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WO2018149473A1 - Articulation tournante pouvant être intégrée - Google Patents

Articulation tournante pouvant être intégrée Download PDF

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Publication number
WO2018149473A1
WO2018149473A1 PCT/EP2017/053235 EP2017053235W WO2018149473A1 WO 2018149473 A1 WO2018149473 A1 WO 2018149473A1 EP 2017053235 W EP2017053235 W EP 2017053235W WO 2018149473 A1 WO2018149473 A1 WO 2018149473A1
Authority
WO
WIPO (PCT)
Prior art keywords
joint
drive member
power
drive
side facing
Prior art date
Application number
PCT/EP2017/053235
Other languages
German (de)
English (en)
Inventor
Orkan Eryilmaz
Jan Haupt
Wolfgang Hildebrandt
Thomas Weckerling
Original Assignee
Gkn Driveline Automotive Ltd.
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 Gkn Driveline Automotive Ltd. filed Critical Gkn Driveline Automotive Ltd.
Priority to DE112017007054.6T priority Critical patent/DE112017007054A5/de
Priority to PCT/EP2017/053235 priority patent/WO2018149473A1/fr
Publication of WO2018149473A1 publication Critical patent/WO2018149473A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/22—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or type of main drive shafting, e.g. cardan shaft
    • B60K17/24—Arrangements of mountings for shafting
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B35/00—Axle units; Parts thereof ; Arrangements for lubrication of axles
    • B60B35/12—Torque-transmitting axles
    • B60B35/121—Power-transmission from drive shaft to hub
    • B60B35/127—Power-transmission from drive shaft to hub using universal joints
    • B60B35/128—Power-transmission from drive shaft to hub using universal joints of the homokinetic or constant velocity type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B35/00—Axle units; Parts thereof ; Arrangements for lubrication of axles
    • B60B35/12—Torque-transmitting axles
    • B60B35/18—Arrangement of bearings
    • 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
    • F16C11/00—Pivots; Pivotal connections
    • F16C11/04—Pivotal connections
    • F16C11/06—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/10—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for axial load mainly
    • 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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/581—Raceways; Race rings integral with other parts, e.g. with housings or machine elements such as shafts or gear wheels
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B2380/00—Bearings
    • B60B2380/10—Type
    • 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
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors
    • 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
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/06—Drive shafts
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F16D2021/0692—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric with two clutches arranged axially without radial overlap

Definitions

  • the invention relates to a swivel joint that can be integrated, in particular, into an axle drive housing of an axle drive unit for transmitting drive power to a power take-off such as the drive wheel of a motor vehicle and an axle drive unit of a motor vehicle, in particular a passenger car (PKW), with such a swivel joint.
  • a power take-off such as the drive wheel of a motor vehicle and an axle drive unit of a motor vehicle, in particular a passenger car (PKW)
  • PKW passenger car
  • the rotary joint is preferably formed as a constant velocity joint and has an outer joint drive member, in which the power entry takes place and are arranged within the power transmission members for transmitting the drive power to an inner Gelenkabtriebsglied, which is in particular to be connected to a leading to a drive wheel half-wave to the drive power to be transmitted via the propeller shaft to a power take-off, in particular a drive wheel of a motor vehicle.
  • the axle drive unit in which the rotary joint is preferably used, at least one coupling unit with clutch drive members, which are non-rotatably connected to a clutch drive member carrier, and provided with Kupplungsabtriebsgliedern which are rotatably connected to a clutch outputting member carrier.
  • the joint drive member of the rotary joint is designed as Kupplungsabretesgliedani the coupling unit.
  • the axle drive unit has an axle drive housing.
  • the coupling unit of the axle drive unit is preferably a friction clutch unit, the clutch drive members are drive disks and the clutch output members are output disks of a disk friction clutch.
  • friction clutch unit verse-
  • These final drive units are used in particular as differential-free, clutch-controlled transverse compensation units, in which the drive power is transmitted to the drive wheels via the individually controllable friction clutches by means of two side shafts.
  • the clutch may be in other applications, but also a positive-acting coupling.
  • axle drive unit which is also provided with a multi-disc clutch, even if it is directed to the rotary joint per se and is not restricted to an axle drive unit with such a rotary joint.
  • the invention is not limited to a hinge provided for such a final drive unit.
  • Achsantriebsakuen of motor vehicles with friction clutches are known from the prior art, in which also constant velocity joints are used.
  • the patent document EP 1 992 843 B1 describes a drive force transmission device which forms an interface between a propeller shaft and an axle with laterally arranged clutches and transmits the drive power with a closed friction clutch from an outer disk carrier to an inner disk carrier toothed with a joint half shaft.
  • a clutch unit forgglingachsmodule with a friction clutch unit is known from this document having a drivable housing and a driven hub and wherein the hub of the friction clutch unit receives the outer joint part of a constant velocity joint.
  • the axle drives described in these documents are highly complex and have a multiplicity of inter-engaging and difficult-to-support components.
  • the object of the invention to provide a rotary joint of the type mentioned, which allows a low cost, a compact design, minimizing the structural complexity and efficient operation of a final drive unit with such a hinge.
  • the object of the invention is also to provide an axle drive unit with such a hinge, with which these advantages are effectively implemented.
  • an axial bearing surface is arranged on the joint drive member on the side facing the power pickup when it is installed as intended.
  • a joint part separate from the joint drive element is mounted on the joint drive member on the side facing the power take-off side when mounted as intended, on whose side facing the power take-off side an axial bearing surface is arranged.
  • the necessary axial bearing of the rotary joint can be supported directly against the joint drive member.
  • the swivel joint can thus be placed in a space-saving manner within an axle drive housing and can be axially supported within the axle drive housing, preferably directly against the axle drive housing.
  • the arrangement and mounting of the rotary joint within the axle drive housing makes it possible in particular by reducing the axial width of a compact design of the final drive unit.
  • the design of the joint drive member eliminates the need for a clutch transmission member carrier, in particular as an output disk carrier of a multi-disk carrier.
  • the rotary joint with the arranged on the joint drive member axial bearing surface allows an optimized interface within the drive train, in particular between the clutch and the propeller shaft at the same time compact and simplified design by the swivel can be positioned within the clutch pack and the Kupplungsabtriebsglieder are directly connected to the joint drive member.
  • the axial bearing of the clutch output and the joint drive coincides.
  • thrust bearing surface is to be understood in such a way that this thrust bearing surface either directly forms a rolling body rolling surface, so that rolling elements of the thrust bearing roll directly on the surface of the joint drive member or on the separate cap member, or that the thrust bearing surface provided only for receiving and supporting a bearing ring is.
  • thrust bearing surface is also not limited to understand that it must be a purely axially loaded bearing surface to support an exclusively axial load. Rather, the thrust bearing surface can also be aligned such that the bearing is able to support a radial load in addition to an axial load, so it is a combined axial and radial bearings.
  • a tapered outer, the power consumer facing cap portion is provided on the joint drive member, on which a sealing region is formed, which is opposite to an outer Effective diameter of the power transmission members of the rotary joint is reduced in diameter and over which the rotary joint is sealed against the final drive housing.
  • the advantage of this aspect of the invention is an improved sealing capability of, for example, a final drive housing while allowing for a compact design.
  • the joint drive member also on the side facing away from the power consumer (the wheel side facing away) on a thrust bearing surface with which the joint drive member against the Kupplungsantriebsgliedong, so in a Reiblamellenkupplung against the drive plate carrier, is axially mounted.
  • the storage is particularly advantageously carried out via at least one axial rolling bearing or a combined axial and radial rolling bearing.
  • a bearing is preferably used via an axial rolling bearing or a combined axial and radial rolling bearing, in particular via a ball bearing which also acts at least axially.
  • the joint drive member is preferably axially mounted on the side facing the power take-off side (the wheel-facing side) within the final drive housing directly against the final drive housing or combined axial and radial bearings.
  • a cap portion designed in one piece with this can be provided on the joint drive member.
  • the joint drive member on the side facing away from the power consumer side has an insertion. It is then preferably provided a closure cap which is a separate component from the joint drive member and which closes the introduction opening provided on the side facing away from the power pickup (the side facing away from the wheel) of the joint drive member and thus seals the rotary joint with respect to the final drive housing.
  • the cap portion provided on the side facing the power take-off side is formed by a cap part separate from the joint drive element, in particular a sheet-metal shaped part, this offers the particular advantage of making the cap part geometrically more flexible and largely independent of the material and the other constructional elements. and manufacture specifications of the joint drive member finished.
  • the joint drive member may have an insertion opening, in particular when a power take-off side (wheel-side) and separate from the joint drive member cap portion on the side facing the power consumer (the wheel facing) side.
  • the joint drive member may then be formed integrally closed on the side facing away from the wheel.
  • the joint drive member has on the side facing away from the power take-off side (the side facing away from the wheel) an axially outwardly extending bearing journal, wherein the outer diameter of the journal is smaller than the outer diameter of the joint drive member, and wherein an axial bearing of the joint drive member between the facing surfaces of the joint drive member and the drive disc carrier takes place.
  • a radial bearing of the joint drive member is then preferably between the bearing pin and the drive plate carrier. In this way, the pivot can be stored on a small diameter, which in turn reduces the bearing losses.
  • the thrust bearing surface of the thrust bearings or combined axial and radial bearings over which the rotary joint is mounted axially or combined axially and radially, directly on the joint drive member, in particular on the cap portion, or on the joint drive member separate cap member is formed.
  • the thrust bearing surface is to be understood as an area with which the rolling elements of the thrust bearing are in direct contact or on which they roll immediately.
  • the surface of the joint drive member or that of the cap member thus acts directly as a bearing surface in this case.
  • a thrust bearing member or the cap member separate Axiallagerring is placed on the thrust bearing surface. The latter is particularly suitable if the material properties of the thrust bearing surface do not appear suitable as a running surface.
  • the bearing surface of the thrust bearing is oriented predominantly to exclusively parallel to the axis of rotation of the joint drive member, so that the thrust bearing ensures a substantially aligned axially parallel to the rotational axis, axial load direction. But it can also be easily inclined to the rotation axis and, for example, frusto-conical or oblique, so that the thrust bearing is able to absorb some radial bearing forces to a part.
  • the thrust bearing surface can therefore be formed in particular on the type of bearing surface of a both axially and radially resilient bearing, in particular a deep groove ball bearing, an angular contact ball bearing, a four-point bearing or a tapered roller bearing.
  • the axial bearing surface is thereby preferably frontally on the side facing the power consumer side of the joint drive member on this or on the separate from the joint drive member cap part, which is placed on the joint drive member arranged.
  • the thrust bearing surface preferably has an effective bearing diameter D3 (mean diameter of the bearing race on which the rolling elements roll), which is greater than the effective outer diameter D1 of the power transmission members.
  • An intended for sealing the interior of the rotary joint Gelenkschutzbalg may be formed such that it engages radially in the inside of the cap portion.
  • the cap portion on the power user sent side (the wheel-facing side) circumferentially bent inwardly to engage around the Gelenkschutzbalg at an outer circumferential edge region.
  • the Gelenkschutzbalg course, be slipped radially outward on the cap portion.
  • the cap member which is separate from the joint drive member, engages with its side facing away from the power take-off (the side facing away from the wheel) the side facing the power pickup (the wheel-facing side) of the joint drive member.
  • the cap part facing toward the joint drive member it is particularly preferable to provide an inwardly or outwardly preferably revolving detent member which engages in a positive locking manner on the joint drive member in a corresponding and preferably also circumferential detent member provided on the joint drive member.
  • the cap member and the joint drive member may also be non-positively connected.
  • the rotary joint can be oil lubricated, wherein the lubrication of the rotary joint in particular via its own oil circuit or alternatively via an integrated in the Achsantriebsö oil circuit can be done, which is provided for lubrication or cooling other Achsantriebsöskomponenten. It is also conceivable one Dip lubrication of the swivel joint in oil.
  • An oil lubrication has the advantage over a grease lubrication of the swivel joint, that a sealing of the swivel joint with respect to the friction clutch space is not absolutely necessary.
  • FIG. 1 shows an axle drive unit for a motor vehicle with a rotary joint and a friction clutch unit in a first embodiment
  • FIG. 2 shows an axle drive unit for a motor vehicle with a rotary joint and a friction clutch unit in a second embodiment
  • FIG 3 shows an axle drive unit for a motor vehicle with a rotary joint and a friction clutch unit in a third embodiment.
  • FIG. 1 shows a section of an axle drive unit 1 for a motor vehicle. Via a friction clutch unit 2, the drive power is transmitted as required via a propeller shaft 22 to a drive wheel connected thereto.
  • the propeller shaft leading to the drive wheel of the vehicle forms, in relation to a swivel joint 7, a power take-off for the drive power transmitted via the swivel joint 7.
  • the rotary joint 7 is designed as a constant velocity joint.
  • the friction clutch unit 2 is essentially formed by an outer disk carrier 4 forming the clutch drive member carrier and an inner disk carrier 6 forming the Kupplungsabtriebsgliedong and by outer disks 3 and inner disks 5.
  • the outer disk 3 as a clutch drive members against rotation on the outer disk carrier 4
  • the inner disks 5 as Kupplungsabtriebsglieder rotatably on the inner disk carrier 6 arranged.
  • the rotary joint 7 has an outer joint part acting as a joint drive member 8, an inner joint part acting as a joint driven member 10, and power transmission members in the form of balls 9 arranged therebetween.
  • the outer joint part functioning as joint drive member 8 is a largely cylindrical hollow body which is open towards the power consumers (on the wheel side) and at the same time forms the inner disk carrier 6 of the coupling unit 2.
  • the outer disk carrier 4 engages around the joint drive member 8 and merges into an intermediate shaft 24 on the side facing away from the power consumers (the side facing away from the wheel).
  • the propeller shaft 22 On the side facing the power consumers (the wheel-facing side) of the rotary joint 7, the propeller shaft 22 rotatably engages via a spline into the Gelenkabtriebsglied 10 of the rotary joint 7 and is axially locked to the inner joint part 10 by a locking ring.
  • the drive power is introduced into the outer disk carrier 4 coming from an intermediate shaft 24 and, with the friction clutch unit 2 closed, transmitted via the balls 9 acting as power transmission members to the articulated output member 10 and subsequently to the propeller shaft 22 via the inner disk carrier 6 formed by the joint drive member 8.
  • the inner disk carrier 6 acts with reference to the clutch as Kupplungsabtriebsgliedong or as output disk carrier, reference to the hinge 7, however, as a joint drive member 8, because with respect to the clutch of the inner disk carrier 6, taking into account the drive power flow is an output member, with respect to the hinge. 7 whereas a drive member.
  • Inner disk carrier 6 and joint drive member 8 are therefore formed by the same component.
  • the transmission interface, via which the drive power is introduced into the rotary joint in order to be forwarded by the latter to the power consumer, is, as shown in the figures, preferably formed by the radially outwardly facing and the power transmission members surrounding part surface of the joint drive member.
  • the pioneering from the pivot 7 end of the cap portion 1 6 is bent inwards.
  • the cap part 1 6 surrounds a Gelenkschutzbalg 20, via which the joint is sealed to the outside.
  • the cap member 1 6 and the joint bellows 20 thus seal the constant velocity joint 7 and thus the final drive housing to the outside.
  • the Gelenkschutzbalg 20 protrudes initially in the axial direction in the cap member 16 and then forms a reversal point at which the Gelenkschutzbalg coming from the power pickup side (in Figure 1 from the left) with radial extension reverses to a power pickup side facing radially outward Form peripheral edge region, which can then be encompassed by the cap portion 1 6 as shown.
  • the fold thus formed ensures that a tensile load and thus a possible slippage of the Gelenkschutzbalgs 20 is avoided by the cap member 16 at an angle of the propeller shaft 22 relative to the rotary joint 7.
  • the rotary joint 7 is roller-mounted within the axle drive housing 11, firstly with a first axial ball bearing 19 via the cap part 16 against the axle drive housing 11 and secondly with a second axial ball bearing 23 via the joint drive member 8 against the outer disk carrier 4.
  • the in 1 illustrated embodiment forms a umlau- fende, directly on the cap member 1 6 trained thrust bearing surface, which is designed in the manner of a deep groove ball bearing and therefore is able to absorb some radial forces, the bearing surface 18 of the ball bearing 19 directly from, so that the rolling elements roll directly on the cap part 1 6.
  • the rolling elements of the second thrust bearing 23, as shown in Figure 1 roll directly on a thrust bearing surface, which is formed by the surface of the joint drive member 8.
  • this bearing surface is preferably designed such that the bearing 23 on the side facing away from the power take-off side of the rotary joint 7 (radabgewandte side) can also absorb radial forces (eg deep groove ball bearings, angular contact ball bearings, tapered roller bearings, etc.).
  • the sealing of the axle drive housing is realized via a radial shaft sealing ring 28 between the axle drive housing 1 1 and the cap part 1 6, which forms an outwardly directed circumferential sealing surface 13.
  • the diameter of this preferably cylindrical sealing surface 13 is smaller than the outer effective diameter D1 of the balls 9 acting as power transmission elements.
  • FIG. 2 A further embodiment of the invention is shown in FIG. 2, which differs from FIG. 1 in particular by the configuration and the mounting of the constant velocity universal joint 7 within the final drive housing. Identical or similar components are identified below with the already introduced reference numerals. In addition, the differences with respect to the embodiment shown in FIG.
  • the outer joint part 8 which functions as a joint drive member, is again in the form of a half body which is open on one side and whose insertion opening 14 is provided on the side of the power take-off.
  • a bearing pin 17 On the side facing away from the power consumers side of the joint drive member 8 protrudes coaxially a bearing pin 17, the outer diameter of which for example corresponds approximately to the propeller shaft 22.
  • a bearing pin receptacle 25 is provided which receives the bearing pin 17.
  • a first thrust ball bearing 19 is again arranged.
  • a rolling bearing can be seen by a combined axial and radial bearing 26. This is preferably a needle bearing.
  • FIG. 3 shows a third variant embodiment.
  • the same or similar components from the previous figures are marked with the already introduced reference numerals. Again, mainly the differences from the previously described embodiments are emphasized.
  • the cap part which in the previously described embodiments formed the sectionally tapered cap portion 12, in the embodiment of Figure 3 is an integral part of the joint drive member 8 and thus formed ein serumein material with this.
  • an insertion opening 14 is provided on the side facing away from the power take-offs in order to allow assembly of the rotary joint 7 the joint drive member 8 is provided.
  • a closure cap 15 is pressed into the insertion opening 14.
  • the rotary joint 7 is arranged as in the other embodiments within the coupling unit 2 and is on the side facing the power consumers (the wheel facing side) within the Axialantriebsgephases 1 1 with an axial ball bearing 19 via the cap portion 12 against the axle drive housing 1 1 axially roller bearings.
  • a vertical, standing, annular surface area of the cap portion 12 may, as in the previously described embodiments, be designed so that it acts directly as a bearing surface 18, so that the rolling elements roll directly on the surface of the joint drive member.
  • the joint drive member 8 On the side facing away from the power consumers (the side facing away from the wheel), the joint drive member 8 is axially supported by means of a further Axialskylzlagers 27 against the Kupplungsantriebsgliedong (in Figure 3, the outer disk carrier 4). On this page is provided between the outer joint part 8 and outer disk carrier 4 in Figure 3 by way of example an axial needle bearing.
  • the average effective diameter of the power take-off side thrust bearing of the rotary joint 7 is greater than the outer effective diameter D1 of the power transmission members.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention vise à fournir une unité d'entraînement d'essieu (1) de véhicule automobile, laquelle permet une configuration compacte, une réduction au minimum de la complexité de construction et un fonctionnement efficace pour des coûts faibles. À cet effet, l'invention concerne une articulation tournante (7) servant à transmettre la puissance d'entraînement à une roue motrice, laquelle articulation tournante comprend un organe d'entraînement d'articulation (8) sur le côté tourné vers le consommateur de puissance (22) duquel est située une surface de palier axial pour un palier axial (19).
PCT/EP2017/053235 2017-02-14 2017-02-14 Articulation tournante pouvant être intégrée WO2018149473A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112017007054.6T DE112017007054A5 (de) 2017-02-14 2017-02-14 Integrierbares Drehgelenk
PCT/EP2017/053235 WO2018149473A1 (fr) 2017-02-14 2017-02-14 Articulation tournante pouvant être intégrée

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2017/053235 WO2018149473A1 (fr) 2017-02-14 2017-02-14 Articulation tournante pouvant être intégrée

Publications (1)

Publication Number Publication Date
WO2018149473A1 true WO2018149473A1 (fr) 2018-08-23

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2017/053235 WO2018149473A1 (fr) 2017-02-14 2017-02-14 Articulation tournante pouvant être intégrée

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DE (1) DE112017007054A5 (fr)
WO (1) WO2018149473A1 (fr)

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3427577A1 (de) * 1984-07-26 1986-02-06 Löhr & Bromkamp GmbH, 6050 Offenbach Ausgleichsgetriebe fuer kraftfahrzeuge
DE3729275A1 (de) * 1987-09-02 1989-03-16 Loehr & Bromkamp Gmbh Gelenkwellenanordnung
DE19731331A1 (de) * 1997-07-22 1998-03-12 Daimler Benz Ag Gelenkwelle
DE10312347A1 (de) * 2003-03-20 2004-10-07 Gkn Driveline International Gmbh Achsgetriebe mit integrierten Gleichlaufdrehgelenken
DE102005036789A1 (de) * 2005-08-02 2007-02-08 Gkn Driveline Deutschland Gmbh Antriebsanordnung an einem Zwischenlager
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