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WO1990007067A1 - Joint articule a rapport de vitesse constant - Google Patents

Joint articule a rapport de vitesse constant Download PDF

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Publication number
WO1990007067A1
WO1990007067A1 PCT/GB1989/001468 GB8901468W WO9007067A1 WO 1990007067 A1 WO1990007067 A1 WO 1990007067A1 GB 8901468 W GB8901468 W GB 8901468W WO 9007067 A1 WO9007067 A1 WO 9007067A1
Authority
WO
WIPO (PCT)
Prior art keywords
roller
arm
guide groove
joint
joint member
Prior art date
Application number
PCT/GB1989/001468
Other languages
English (en)
Inventor
Colin Francis Samuel Turner
Colin Arthur Bird
Original Assignee
Hardy Spicer Limited
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 Hardy Spicer Limited filed Critical Hardy Spicer Limited
Priority to KR1019900701791A priority Critical patent/KR910700417A/ko
Publication of WO1990007067A1 publication Critical patent/WO1990007067A1/fr

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
    • 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
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/202—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints
    • F16D3/205—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints the pins extending radially outwardly from the coupling part
    • F16D3/2055—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints the pins extending radially outwardly from the coupling part having three pins, i.e. true tripod 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
    • 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
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/202—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints
    • F16D3/205—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints the pins extending radially outwardly from the coupling part
    • 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
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/202—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints
    • F16D2003/2026—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints with trunnion rings, i.e. with tripod joints having rollers supported by a ring on the trunnion

Definitions

  • a joint of the type to which the invention relates comprises an outer joint member having a rotational axis and three guide grooves extending parallel to its rotational axis and equally circumferentially spaced thereabout; an inner joint member disposed inside the outer member, having a rotational axis and three arms equally spaced about this rotational axis extending radially into the guide grooves of the outer joint member; each arm carrying a roller which engages opposed side portions of the corresponding guide groove and is constrained to roll therealong; each roller being able to rotate about, slide lengthwise of, and tilt relative to the arm by which it is carried.
  • Such a joint will hereafter be referred to as a tripod joint of the kind specified.
  • each roller In a tripod joint of the kind specified, the constraint of each roller to rolling movement along its respective track in the outer joint member, without tilting relative thereto, means that the joint has a reduced frictional resistance to plunge (i.e. relative axial movement between the outer and inner joint members) and rotation when the joint is articulated.
  • plunge i.e. relative axial movement between the outer and inner joint members
  • each roller tilts relative to the arm by which it is carried rather than relative to the track in which it is engaged. It will be appreciated that if the roller tilted relative to the track, it would not be able to roll along the track but would have to slide therealong in the tilted condition, which obviously would produce a greater frictional resistance to such movement, and have the result that the joint would tend to generate and transmit vibrations.
  • each roller is carried by its respective arm so as to be able to undergo the necessary rotational, sliding and tilting movement relative thereto.
  • each arm has an outer cylindrical surface and each roller has an inner cylindrical surface, between these two surfaces there being disposed inner and outer guide rings which have interengaging part-spherical surfaces.
  • a needle roller bearing is disposed between the outer surface of the outer guide ring and the internal cylindrical surface of the roller.
  • the roller is able to tilt relative to the arm by virtue of the interengaging part-spherical surfaces of the inner and outer guide rings.
  • the inner guide ring is able to slide lengthways on the arm.
  • the roller is able to rotate about the arm by virtue of the needle roller bearing between the outside of the outer guide ring and the inner cylindrical surface of the roller.
  • Such an arrangement for supporting the roller on the arm is relatively complex involving a large number of separate components and therefore is expensive to manufacture.
  • the roller is able to rotate about the arm easily by virtue of the needle roller bearing disposed between the outside of the outer guide ring and the inner cylindrical surface of the roller, there is a relatively high resistance to sliding movement of the roller lengthwise of the arm.
  • GB 2 018 393 A also discloses a tripod joint of the kind specified wherein each arm of the inner joint member has a part-spherical surface, engaged by an internal part-spherical surface of a guide ring on which the roller is received. There is, however, no disclosure as to how such a joint is assembled.
  • each of the arms of the inner joint member comprises a part- spherical surface
  • the respective roller is carried thereon by an inner roller element having a part- spherical internal surface engaging the part-spherical surface of the arm so as to be able to tilt thereon, the inner roller element having a cylindrical external surface on which the roller is able to rotate and move lengthwise of the arm, each of said arms of the inner joint member also having relieved portions facing in opposite directions along the axis of the inner joint member to provide for assembly of the inner roller element thereon.
  • each roller relative to the arm by which it is carried takes place at the interfitting part- spherical surfaces of the arm and inner roller element.
  • Rotation of the roller relative to the arm, and the necessary sliding movement of the roller lengthwise of the arm take place between the internal surface of the roller and the cylindrical external surface of the inner roller element.
  • the relative sliding movement of the roller lengthwise of the arm does not take place in isolation but in addition to rotation of the roller about the arm, so that the lengthwise movement is superimposed on an already existing rotation in the bearing and therefore takes place with minimum resistance.
  • relieved portions of the arms of the inner joint member face in opposite directions axially thereof, leaving the part-spherical surface unbroken in directions tangentially of the inner joint member to engage the part-spherical internal surface of the inner roller element, when the joint is transmitting torque the forces applied between arm and inner roller element are between the interfitting part-spherical surfaces thereof.
  • the axially facing relieved portions are not detrimental to the torque transmitting capability of the joint, and provide the necessary clearance for the rollers to tilt on the arms.
  • the inner roller element may be provided, in its interior having the part-cylindrical surface, with diametrically opposed cutaways so that the inner roller element is able to be placed on the arm by moving it in a direction perpendicular to the rotational axis of the inner joint member, with the part-spherical surface portion of the arm passing through the internal cutaways of the inner roller element while the flats on the arm face the remaining part-spherical internal surface portions of the inner roller element.
  • the inner roller element when the inner roller element is suitably positioned on the arm, the inner roller element can be turned through 90° about the axis of the arm, perpendicular to the rotational axis of the inner joint member, so that the part-spherical surface portions of arm and inner roller element engage and the flats of the arm face the internal cutaways of the inner roller element.
  • a retaining element is then fitted to the inner roller element to engage the arm to prevent a reverse of the 90° rotation of the inner roller element and ensure that it remains held to the arm.
  • Such a retaining element preferably comprises a resilient member extending diametrically across the inner roller element, and engaging a slot provided in the end of the arm.
  • each inner roller element may be "sprung” onto its arm.
  • This procedure involves deforming the inner roller element by applying oppositely directed forces thereto in the direction axially of the inner joint member, i.e. in the directions faced by the relieved portions of the arm. This causes an increase in the internal dimension of the inner roller element in the direction tangentially of the inner joint member, to enable it to be fitted onto the arm. Thereafter, when the forces applied to the inner roller element are released, assuming the deformation of the inner roller element has not exceeded its elastic limit, the inner roller element once again assumes its original shape and is then held captive on the arm by virtue of the interengaging part-spherical surfaces of arm and inner roller element.
  • each of the arms of the inner joint member comprises a part-spherical surface
  • the respective roller is carried thereon by an inner roller element of plastics material moulded in situ on the arm so as to have a part-spherical internal surface engaging the part- spherical surface of the arm for tilting thereon, the inner roller element having a cylindrical external surface on which the roller is able to rotate and move lengthwise of the arm.
  • joints according to the invention relate to the engagement between each roller and its guide groove in the outer joint member, so that the roller is constrained to roll along the guide groove and not tilt therein, with the result that when the joint is articulated the roller tilts relative to the inner joint member.
  • Each roller is an annular component, having an internal surface which engages the cylindrical external surface of the inner roller element.
  • the external surface of the roller, which engages the opposed side portions of the guide groove is a surface of revolution about a roller axis extending through the centre of the roller.
  • the roller axis is perpendicular to the axis of rotation of the inner joint member and coincides with the centre line of the arm on which the roller is carried.
  • Each roller is preferably constrained against tilting within its guide groove by the nature of the engagement between the external surface of the roller and the side portions of the guide groove it engages.
  • the roller external surface and each roller-engaging side portion of a guide groove may be so configured as to provide contact therebetween at two spaced points, so called angular contact. This may be achieved by having the roller-engaging side portion of the guide groove of gothic arch cross-sectional shape.
  • the external surface of the roller may be a surface of revolution of an arc about the roller axis, the centre of curvature of such arc being offset from the roller axis in order to provide the required angular contact with the side portions of the guide groove.
  • the external surface of the roller is a surface of revolution, about the roller axis, of a truncated gothic arch shape. The advantage of this configuration is described hereafter.
  • Such a mode of engagement between the roller and guide groove is effective to prevent the roller from tilting relative to the groove when the joint is actually transmitting torque, and to limit tilt of the roller when no torque is being transmitted.
  • each of the opposed roller-engaging side portions of each guide groove may comprise at least one shoulder portion engagable with a corresponding end face of the roller to constrain the roller from tilting in the guide groove when no torque is being transmitted.
  • the guide groove may present two such shoulder portions engagable with both end faces of the roller, or only one shoulder portion, engagable with the radially innermost or radially outermost (having regard to the joint as a whole), end face of the roller, as the case may be.
  • the or each such shoulder is inclined so as to have line contact with the. roller when the latter begins to tilt.
  • a further way in which tilting of rollers relative to the outer joint member can be prevented is by providing each roller with a part extending radially outwardly beyond the outermost end of the arm by which it is carried, and by providing each guide groove with an abutment surface engagable with an end face of the outwardly extending part of the roller, to constrain the roller from tilting.
  • a respective guide element may be provided engaging diametrically opposed parts of each roller and also engaging a base portion of the respective guide groove for sliding movement therealong, to constrain the roller from tilting in the guide groove.
  • each roller may have an external surface which is concave (preferably a concave gothic arch) as the roller is viewed in section, i.e. the external surface of the roller as a whole is diabolo shaped.
  • the opposed sides of each guide groove may comprise ribs whose cross-sectional shape is complementary to that of the external roller surface, preferably to have angular contact engagement therewith.
  • Such a diabolo shaped roller cannot tilt substantially relative to the outer joint member.
  • a needle roller bearing assembly is preferably interposed between the external cylindrical surface of each inner roller and an internal surface of each roller. Then, the above described rotation, and relative sliding movement lengthwise of the arm, of the roller relative to the inner roller element takes place at such bearing, and there is a greatly reduced frictional resistance to these relative movements.
  • a plain bearing were to be provided at this point.
  • Figure 1 is an elevation, partly in section, of an embodiment of tripod joint according to the invention, in the articulated condition;
  • Figure 2 is an end view, partly in section, of part of the joint of Figure 1;
  • Figure 3 is a perspective view of the inner joint member of the joint of Figure 1 illustrating how an inner roller may be fitted thereto;
  • Figure 4 is a view as Figure 3 of an alternative inner joint member and mode of fitting an inner roller thereto;
  • Figure 5 is an enlargement of part of Figure 2, showing further detail of the configuration of a roller of the joint and guide groove side portion engaged thereby;
  • Figures 6A and 6B show diagrammatically further possible configurations of roller and guide groove
  • Figure 7 is a view as Figure 2, showing a modification of the joint according to the invention.
  • Figures 8, 9 and 10 are views as Figure 2 showing yet further modified embodiments of joint according to the invention.
  • Figures 11 and 12 are views as Figures 1 and 2 of a further embodiment of joint according to the invention.
  • Figure 13 shows yet a further modification of a oint according to the invention.
  • a joint according to the invention comprises an inner joint member 10 and an outer joint member 11.
  • the inner joint member comprises an annular body 12 provided in its interior with splines 13 for torque transmitting engagement with a shaft element 9.
  • the axis of rotation of the inner joint member is indicated at 19.
  • the inner joint member has three arms 14 extending radially outwardly from the body 12, equally circumferentially spaced around it.
  • Each arm 14 comprises part-spherical surface portions 15 which face generally tangentially of the inner joint member, and flats 16 which face in opposite directions along the rotational axis of the inner joint member. Only the flats 16 on the corresponding sides of the arms 14, facing the same direction as one another, are visible in Figure 3.
  • the outer joint member 11 is generally in the form of a cup-shaped component, in whose interior there are provided three guide grooves 20 extending into the outer joint member from the open end thereof and parallel to the rotational axis 17 thereof.
  • the arms 14 extend into the guide grooves 20, and each arm 14 carries a roller assembly comprising a roller 21 and an inner roller element 22.
  • the roller 21 has an external surface 122 which engages opposed side portions 137 of the groove 20 in a manner to be described in greater detail hereafter, and the inner roller element 22 comprises a part- spherical internal surface 23 and a cylindrical external surface 24.
  • a needle roller bearing assembly comprising a plurality of needle rollers 25 is interposed between the roller 21 and inner roller element 22, the needle rollers 25 running against the external cylindrical surface 24 of the inner roller element 22 and a recessed internal cylindrical surface 26 of the roller 21.
  • the roller 21 is thus able to rotate about the arm 14, slide lengthwise of the arm (i.e. in a direction perpendicular to the rotational axis of the inner joint member 10), and tilt relative to the arm 14.
  • the rotation of the roller 21 and sliding movement thereof relative to the arm 14 take place at the needle roller bearing assembly interposed between the roller and inner roller element.
  • the tilting of the roller takes place by movement of the inner roller element 22 relative to the arm 14 at the interengaging part-spherical surfaces thereof.
  • the inner roller element 22 In its interior having the part-spherical internal surface 23, the inner roller element 22 is provided with two diametrically opposed cutaways 27, most of one such cutaway and a small part only of the other being visible in Figure 3. These cutaways are so dimensioned that the inner roller element is able to be placed on the arm 14 by moving it in a direction perpendicular to the rotational axis of the inner joint member, i.e.
  • a retaining element is fitted, in the form of a short strip 29 of resilient material, e.g. spring steel which extends diametrically across the inner roller element engaging in diametrically opposed parts of an undercut annular groove 30 adjacent the end face of the inner roller element. Lugs 31 at the ends of the resilient retaining member 29 engage in diametrically opposed recesses 32 in the inner roller element, so that the retaining member 29 cannot move around the inner roller element.
  • the retaining element 29 fits in a slot 33 extending into the arm 14 from the free end thereof, and parallel to the rotational axis of the inner joint member.
  • the width of the retaining member 29 is less than that of the slot 33, so that tilting movement of the inner roller element can take place freely relative to the arm; the base of the slot 33 is not flat but in the form of two inclined surfaces to provide the necessary freedom to the inner roller element without unduly weakening the arm. Further, the inner xoller element is able to pivot to a small extent universally on the arm: this assists in accommodating any slight misalignment which might arise between the components of the joint due to production tolerances, therefore helping the free- running characteristics of the joint.
  • the inner roller element 22 could, in an alternative construction, not be provided with the internal annular groove 30.
  • the retaining element 29 could then be held to the inner roller element 22 by deforming the material of the latter in the region of the recesses 32 while the retaining element is in position.
  • deformation of the inner roller element must not distort the external cylindrical surface thereof in the region where it is engaged by the needle rollers 25 in service.
  • the inner roller element would be provided with a diametrically opposed pair of apertures through which a pin could be inserted and retained, to extend through the slot 33.
  • FIG. 4 there is shown an alternative configuration of inner joint member, and inner roller element for assembly onto one of the arms thereof.
  • the inner joint member is indicated at 121 and its arms at 141.
  • Each arm comprises part-spherical surface portions 151 facing tangentially relative to the rotational axis of the inner joint member, and flats 161 facing in opposite directions parallel to such axis, the flats 161 facing in one such direction only being visible in Figure 4.
  • the inner roller element indicated generally at 221, has a part-spherical internal surface 231, with no cutaways therein.
  • the inner roller element has no recesses as the recesses 32 in the embodiment of Figure 3, nor do the arms 141 have slots therein as the slots 33 in the embodiment of Figure 3.
  • the inner roller element is deformed slightly by applying to it diametrically opposed forces as indicated by arrows 222 in Figure 4. This causes the internal dimension of the inner roller element to increase in the direction perpendicular to that in which the force is applied, until the inner roller element can be fitted onto the arm by moving in the direction lengthwise thereof.
  • the inner roller element may have to be pressed on to the arm.
  • the release of the force which had been applied as indicated by arrows 222 enables the inner roller element to return to its circular shape, so that the part-spherical surfaces 151, 231 engage and the inner roller element is then held captive on the arm.
  • the deformation of the inner roller element should be within the elastic range thereof so that it returns to its undeformed shape, and it will further be appreciated that this method of assembly will only be possible if the inner roller element is sufficiently thin walled to enable it to be deformed enough to be fitted without excess force having to be applied thereto.
  • the inner joint member of either configuration above described would usually be manufactured by suitable machining operations on a forged blank.
  • the flats on the arms would be present on the forged blank, and the part-spherical surface portions of the arms turned and ground to the required shape and surface finish while the flats would be left rough as forged.
  • the flats provide clearance for the inner roller elements to tilt sufficiently on the arms to give the joint the required articulation angle capability, without requiring the arms to be provided with recesses or cutaways in the region of their roots where they join the annuar body part 12 of the inner joint member.
  • the strength of the arms in respect of the torque capacity of the joint is primarily determined by the dimension of each arm at its root portion, in the direction circumferentially of the inner joint member: the cross-sectional shape of the root portion may be elongated in such circumferential dimension as compared with its dimension in the direction axially of the joint member.
  • the arms at least on their part-spherical surface portions, may be treated so as to reduce friction between them and the inner roller elements.
  • the application of a low-friction coating to the arms can substantially reduce frictional resistance to tilting of the roller assemblies on the arms, thereby improving the performance of the joint.
  • the roller 21 is constrained not to tilt within the guide groove 20 in the outer joint member by virtue of -he manner in which the roller engages the opposed side portions of the guide groove.
  • the external surface of the roller may be a surface of revolution of an arc about the roller axis extending through the centre of the roller, the centre of curvature of the arc being offset from such roller axis.
  • Each side portion of the guide groove may have a surface of "gothic arch" shape as viewed along the guide groove, so as to have contact with the external surface of the roller at two spaced points. This mode of engagement between roller and side portion has the effect, when the joint is transmitting torque, of guiding the roller so as not to tilt relative to the outer joint member.
  • roller and guide groove is as shown in Figure 5 of the drawings.
  • the external surface of the roller is a truncated gothic arch shape in this section, comprising arcuate portions having respective centres of curvature 122A, 122B offset to opposite sides of the transverse centre plane, indicated at 121, of the roller.
  • the side portion 137 of the guide groove 20 where it is engaged by the roller is a gothic arch shape in section, comprising arcuate portions with respective centres of curvature 137A and 137B also offset on opposite sides of the plane 121.
  • the radii of curvature of the arcuate parts of the guide groove side portion 137 are slightly greater than the radii of curvature of the arcuate parts of the roller external surface, with the result that contact therebetween is established at two spaced "points" 138, 139 (in practice small elliptical areas when the joint is transmitting torque and deformation occurs as the roller is pressed against the groove side portion).
  • the above described engagement between the roller and guide groove side portion at two spaced points is the condition generally known as "angular contact".
  • the angles indicated at P between the perpendiculars at the contact points and the roller centre plane 121 are known as the pressure angles.
  • the condition of angular contact between the roller and guide groove has the effect, when torque is being transmitted, that the roller is guided so that it stays in alignment relative to the guide groove, with its axis 124 perpendicular to the rotational axis of the outer joint member.
  • roller Any tendency for the roller to tilt in the guide groove so that its axis inclines to the axis of the outer joint member, in the same sense that axis 19 is inclined to the axis 17 in Figure 1, results in the establishment of a couple which tends to restore the roller to the correct alignment.
  • the restoring couple established if there is any tendency of the roller to tilt is greater than if the cross-sectional shape of the external surface of the roller were (as previously referred to) a single arc of a radius chosen to provide angular contact with the track groove side portion at the same pressure angle.
  • This is a result of the reduction of the rate at which the surfaces of the roller and groove side portion diverge from one another with increasing distance from the contact points therebetween, as they are viewed in cross-section.
  • an increase in pressure angle occurs with a consequent increase in the offset of the contact "points" 138, 139 from the roller central plane 121.
  • the rate of change of the offset distance X relative to the rate of change of pressure angle P is greater than can be achieved with a roller whose external surface is in the section of a single arc.
  • both the external surface of the roller and the shape of the side portion of the guide groove are symmetrical about the plane 121.
  • the centres of curvature 122A, 122B are equally offset from the plane 121.
  • one problem in the production of the outer joint members of tripod joints and the provision of the guide grooves therein by a forming process is that of distortion, arising from the manufacturing process and from heat treatment.
  • the result of such distortion is that the gothic arch cross-sectional shape of the side portion of the guide groove may be misaligned or non- symmetrical about the plane 121, so that it is not engaged by the roller with equal pressure angles. This could then lead to scuffing of the roller as it rolls along the guide groove.
  • Figure 6A shows, in a broken line indicated at 337A, one possible deviation of the guide groove side portion from the symmetrical configuration thereof indicated at 137.
  • the centre of curvature of the corresponding arcuate part of the gothic arch section of the guide groove side portion is indicated at 237B, offset from the plane 121 by a lesser distance than the centre of curvature 137A of the undistorted surface part.
  • the centre of curvature 222B of the corresponding arcuate part of the gothic arch section of the external surface of the roller is offset from the plane 121 by a lesser distance than is the centre of curvature 122A of the other arcuate part of the roller surface.
  • Figure 6B shows an alternative condition wherein distortion of the joint outer member has produced a surface 337B whose centre of curvature, at 237B, is offset from the plane 121 by a greater distance than is the centre of curvature 137A of the other part of the gothic arch section of the groove side portion.
  • the centre of curvature 222B of the corresponding arcuate part of the gothic arch section of the roller is offset from the plane 121 by a greater distance than is the centre of curvature 122A of the other arcuate section of the roller's external surface.
  • the gothic arch cross sectional shape of the guide groove side portion and of the roller external surface could comprise respective arcuate portions whose radii and centres of curvature can be selected as above described with the possibility of compensating for joint outer member distortion.
  • the same benefits in terms of improved control of roller alignment can be obtained with other gothic arch surface shapes.
  • the surfaces of the roller and/or guide groove side portion where they engage could be of part-elliptical or part-involute section. This could lead to a further reduction of the rate at which the surfaces of the roller and groove side portion diverge from one another with increasing distance from the contact points therebetween, as they are viewed in cross-section.
  • the nature of the engagement between the roller and each guide groove side portion is effective, when the joint is transmitting torque, to resist any tendency of the roller to tilt within the guide groove.
  • production tolerances necessarily mean that there will be some clearance between roller and guide groove in the direction diametrically of the roller, and when the joint is not transmitting torque the roller will tend to move away from the guide groove side portion it was previously engaging.
  • the roller Even with the gothic arch/gothic arch configuration of the surfaces of the roller and guide groove side portion according to the invention, the roller will then be able to tilt to some extent before clearances are absorbed and no further tilting is possible.
  • Figure 7 shows, in a view corresponding to that of Figure 2, an outer joint member whose guide groove 20 is provided, adjacent its side portions engaged by the external surface of the roller, with guide shoulders 39.
  • the shoulders are engagable with the end face 40 of the roller 21 and arranged such that when the roller is exactly aligned in the guide groove, with its axis perpendicular to the axis of rotation of the outer joint member, there is a very slight clearance between the shoulders and end face of the roller. As soon as the roller begins to tilt, it contacts the shoulder and substantial tilting is prevented.
  • shoulders engagable with the opposite end face of the roller may be provided.
  • Figure 7A shows in greater detail one of the shoulders 39, and illustrates that the shoulder is inclined so as to have line contact with the edge of the end face of the foiler when the roller begins to tilt.
  • FIG. 8 of the drawings shows an alternative configuration of outer joint member and the guide groove therein, and the roller carried by the arm of the inner joint member.
  • the inner roller element engaging the part-spherical surface of the arm of the inner joint member is the same as in the above described embodiments, and therefore will not be further referred to.
  • FIG 8 there is shown an outer joint member 50 with a guide groove indicated generally at 51, having opposed side portions 52, 53 which engage the external surface of a roller 54 with the two point angular contact as above described.
  • the roller 54 engages the inner roller element with the intermediary of a needle roller bearing assembly in the same manner as above described.
  • the roller has an annular extension 55 which extends radially outwardly (of the joint as a whole) beyond the end of the arm of the inner joint member and terminates in an end face 56.
  • the guide groove 51 is provided with a radially inwardly extending rib 57 having a flat abutment surface 58, facing the end of the arm of the inner joint member.
  • FIG. 9 shows a further embodiment of joint according to the invention.
  • the inner joint member, arm thereof, and inner roller elements supported on the arms by needle roller bearings are all identical to the corresponding components of the joints described above.
  • the roller, 60 has a recessed interior surface containing needle roller bearings 61 as above described.
  • the external surface 62 of the roller is, however, of concave gothic arch section so that the roller as a whol is diabolo shaped.
  • Opposite sides of the guide groove i the outer joint member are provided with longitudinally extending ribs 63 with opposed surfaces 64 which engage the external surface 62 of the roller.
  • the surfaces 64 are preferably of gothic arch cross-sectional shape, to provide for angular contact with the roller surface 62 i the manner above described.
  • a needle roller bearing assembly is interposed between the external cylindrical surface of each inner roller and an internal surface of the respective roller.
  • a plain bearing were to be provided at this point.
  • the inner roller element 71 is made of a suitable material such as a plastics or sintered metallic bearing material, such that the needle roller bearing assembly is not required between it and the roller 72.
  • the inner roller element 71 is fitted to the arm 70 in the same manner as above described with reference to Figure 3 of the drawings.
  • Figures 11 and 12 are respectively a partly sectioned elevation corresponding to Figure 1, and a partly sectioned partial end view corresponding to Figure 2, of a"joint according to this embodiment.
  • the joint comprises an inner joint member 10 and an outer joint member 11, the inner joint member comprising an annular body 12 provided in its interior with splines 13 for torque transmitting engagement with a shaft element 9 having a rotational axis 19.
  • each arm 80 extends radially outwardly from the body 12, equally circumferentially spaced around the body, and each arm 80 has a surface 81 of truncated spherical form, i.e. a part-spherical surface which extends all the way around the arm.
  • the outer joint member 11 is in the form of a cup- shaped component with three guide grooves 20 in its interior, extending from the open end thereof and parallel to the rotational axis 17 of the joint member.
  • the arms 80 extend into the guide grooves, and each arm carries a roller assembly comprising a roller 84 and inner roller 82.
  • the inner roller element 82 has an internal part-spherical surface 83 extending all the way around its internal periphery and, since the inner roller element has been moulded in situ on the arm 80, this internal surface exactly matches the surface 81 of the arm so that the inner roller element is able to tilt on the arm.
  • the inner roller element has a cylindrical external surface with which an internal cylindrical surface 85 of the roller 84 engages, so that the roller 84 is able to slide on and rotate about the inner roller element.
  • a further alternative is to have inner roller elements which are diametrically split to enable them to be fitted to the arms of the inner joint member. When the rollers are fitted to the inner roller elements, the latter are held together and captive on the arms of the inner joint member.
  • FIG. 13 of the drawings there is shown yet a further means for preventing tilting of a roller 21 in its guide groove.
  • This is a guide element comprising a base portion 130 which is flat and lies against a complementary base portion 135 of guide groove 20.
  • Two limbs 131 extend radially inwardly of the joint as a whole, from the base portion 30, at opposite end thereof.
  • Each limb 131 terminates in two spaced tabs 134 which lie in the external peripheral surface of the roller 21, and inwardly bent tongues 132 which lie against the flat end surface of the roller.
  • the guide element is of resilient sheet material, e.g. spring steel.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Automatic Assembly (AREA)
  • Pivots And Pivotal Connections (AREA)
  • Sealing Devices (AREA)

Abstract

Joint articulé de type joint à tripode à rapport de vitesse constante, se composant d'un membre de joint interne (10) muni de trois broches s'étendant vers l'extérieur et sur lesquelles sont montés des galets de roulement (21) qui s'engagent dans les cannelures de guidage (20) d'un membre de joint (11), lesdits galets de roulement devant pouvoir rouler sans basculer dans les cannelures de guidage, pivoter autour des broches du membre de joint interne, glisser le long de celles-ci et basculer par rapport à elles. Chaque broche (14) comporte une surface en partie sphérique (15) qui reçoit un élément de roulement interne (22) pouvant basculer sur ladite broche, ledit élément de roulement interne (22) ayant une surface cylindrique externe (24) autour de laquelle pivote et glisse un galet de roulement (21).
PCT/GB1989/001468 1988-12-17 1989-12-08 Joint articule a rapport de vitesse constant WO1990007067A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1019900701791A KR910700417A (ko) 1988-12-17 1989-12-08 일정 속도비 유니버설 죠인트

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB888829530A GB8829530D0 (en) 1988-12-17 1988-12-17 Constant velocity ratio universal joints
GB8829530.8 1988-12-17

Publications (1)

Publication Number Publication Date
WO1990007067A1 true WO1990007067A1 (fr) 1990-06-28

Family

ID=10648706

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB1989/001468 WO1990007067A1 (fr) 1988-12-17 1989-12-08 Joint articule a rapport de vitesse constant

Country Status (7)

Country Link
KR (1) KR910700417A (fr)
CA (1) CA2005709A1 (fr)
ES (1) ES2038567A6 (fr)
FR (1) FR2640708A1 (fr)
GB (2) GB8829530D0 (fr)
IT (1) IT1238109B (fr)
WO (1) WO1990007067A1 (fr)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2681113A1 (fr) * 1991-09-11 1993-03-12 Gkn Automotive Ag Joint tripode.
EP0532992A3 (en) * 1991-09-18 1993-06-16 Loehr & Bromkamp Gmbh Tripod joint
DE4331108C1 (de) * 1993-09-15 1995-01-05 Gkn Automotive Ag Gleichlaufdrehgelenk
WO1998009089A1 (fr) * 1996-08-30 1998-03-05 Renault Joint de transmission tripode et procedes de montage d'un tel joint de transmission
USRE36163E (en) * 1992-09-10 1999-03-23 Lohr & Bromkamp Gmbh Tripod joint
EP1225359A1 (fr) 2001-01-19 2002-07-24 Honda Giken Kogyo Kabushiki Kaisha Joint universel homocinétique
US6837794B1 (en) 1996-02-05 2005-01-04 Ntn Corporation Tripod type constant velocity universal joint
US7819752B2 (en) 2007-05-17 2010-10-26 Hyundai Wia Corporation Constant velocity joint of tripod type
US7878914B2 (en) 2007-05-17 2011-02-01 Hyundai Wia Corporation Constant velocity joint of tripod type
US8025575B2 (en) 2007-05-17 2011-09-27 Hyundai Wia Corporation Constant velocity joint of tripod type
US8251827B2 (en) 2007-11-29 2012-08-28 Hyundai Wia Corporation Constant velocity joint of tripod type
DE102022133034A1 (de) 2022-12-12 2024-06-13 Ifa - Technologies Gmbh Gelenkaußenteil, Gelenkinnenteil und Roller für ein Verschiebegelenk vom Typ einer Tripode, Verschiebegelenk vom Typ einer Tripode und Verfahren zur Herstellung eines Gelenkinnenteils

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US5167583A (en) * 1989-11-03 1992-12-01 Gkn Automotive Ag Tripod joint having an inner part with spherical journals provided with roller members guided in an outer part
DE3936600C2 (de) * 1989-11-03 1994-01-13 Loehr & Bromkamp Gmbh Tripodegelenk
DE69114871T2 (de) * 1990-02-08 1996-05-23 Toyota Motor Co Ltd Homokinetisches Universalgelenk des Plungertyps.
US5256107A (en) * 1990-02-08 1993-10-26 Toyota Jidosha Kabushiki Kaisha Sliding type constant velocity universal joint having regulating device for maintaining position of roller constant
US5019016A (en) * 1990-04-10 1991-05-28 Gkn Automotive Inc. Anti-shudder tripod constant velocity universal joint
DE4034758C2 (de) * 1990-11-02 1995-01-05 Gkn Automotive Ag Tripodegelenk
DE4034806C2 (de) * 1990-11-02 1995-01-26 Gkn Automotive Ag Tripodegelenk
DE4102001C2 (de) * 1991-01-24 1999-02-04 Girguis Sobhy Labib Gleichlaufdrehgelenk
US5213545A (en) * 1991-04-01 1993-05-25 Ide Russell D Coupling for use in a constant velocity shaft
US5171185A (en) * 1991-07-23 1992-12-15 Gkn Automotive, Inc. Telescopic tripod universal joint
DE4229251A1 (de) * 1992-01-24 1993-07-29 Voith Gmbh J M Rollenkupplung
ES2088759B1 (es) * 1992-12-08 1998-08-01 Gkn Automotive Ag Articulacion giratoria sincronica
DE4327606C2 (de) * 1993-08-17 1995-05-24 Loehr & Bromkamp Gmbh Tripodegelenk mit Montagesicherung
FR2732735B1 (fr) * 1995-04-04 1998-07-31 Renault Joint de transmission homocinetique
DE19843126A1 (de) * 1998-09-21 2000-03-23 Werner Herrmann Gelenk
FR2785342B1 (fr) * 1998-11-02 2002-05-10 Ntn Toyo Bearing Co Ltd Joint homocinetique universel
EP1643143B1 (fr) * 1998-12-08 2007-10-03 Honda Giken Kogyo Kabushiki Kaisha Joint universel homocinétique
DE19860589C1 (de) * 1998-12-29 2000-08-03 Pankl R & D Gmbh Bruck An Der Tripodgelenk
US6699134B2 (en) 2001-02-21 2004-03-02 Visteon Global Technologies, Inc. Anti-shudder tripod type CV universal joint
JP3894760B2 (ja) * 2001-09-26 2007-03-22 Ｎｔｎ株式会社 等速自在継手
US20090305793A1 (en) * 2004-08-06 2009-12-10 Peter Bongartz Rotary homokinetic joint
JP4541203B2 (ja) * 2005-03-24 2010-09-08 Ｎｔｎ株式会社 トリポード型等速自在継手
US7435181B2 (en) * 2005-10-25 2008-10-14 Delphi Technologies, Inc. Tripot ball with two point contact
KR100815677B1 (ko) * 2006-05-11 2008-03-20 위아 주식회사 트라이포드식 등속조인트
BRPI0722104A2 (pt) * 2007-10-23 2015-02-10 Gkn Driveline Int Gmbh Junta trípode, corpo de rolamento para ela, uso deste, e veículo motorizado
DE102007053999A1 (de) 2007-11-13 2009-05-14 Volkswagen Ag Tripodegelenk
DE102007059377A1 (de) 2007-12-10 2009-06-18 Volkswagen Ag Tripodegelenk
JP5253991B2 (ja) * 2008-12-22 2013-07-31 Ｎｔｎ株式会社 鍛造方法、閉塞鍛造金型、及びトリポード型等速自在継手
DE102013216352B3 (de) * 2013-08-19 2014-11-27 Capital Technology Beteiligungs Gmbh Tripodgelenk mit segmentierten Rollkörpern

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FR2369456A1 (fr) * 1976-10-27 1978-05-26 Hitachi Construction Machinery Joint universel a vitesse constante
GB2018393A (en) * 1978-04-05 1979-10-17 Honda Motor Co Ltd Constant velocity universal joints
DE3103172A1 (de) * 1980-02-25 1981-12-17 Honda Giken Kogyo K.K., Tokyo Gleitendes gleichlauf-universalgelenk
GB2099549A (en) * 1981-06-01 1982-12-08 Glaenzer Spicer Sa A tripod homokinetic joint having swivelling rollers
DE3219189A1 (de) * 1981-06-01 1982-12-30 Glaenzer Spicer Sa Tripode-gleichlaufgelenk
US4589856A (en) * 1985-02-28 1986-05-20 The Zeller Corporation Tripot universal joint of the end motion type
GB2188701A (en) * 1986-04-02 1987-10-07 Ntn Toyo Bearing Co Ltd Homokinetic universal joint
GB2195167A (en) * 1986-09-17 1988-03-30 Ntn Toyo Bearing Co Ltd Universal joints
US4747803A (en) * 1985-09-17 1988-05-31 Ntn Toyo Bearing Co., Ltd. Tripod homokinetic universal joint with cylindrical rollers and a flat roller guide
GB2199113A (en) * 1986-12-05 1988-06-29 Glaenzer Spicer Sa A telescopic transmission joint, in particular for a vehicle
DE3722579A1 (de) * 1986-12-23 1988-07-07 Nippon Seiko Kk Universalgelenk
FR2610681A1 (fr) * 1987-02-05 1988-08-12 Honda Motor Co Ltd Joint universel de type coulissant
GB2204659A (en) * 1987-04-30 1988-11-16 Honda Motor Co Ltd Universal joints
EP0291691A1 (fr) * 1987-05-06 1988-11-23 Glyco-Metall-Werke Daelen & Loos GmbH Joint universel pour installation dans les arbres transmettant des couples rotatifs

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2369456A1 (fr) * 1976-10-27 1978-05-26 Hitachi Construction Machinery Joint universel a vitesse constante
GB2018393A (en) * 1978-04-05 1979-10-17 Honda Motor Co Ltd Constant velocity universal joints
DE3103172A1 (de) * 1980-02-25 1981-12-17 Honda Giken Kogyo K.K., Tokyo Gleitendes gleichlauf-universalgelenk
GB2099549A (en) * 1981-06-01 1982-12-08 Glaenzer Spicer Sa A tripod homokinetic joint having swivelling rollers
DE3219189A1 (de) * 1981-06-01 1982-12-30 Glaenzer Spicer Sa Tripode-gleichlaufgelenk
US4589856A (en) * 1985-02-28 1986-05-20 The Zeller Corporation Tripot universal joint of the end motion type
US4747803A (en) * 1985-09-17 1988-05-31 Ntn Toyo Bearing Co., Ltd. Tripod homokinetic universal joint with cylindrical rollers and a flat roller guide
GB2188701A (en) * 1986-04-02 1987-10-07 Ntn Toyo Bearing Co Ltd Homokinetic universal joint
GB2195167A (en) * 1986-09-17 1988-03-30 Ntn Toyo Bearing Co Ltd Universal joints
GB2199113A (en) * 1986-12-05 1988-06-29 Glaenzer Spicer Sa A telescopic transmission joint, in particular for a vehicle
DE3722579A1 (de) * 1986-12-23 1988-07-07 Nippon Seiko Kk Universalgelenk
FR2610681A1 (fr) * 1987-02-05 1988-08-12 Honda Motor Co Ltd Joint universel de type coulissant
GB2204659A (en) * 1987-04-30 1988-11-16 Honda Motor Co Ltd Universal joints
EP0291691A1 (fr) * 1987-05-06 1988-11-23 Glyco-Metall-Werke Daelen & Loos GmbH Joint universel pour installation dans les arbres transmettant des couples rotatifs

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2681113A1 (fr) * 1991-09-11 1993-03-12 Gkn Automotive Ag Joint tripode.
ES2062910A2 (es) * 1991-09-11 1994-12-16 Gkn Automotive Ag Articulacion de tripode.
EP0532992A3 (en) * 1991-09-18 1993-06-16 Loehr & Bromkamp Gmbh Tripod joint
USRE36163E (en) * 1992-09-10 1999-03-23 Lohr & Bromkamp Gmbh Tripod joint
DE4331108C1 (de) * 1993-09-15 1995-01-05 Gkn Automotive Ag Gleichlaufdrehgelenk
US6837794B1 (en) 1996-02-05 2005-01-04 Ntn Corporation Tripod type constant velocity universal joint
WO1998009089A1 (fr) * 1996-08-30 1998-03-05 Renault Joint de transmission tripode et procedes de montage d'un tel joint de transmission
FR2752890A1 (fr) * 1996-08-30 1998-03-06 Renault Joint de transmission tripode et procedes de montage d'un tel joint de transmission
US6752721B2 (en) 2001-01-19 2004-06-22 Honda Giken Kogyo Kabushiki Kaisha Constant velocity universal joint
EP1225359A1 (fr) 2001-01-19 2002-07-24 Honda Giken Kogyo Kabushiki Kaisha Joint universel homocinétique
US7819752B2 (en) 2007-05-17 2010-10-26 Hyundai Wia Corporation Constant velocity joint of tripod type
US7878914B2 (en) 2007-05-17 2011-02-01 Hyundai Wia Corporation Constant velocity joint of tripod type
US8025575B2 (en) 2007-05-17 2011-09-27 Hyundai Wia Corporation Constant velocity joint of tripod type
US8251827B2 (en) 2007-11-29 2012-08-28 Hyundai Wia Corporation Constant velocity joint of tripod type
DE102022133034A1 (de) 2022-12-12 2024-06-13 Ifa - Technologies Gmbh Gelenkaußenteil, Gelenkinnenteil und Roller für ein Verschiebegelenk vom Typ einer Tripode, Verschiebegelenk vom Typ einer Tripode und Verfahren zur Herstellung eines Gelenkinnenteils
WO2024125715A1 (fr) 2022-12-12 2024-06-20 Ifa-Technologies Gmbh Partie interne de joint pour joint coulissant de type trépied, et joint coulissant de type trépied

Also Published As

Publication number Publication date
GB2226102A (en) 1990-06-20
KR910700417A (ko) 1991-03-15
FR2640708A1 (fr) 1990-06-22
GB2226102B (en) 1992-06-10
IT8968108A0 (it) 1989-12-15
GB8829530D0 (en) 1989-02-01
IT1238109B (it) 1993-07-07
GB8927793D0 (en) 1990-02-14
CA2005709A1 (fr) 1990-06-17
ES2038567A6 (es) 1993-07-16

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