WO1991007601A1 - Croisillon pour cardan - Google Patents

Croisillon pour cardan Download PDF

Info

Publication number
WO1991007601A1
WO1991007601A1 PCT/SE1990/000711 SE9000711W WO9107601A1 WO 1991007601 A1 WO1991007601 A1 WO 1991007601A1 SE 9000711 W SE9000711 W SE 9000711W WO 9107601 A1 WO9107601 A1 WO 9107601A1
Authority
WO
WIPO (PCT)
Prior art keywords
cross
plug
recess
length
arms
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/SE1990/000711
Other languages
English (en)
Inventor
Jari Hyvärinen
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.)
Saab AB
Original Assignee
Saab Scania AB
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 Saab Scania AB filed Critical Saab Scania AB
Priority to BR909007825A priority Critical patent/BR9007825A/pt
Publication of WO1991007601A1 publication Critical patent/WO1991007601A1/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
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • F16C41/02—Arrangements for equalising the load on a plurality of bearings or their elements
    • 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
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/26—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected
    • F16D3/38—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another
    • F16D3/40—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another with intermediate member provided with two pairs of outwardly-directed trunnions on intersecting axes
    • F16D3/41—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another with intermediate member provided with two pairs of outwardly-directed trunnions on intersecting axes with ball or roller 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/41—Couplings

Definitions

  • the present invention relates to a cross for a universal joint, in which each of the arms of the cross has at its outer end an external cylindrical bearing surface and, arranged coaxially with this, a recess which opens into the end of the arm.
  • Universal joints are used in transmissions in orderto transfer torque, for example in a universal driving shaft for a lorry.
  • the bearings usually roller bearings, in which the ends of the arms of the cross forming part of the universal joint rest, are exposed to high stresses and wear relatively quickly.
  • the most common form of damage forthe bearing boxes is constituted by surface fatigue damage, so-called pitting, on the axially outer end of the normally cylindrical bearing boxes. The loading on the bearing boxes is therefore obviously greatest at this axially outer end.
  • Crosses are in this connection often solid, but it is also the case that they are provided with different types of holes and channels in the arms for different purposes.
  • one type of cross for example according to SE-C-344994 or US- C-3 858413, there are axial lubricant channels forthe purpose of supplying lubricant to the bearings via the ends of the arms.
  • These lubricant channels have in this connection a diameter which does not affect the rigidity of the ends of the arms to any significant extent in comparison with solid crosses. The bearing life is therefore equally problematic as in the case of solid crosses, as described above.
  • the arm ends of the cross are provided with recesses, into which rubber buffers are introduced in orderto prevent play in the axial direction of the arms.
  • This type of cross is, however, usually intended for relatively small loads and the bearings are thus not exposed to any major loads.
  • these crosses also have a rigidity which is essentially identical to the rigidity of a solid cross.
  • the aim of the invention is to improve existing types of cross in order thus to achieve an increased life of the bearings in which the ends of the arms of the cross are intended to rest.
  • the recess can be dimensioned with a diameter of such a size that there is achieved, in relation to a solid cross, a change in the fiexural rigidity of the arms, which leads to a better load distribution in the bearings and thus an increased bearing life.
  • the recess can be wider in its outer part which is intended forthe plug, as a result of which an annular surface is formed, against which the plug bears in the axial direction.
  • each of the arms there can be in each of the arms an axial lubricant channel, the plug having an axial hole which is connected, via the recess, to the lubricant channel.
  • the bearings 3a and 3c are in this case each arranged in their holder 4a and 4c respectively, which are intended to be joined to one part, while the bearings 3b and 3d are intended to be joined to the other part.
  • the bearing 3a like the other bearings 3b-3d, is constituted by a roller bearing, in which a number of roller-shaped bearing boxes 5a are in contact on the one hand with an external cylindrical bearing surface 6a on the outer end of the arm 2a and on the other hand with an internal cylindrical surface on an outer race 7a. Between the arm 2a and the outer race 7a there is a packing 8a which has the function of protecting the bearing and retaining lubricant in the same.
  • a lubrication nipple 9 which is centrally mounted on the cross and from which lubricant can be supplied to the bearings via channels, for example the channel 10a, which are arranged centrally in the arms and which run out in the ends of the arms.
  • Size and design of the bearing boxes 5a can vary according to requirements. In the example shown here, there are two bearing boxes which are arranged axially one after another and which together extend along the whole length of the bearing surface 6a. Alternatively, it is possible to use instead a single bearing box, the length of which is identical to the length of the bearing surface 6a.
  • the special design, according to the invention, of the ends of the arms of the cross 1 can be seen from Fig. 3, in which the end of the arm 2a is shown.
  • a cylindrical recess 11a opens into the free end of the arm 2a and is connected to the channel 10a.
  • the purpose of the recess 11a is to bring about a deliberate reduction of the rigidity of the arm 2a of the cross 1 and thus increase its elasticity. This reduction of the rigidity is of such a size that it can generally be considered to result in the arm 2a receiving an abnormally great elasticity.
  • the recess 11 a has a length I and a diameter d.
  • the recess 11 a In its outer part, the recess 11 a has a widened part 12a which has a length I' and a diameter d' which is greater than the diameter d. In the widened part 12a of the recess 11a, there is pressed-in a reinforcing plug 13a, in which there is a central continuous hole 14a.
  • the race 6a has a length L and a diameter D.
  • annular surface 15-a against which the plug 13a bears.
  • the length I of the recess 11a is preferably essentially identical to the length L of the race 6a but can also be greater than the length L.
  • the length I' of the plug 13a expediently amounts to at most half of the length L of the bearing surface 6a, while the diameter d' expediently amounts to at least half of the diameter D of the bearing surface 6a.
  • the plug 13a is expediently mounted in the widened part 12a of the recess 11a by means of a drive fit and thus reinforces the outside wall 16a of the arm 2a. It is in this connection important that the fit between plug and recess is suitably firm, since the end of the arm becomes too weak if the fit is too loose, but has undesirable internal stresses if the fit is too tight. A drive fit or light drive fit has proved to be most advantageous in the tests which have been carried out. The plug thus partially compensates the earlier deliberate reduction of the rigidity of the arm of the cross and causes the end of the arm to be reinforced while the race around the remaining part of the recess continues to be elastic.
  • Mounting the plug 13a can advantageously be carried out relatively early in the manufacture of the cross after the recess has been bored, and, by means of expedient design of the hole 14a, the plug can subsequently be used for clamping the cross during continued working. After mounting the plug, the end surface of the arm can further be ground and hardening can take place.
  • Tests with an embodiment according to the invention have resulted in more than a doubling of the bearing life compared with that in the case of a conventional embodiment.
  • the hole 14a in the plug 13a is utilised, as has been made clear, both for clamping of the cross and for supplying lubricant to the bearing. It is of course also possible to make the cross without channels for lubricant and to dispense with the possibility of being able to clamp the cross via the plug.
  • the plug 13a can then be made solid, but it continues to be essential that the recess 11a is sufficiently great in orderto impartto the end of the arm the desired elasticity.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • General Details Of Gearings (AREA)
  • Support Of The Bearing (AREA)

Abstract

Un croisillon (1) destiné à un cardan comporte des évidements axiaux (11a) situés dans les extrémités des bras (2a). Dans la partie extérieure de chacun de ces évidements (11a), on fait entrer par pression une cheville de renforcement (13a). Grâce a ces moyens, chaque bras est doté d'une élasticité modifiée permettant d'obtenir une charge plus uniforme sur le support avec lequel le bras est destiné à agir mutuellement. Cet agencement permet de prolonger la durée de vie du support.
PCT/SE1990/000711 1989-11-09 1990-11-05 Croisillon pour cardan Ceased WO1991007601A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
BR909007825A BR9007825A (pt) 1989-11-09 1990-11-05 Cruz para uma junta universal

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE8903751-9 1989-11-09
SE8903751A SE463832B (sv) 1989-11-09 1989-11-09 Knutkors till kardanknut

Publications (1)

Publication Number Publication Date
WO1991007601A1 true WO1991007601A1 (fr) 1991-05-30

Family

ID=20377423

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE1990/000711 Ceased WO1991007601A1 (fr) 1989-11-09 1990-11-05 Croisillon pour cardan

Country Status (4)

Country Link
EP (1) EP0500676A1 (fr)
BR (1) BR9007825A (fr)
SE (1) SE463832B (fr)
WO (1) WO1991007601A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3651663A (en) * 1969-08-18 1972-03-28 Lemfoerder Metallwaren Ag Universal joint construction
US3858413A (en) * 1973-05-02 1975-01-07 Jury Mitrofanovich Nemtsov Universal joint
DE2933505C2 (de) * 1979-08-18 1983-11-10 Uni-Cardan Ag, 5200 Siegburg Kreuzgelenk
SE432294B (sv) * 1976-05-13 1984-03-26 Rockwell International Corp Universalledanordning

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3651663A (en) * 1969-08-18 1972-03-28 Lemfoerder Metallwaren Ag Universal joint construction
US3858413A (en) * 1973-05-02 1975-01-07 Jury Mitrofanovich Nemtsov Universal joint
SE432294B (sv) * 1976-05-13 1984-03-26 Rockwell International Corp Universalledanordning
DE2933505C2 (de) * 1979-08-18 1983-11-10 Uni-Cardan Ag, 5200 Siegburg Kreuzgelenk

Also Published As

Publication number Publication date
SE463832B (sv) 1991-01-28
EP0500676A1 (fr) 1992-09-02
SE8903751D0 (sv) 1989-11-09
BR9007825A (pt) 1992-09-08

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