[go: up one dir, main page]

WO2014187459A1 - Ensemble de transmission - Google Patents

Ensemble de transmission Download PDF

Info

Publication number
WO2014187459A1
WO2014187459A1 PCT/DE2014/200233 DE2014200233W WO2014187459A1 WO 2014187459 A1 WO2014187459 A1 WO 2014187459A1 DE 2014200233 W DE2014200233 W DE 2014200233W WO 2014187459 A1 WO2014187459 A1 WO 2014187459A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
spacer sleeve
shaft
transmission shaft
face
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/DE2014/200233
Other languages
German (de)
English (en)
Inventor
Alex NICOLAS QUECK
Maximilian Wenninger
Georg Draser
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and 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 and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of WO2014187459A1 publication Critical patent/WO2014187459A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/061—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing mounting a plurality of bearings side by side
    • 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
    • F16H57/0018—Shaft assemblies for gearings
    • F16H57/0031—Shaft assemblies for gearings with gearing elements rotatable supported on the shaft
    • 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 transmission unit with a gear shaft, a gear wheel and a further gear element, both of which are arranged on or on the transmission shaft, and a spacer sleeve which is arranged between the first gear and the further gear element and is supported on the front side of each of these , Background of the invention
  • DE 38 07 310 A1 shows a gear unit, which is formed from a gear shaft portion of a plurality of gears on the transmission shaft portion and a spacer sleeve.
  • the spacer sleeve is arranged axially between two gear wheels mounted on the gear section by means of loose wheel bearings and keeps them axially at a distance.
  • Axial distances between two gears for example, necessary to maintain axial clearance for the mobility of switching elements, with which the gears or other components are operated, or to secure space for the arrangement in the transmission.
  • switching elements are, for example, components of synchronous switching clutches with which these gears can be selectively coupled in a torque-proof manner to the transmission shaft.
  • Spacers are exposed in certain arrangements briefly or permanently high axial forces. These forces act, for example, during assembly on the spacer sleeve when it is loaded during pressing in the gear unit, for example, together with gears or other transmission elements by the pressing forces with. Such assembly forces are in the order of magnitude of 60 to 80 kN. Between preloaded angle bearings spacers are often permanently loaded axially. For such applications, the spacers must be designed axially highly resilient.
  • JP 1 1 -303947 AA shows a spacer sleeve which surrounds at least one gear shaft section on the circumferential side of the axis of rotation and thereby holds at least one gear element in the form of a gear to a rolling bearing on a shaft portion of a drive shaft at an axial distance.
  • the spacer sleeve has a rectified with the axis of rotation section with the outlines of a hollow cylinder. In this case, the hollow cylinder is circular-cylindrical.
  • US Pat. No. 7,036,391 B2 shows two spacer sleeves made of hollow cylindrical sections in an axially preloaded bearing arrangement of a driven drive.
  • spacers are mostly involved in the axial force flow because they need to absorb the introduced due to the helical gear axial force, they are often forged or milled.
  • DE 10 2007 059 095 A1 shows a deep-drawn spacer sleeve with a board. In the area in which the board merges into the axial cylinder, the spacer sleeve is rounded due to the production process, which makes support on a shaft shoulder more difficult. Effective support on radially only slightly projecting shaft shoulders or retaining rings is not or only with difficulty possible and requires larger sized components. If oil supply to adjacent components continues to be required via the spacer sleeve, the spacer sleeve must be further weakened by means of oil penetration holes.
  • the notch stresses reduce their strength, so that the support is further impeded.
  • the thus required semifinished product thickness is opposed to an increasing lightweight construction and worsens the support on a shaft-near transmission component such as a shaft shoulder on, so that under certain circumstances, must be resorted to a machined spacer sleeve.
  • the object of the invention is therefore to provide a gear unit and a spacer sleeve for a gear unit, which are each inexpensive to produce and avoid the above-mentioned disadvantages.
  • the spacer sleeve is supported by a circumferentially changing radius at the front-side first end of two different components of the transmission unit.
  • the invention is based on the idea that for effective support simultaneous support of the spacer sleeve over the full circumference is not required for both components, but more or less regularly arranged in the circumferential direction discrete support points are sufficient, so that the spacer sleeve for a given Angle is supported either on the first gear or on the gear shaft fixed component.
  • On the Anformung a collar or Bordes is omitted, which can also simplify the production in the case of a spacer sleeve with longitudinal grooves.
  • the spacer sleeve at its first end face in the circumferential direction has a constant material thickness with a radius which changes as a function of the circumferential angle.
  • it has, seen in cross section, for example, a wave-shaped course over its circumference, wherein the wave troughs and the wave crests can be supported on different, concentrically arranged gear components.
  • An end-board is not required.
  • the wave-shaped end can be formed even with a solid spacer sleeve or a spacer sleeve made of plastic.
  • the material thickness at the spacer sleeve end can vary over the circumference and thus at least partially the variable outer radius can be generated, or it can be constant as in a spacer sleeve made of sheet metal.
  • a spacer made of sheet metal is particularly torsion-resistant and inexpensive to produce.
  • the maximum number of undulating elevations over the circumference depends on the radius of the spacer sleeve. Particularly suitable are three, four or five radial elevations, each of which is evenly spaced apart.
  • the spacer sleeve nestles preferably on the transmission shaft; and the radially protruding portions may be in the form of a sinusoidal half-wave.
  • the wave-shaped spacer sleeve combines further advantages: Due to the dropping board, a spacer sleeve according to the invention is no longer subjected to bending stresses, but the axial force is introduced directly into the sleeve jacket. Since the spacer sleeve is thus stressed only on pressure, the strength is further increased. Due to the discrete support points on the gear or the further transmission element can flow between these oil from the environment to the gear. If the gearwheel is mounted on the shaft as idler gear, the oil supply of the bearing can thus be ensured without the spacer sleeve having to be provided with additional bores.
  • the spacers are preferably provided as spacers between two adjacent to each other on a gear shaft portion gears.
  • the further transmission element is thus a second gear.
  • Gears are both on the transmission shaft section, z. B. by press fit, fixed or integrally formed with the transmission shaft portion and thus not rotatable to the gear shaft portion gears or rotatably mounted on the transmission shaft portion gears. The latter are z. B.
  • gear wheel or idler gear and often stored by means of rolling bearings rotatably mounted on the transmission shaft sections. It is also conceivable that the spacer sleeve is arranged between a gear wheel firmly seated on the transmission shaft section and a loose wheel.
  • the spacers are used as spacers between a gear and another transmission element, such.
  • B a transmission housing, a shaft shoulder or a bearing.
  • the spacer sleeve also keeps other arbitrary gear elements such as disc-shaped components or gear bearings, sitting on a gear shaft, shaft sections or similar elements, at a distance and / or is supported on housings or shaft paragraphs from. It is also conceivable that the spacer sleeve holds two oppositely biased angular contact bearing assemblies, for example in axle drives at a distance.
  • the spacer sleeve is designed substantially as a hollow cylinder.
  • a circular or polygonal hollow cylinder still has the basic shape or the outline of a hollow cylinder even after attachment of a radial collar, after the introduction of a circumferential groove inside or outside or after the introduction of openings or recesses on the surface.
  • the polygon may also have corners that are rounded with convex or concave radii.
  • an embodiment of the invention provides that the spacer sleeve is sleeve-shaped as a drawn part.
  • Another embodiment provides that such spacers are made of sheet metal strips. These spacers are formed, for example, by a metal strip which is circularly curved, the bending ends are guided towards each other and positively, positively and / or materially connected to each other. Spacers can be produced very accurately.
  • Various moldings are without additional effort when pulling, cutting or bending to produce. As a result, these parts are particularly advantageous over the prior art from machining production, because in this additional form elements such as depressions in grooves and collars are only to produce by consuming material removal such as turning, planing and milling and only with a lot of material removal.
  • Sheet metal spacers according to the invention may be lighter than the solid rings of the prior art, in particular when the sheet metal thickness of the metal sheet, the spacer sleeves is smaller than the bridging dimension between the inner envelope contour and the outer envelope contour of the spacer sleeve.
  • the inner envelope contour is described for example in a solid-shaped sleeve by the inner diameter and the outer envelope contour by the outer diameter.
  • the bridge dimension in this case is half the difference between the outer diameter and the inner diameter.
  • the gear shaft section is seen for example in cross section a triangular, square or another polygonal profile or, as already mentioned, outside cylindrical.
  • the réellehullkontur is then described accordingly by a triangle, square or by another polygon.
  • the outer envelope contour is a triangle, quadrangle or polygon which corresponds to this and is enlarged on the sides by the bridge dimension or has a different geometry.
  • envelope contour is therefore not only suitable for cylindrical cross sections according to the above explanation.
  • the dimensions of an inner envelope contour for a spacer sleeve, which is seated with an interference fit on the transmission shaft section, are correspondingly smaller than the nominal dimension of the transmission shaft section at the seat of the spacer sleeve in the press fit.
  • the sheet metal of the spacer sleeve is thinner than the bridging dimension, the distance between inner envelope contour and outer envelope contour is bridged by form elements such as beads, embossments, radial rims, doublings and other shaped by non-cutting deformation shaped elements.
  • an embodiment of the invention provides that the sheet metal of the spacer sleeves has groove-shaped recesses at least in sections.
  • the groove-shaped depressions are longitudinally extending.
  • the depressions are either put through, embossed or bent, so that during their production only a small proportion (bending portion) of the sheet is plastically deformed.
  • the wall sections delimiting the depressions thus bridge the bridging dimension between the inner envelope contour and the outer envelope contour.
  • the sheet, which radially delimits the channel-shaped recesses is as thick in the radial direction as the sheet at the sections adjacent to the recesses.
  • Such spacers are rings made by bending and bending similar methods. They thus have a low degree of deformation.
  • the metal sheet of the spacer sleeve, which limits the channel-shaped recesses radially is at least partially thinner in the radial direction than the metal sheet of the circumferentially adjacent sections of the spacer sleeve in the radial direction.
  • a radial height is designed if necessary, which corresponds to a multiple of the thickness of the sheet.
  • One, two, but preferably three or more of the channel-shaped depressions extend spirally or in the longitudinal direction of the spacer sleeve.
  • the longitudinal direction are to be understood with the center axis of the spacer sleeve and the transmission shaft section parallel directions.
  • the longitudinal direction is rectified with the (rotation) or symmetry axis.
  • the channel-shaped recesses of the spacer sleeve with a substantially cylindrical cross-section are bounded radially inwardly or outwardly by the sheet metal of the sleeve.
  • the spacer sleeve and the transmission shaft portion include channels therebetween, through the lubricating oil z. B. from the rolling bearing of a loose wheel for rolling bearing a held by means of the spacer sleeve at a distance further idler gear can be passed.
  • An embodiment of the invention provides that the circumferentially closed portion, the sleeve shaft, has at least one radial opening.
  • the volume and thus the volume-dependent weight of spacers with a relatively thick wall can be reduced by the proportion of the material which is removed from the spacer sleeve in order to create the opening.
  • a plurality of circumferentially distributed over the section openings are provided.
  • the spacer sleeve has the contour of the wave-shaped, axial end over its entire axial length. In one embodiment, it is provided that, viewed in longitudinal section, the distance between the regions intended by the gear shaft at the end approaches, if necessary, continuously approaches the gear shaft after a short, constant distance.
  • the spacer sleeve In a second axial shaft portion, the spacer sleeve has an annular contour which corresponds to the outer contour of the transmission shaft and therefore is generally circular cylindrical. In this second axial shaft portion, the spacer sleeve can be fixed non-positively on the transmission shaft.
  • a high strength of the spacer sleeve is achieved when the material of the spacer sleeve is made of steel.
  • a cold forming technically produced, in particular drawn spacer sleeve and a transmission unit with such a spacer sleeve is proposed.
  • the sheet material is also available in its full wall thickness, as it is not stretched there due to the lack of transition there.
  • a support on gear shaft close arranged components is possible due to the attributable bending radius, since no high bending radius is built.
  • corrugated shaft end By way of a corrugated shaft end, whose outer radius thus varies over the circumference, support can nevertheless be achieved at a plurality of components arranged concentrically around the transmission shaft and axially adjacent to the spacer sleeve.
  • the corrugated shaft end stiffens the spacer sleeve additionally.
  • FIG. 1 shows a non-inventive embodiment of an arrangement with two gears in the form of loose wheels, which are spaced by a spacer sleeve, in a longitudinal section along the axis of rotation of a gear shaft,
  • FIG. 2 shows the cross section of the spacer sleeve from FIG. 1, cut along the line II-II,
  • FIG. 3 shows a longitudinal section through the entire spacer sleeve according to FIG. 1 along the line III-III;
  • FIG. 4 shows an embodiment according to the invention of an arrangement with two gears in the form of loose wheels, which are spaced apart by a spacer sleeve, in a longitudinal section along the axis of rotation of a transmission shaft;
  • FIG. 5 shows the cross section of the spacer sleeve according to FIG. 4 in a front view
  • FIG. 6 shows a longitudinal section through the spacer sleeve according to FIG. 4,
  • Figure 7 is an end view of a schematically illustrated, further spacer sleeve on a gear shaft
  • Figure 8 is a longitudinal section of the spacer sleeve with a wave-shaped
  • Figure 9 is a longitudinal section of a spacer sleeve with two wave-shaped Ends and
  • Figure 10 is a longitudinal section of a spacer sleeve with a flat end and a wave-shaped end.
  • Figure 1 shows a spacer sleeve 1, which surrounds a portion of a transmission shaft 2.
  • a first gear 3 and a further gear element 8 in the form of a second gear 4 are arranged at an axial distance A to each other on the transmission shaft 2.
  • the gears 3 and 4 are rotatably mounted according to their function as idler gears with rolling bearings 15 and 16 on the transmission shaft 2.
  • the spacer sleeve 1 is shown in Figures 2 and 3 as a single part. It is made as a sleeve-shaped drawn part made of sheet metal and has a radial collar 7.
  • the construction, the function and mode of operation of the spacer sleeves 1 shown in FIGS. 5, 6 and 8 to 10 essentially correspond to the spacer sleeve 1 from FIGS. 2 and 3.
  • the second gear 4 is axially supported on the collar 7.
  • the first gear 3 runs on the first end face 23 axially.
  • the spacer sleeve 1 bridges the bridging dimension B, which is half the difference between the outside diameter D a , the outside contour 10 and the inside diameter D, of the inner envelope contour 9.
  • the sheet thicknesses Si and S 2 of the sheet metal from which the spacer sleeve 1 is made are smaller than the bridge dimension B between the cylindrical inner envelope contour 9 and the cylindrical outer envelope contour 10.
  • the diameter D 1, the inner envelope contour 9 can be larger, equal or smaller be as the transmission shaft diameter D w of the portion of the transmission shaft 2, on which the spacer sleeve 1 is arranged - depending on whether a play-seat, a transition fit or a press fit between the spacer sleeve 1 and the transmission shaft 2 are provided.
  • the sheet metal of the spacer sleeve 1 is thinner than the bridge dimension B with the sheet thicknesses Si and S 2 and is radially bridged by form elements in the form of radial groove-shaped depressions 12.
  • the depressions 12 are introduced during the forming process and run longitudinally rectilinearly and parallel to the rotational axis 13.
  • the wall sections 14 which delimit the depressions 12 circumferentially or tangentially thus bridge the bridging dimension B between inner envelope contour 9 and outer envelope contour 10.
  • the depressions 12 are radially outwardly bounded to the outer envelope contour 10 with the wall portions 17 so that the recesses 12 may form axial lubrication channels between the gears 3 and 4.
  • the wall thickness depends on load, material and degree of deformation.
  • the sheet thickness S 2 of the spacer sleeve 1 is thinner in the region of the groove-shaped depressions 12 than the sheet thickness Si of the circumferentially adjacent surface portions 11. Due to the design and dimension of the sections of the sheet with which the channel-shaped recesses 12 are axially, circumferentially, tangentially or radially limited, if necessary, a radial height is designed which corresponds to a multiple of the thickness Si of the sheet.
  • Figure 4 shows a gear unit 20, in which a spacer sleeve 1 is formed so that it at its first end face 23, which is directed toward the first gear 3, a wave-shaped course and at its second end face 24 as in the prior art Collar 7 has.
  • the spacer sleeve 1 is supported on a shaft shoulder 19.
  • the spacer sleeve 1 has wave-shaped alternating radial sections 21, 22, which abut against the transmission shaft 2 as first radial sections 21 and are intended as second radial sections 22 of the transmission shaft 2.
  • the second radial sections 22 form with the transmission shaft 2 cavities 26, which can be used for oil supply.
  • the spacer sleeve 1 is supported by its first radial sections 21 a transmission shaft fixed component, which is axially secured.
  • the transmission shaft fixed component is presently designed as a securing ring 5.
  • the getriebewel lenfeste component as another, at least axially fixed, manufactured separately from the transmission shaft 2 component or as a integrally connected to the transmission shaft 2 functional element such as a shaft shoulder may be formed.
  • the spacer sleeve 1 has a plurality of, in the case of Figure 5, three alternating first and second radial sections 21, 22.
  • the thin-walled spacer sleeve 1 intersects in the transition between these radial sections in a circumferential direction extending gap 6, which is formed between the locking ring 5 and the gear 3. This allows the oil to flow either directly or through the cavity 26 to the roller bearing 15.
  • the introduction of oil holes on the first end face 23 can be omitted.
  • the spacer sleeve 1 has at its first end face 23 and no bending radii, so that it can be supported with its entire material thickness of the first gear 3 and the securing ring 5.
  • the spacer sleeve 1 is therefore claimed here only on pressure and not on bending.
  • the cavities 26 formed by the alternating shaft sections are not formed in the embodiment according to Figures 5, 6 and 7-10 as over the entire length of the spacer sleeve 1 extending axial grooves, but taper in the direction of the second end face 24.
  • the spacer sleeve 1 points Thus, between the first end face 23 and the second end face 24 on an axial Komplementärabêt 27, in the region of the inner envelope contour 9 of the spacer sleeve 1 fully corresponds to the outer shell contour of the transmission shaft 2.
  • a press fit is well suited for fastening the spacer sleeve 1 on the transmission shaft. 2
  • FIGS. 8 to 10 show different variants of the spacer sleeve 1.
  • the spacer sleeves 1 that they at their first end face 23 each have a corrugated end with alternating first radial sections 21st and second radial portions 22 which are spaced differently from the transmission shaft 2.
  • the spacer sleeve 1 according to FIG. 8 has a collar 7.
  • the spacer sleeve 1 according to FIG. 9 has corrugated ends on both sides, and the spacer sleeve 1 according to FIG. 10 has a corrugated and a flat end, wherein the flat end lies completely against the transmission shaft 2.
  • first gear D a outer diameter second gear D, inner diameter

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gears, Cams (AREA)

Abstract

L'invention concerne un ensemble de transmission (20) comportant un arbre de transmission (2) pourvu d'une première roue dentée (3) et d'un autre élément de transmission (8). La première roue dentée (3) et l'autre élément de transmission (8) sont disposés sur l'arbre de transmission (2) ou au niveau de ce dernier. L'ensemble de transmission comporte également un manchon d'écartement (1), qui est disposé entre la première roue dentée (3) et l'élément de transmission (8) et qui s'appuie frontalement respectivement contre ces derniers. Le manchon d'écartement (1) comporte, au niveau de sa première face frontale (23) orientée en direction de la première roue dentée (3), un rayon variable sur toute la circonférence et s'appuie côté circonférence aussi bien sur la première roue dentée (3) que sur un élément solidaire de l'arbre de transmission.
PCT/DE2014/200233 2013-05-23 2014-05-23 Ensemble de transmission Ceased WO2014187459A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201310209579 DE102013209579B3 (de) 2013-05-23 2013-05-23 Getriebeeinheit
DE102013209579.1 2013-05-23

Publications (1)

Publication Number Publication Date
WO2014187459A1 true WO2014187459A1 (fr) 2014-11-27

Family

ID=51062598

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2014/200233 Ceased WO2014187459A1 (fr) 2013-05-23 2014-05-23 Ensemble de transmission

Country Status (2)

Country Link
DE (1) DE102013209579B3 (fr)
WO (1) WO2014187459A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018131090A1 (de) 2018-12-06 2020-06-10 Schaeffler Technologies AG & Co. KG Elastische Distanzhülse einer Getriebeeinheit
US12404922B2 (en) 2022-01-04 2025-09-02 Jing-Jin Electric Technologies Co., Ltd. Power shaft structure of electric drive assembly

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015206351B3 (de) * 2015-03-10 2016-09-01 Schaeffler Technologies AG & Co. KG Lageranordnung mit zwei Schrägwälzlagern und einer Ausgleichshülse
FR3078756B1 (fr) * 2018-03-09 2020-04-10 Renault S.A.S Agencement pour l’arret axial d’un pignon sur un arbre
DE102021122861A1 (de) 2021-09-03 2023-03-09 Kirchhoff Automotive Deutschland Gmbh Einheit, zum Verbauen in einem Kraftfahrzeug und zum Anschließen an eine Bauteilaufnahme eines Kraftfahrzeuges sowie Verfahren zum Herstellen einer solchen Einheit

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3807310A1 (de) 1987-03-17 1988-10-06 Volkswagen Ag Stufenwechselgetriebe
JPH11303947A (ja) 1998-04-17 1999-11-02 Honda Motor Co Ltd ギヤ機構
US7036391B2 (en) 2001-03-07 2006-05-02 Fuji Jukogyo Kabushiki Kaisha Differential unit
FR2897404A1 (fr) * 2006-02-16 2007-08-17 Renault Sas Dispositif d'arret axial d'un pignon fou de boite de vitesses et procede de montage d'un tel dispositif
WO2008074708A1 (fr) * 2006-12-16 2008-06-26 Schaeffler Kg Bague d'écartement et groupe modulaire avec bague d'écartement
DE102007059095A1 (de) 2007-12-07 2009-06-10 Schaeffler Kg Distanzring
KR20090091168A (ko) * 2006-12-16 2009-08-26 섀플러 카게 스페이서 링과, 스페이서 링을 포함하는 어셈블리

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2397905A (en) * 1944-08-07 1946-04-09 Int Harvester Co Thrust collar construction
AT243580B (de) * 1963-03-12 1965-11-25 Reich Maschf Gmbh Karl Befestigung von Zahnrädern kleinen Durchmessers am Ende einer Welle
US4485686A (en) * 1982-03-25 1984-12-04 Eaton Corporation Gear retainer

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3807310A1 (de) 1987-03-17 1988-10-06 Volkswagen Ag Stufenwechselgetriebe
JPH11303947A (ja) 1998-04-17 1999-11-02 Honda Motor Co Ltd ギヤ機構
US7036391B2 (en) 2001-03-07 2006-05-02 Fuji Jukogyo Kabushiki Kaisha Differential unit
FR2897404A1 (fr) * 2006-02-16 2007-08-17 Renault Sas Dispositif d'arret axial d'un pignon fou de boite de vitesses et procede de montage d'un tel dispositif
WO2008074708A1 (fr) * 2006-12-16 2008-06-26 Schaeffler Kg Bague d'écartement et groupe modulaire avec bague d'écartement
KR20090091168A (ko) * 2006-12-16 2009-08-26 섀플러 카게 스페이서 링과, 스페이서 링을 포함하는 어셈블리
DE102007059095A1 (de) 2007-12-07 2009-06-10 Schaeffler Kg Distanzring

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018131090A1 (de) 2018-12-06 2020-06-10 Schaeffler Technologies AG & Co. KG Elastische Distanzhülse einer Getriebeeinheit
US12404922B2 (en) 2022-01-04 2025-09-02 Jing-Jin Electric Technologies Co., Ltd. Power shaft structure of electric drive assembly

Also Published As

Publication number Publication date
DE102013209579B3 (de) 2014-10-23

Similar Documents

Publication Publication Date Title
DE3722127C2 (de) Haltering, insbesondere für Freilaufkupplung
DE102013011816B4 (de) Getriebe mit einem ersten und einem zweiten Gehäuseteil
EP2606248B1 (fr) Cage de type double peigne pour palier à rouleaux cylindriques à deux rangées, dotée d'un équilibrage des masses
EP2104790A1 (fr) Bague de synchronisation d'un dispositif de synchronisation
DE102020207154B4 (de) Elastomerverbundlager und Anordnung aus einem Kraftfahrzeugaufbau und einem Hilfsrahmen
EP1090233A1 (fr) Palier radial a plusieurs rangees
DE102013209579B3 (de) Getriebeeinheit
DE112009002345T5 (de) Verarbeitung von Videodaten in Geräten mit eingeschränkten Ressourcen
EP1704339B1 (fr) Chemin de roulement exterieur d'un roulement de roue et fixation axiale du roulement exterieur
DE10306926B4 (de) Axiallager
WO2011064062A1 (fr) Palier à roulement muni de saillies du type bosse appliquées sur la bague extérieure de palier
EP1568554B1 (fr) Manchon d'immobilisation pour un colonne de direction
DE102010007668B4 (de) Getriebeelement für ein Spannungswellengetriebe, Nockenwellenversteller sowie Lenkkrafthilfe
WO2015067262A2 (fr) Douille coulissante pour le montage de roues planétaires
EP1430232B1 (fr) Frein a disque destine notamment a un vehicule utilitaire
DE102008006627B4 (de) Differentialkorb aus Halbschalen und Verfahren zur Herstellung eines Differentialkorbs
EP1978275B1 (fr) Articulation, en particulier sur une plateforme pivotante entre un wagon avant et un wagon arrière d'un bus à plateforme pivotante
EP2547925A1 (fr) Coquille de coussinet lisse
EP1744069A1 (fr) Disposition de butée à roulement
DE102007027934A1 (de) Welle-Nabe-Baugruppe mit Spreizelement
DE112016000828T5 (de) Kegelrollenlager
DE102006021446A1 (de) Welle einer Wasserpumpe eines Verbrennungsmotors
WO2008074708A1 (fr) Bague d'écartement et groupe modulaire avec bague d'écartement
DE102012207528B3 (de) Wälzlager
DE102014203948A1 (de) Axiale Positionierung eines Sonnenrades in einem Leichtbaudifferenzial

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 14734732

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 14734732

Country of ref document: EP

Kind code of ref document: A1