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WO1990008272A1 - Raccord a bride resistant a la torsion - Google Patents

Raccord a bride resistant a la torsion Download PDF

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Publication number
WO1990008272A1
WO1990008272A1 PCT/EP1990/000089 EP9000089W WO9008272A1 WO 1990008272 A1 WO1990008272 A1 WO 1990008272A1 EP 9000089 W EP9000089 W EP 9000089W WO 9008272 A1 WO9008272 A1 WO 9008272A1
Authority
WO
WIPO (PCT)
Prior art keywords
flange
screws
fitting
axial
threaded
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/EP1990/000089
Other languages
German (de)
English (en)
Inventor
Wolf-Dieter Krumpholz
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.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
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 ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of WO1990008272A1 publication Critical patent/WO1990008272A1/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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/0018—Shaft assemblies for gearings
    • F16H57/0025—Shaft assemblies for gearings with gearing elements rigidly connected to a shaft, e.g. securing gears or pulleys by specially adapted splines, keys or methods
    • 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
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B19/00—Bolts without screw-thread; Pins, including deformable elements; Rivets
    • F16B19/02—Bolts or sleeves for positioning of machine parts, e.g. notched taper pins, fitting pins, sleeves, eccentric positioning 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/076—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end by clamping together two faces perpendicular to the axis of rotation, e.g. with bolted flanges
    • 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
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B35/00—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws
    • F16B35/04—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws with specially-shaped head or shaft in order to fix the bolt on or in an object
    • F16B35/041—Specially-shaped shafts
    • F16B35/048—Specially-shaped necks

Definitions

  • the invention relates to a non-rotatable flange connection according to the preamble of claim 1.
  • Such flange connections are often used in gearboxes, for. B. required for ring gear attachments in planetary gear.
  • DE-Cl 30 13 431 there is axial between the planet gear pin and the gear-side end face of the one
  • a flange brake serving as a ring gear carrier is also provided.
  • the flange designed in the example as a stub-like flange attachment is secured with the other flange designed as a ring gear carrier by means of dowel screws with threaded shank and normal screw head both in the direction of rotation and in the axial direction.
  • the threads of the fitting screws can also have a certain axial feed of the flange they guide z. B. to adjust a
  • the dowel screws engage in threaded holes in the front edge area of the stub-like flange attachment, which in this case serves as a housing tube,
  • TM bearing is also to be expanded.
  • cheap and highly resilient axial seals can be used for a connection of fluid channels (e.g. brake pressure lines) that may be provided in the sealing gap between the housing and ring gear carrier.
  • fluid channels e.g. brake pressure lines
  • the flange connection is also determined by the screw heads. In the example considered, they are still within the axial overlap by a brake cylinder. If, however, an extremely short overall length and a minimum distance between the ring gear carrier and the planet gear pin are to be achieved while leaving a brake, the heads of the thread-fitting screws are disruptive with this flange connection, because an enlarged axial gap between the ring gear carrier and the planet gear pin is necessary because of this. This axial gap creates various leverage effects that increase the strength of the components and also increase the bearing load. When used on steerable axles, the steering geometries deteriorate with increasing axial length. For this reason, the shortest possible distance from the center of the bearing or the ring gear flange to the free end of the gear is required, in particular in the case of wheel heads with reducing gears, so that the wheel head housing cover does not axially out of the
  • the object of the invention is to be seen in creating an axially short and permanently exactly centered, non-rotatable flange connection while avoiding multi-axis stress on the fitting screws.
  • Either normal machine screws are used as axial brackets in addition to the dowel screws on approximately the same bolt circle, or one flange is screwed onto an external thread of a pipe-like projection of the other flange like a threaded nut up to a fixed stop by means of an internal thread in its central bore.
  • the clamping connection can be relieved of axial forces by means of conical head fitting screws and conical sleeves and can only be used for torque support. Your fit is also no wear, e.g. B. by fretting corrosion, which leads to a deterioration of the centering or to the unwanted Relaxation could result.
  • With a central thread in or on the flange halves to be connected would be manufacture and
  • the conical sleeves are inserted directly into the cylindrical bores of the flange halves and slit lengthways. Thanks to its cylindrical contour, simple cylindrical bores can be provided.
  • the flange which is axially adjustably fastened with a thread connection separated from the anti-rotation lock, can also serve directly as a bearing adjusting ring for axial bearings rotating on the counter flange.
  • Fig. 1 shows the example of a cross section through the upper half of a simple wheel head reducer, the design of the separate threaded connection provided separately from the fitting screws for axial fastening by a central thread.
  • the axial length of the flange connection remains as short as the flanges themselves.
  • Fig. 2 shows a partial section of the arrangement of the fitting screws with conical head and conical sleeve and their use in threaded holes in a central threaded connection between the flange halves.
  • Fig. 3 shows the schematic arrangement of the holes placed in the middle of the threads on the end face of the downstream flange or housing tube and the upstream flange or ring gear carrier and an embodiment of a conical screw head with a longitudinally slotted cone sleeve.
  • Fig. 4 shows a flange connection, in which the centering or anti-rotation is also achieved by means of dowel screws with conical upper ends, but the further threaded connection
  • Fig. 5 shows the front view with the
  • Fig. 6 shows an example of a fitting screw designed as an expansion screw.
  • FIG. 7 shows the front view of the expansion screw
  • Fig. 8 shows a matching cone sleeve with a longitudinal slot.
  • Fig. 9 shows the front view of the cone sleeve.
  • the flange halves 1 and 10 to be connected to one another are axially fixed by a single central threaded connection 15, 16 and secured against rotation by cone-head fitting screws 21 which are inserted in aligned cylindrical fitting bores 21A with cone sleeves 25.
  • the flange halves 1 and 10 are in the present example housing tube and ring gear carrier of a wheel hub gear.
  • the housing tube which is generally held on the chassis in a rotationally fixed manner, surrounds a shaft 2 on the one flange half 1 as a tube-stub-like attachment, which shaft is provided with a sun gear 3 just in front of a gear-side end face of the housing tube.
  • This sun gear 3 meshes with one or more planet gears 4, which rotate on planet bolts 5 or planet gear bearings 6 supported thereon and by one each
  • Axial securing 8 at the free end of the planet pin 5 and by the housing cover 7 carrying the planet pin 5 are axially fixed.
  • a ring gear 9 is arranged radially outside the planet gears 4, the planet gear 4 also engaging in the internal toothing thereof.
  • the ring gear 9 is fastened axially and in the direction of rotation to the housing tube 1 by means of the second flange half 10 serving as a ring gear carrier. This supports the inner race of a bearing 11 placed on the housing tube of the first flange half 1 for a wheel hub 12, which with the
  • Housing cover 7 is connected.
  • the bearing 11 is protected by a hub seal 13 on a housing collar 14 on its side facing away from the transmission against oil loss or ingress of dirt.
  • the ring disk-shaped second flange 10 serving as a ring gear carrier has a
  • the second flange 10 used as a ring gear carrier has radial thrust faces 17 on the bearing side radially above the thread 15, 16, which in the end position against the inner ring of the gear-side bearing 11 and, in the case of accommodating lines in the housing tube of the first flange 1 and in the second as a ring gear carrier used flange 10 presses against one of the contact surfaces of the first flange 1 upstream axial seal 19.
  • This axial seal 19 allows a simple and reliable co-sealing for the transfer of a fluid channel 20 which can optionally be accommodated in both flange halves 1, 10, as described for. B. can be provided with integrated brake actuating cylinders when using second flange halves 10 used as a ring gear carrier.
  • the anti-rotation lock of the two flange halves 1 and 10 relative to one another is achieved by means of fitting screws 21 (not visible in FIG. 1) of any type which, for example, extends axially through the second flange half 10 into the contact surface 17 of the first flange half 1 on the circumference of the thread 15, 16 are screwed in.
  • this threaded connection 15, 16 is shown with a fitting screw 16 embedded therein in a side section.
  • the fitting screws 21 are included in the free end of the tubular stub-like projection of the first flange half 1 serving here as the housing tube.
  • the screw head 22 opposite its threaded shaft 23 consists of an outer cone 23A which widens towards the head end and which, by means of the threaded shaft 23, enters the corresponding blind hole in the wall cross section of the first Flange half 1 is used as a centering and anti-rotation device.
  • the outer cone area 22A here has a length which, when the screw 21 is in the end position, no longer protrudes beyond the front edge of the flange connection 1 or 10 on the gearbox side.
  • a hexagon socket is incorporated into the screw head 22 as the tool access profile 24.
  • the bore in the area of the threaded connection 15, 16 receives slotted cone sleeves 25, which have a somewhat greater length than the outer cone area 22A and taper somewhat more.
  • Screws 21 only the surface pressure resulting from the moment from the ring gear 9 to the screw head 22 and from this to the housing tube 1. Since this computes relatively small or a few screws as necessary, twice as much holes can easily be provided in a correspondingly narrow angular distribution as screws. It is then possible to gradually increase the setting torque for the bearing 11 by rotating the second flange 10 serving as a ring gear carrier by a half pitch angle Alpha and then an inner half of the borehole of the first flange part 1 with the next outer half of the borehole of the other flange part 10 Cover is brought.
  • the threaded connection 15, 16 or the type of fitting screws 21 does not require any additional space in the axial gap 26 between the second flange half 10 and the free end on the bearing side the planet pin 5, so that an extremely short gearbox is achieved. Thanks to the ability to compensate for tolerance errors, e.g. B. due to fretting corrosion, the ring gear and the ring gear carrier with the conical heads of the fitting screws 21 can be easily and reliably re-assembled as often as required, even with repeated installation and removal, with the most favorable setting of the bearing 11. It also reduces the risk of loosening the backlash-free ring gear flange connection, eg. B. due to frequent changes of direction.
  • Fine thread approach to axially secure the second flange half 10 and to provide an option for the bearing.
  • FIG. 4 shows a further alternative of such a rotationally fixed flange connection 1, 10, in which, however, the axial fastening does not take place via a single threaded connection 15, 16 machined into the flange halves 1, 10, but rather via a plurality of axial securing screws 21C designed as normal machine screws .
  • These are offset on the circumference of the fitting screws 21 in the second flange half 10 serving as ring gear carriers in through holes 21B with their heads 22 recessed axially flush with the outer surface and with a threaded shaft 23 in the inner collar of the first flange half 1 projecting here as a housing tube in corresponding axially parallel threaded holes 21D attached.
  • the thread of the axial securing screws 21B be chosen stronger than that for the fitting screws 21, so that with fewer axial retaining screws 21B there is space for several fitting screws 21.
  • the latter are provided with an expansion region 23C which is situated between the threaded shaft 23 and the outer cone region 23A, in order to be familiar with the mounting of the screws with prestress.
  • the outer cone region 23A ends here with an access profile 24 shaped as a small external hexagon, which, in a similar manner to the hexagon heads of the axial securing screws 21B, is flush with the outer surface of the flange 10 used as the ring gear carrier, in that the cylindrical fitting holes 21A extend far enough into the housing tube used flange 1 are inserted to insert an externally cylindrical conical sleeve 25 so that about half of it comes to rest in each of the two flanges 1, 10.
  • this conical sleeve 25 spreads tightly into the fitting bore 21A thanks to a longitudinal slot 25A and thereby prevents the occurrence of play or of eccentricities in the assembled one
  • Dowel screws 21 and the axial securing screws 21C are shown on the outer surface of the flange 10 serving as a ring gear carrier.
  • the flange 10 serving as a ring gear carrier.
  • only four axial screws 2IC are necessary, so that space for six fitting screws 21 lying approximately on the same bolt circle is gained.
  • the preferred fitting screw 21 is shown as an expansion screw, that is, between the threaded shaft 23 and an outer cone region 23A with approximately 1: 4 cone
  • the expansion region 23C is provided, the length of which corresponds at least approximately to that of the cone region 23A.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)
  • Retarders (AREA)

Abstract

Dans ce raccord à bride résistant à la torsion, la résistance torsionnelle et le centrage des deux moitiés du raccord à bride (1, 10) sont assurés selon un procédé connu, à l'aide de vis calibrées (21) dont les têtes (22) peuvent être dotées d'une région extérieurement conique (23A). Les vis calibrées (21) sont dans une large mesure libres de charges axiales, ces dernières étant supportées par un raccord fileté séparé (15, 16 et 21C, 21D, respectivement). Cette structure est particulièrement avantageuse pour les boîtes planétaires où il s'agit d'assurer une grande précision même avec des charges alternantes de couple et des ensembles de faibles dimensions. L'interstice axial (26) entre porte-couronne (10) et axe de satellite (5) est maintenu aussi petit que possible grâce au fait qu'on utilise des vis à douille (24). La bride extérieure (10) qui sert de porte-couronne est utilisée pour régler un palier (11). Selon une variante, un raccord fileté (15, 16) servant à la fixation axiale empêche cette bride de se dévisser grâce à des vis calibrées (21) dont les alésages filetés correspondants coupent à moitié à la fois le filetage femelle et le filetage mâle (15, 16). Grâce à des vis calibrées (21) dotées de têtes extérieurement coniques (23A) et de douilles (25) ou élargissements d'alésages coniques correspondants, on évite les erreurs de centrage et l'apparition, sur la durée, de jeux. Une autre variante permet une fixation axiale séparée grâce à des vis filetées simples (21C) agencées à l'intérieur de la bride (1) et dont les têtes sont noyées dans la bride posée (10), avec un jeu radial.
PCT/EP1990/000089 1989-01-21 1990-01-17 Raccord a bride resistant a la torsion Ceased WO1990008272A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP3901758.3 1989-01-21
DE3901758 1989-01-21

Publications (1)

Publication Number Publication Date
WO1990008272A1 true WO1990008272A1 (fr) 1990-07-26

Family

ID=6372536

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1990/000089 Ceased WO1990008272A1 (fr) 1989-01-21 1990-01-17 Raccord a bride resistant a la torsion

Country Status (4)

Country Link
EP (1) EP0489007A1 (fr)
JP (1) JPH04503241A (fr)
DE (1) DE4001106A1 (fr)
WO (1) WO1990008272A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116252171A (zh) * 2023-05-15 2023-06-13 江苏佳杰特种螺钉有限公司 一种法兰的紧固装置

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4425961A1 (de) * 1993-07-23 1995-02-02 Ims Morat Soehne Gmbh Planetengetriebe und dessen Verwendung
IT1321232B1 (it) * 2000-06-27 2003-12-31 Tecnoingranaggi Riduttori S N Riduttore epicicloidale .
DE10144803B4 (de) * 2001-09-12 2006-03-09 Zf Friedrichshafen Ag Planetengetriebe
US8112862B2 (en) * 2009-12-18 2012-02-14 General Electric Company Methods of assembling rotors having non-complementary flange openings
DE102015215173A1 (de) * 2015-08-07 2017-02-09 Zf Friedrichshafen Ag Hohlrad mit Zentrierstift
PT3938666T (pt) * 2019-03-15 2024-11-13 Acument Intellectual Properties Llc União aparafusada utilizando manga deformável com ranhuras longitudinais
DE102024208952B3 (de) * 2024-09-19 2025-11-20 Zf Friedrichshafen Ag Angetriebene Achse, Arbeitsmaschine und Verfahren zum Herstellen einer Verbindung eines Hohlrads eines Radkopfs mit einem Achskörper einer Achse

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR940797A (fr) * 1947-02-10 1948-12-22 Dispositif d'entraînement de pièces mécaniques
US3328058A (en) * 1964-06-29 1967-06-27 T J Gundlach Company Shaft coupling
GB1076529A (en) * 1965-12-03 1967-07-19 Durabla Mfg Company Threaded connection in a fluid control valve and method of assembling same
US3603626A (en) * 1969-01-27 1971-09-07 Standard Pressed Steel Co High-strength joint and fastener assembly therefor
DE3013431A1 (de) * 1980-04-05 1981-11-26 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Radkopf fuer triebraeder von fahrzeugen
EP0040832A1 (fr) * 1980-05-28 1981-12-02 ALSTHOM-ATLANTIQUE Société anonyme dite: Dispositif d'accouplement entre deux rotors

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR940797A (fr) * 1947-02-10 1948-12-22 Dispositif d'entraînement de pièces mécaniques
US3328058A (en) * 1964-06-29 1967-06-27 T J Gundlach Company Shaft coupling
GB1076529A (en) * 1965-12-03 1967-07-19 Durabla Mfg Company Threaded connection in a fluid control valve and method of assembling same
US3603626A (en) * 1969-01-27 1971-09-07 Standard Pressed Steel Co High-strength joint and fastener assembly therefor
DE3013431A1 (de) * 1980-04-05 1981-11-26 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Radkopf fuer triebraeder von fahrzeugen
EP0040832A1 (fr) * 1980-05-28 1981-12-02 ALSTHOM-ATLANTIQUE Société anonyme dite: Dispositif d'accouplement entre deux rotors

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116252171A (zh) * 2023-05-15 2023-06-13 江苏佳杰特种螺钉有限公司 一种法兰的紧固装置
CN116252171B (zh) * 2023-05-15 2023-07-18 江苏佳杰特种螺钉有限公司 一种法兰的紧固装置

Also Published As

Publication number Publication date
DE4001106A1 (de) 1990-07-26
JPH04503241A (ja) 1992-06-11
EP0489007A1 (fr) 1992-06-10

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