸台部的弧面能够相互匹配地实现调心功能。
在一种有利的实施方式中，第一构件的凸台部构造在第一构件的内周面的轴向中间位置处。由此第一构件、例如齿轮的可以在轴向上对称地构造，有利于增强支承稳定性。另外，在本实施方式中，动压滑动轴承组件的两个动压滑动轴承允许完全相同地构造。两个动压滑动轴承可以彼此互换，这有利于节省设计成本以及制造和维修成本。
在一种优选的实施方式中，第二构件构造有向动压滑动轴承组件提供液压介质的输入通路。由此无需设置另外的用于液压介质的输入通路。动压滑动轴承单元可以紧凑且低成本地实施。
在一种优选的实施方式中，第二构件构造有将液压介质从动压滑动轴承组件排出的输出通路。由此无需设置另外的用于液压介质的输出通路。动压滑动轴承单元可以紧凑且低成本地实施。
根据本申请的动压滑动轴承组件以及动压滑动轴承单元可以应用于各种领域、尤其可以用于风电领域。具体地，动压滑动轴承组件例如可以在风力发电机的齿轮箱中将行星齿轮可相对旋转地支承在相应的行星齿轮轴上。
在此提供的动压滑动轴承组件构造为多功能轴承组件，其可以同时承受径向载荷、轴向载荷和倾覆力矩。然而动压滑动轴承组件结构简单，易于安装且成本较低。特别地，动压滑动轴承组件能够承载偶发的轴向载荷，因此不需要额外的推力轴承，可以降低成本。特别地，动压滑动轴承和第一构件、例如行星齿轮的凸台部的配合面均构造为弧面。由此易于沿轴向在动压滑动轴承和凸台部之间形成液压介质膜、例如油膜，有利于动压滑动轴承承受轴向载荷；同时弧面形的配合面在第一构件、例如行星齿 轮倾覆时可以实现调心功能，动压滑动轴承能够承受倾覆力矩。特别地，对动压滑动轴承的外周面和朝向于另一动压滑动轴承的轴向端面、尤其经弧形修型的表面进行硬化涂层，即对动压滑动轴承的用于形成液压介质膜、优选油膜的表面进行硬化涂层，由此动压滑动轴承组件可以适应在启停阶段中在动压滑动轴承和第一构件、例如行星齿轮之间的干摩擦和边界摩擦。
附图说明
下面将参考附图来描述本申请示例性实施例的特征、优点和技术效果。
图1是根据第一实施方式的动压滑动轴承单元的示意性的轴向剖视图，
图2是根据图1的动压滑动轴承单元中的动压滑动轴承的示意性的立体图，
图3是根据图1的动压滑动轴承单元中的隔圈的示意性的立体图，
图4是根据第二实施方式的动压滑动轴承单元的示意性的轴向剖视图，以及
图5是根据图4的动压滑动轴承单元中的动压滑动轴承的示意性的立体图。
具体实施方式
图1示出了根据第一实施方式的动压滑动轴承单元的示意性的轴向剖视图。本实施方式中，动压滑动轴承单元应用在风力发电机的齿轮箱中。
在此，动压滑动轴承单元包括实施为行星齿轮10的第一构件和实施为行星齿轮轴20的第二构件。行星齿轮轴20在此固定在行星架30上。
动压滑动轴承单元还包括动压滑动轴承组件。动压滑动轴承组件沿径向布置在行星齿轮10和行星齿轮轴20之间，以将行星齿轮10可相对旋转地支承在行星齿轮轴20上。
如图1所示，动压滑动轴承组件包括两个动压滑动轴承，即第一动压 滑动轴承40和第二动压滑动轴承50。两个动压滑动轴承40、50具有基本呈套筒状的结构。在本实施方式中，第一动压滑动轴承40和第二动压滑动轴承50完全相同地设计与制造，由此可以实现彼此的互换，这有利于节省设计成本以及制造和维修成本。在完成装配后，如图1所示，第一动压滑动轴承40和第二动压滑动轴承50相对地布置。
第一动压滑动轴承40和第二动压滑动轴承50同心地且沿轴向排列地固定在行星齿轮轴20的外周面处。在此，第一动压滑动轴承40以及第二动压滑动轴承50与行星齿轮轴20实现紧配合。
动压滑动轴承组件还包括隔圈60，其沿轴向布置在第一动压滑动轴承40和第二动压滑动轴承50之间。在这种情况下，在轴向上依次排列的行星齿轮轴20的凸缘203、第二动压滑动轴承50、隔圈60、第一动压滑动轴承40以及行星架30相互抵靠。
行星齿轮10具有用于环绕动压滑动轴承组件和行星齿轮轴20的中心孔，在中心孔的内周面处构造有环形的凸台部101。在本实施方式中，凸台部101布置在中心孔的内周面的轴向中间处。
第一动压滑动轴承40和第二动压滑动轴承50如此容纳在行星齿轮10的中心孔中，使得行星齿轮10的凸台部101伸入到在第一动压滑动轴承40和第二动压滑动轴承50之间的轴向间隙中。在这种情况下，隔圈60位于行星齿轮10的凸台部101的径向内侧。
在本实施方式中，液压介质为用于润滑齿轮箱中各个构件的润滑油。在此，油能够流入在两个动压滑动轴承40、50的外周面和行星齿轮10的中心孔的内周面之间的径向间隙并且形成用作液压介质膜的油膜。由此在两个动压滑动轴承40、50的外周面和行星齿轮10的中心孔的内周面之间能够形成径向动压支承部。油还能够流入在两个动压滑动轴承40、50的彼此靠近的轴向端面和行星齿轮10的凸台部101的轴向端面之间的两个轴向间隙并且形成用作液压介质膜的油膜。由此能够在动压滑动轴承40、50的彼此靠近的轴向端面和行星齿轮10的凸台部101的轴向端面之间形成轴向动压支承部。
如图1所示，第一动压滑动轴承40的外周面和靠近第二动压滑动轴 承50的轴向端面分别通过弧面405连接过渡，并且第二动压滑动轴承50的外周面和靠近第一动压滑动轴承40的轴向端面分别通过弧面505连接过渡。同时，行星齿轮10的内周面和凸台部101的两个轴向端面分别通过弧面连接过渡。当行星齿轮10存在倾覆力矩时，两个动压滑动轴承40、50以及行星齿轮10的凸台部的101的弧面形的配合面可以相互协调地实现调心功能，从而适应各种实际工况。
在本实施方式中，第一动压滑动轴承40的外周面和靠近第二动压滑动轴承50的轴向端面经硬化涂层，并且第二动压滑动轴承50的外周面和靠近第一动压滑动轴承40的轴向端面经硬化涂层。由此可以使动压滑动轴承40、50的上述表面适应启停阶段中在动压滑动轴承40、50和行星齿轮10之间的干摩擦和边界摩擦。
图2和图3分别示出了根据第一实施方式的动压滑动轴承单元中的第一动压滑动轴承40和隔圈60的示意性的立体图。尤其结合图1至图3可见用作液压介质的油的流动路径。
如图1和图2所示，在各个动压滑动轴承40、50的外周面处构造有沿轴向延伸的液压介质腔、即液压油腔401、501以及沿周向延伸的液压介质通道、即油道404。在此，液压油腔401、501与油道404在此相互连通。在本实施方式中，在动压滑动轴承40、50的外周面处分别设置两个沿径向对置的液压油腔401、501，并且在动压滑动轴承40、50的外周面处的轴向中间位置布置油道404。由此有利于油膜沿轴向以及沿周向形成在整个动压滑动轴承的外周面。此外，各个动压滑动轴承40、50造有入油孔402、502形式的液压介质输入部。入油孔402、502从动压滑动轴承40、50的中心孔的内周面连通至液压油腔401、501。各个动压滑动轴承40、50还构造有泄压槽403、503形式的液压介质输出部。泄压槽403、503从液压油腔401、501延伸至动压滑动轴承40、50的彼此靠近的轴向端面、尤其弧面405、505。
如图1和图3所示，隔圈60构造有在其外周面处的环形槽601以及连通环形槽601和隔圈60的内周面的通孔602。
如图1所示，在行星齿轮轴20内部构造有向动压滑动轴承组件提供 油的输入通路。在此，行星齿轮轴20的输入通路借助进油孔201连接至动压滑动轴承40、50的入油孔402、502。在行星齿轮轴20内部还构造有将油从动压滑动轴承组件排出的输出通路。在此，隔圈60的通孔602通向行星齿轮轴20的输出通路的回油孔202。
由此，借助油泵输送的油可以依次经由行星齿轮轴20的输入通路和动压滑动轴承40、50的入油孔402、502进入液压油腔401、501。油可以从液压油腔401、501以及与液压油腔401、501连通的油道404流动至动压滑动轴承40、50的外周面。此外，油还可以从液压油腔401、501以及与液压油腔401、501连通泄压槽403、503流动至两个动压滑动轴承40、50的彼此靠近的弧面405、505以及轴向端面。流至两个动压滑动轴承40、50的轴向间隙中的油可以汇聚到隔圈60的环形槽601中，并且可以进一步通过通孔602排出到行星齿轮轴20内部的输出通路。
图4示出了根据第二实施方式的动压滑动轴承单元的示意性的轴向剖视图。根据本实施方式的动压滑动轴承单元与根据第一实施方式的动压滑动轴承单元类似地构造。下面仅阐述两个实施方式的不同之处。
在根据本实施方式的动压滑动轴承单元中，动压滑动轴承组件包括相同构造且相对布置的两个动压滑动轴承，即第一动压滑动轴承70和第二动压滑动轴承80。
图5示出了根据第二实施方式的动压滑动轴承单元中的动压滑动轴承70的示意性的立体图。
如图4和图5所示，在本实施方式中，第一动压滑动轴承70和第二动压滑动轴承80彼此贴靠地布置。在动压滑动轴承70、80的彼此贴靠的端部处构造有呈环形的轴向凸出部706、806，其中，轴向凸出部706、806构造在动压滑动轴承70、80的径向内侧区域。第一动压滑动轴承70的轴向凸出部706设有沿轴向凹陷的凹口707。第二动压滑动轴承80的轴向凸出部806设有沿轴向凹陷的凹口。在此，分属于两个动压滑动轴承70、80的轴向凸出部706、806通过相互贴靠来彼此组合，由此在功能上基本替代在第一实施方式中的隔圈60。在这种情况下，分属于两个轴向凸出部706、806的凹口可以组合成连通至行星齿轮轴20的内部的输出通路的通 孔。
由此，借助油泵输送的油可以依次经由行星齿轮轴20的输入通路和动压滑动轴承70、80的入油孔702、802进入液压油腔701、801。油可以从液压油腔701、801以及与液压油腔701、801连通的油道流动至动压滑动轴承70、80的外周面。此外，油还可以从液压油腔701、801以及与液压油腔701、801连通泄压槽703、803流动至两个动压滑动轴承70、80的彼此靠近的轴向端部处的弧面705、805，进而流至轴向凸出部706、806的外周面。在此汇集的油进一步通过由两个轴向凸出部706、806的凹口组合形成的通孔排出到行星齿轮轴20内部的输出通路。
根据上述两个实施方式的动压滑动轴承组件构造为多功能轴承组件，其可以同时承受径向载荷、轴向载荷和倾覆力矩。同时，动压滑动轴承组件结构简单、易于安装且成本较低。
附图标记列表
10    第一构件，行星齿轮
101   凸台部
20    第二构件，行星齿轮轴
201   进油孔
202   回油孔
203   凸缘
30    行星架
40    动压滑动轴承，第一动压滑动轴承
401   液压介质腔，液压油腔
402   液压介质输入部，入油孔
403   液压介质输出部，泄压槽
404   液压介质通道，油道
405   弧面
50    动压滑动轴承，第二动压滑动轴承
501   液压介质腔，液压油腔
502   液压介质输入部，入油孔
503   液压介质输出部，泄压槽
505   弧面
60    隔圈
601   环形槽
602   通孔
70    动压滑动轴承，第一动压滑动轴承
701   液压介质腔，液压油腔
702   液压介质输入部，入油孔
703   液压介质输出部，泄压槽
704   液压介质通道，油道
705   弧面
706   轴向凸出部
707   凹口
80    动压滑动轴承，第二动压滑动轴承
801   液压介质腔，液压油腔
802   液压介质输入部，入油孔
803   液压介质输出部，泄压槽
805   弧面
806   轴向凸出部

Claims (10)

  1. 动压滑动轴承组件，其用于沿径向布置在能够相对彼此旋转的第一构件(10)和第二构件(20)之间，其中，所述第一构件(10)具有用于环绕所述第二构件(20)的内周面，并且在所述内周面处构造有凸台部(101)，其中，
    所述动压滑动轴承组件包括两个动压滑动轴承(40、50；70、80)，
    所述动压滑动轴承(40、50；70、80)能够如此同心地且沿轴向排列地固定于所述第二构件(20)，使得所述凸台部(101)沿轴向容纳在所述动压滑动轴承(40、50；70、80)之间，其中，
    各个动压滑动轴承(40、50；70、80)的外周面和彼此靠近的轴向端面分别通过弧面(405、505；705、805)连接过渡。
  2. 根据权利要求1所述的动压滑动轴承组件，其特征在于，所述动压滑动轴承(40、50；70、80)的各自的外周面和彼此靠近的轴向端面经硬化涂层。
  3. 根据权利要求1或2所述的动压滑动轴承组件，其特征在于，在所述动压滑动轴承(40、50；70、80)的外周面处构造有沿轴向延伸的液压介质腔(401、501；701、801)。
  4. 根据权利要求3所述的动压滑动轴承组件，其特征在于，所述动压滑动轴承(40、50；70、80)构造有液压介质输入部(402、502；702、802)，所述液压介质输入部(402、502；702、802)从所述动压滑动轴承(40、50；70、80)的内周面连通至所述液压介质腔(401、501；701、801)。
  5. 根据权利要求3或4所述的动压滑动轴承组件，其特征在于，所述动压滑动轴承(40、50；70、80)构造有液压介质输出部(403、503；703、803)，所述液压介质输出部(403、503；703、803)从所述液压介质腔(401、501；701、801)连通至所述动压滑动轴承(40、50；70、80)的彼此靠近的轴向端面。
  6. 根据权利要求5所述的动压滑动轴承组件，其特征在于，沿轴向在 所述动压滑动轴承(40、50)之间设置隔圈(60)，其中，所述隔圈(60)构造有在所述隔圈的外周面处的环形槽(601)以及连通所述环形槽(601)和所述隔圈(60)的内周面的通孔(602)。
  7. 根据权利要求5所述的动压滑动轴承组件，其特征在于，在所述动压滑动轴承(70、80)的彼此靠近的端部处构造有呈环形的轴向凸出部(706、806)，其中，所述轴向凸出部(706、806)布置在所述动压滑动轴承(70、80)的径向内侧区域并且设有沿轴向凹陷的凹口(707)。
  8. 根据权利要求3至7中任一项所述的动压滑动轴承组件，其特征在于，在所述动压滑动轴承(40、50；70、80)的外周面处还构造有沿周向延伸的液压介质通道(404；704)，所述液压介质通道(404；704)与所述液压介质腔(401、501；701、801)连通。
  9. 根据上述权利要求中任一项所述的动压滑动轴承组件，其特征在于，所述两个动压滑动轴承(40、50；70、80)相同地构造。
  10. 动压滑动轴承单元，包括：
    -能够相对彼此旋转的第一构件(10)和第二构件(20)其中所述第一构件(10)具有用于环绕所述第二构件(20)的内周面，其中，在所述内周面处构造有凸台部(101)，以及
    -沿径向布置在所述第一构件(10)和所述第二构件(20)之间的、根据上述权利要求中任一项所述的动压滑动轴承组件，
    其中，所述动压滑动轴承组件的动压滑动轴承(40、50；70、80)如此同心地且沿轴向排列地固定于所述第二构件(20)，使得所述凸台部(101)沿轴向容纳在所述动压滑动轴承(40、50；70、80)之间，
    其中，所述第一构件(10)的内周面和所述凸台部(101)的两个轴向端面分别通过弧面连接过渡，并且，各个动压滑动轴承(40、50；70、80)的外周面和彼此靠近的轴向端面分别通过弧面(405、505；705、805)连接过渡。
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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006009575A (ja) * 2004-06-22 2006-01-12 Ntn Corp 遊星歯車装置
CN102518787A (zh) * 2011-12-13 2012-06-27 哈尔滨东安发动机（集团）有限公司 风电齿轮箱的行星传动结构
CN102792018A (zh) * 2010-02-12 2012-11-21 三菱重工业株式会社 用于的风力涡轮发电机齿轮箱和风力涡轮发电机
CN202707789U (zh) * 2012-07-19 2013-01-30 嘉善金泰工程塑业有限公司 驱动桥用滑动轴承
JP2019215016A (ja) * 2018-06-11 2019-12-19 Ntn株式会社 転がり軸受

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006009575A (ja) * 2004-06-22 2006-01-12 Ntn Corp 遊星歯車装置
CN102792018A (zh) * 2010-02-12 2012-11-21 三菱重工业株式会社 用于的风力涡轮发电机齿轮箱和风力涡轮发电机
CN102518787A (zh) * 2011-12-13 2012-06-27 哈尔滨东安发动机（集团）有限公司 风电齿轮箱的行星传动结构
CN202707789U (zh) * 2012-07-19 2013-01-30 嘉善金泰工程塑业有限公司 驱动桥用滑动轴承
JP2019215016A (ja) * 2018-06-11 2019-12-19 Ntn株式会社 転がり軸受

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