WO2023093940A1 - Rondelle de butée, et boîte de vitesses planétaire comportant au moins une rondelle de butée de ce type - Google Patents

Rondelle de butée, et boîte de vitesses planétaire comportant au moins une rondelle de butée de ce type Download PDF

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Publication number
WO2023093940A1
WO2023093940A1 PCT/DE2022/100869 DE2022100869W WO2023093940A1 WO 2023093940 A1 WO2023093940 A1 WO 2023093940A1 DE 2022100869 W DE2022100869 W DE 2022100869W WO 2023093940 A1 WO2023093940 A1 WO 2023093940A1
Authority
WO
WIPO (PCT)
Prior art keywords
thrust washer
oil guide
oil
guide groove
radially
Prior art date
Application number
PCT/DE2022/100869
Other languages
German (de)
English (en)
Inventor
Wolfgang Fugel
Andreas CHRISTL
Original Assignee
Schaeffler Technologies AG & Co. KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2023093940A1 publication Critical patent/WO2023093940A1/fr

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Classifications

    • 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
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0482—Gearings with gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/44—Needle bearings
    • F16C19/46—Needle bearings with one row or needles
    • F16C19/463—Needle bearings with one row or needles consisting of needle rollers held in a cage, i.e. subunit without race rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts

Definitions

  • the invention relates to a thrust washer with a central axial through hole and with two sides of the disk facing away from one another, at least one of the sides of the disk being provided with at least one oil guide groove extending radially, the oil guide groove being formed on the circumferential side between contact surfaces pointing in the axial direction on the at least one side of the disk and wherein the oil guide groove is open towards the outer contour of the thrust washer and towards the through hole, and wherein the oil guide groove is wider at its end ending on the outer contour than the inner end ending at the through hole, with the oil guide groove ending in a radial recess provided on the inner circumference.
  • Ring-shaped thrust washers of this type are used for the axial start-up of the planet gear and protect the planet carrier and the planet gears from wear.
  • the planet gear runs with a flat front surface against the flat contact surface of the thrust washer.
  • the planetary gear is rotatably mounted on a planetary pin fixed to the planetary carrier via a roller bearing, usually a needle bearing.
  • thrust washers such as those according to JP 2017 - 180 584 A and DE 10 2019 212 217 A1
  • their oil guide grooves have a wedge-shaped cross section, which is predetermined by ramp-like formations of the groove base of the oil guide grooves.
  • Oil guide grooves are wider at the outer end than at the inner end. A passage of oil through the respective thrust washer is ensured in that each oil guide groove opens into a radial recess provided on the inner circumference.
  • the planetary bolt is usually provided with an axially extending blind bore provided, from which at least one radial bore goes off, which opens out on the bolt lateral surface, ie immediately below the needle bearing.
  • the oil is guided from the inside into the bearing area via this bore structure, usually in conjunction with an oil-collecting oil drip tray, from where it is distributed in the bearing area itself on the one hand, but also reaches the wheel and disk surfaces that abut one another on the other.
  • the oil flowing in from the inside is caught on the inner circumference via the wide opening cross section of the lubricant groove and can be distributed in the lubricant groove due to rotation and discharged to the outside.
  • the surfaces that come into contact with one another are lubricated by the oil in the lubricant grooves, so that despite the rotational movement of the front face of the planet wheel, there is no appreciable wear when it comes into contact with the fixed disk surface.
  • the oil is supplied from the inside, ie via the correspondingly hollow planetary pin.
  • the formation of the bore structure is correspondingly complex, as is the production and assembly of an oil drip tray as a separate component.
  • the invention is based on the object of specifying a thrust washer that enables a simplified configuration of a planetary gear.
  • each oil guiding groove has two groove sections which are identical to one another and are mirror images of an imaginary line of symmetry
  • the thrust washer has an overall thickness which is greater than the starting thickness of a metal sheet, the overall thickness being an axial dimension between the axially most protruding contours of the sides of the washer and the thrust washer being formed from the metal sheet, c.
  • the axial depth of the oil guide groove is described over its entire course from the through-hole to the outer contour and between two opposite walls by an axial depth dimension that remains constant over the course, with the axial depth dimension being a difference between the total thickness of the thrust washer and a radial course of the
  • the through hole is of constant sheet metal thickness towards the outer contour, and the sheet metal thickness is a distance which exists axially between the groove base of the oil guide groove (6) and the side of the disk facing away from the oil guide groove.
  • the sheet thickness corresponds to the initial thickness of the metal sheet.
  • the walls are mirror images of each other and are designed to be geometrically identical.
  • At least three oil guide grooves and radial recesses are provided, distributed equidistantly around the circumference. that if there are several oil guide grooves, all the oil guide grooves have the same geometry and the same course, or that oil guide grooves of different geometries with different widths are provided, that an anti-rotation element is provided, which protrudes from one side of the disk and is located radially opposite the end of an oil guide groove.
  • the thrust washer according to the invention makes it possible to guide the oil from radially outside into the thrust area as well as the bearing area. This means that, if necessary, an oil supply from the inside via the planet bolts in connection with a Lubricant drip tray can be dispensed with or that the oil supply to the planetary bearings is improved.
  • the thrust washer according to the invention has at least one oil guiding groove, which has a specific groove geometry. A plurality of such oil guide grooves are preferably provided.
  • One or the respective oil guide groove which is radially open on the outer and inner circumference, ie on the edge of the central through-hole, is wider on the outer contour than on the inner circumference, ie it narrows from radially outside to radially inside.
  • the or each lubricant groove opens into a radial recess, that is to say a recess which locally widens the inner diameter of the disk.
  • the planet bolt penetrates the central mounting hole of the thrust washer with little play.
  • the needle bearing follows the planetary pin radially. Due to the design of the radial recesses, the oil flowing in via the oil guide groove from radially outside reaches the bearing area more quickly, while during the flow through the lubricant groove it naturally also reaches the area of the surfaces of the planet wheel and the thrust washer that abut and rotate relative to one another.
  • This specific geometry of the oil guide groove makes it possible to convey the scooped or dripping oil or the oil foam from radially outside to radially inside and to feed it to the bearing area.
  • the front face of the planetary gear is arranged at a minimum distance from the oil guide groove or, in the event of a start, rests against the thrust washer.
  • the oil guide groove therefore forms a kind of funnel towards the outside. This means that the oil can enter from radially outside or initially reaches the entrance of the oil guide groove via the surrounding structure, and this can also take place when passing through an oil sump in the planetary gear.
  • the thrust washer according to the invention thus makes it possible to design the planetary gear or the planetary wheel bearing in a simpler way, since simple, solid and non-drilled planetary bolts can be used, and an oil drip tray can also be dispensed with.
  • At least three, preferably four oil guide grooves and radial recesses distributed equidistantly around the circumference are provided, so that a correspondingly large groove or nozzle volume, through which the oil can be conveyed inwards and can escape at various positions around the circumference.
  • one or more of the oil guide grooves that are adjacent to this feed area can be wider than the lubricant grooves that are distant from it.
  • the or each oil guide groove is drawn or coined or otherwise cold formed.
  • the thrust washer consists of a corresponding sheet metal or metal strip and is correspondingly formed by deep-drawing to form the oil groove structure.
  • the material thickness does not change as a result of this drawing process, and consequently neither do the corresponding properties of the thrust washer resulting from the material thickness.
  • the disk sides on both sides of the thrust washer according to the invention are planar, but are provided with a height relief due to drawing.
  • relief-like structures in the form of elevations and depressions form on both sides of the disk, the sides of the disk being planar despite the resulting structures or reliefs, so that there is a planar contact surface in particular on the side facing the planet wheel forms and the planetary gear end face has a correspondingly large surface contact with the thrust washer in the event of a start.
  • Another advantage of deep-drawing without changing the material thickness and in particular the design with the two parallel flat disk surfaces is that the total thickness of the thrust washer can be easily varied and adjusted in relation to the given installation space. This allows you to work with extremely small tolerances. It is also advantageous that a correspondingly thin metal sheet can be used as the starting material, with the final total thickness of the thrust washer being greater than the starting thickness of the metal sheet.
  • a metal sheet or metal strip with a thickness of 0.65 mm is used, which is correspondingly deep-drawn to form the lubricant grooves and, for example, has a final total thickness of 1 mm when forming a groove depth of 0.35 mm described by the axial depth dimension.
  • the numerical values given are only examples, of course a slightly thinner or thicker metal strip can also be used in the application, just as the axial depth dimension can of course also be selected differently and thus also the resulting pane thickness.
  • a connecting element can be provided which protrudes on the disk side facing the planet carrier. A torsion-proof positioning of the thrust washer relative to the planet carrier is ensured via this anti-twist element.
  • the axially protruding anti-rotation element engages in a corresponding receptacle on the planet carrier, so that this engagement prevents the thrust washer from rotating.
  • the anti-rotation element interacting with the planet carrier of the planetary gear is formed at the outer open end, i.e. radially outside at the outlet or inlet of the oil guide groove in the bottom of the groove, i.e. in the recessed area, of at least one of the oil guide grooves.
  • the geometry of the anti-rotation element essentially includes the initial strength of the sheet metal for the production of the thrust washer, can be integrated into the cutting of the sheet metal blank and remains essentially unaffected by the deformations in the forming process of the washer.
  • an anti-wear coating can be applied at least to the disk side facing the planet wheel.
  • the thrust washer can also be coated on all sides with such a wear protection coating, which is possible in particular if the wear protection coating is applied as part of a drum coating.
  • the invention also relates to a planetary gear comprising a planetary carrier and several planetary gears rotatably mounted thereon on respective planetary bolts, each planetary gear being offset axially towards the planetary carrier via at least one thrust washer of the type described above.
  • Each planet wheel is preferably supported on both axial sides via two such thrust washers, with the two thrust washers being of identical design.
  • such a planetary gear has a sun wheel, which meshes with its teeth with the toothed planet wheels and consequently rotates relative to the planet carrier.
  • Oil is preferably supplied via a central shaft which passes through the sun gear and has a corresponding channel structure, which oil emerges radially from the shaft via a radial bore in the channel structure and reaches the sun gear on the inside.
  • the sun gear has one or more radial bores, with the oil exiting radially via the one or more radial bores and optionally via an axial bearing, via which the sun gear is mounted axially on the shaft, and from radially inside to the planet gears and their arrangement on the planet bolts reached.
  • Figure 1 is a perspective view of a thrust washer according to the invention
  • Figure 2 is a plan view of the thrust washer from Figure 1
  • FIG. 3 shows a sectional representation of the principle of a planetary gear with thrust washers serving to support the planetary gears.
  • FIGS. 1 and 2 show a thrust washer 1 according to the invention, which was produced from a thin metal strip formed by deep-drawing and having a total thickness of between, for example, 0.6 to 1.0 mm.
  • the thrust washer 1 has an even or planar first disk side 2, which is described in Figure 3 and which, in the assembly position, is positioned axially directly adjacent to the end face of a planet gear to be supported on the thrust washer 1, the planet gear with its end face against the disk side 2 running.
  • On the other side there is an opposite, likewise flat or planar second disk side 3 which, in the assembled position, bears flat against a support surface of a planetary carrier.
  • an anti-rotation element 4 is provided on the thrust washer 1 in the form of an anti-rotation element 4 that first extends radially and then at an angle in the axial direction, which engages in a corresponding receptacle on the planetary carrier, so that the thrust washer 1 is coupled to the planetary carrier in the assembly position relative to the planetary carrier is.
  • the thrust washer 1 is otherwise ring-shaped and has a central receiving bore 5 through which a planet bolt, on which a planet wheel is rotatably mounted via a bearing device, engages in the assembled position.
  • the thrust washer 1 made of the thin metal strip is shaped accordingly, as described, with this shaping on the one hand Anti-rotation element 4 is formed, but on the other hand, corresponding profiles are also formed on both sides of the pane 2, 3, with the pane thickness not changing as a result of the deep-drawing despite the forming.
  • four oil guide grooves 6 are formed on the disk side 2 pointing towards the planet wheel in the assembly position in the example shown, which extend radially and are open towards the outer contour 7 at the outer end, just as they are open towards the inner circumference 8 at the inner end.
  • the oil guide grooves 6 have a V-shaped geometry, see also FIG.
  • the oil guide grooves 6 open into corresponding radial recesses 9, via which the inner circumference is locally enlarged radially. These radial recesses 9 ensure that the oil flowing through the oil guide grooves 6 from radially outside to radially inside can escape early towards the bearing unit.
  • the areas to the left and right of the respective oil guide groove 6 are of course raised with respect to the respective oil guide groove 6 and are designed to be closed radially on the inner circumference, i.e. they rise up relative to the bottom surface of the oil guide grooves 6 and close radially on the inside to the level of the inner circumference.
  • the thrust washer 1 In the assembly position, when consequently the thrust washer 1 is mounted on the planet bolt, the thrust washer 1 lies flat against the planet carrier with the disk side 3, which is formed by the flat rear sides of the oil guide grooves 6. Equally, however, the thrust washer 1 also rests in the area of the inner circumference all the way around between the oil guide groove rear sides on the planet carrier.
  • FIG. 3 shows a sectional representation of the principle of a planetary gear 12 according to the invention, comprising a central shaft 13 on which a sun wheel 14 is axially rotatably mounted via an axial bearing 15 .
  • the toothing 17 of the respective planet wheel 18 meshes with a toothing 16 of the sun wheel.
  • a plurality of planet gears 18 together with planet bolts 20 are arranged on the planet carrier 21 on a circular path.
  • a thrust washer 1 according to the invention is arranged on both sides between the planet wheel 18 and the planet carrier 21, which is secured against rotation on the planet carrier 21 with the respective anti-rotation element 4, which engages in a corresponding receptacle on the planet carrier 21, as described.
  • each thrust washer 1 is consequently positioned adjacent to the corresponding side surface 22 of the planetary carrier 21 .
  • the opposite disk surface 2 is positioned directly adjacent to the end surface 23 of the planetary wheel 18, which means that the end surface 23 is adjacent to the oil guide grooves 6 and runs against the disk surface 2 in the event of start-up.
  • Both the roller bearing 19 and the axial contact surfaces of the thrust washers 1 and the planet gear 18 must be supplied with oil for lubrication. This is due to the integration of the thrust washer 1 according to the invention from radially outside of the planet wheel and not from the radially inside, as was previously the case with corresponding bore structures in the planetary pin 20 .
  • the shaft 13 is provided with a channel structure comprising an axially extending channel bore 24 from which at least one radial bore 25 which is open towards the sun gear 14 extends.
  • the sun gear 14 in turn is provided with at least one radial bore 26 which is open on the one hand to the radial bore 25 and on the other hand to the planetary gear arrangement.
  • the oil If oil is supplied via the channel structure in the shaft 13 , the oil leaves this and enters a distributor space 27 between the shaft 13 and the sun wheel 14 . From there, the oil flows on the one hand to the radial bore or bores 26 and, as it were, reaches the left-hand area of the planetary gear arrangement. On the other hand, the oil flows to the axial bearing 15 and radially through it, so that it reaches the right-hand area of the planetary gear arrangement. As the sun gear 14 rotates, the oil is driven radially in the direction of the planetary gear assembly with a certain pressure due to centrifugal force.
  • the oil guide grooves 6 are open radially on the outer contour 7 as well as on the inner circumference.
  • the oil flowing in from the sun gear 14 can now enter the adjacent oil guide groove 6 or the various oil guide grooves 6 distributed around the circumference, with this entry area being relatively wide due to the V-shaped geometry, so that a correspondingly large quantity of oil can be collected.
  • the respective end faces 23 of the planet wheel are only positioned at a minimal axial distance from the side of the disk 2 or are in contact with it when starting up. This means that the oil guide grooves 6 are more or less closed axially via the end faces 23, so that ultimately corresponding oil guide channels are formed between the respective thrust washer 1 and the end face 23 of the planet wheel 18, which have a radially inwardly tapering geometry.
  • the oil discharged from the sun gear 14 flows at least into the adjacent pocket 11, from where, after the pocket 11 only moves at the reduced speed of the planet carrier 21, it also flows radially inwards to a certain extent and through the gap on the inner circumference of the thrust washer 1 to the planet pin 20 can flow out.
  • the configuration of the thrust washer 1 shown in Figures 1 and 2 shows a symmetrical segmentation of the sides of the washer, after the oil guide grooves 6 are distributed equidistantly around the circumference and all have the same V-shape in terms of width, i.e. the same geometry.
  • the oil guide grooves 6 it is also conceivable for the oil guide grooves 6 to have different parts Execute width profile, with the width of the oil guide groove 6 and the ultimate nozzle width or the channel volume is influenced and therefore the oil flow.
  • a defined flow of oil can also reduce the axial play of the thrust washer via the oil cushion that builds up.
  • the thrust washer 1 is produced by forming or deep-drawing and/or embossing a thin metal strip to form the corresponding surface profiles.
  • the result after the forming is a corresponding disk width that is wider than the initial width of the original metal strip.
  • a defined final pane width can be set by forming, using a very thin metal strip, which is advantageous in terms of both material consumption and weight.
  • the overall width of the thrust washer 1 can be varied and adapted to the actual installation space conditions by the corresponding penetration depth, i.e. the variation of the depth of the oil guide grooves 6, so that the thickness of the washer can be easily adapted in relation to a desired, permissible axial play or corresponding tolerances is possible.
  • Each oil-guiding groove 6 has two groove sections 6a, 6b which are formed as mirror images of one another and are identical to an imaginary line of symmetry S1 or S2.
  • the axes of symmetry S1 and S2 intersect on the central axis M of the thrust washer 1 , the central axis M being the axis of symmetry of the thrust washer 1 at the same time, subject to the different geometry on the anti-rotation element 4 .
  • the thrust washer 1 has an overall thickness T which is greater than the initial thickness t of a metal sheet from which the thrust washer 1 is made.
  • the total thickness T is an axial dimension between the axially most protruding contours of disk sides 2 and 3.
  • the most protruding contours are at least on one side through the contact surfaces 10a lying in a common radial plane, which are in contact with the planetary carrier 21 or in sliding contact with the planet wheel 23.
  • the axial groove depth of the oil guide groove 6 is described over its entire course from the through hole H to the outer contour 7 of the thrust washer 1 and between two opposing walls W by an axial depth dimension d that remains constant over the course, i.e.
  • the oil guide groove 6 is, subject to rounded edges the walls W of the oil guide groove 6 everywhere the same depth.
  • the axial depth d corresponds to a difference between the total thickness T of the thrust washer 1 and a sheet metal thickness tx that is constant in the radial course from the through-hole H to the outer contour 7 .
  • the sheet metal thickness tx is a distance which is axially between the groove base GG of the oil guide groove 6 and the respective side of the disc facing away from the oil guide groove 6 or 3.
  • the respective anti-rotation element 4 can advantageously be punched or cut out on the thin sheet metal or sheet metal strip already in the blank, because at the outer open end, i.e. in the flat area in the almost initial state with the initial sheet metal thickness (initial thickness t) of the sheet metal material, at least one of the oil guide grooves 6 of the finished thrust washer (1) and is therefore hardly or not at all changed in its geometry during the molding process of the oil guide grooves 6.
  • the two thrust washers 1 used per planet wheel 18 are preferably identical, so that identical parts can be used, which is advantageous both in terms of production and assembly.

Abstract

L'invention concerne une rondelle de butée (1) et une boîte de vitesses planétaire. La rondelle de butée doit être disposée entre un pignon satellite (18) et un porte-satellites (21) d'une boîte de vitesses planétaire (12). Sur le côté rondelle (2) faisant face au pignon satellite (18), une ou plusieurs rainures de guidage d'huile s'étendant radialement (6) sont prévues, qui sont ouvertes radialement au niveau du contour externe (7) et au niveau de la périphérie interne (8) de la rondelle (1). La ou chaque rainure de guidage d'huile (6) est plus large au niveau de l'extrémité externe qu'au niveau de l'extrémité interne. La ou chaque rainure de guidage d'huile (6) mène à un évidement radial (9) prévu au niveau de la périphérie interne (8).
PCT/DE2022/100869 2021-11-26 2022-11-21 Rondelle de butée, et boîte de vitesses planétaire comportant au moins une rondelle de butée de ce type WO2023093940A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021131138.1 2021-11-26
DE102021131138 2021-11-26

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Publication Number Publication Date
WO2023093940A1 true WO2023093940A1 (fr) 2023-06-01

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3597027A (en) 1969-02-28 1971-08-03 Gen Motors Corp Thrust bearing
US4795220A (en) * 1986-12-19 1989-01-03 Daido Metal Company Ltd. Thrust bearing
US7252615B2 (en) * 2004-03-22 2007-08-07 General Motors Corporation Lubrication system and method for hybrid electro-mechanical planetary transmission components
JP2017180584A (ja) 2016-03-29 2017-10-05 大豊工業株式会社 ワッシャ
DE102019212217A1 (de) 2018-08-21 2020-02-27 Zf Friedrichshafen Ag Anlaufelement für ein hydrodynamisches Axiallager und hydrodynamisches Axiallager
DE102020207471A1 (de) * 2019-09-17 2021-03-18 Zf Friedrichshafen Ag Anlaufelement für ein hydrodynamisches Axiallager

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3597027A (en) 1969-02-28 1971-08-03 Gen Motors Corp Thrust bearing
US4795220A (en) * 1986-12-19 1989-01-03 Daido Metal Company Ltd. Thrust bearing
US7252615B2 (en) * 2004-03-22 2007-08-07 General Motors Corporation Lubrication system and method for hybrid electro-mechanical planetary transmission components
JP2017180584A (ja) 2016-03-29 2017-10-05 大豊工業株式会社 ワッシャ
DE102019212217A1 (de) 2018-08-21 2020-02-27 Zf Friedrichshafen Ag Anlaufelement für ein hydrodynamisches Axiallager und hydrodynamisches Axiallager
DE102020207471A1 (de) * 2019-09-17 2021-03-18 Zf Friedrichshafen Ag Anlaufelement für ein hydrodynamisches Axiallager

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