EP0484420A4 - Undercut free constant velocity joint - Google Patents
Undercut free constant velocity jointInfo
- Publication number
- EP0484420A4 EP0484420A4 EP19900911767 EP90911767A EP0484420A4 EP 0484420 A4 EP0484420 A4 EP 0484420A4 EP 19900911767 EP19900911767 EP 19900911767 EP 90911767 A EP90911767 A EP 90911767A EP 0484420 A4 EP0484420 A4 EP 0484420A4
- Authority
- EP
- European Patent Office
- Prior art keywords
- joint member
- axis
- constant velocity
- velocity universal
- ball
- 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.)
- Withdrawn
Links
- 230000005540 biological transmission Effects 0.000 claims description 5
- 238000000034 method Methods 0.000 description 9
- 238000005452 bending Methods 0.000 description 6
- 238000004519 manufacturing process Methods 0.000 description 5
- 238000003754 machining Methods 0.000 description 4
- 238000003466 welding Methods 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 230000001010 compromised effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000002788 crimping Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 238000005242 forging Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000002156 mixing Methods 0.000 description 1
- 238000009497 press forging Methods 0.000 description 1
- 238000005245 sintering Methods 0.000 description 1
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
- F16D3/22—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D3/2237—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts where the grooves are composed of radii and adjoining straight lines, i.e. undercut free [UF] type 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
-
- 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
- F16D3/22—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D3/224—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere
-
- 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
- F16D3/22—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D2003/22313—Details of the inner part of the core or means for attachment of the core on the shaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2300/00—Special features for couplings or clutches
- F16D2300/12—Mounting or assembling
Definitions
- the present invention relates to a constant velocity universal joint for use in any application requiring torque transmission through a varying angle. More particularly, the invention involves a universal joint that utilizes a plurality of balls to transmit a torque from an inner joint member to an outer joint member.
- the interior of the outer joint member contains a series of grooves that are in radial alignment with a complementary series of grooves that are positioned on the exterior of the inner joint member.
- a rage is positioned between the outer joint member and the inner joint member to guide the balls as they traverse the grooves during articulation of the universal joint.
- the prior art reveals a wide variety of devices that permit the transmission of a rotational torque from one shaft that is angularly displaced with respect to another shaft coupled thereto.
- most of the prior art devices require extensive machining of the individual parts to assure satisfactory assembly and operation of the device.
- the overall strength of the prior art devices was compromised by the required machining of the individual parts.
- the present invention differs from the undercut-free constant velocity joint that is shown and described in U.S. Patent No. 3,879,960, entitled "Constant Velocity Joint" issued April 29, 1975, to Hans-Heinrich Welschof et al.
- the constant velocity joint described in the above-referenced patent shows an outer joint member in which the individual ball grooves are divergent with respect to the central axis of the universal joint, when viewed from the open end of the outer joint member.
- the ball grooves that are positioned in the inner joint member are convergent with respect to the central axis of the universal joint.
- the balls are maintained in a spaced apart planar joint.
- the balls are maintained in a spaced apart planar relationship with one another by means of a cage that is positioned hetween the outer joint member and the inner joint member.
- the outer joint member does not lend itself to press forging techniques since the opening therein is of smaller diameter than the diameter of the interior cavit3 * therein.
- the lip of the outer joint member is thin because of the divergent nature of the ball grooves. The thin areas of the outer joint member occur at one of the areas of maximum stress in the universal joint, particularly when large angles of articulation are employed.
- the present invention differs from the above-described universal joint in that the divergence and convergence of the ball grooves in the outer joint member and the inner joint member are in reverse order. Then, too, the free end of the outer joint member is of increased thickness in the present invention.
- the present invention does not have any undercuts that must be made in the hub area as does the above reference.
- the ball cage of the present invention is quite simple with concentric spherical surfaces being employed. Also, the hub and inner torque members utilize concentric spherical surfaces.
- the outer joint member is separate from the axle-hub combination with which it coacts.
- a rylindrica] sleeve unites the outer joint member to th * 3 hub by welding and crimping techniques.
- a ball cage supporting element is used to retain the balls in the grooves to engage the balls on one side.
- the ball cage supporting element does not contact the spherical surfaces of the outer joint member or the inner joint member, but instead, the ball cage contacts a spherical surface 30 in the interior of the joint near the central hub as shown in Figure 1.
- the ball cage contains a series of fingers that are intercalated with respect to the balls. This universal joint requires extensive machining to fabricate the joint as well as complicated tools for fabricating the various details.
- the present invention is an improvement over -the universal joint shown and described in the patent 4,610,643, in that fewer parts are utilized and there is less frictional contact with the ball cage. Additionally, the present invention provides a ball cage with apertures therein that completely circumscribes each ball. Further, by providing a universal joint with an outer joint member having a thick structural section near its open end, the area of highest load concentration upon articulation, the joint is more reliable and durable. The outer joint member fabrication is simplified and the cost of fabrication is significantly reduced.
- the present invention is a constant velocity universal joint for use in transmitting a driving torque from a first axial direction to another axial direction, angularly disposed with respect to th ⁇ first direction.
- the invention includes an outer joint member that contains a plurality of axially extending grooves therein.
- An inner joint member is positioned within the outer joint member and a plurality of mutually dependent grooves are carried by the inner and outer joint members.
- the outer joint member is coupled to a hub that is formed as an integral part of a first torque transmitting shaft and a plurality of balls are held in planar relationship to one another by a cage that is positioned between and in contact with the outer and inner joint members.
- a second torque shaft is coupled to the inner joint member by any convenient disconnect means.
- a primary object of the present invention is to provide a universal joint that requires a minimum amount of machining in the manufacture thereof. Another object of the present invention is to provide a universal joint in which the major components are undercut-free. A further object of the present invention is to provide a design that lends itself to cold impact press forming of the parts of the universal joint. Another object of the present invention is to reduce the contact area of the ball cage with the outer joint member and the inner joint member of the universal joint.
- Still another object of the present invention is to provide a universal joint with enhanced strength characteristics.
- a further object of the present invention is to provide a universal joint that is easy to assemble and disassemble.
- Figure 1A is a part sectional view of a prior art undercut-free outer joint member
- Figure IB is a graphical representation of the prior art under-cut free constant velocity joint forces experienced in the ball track as the bending angle increases.
- Figure 1 is a part sectioned side view that shows the universal joint of the present invention
- Figure 2 is a part sectioned side view that shows the universal joint in an angular drive attitude
- Figure 3 is a part sectioned side elevational view of the integral hub and output shaft;
- Figure 4 is an end view of the hub and output shaft as viewed along lines 4-4 of Figure 3;
- Figure 5 is an elevational end view of the outer joint member that shows the pairs of grooves positioned on the interior surface thereof;
- Figure 6 is a sectioned view taken along section lines
- Figure 7 is an end view of the inner joint member that shows the pairs of grooves positioned on the exterior surface of the inner joint member
- Figure 8 is a sectioned view taken along section lines 8-8 of Figure 7 that shows the curvilinear surfaces for the balls and the cage.
- FIG. 1A there is illustrated a prior art undercut-free constant velocity universal joint in part section view that has application for many uses such as the coupling of drive shafts and other applications.
- the graph illustrated in Figure IB represents the forces experienced in the outer joint member as the bending angle increases. The bending is the angle of articulation between the central axis of the outer joint member and the central axis of the inner joint member. The graph clearly shows that the greatest forces are experienced at maximum bending angle and in the area near the open end of the outer joint member.
- Figure 1 is a part sectioned side elevational view that shows the universal joint of the present invention.
- the overall apparatus is identified by the numeral 10 as shown.
- An output shaft 14 is positioned at the left-hand side of the overall apparatus 10.
- the output shaft 14 is coupled to a hub 16 that can be, as shown, an integral part of the output shaft 14.
- the hub 16 and the output shaft 14 are coaxial along an output axis 20.
- An input axis 18 is shown coincidental with the output axis 20.
- the hub 16 has a cylindrical external surface 22 that abuts a radially inward lip 24.
- the lip 24 is planar and is perpendicular to the output axis 20.
- the hub 16 has a concavity that is formed by an arcuate section 26, a frustoconical section 28, and a spherical section 30. The blending together of the above three sections produces a concavity that can be readily formed by press and forge techniques.
- An outer joint member 32 has an exterior surface 34 that is cylindrical about the output axis 20.
- the left-hand end of the outer joint member 32, as viewed in Figure 1, has an internal
- the internal cylindrical surface 36 of the outer joint member 32 coacts with the cylindrical external surface 22 of the hub 16 in order to couple the hub 16 and the outer joint member 32 in a manner to be more fully described hereinafter.
- the outer joint member 32 has an interior spherical surface 38.
- the interior spherical surface 38 is defined by a radius that has its locus situated on the input axis 18 at a point L.
- the left-hand end 40 of the outer joint member 32 is planar in configuration and has a radial extent spanning the distance between the internal cylindrical surface 36 and the interior spherical surface 38.
- the juncture between the end 40 and the interior spherical surface 38 can be beveled as identified by the number 42.
- the right-hand end 44 of the outer joint member 32 has a planar configuration and has a radial extent that extends between the exterior surface 34 and the interior spherical surface 38.
- the juncture between the end 44 and the interior spherical surface 38 is beveled at approximately 45 as will be commented on elsewhere. Thus, it is evident that a large cavity passes through the central axial region of the outer joint member 32.
- a plurality of axially extending arcuate ball races or grooves 46 is cut into and through the interior spherical surface 38 of the outer joint member 32.
- the mid line or, the most radially outward extent of each ball race has a circular section 48 that is coupled to an essentially linear section 50.
- the circular section 48 has a radius with a locus that is positioned on the output axis 20 to the left of the point L.
- « 46 has their mid lines lying in a plane that, also contains the output axis 20.
- An inner joint member 52 is positioned within the open cavity that passes through the outer joint member 32.
- the inner joint member 52 is positioned symmetrically about the input axis 18.
- the inner joint member 52 has an internal cylindrical bore 54 that is equipped with axially extending splines 56.
- the inner joint member 52 has radially extending left and right-hand essentially planar ends 58 and 60.
- the most radial exterior surface 62 of the inner joint member 52 is spherical in configuration with the spherical extent terminating at the juncture with the planar ends 58 and 60.
- the inner joint member 52 contains a plurality of axially extending arcuate ball races or grooves 64 that are cut into and through the exterior spherical surface 62.
- the mid line or, the most radial inward extent of each ball race 64 has a circular section 66 that is connected to an essentially linear section 68.
- the circular section 66 has a radius with a locus that is positioned on the input axis 18 to the right of the point L.
- the distance of the locus of the circular section 66 from the point L should be essentially equal to the distance of the locus of the circular section 48 of the outer joint member from the point L.
- a ball cage 70 is positioned within the cavity of the outer joint member 32 and is spaced exteriorly of the inner joint member 52 in telescoped arrangement.
- the ball cage 70 has exterior and interior spherical surfaces 72 and 74 that are concentric with one another.
- the exterior spherical surface 72 is terminated at its left-hand end, as viewed in Figure 1, by a radially inwardly extending end 76.
- the most radially inward portion of the end 76 intersects an axially extending cylindrical bore 78.
- the cylindrical bore terminates at its right-hand end with an intersection with the interior spherical surface 74.
- the exterior spherical surface 72 of the ball cage 70 terminates at its right-hand end by a radially inwardly extending end 80.
- the most radially inward portion of the end 80 intersects an axially extending cylindrical bore 82.
- the cylindrical bore 82 terminates at its left-hand end with an intersection with the interior spherical surface 74.
- the exterior sp e rical surface 72 of the ball cage 70 is in rotational contact with the interior spherical surface 38 of the outer joint member 32.
- the interior spherical surface 74 of the ball cage 70 is in rotational contact with the exterior spherical surface 62 of the inner joint member 52.
- a plurality of radially extending bores or windows 84 is positioned in thp wall created by the exterior and interior spherical surfaces 72 and 74 of the ball cage 70.
- the axes of the bores 84 pass through the point L on the input shaft 12.
- Each axis 84 is coincident with the mid line of the ball races 46 and 64.
- the axis of each bore 84 lies in a plane that contains the mid lines of each pair of mid lines associated with the ball races 46 and 64.
- a spherical ball 86 is positioned within the confinement of each bore 84 so that it can translate simultaneously along the mid lines of the ball races 46 and 64.
- the input shaft 12 has externally protruding splines 88 that mesh with the splines 56 that extend axially along the cylindrical bore 54 of the inner joint member 52.
- the cylindrical bore 54 of the inner joint member 52 contains a reentrant groove 90 for the containment of a fingerlock retaining ring 92.
- a plurality of cantilevered resilient fingers 94 snap over a radially disposed ledge 96 that circumscribes the input shaft 12.
- the fingerlock retaining ring 92 prevents axial movement of the input shaft 12 with respect to the inner joint member 52.
- Figure 2 is a part sectioned side view of the overall apparatus 10 that shows the universal joint in an angular drive
- the output shaft 14, the attached hub 16 and the outer joint member 32 remain in fixed relationship to one another and do not move, other than rotatively.
- the input shaft 12 has assumed a position so that its input axis 18 is angularly disposed with respect to the output axis 20 of .the output shaft 14.
- the inner joint member 52 also moves through the same angle since it is fixed with respect to the input shaft 12.
- the spherical balls 86 translate along the most vertically oriented spherical ball 86 moves the furthest to the right while the lowest diametrically positioned spherical ball 86 moves correspondingly to the left along another pair of ball races 46 and 64. The remaining spherical balls 86 move correspondingly along the ball races 46 and 64.
- a pair of spherical balls 86 lies on the input axis 18, there would be no translation along the ball races 46 and 64.
- the above discussion assumes that there is no rotation of the input and output shafts 12 and 14.
- the ball cage 70 rotates a lesser amount as can be seen in Figure 2. It is important that the ball cage 70 always articulates so that the axis 98 of the bores 84 remains positioned so that the point L lies thereon. In this manner, a constant velocity will be achieved through the overall apparatus 10.
- FIG. 3 is a part sectioned side elevational view of the integral hub 16 and the output shaft 14.
- the output shaft 14 can be divided into cylindrical axial extents 102 and 104, each containing an arcuate array of longitudinally aligned splines 106.
- the hub 16, which is an extension of the output shaft 14, has an internal cavity defined by the arcuate section 26, the frustoconical section 28, and the spherical section 30. Since there is no undercutting required in the formation of the internal cavity of the hub 16, it can be formed by press or forging techniques.
- Figure 4 is an end view of the hub cavity as viewed along lines 4-4 of Figure 3.
- the lip 24 is shown in its planar view along with the lines of intersection between the previously mentioned surfaces of the cavity within the hub 16.
- Figure 5 is an elevational end view of the outer joint member 32 that shows the diametrically opposed pairs of grooves positioned on the interior spherical surface 38 of the outer joint member 32.
- the ball races 46 are not undercut; thus, they can be formed by press or forge techniques. If sintering techniques are employed in the fabrication of the outer joint member 32 then metal removal techniques need not be employed to form the spherical interior surface 38.
- the cross-sectional configuration of the ball race 46 is shown as circular with tangential parallel extensions 108 coupled thereto.
- Figure 5 shows the curvilinear surface of the circular and linear sections 48 and 50.
- the interior spherical surface 38 is also shown.
- Figure 7 is an end view of the inner joint member 52 that shows the pairs of diametrically opposed ball races 64 positioned on the exterior spherical surface 62 of the inner joint member 52.
- the number of ball races 64 equals the number of ball races 46 as previously shown in Figure 5.
- the cylindrical bore 54 contains the splines 56 which are in axial alignment with the input axis 18.
- Figure 8 is a sectional view taken along section lines 8-8 of Figure 7 that shows the curvilinear mid line of the ball race 64 and the exterior spherical surface 62 of the inner joint member 52.
- the planar left and right ends 58 and 60 permit the employment of easy fabrication techniques as previously commented on.
- ASSEMBLY AND OPERATION The assembly of the overall apparatus 10 of the present invention is very straightforward. Also, the geometry of the components of the overall apparatus 10 permit automated assembly.
- the inner joint member 52 is positioned so that its left-hand edge, as viewed in Figure 1, is facing up.
- the ball cage 70 is lowered concentrically, and in axial alignment, around the inner joint member 52 until the bores 84 are opposite the circular section 66 of the ball race 64.
- the spherical balls 86 are then inserted into each of the bores 84. As the spherical balls 86 move radially inward, they will contact the circular section 66 of the ball race 64 and remain stationary.
- the outer joint member 32 is then telescoped over the ball cage 70.
- the ball cage 70 is then moved into final axial alignment.
- the spherical balls 86 are now held against radially outward disengagement by the ball races 46.
- the cylindrical external surface 22 of the hub 16 is then moved into engagement with the internal cylindrical surface 36 of the outer joint member 32 and then immobilized therewithin.
- the immobilization technique can involve a press fit, welding, or a snap ring placement as depicted at 108a in Figure 2.
- the input shaft 12 can be inserted into the cylindrical bore 54 so that the splines 56 and 88 slide into engagement.
- the resilient fingers 94 of the previously inserted retaining ring 92 engage with the ledge 96 on the input shaft 12, locking it into its final position.
- a torque is applied to the input shaft 12, causing it and the spline coupled inner joint member 52 to rotate.
- the torque is then transmitted from the inner joint member 52 to the spherical balls 86 by contact with the ball races 64.
- the spherical balls 86 then transmit the torque to the outer joint member 32 via the ball races 46. Since the outer joint member is non-rotatively attached to the lip 24 of the hub 16, the hub 16 rotates along with the integrally attached output shaft 14.
- the spherical balls 86 will remain at one location along the ball races 46 and 64 during rotation of the overall apparatus 10. Since the spherical balls are centrally positioned within the ball races 46 and 64, the stresses are fairly well distributed through the outer joint member 32 and the inner joint member 52.
- the spherical balls 86 no longer track in a single circular path about. the input axis 18.
- the spherical balls 86 will traverse nearly the entire length of the ball races 46 and 64. Since the spherical balls 86 are fixed against lateral movement with respect to the
- the ball cage 70 not only rotates on its exterior and interior spherical surfaces 72 and 74 but, also, the ball cage must rotate when the input axis 18 shifts position from left to right about an axis that passes through the point L.
- the rotational axis for the ball cage 70 is perpendicular to the input axis 18 only when the input, and output axes 18 and 20 are in alignment.
- the amount and frequency of the rotation of the ball cage 70 about its axis depends on the frequency and magnitude of the change in the angle as identified in Figure 2 by reference numeral 110.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Automatic Assembly (AREA)
- Rolling Contact Bearings (AREA)
- Diaphragms For Electromechanical Transducers (AREA)
- Pens And Brushes (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US384836 | 1982-06-04 | ||
US38483689A | 1989-07-25 | 1989-07-25 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0484420A1 EP0484420A1 (fr) | 1992-05-13 |
EP0484420A4 true EP0484420A4 (en) | 1992-09-09 |
Family
ID=23518959
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19900911767 Withdrawn EP0484420A4 (en) | 1989-07-25 | 1990-06-22 | Undercut free constant velocity joint |
Country Status (9)
Country | Link |
---|---|
EP (1) | EP0484420A4 (fr) |
JP (1) | JPH05501905A (fr) |
KR (1) | KR920704031A (fr) |
CN (1) | CN1028665C (fr) |
AU (1) | AU644806B2 (fr) |
BR (1) | BR9007553A (fr) |
CA (1) | CA2016894A1 (fr) |
ES (1) | ES2024838A6 (fr) |
WO (1) | WO1991001453A1 (fr) |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN100419293C (zh) * | 2002-03-14 | 2008-09-17 | 韩国德尔福汽车系统公司 | 汽车驱动轴用球窝接头 |
JP2004116666A (ja) | 2002-09-26 | 2004-04-15 | Ntn Corp | 固定型等速自在継手及びその製造方法 |
DE10337612B4 (de) * | 2002-11-15 | 2009-11-05 | Gkn Driveline International Gmbh | Gegenbahngelenk mit Steuerwinkelumkehr |
JP2006258170A (ja) * | 2005-03-16 | 2006-09-28 | Ntn Corp | 固定式等速自在継手 |
ITMI20061838A1 (it) * | 2005-10-05 | 2007-04-06 | Shaft Form Engineering Gmbh | Giunto omocinetico a sfere |
JP4833169B2 (ja) * | 2007-08-21 | 2011-12-07 | 株式会社リコー | 等速ジョイントおよび画像形成装置 |
US8414406B2 (en) * | 2010-07-19 | 2013-04-09 | Dana Automotive Systems Group, Llc | Constant velocity joint assembly and method of securing a shaft to the assembly |
CN102661326A (zh) * | 2012-05-07 | 2012-09-12 | 大连橡胶塑料机械股份有限公司 | 万向转套装置 |
CN102767577B (zh) * | 2012-07-11 | 2015-04-01 | 南京冠盛汽配有限公司 | 低震动自动滑移补偿复式花键万向节 |
CN103738685B (zh) * | 2013-12-17 | 2016-03-02 | 徐工集团凯宫重工南京有限公司 | 一种盾构螺旋输送机驱动用万向连接装置 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1975758A (en) * | 1933-09-25 | 1934-10-02 | Bernard K Stuber | Universal joint |
DE2522670B1 (de) * | 1975-05-22 | 1976-05-06 | Loehr & Bromkamp Gmbh | Hinterschnittfreies Gleichlaufdrehgelenk |
GB2206949A (en) * | 1987-07-09 | 1989-01-18 | Spicer Hardy Ltd | Outer member for constant velocity ratio universal joint |
FR2623579A1 (fr) * | 1987-11-25 | 1989-05-26 | Uni Cardan Ag | Joint homocinetique |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1665280A (en) * | 1927-04-02 | 1928-04-10 | Alfred H Rzeppa | Universal joint |
US1916442A (en) * | 1929-08-21 | 1933-07-04 | Alfred H Rzeppa | Universal joint |
US2309939A (en) * | 1939-12-09 | 1943-02-02 | Adiel Y Dodge | Universal joint |
US2322570A (en) * | 1941-12-26 | 1943-06-22 | Adiel Y Dodge | Universal joint |
US3324682A (en) * | 1965-09-24 | 1967-06-13 | Dana Corp | Ball type constant velocity universal joint |
US3541809A (en) * | 1969-03-06 | 1970-11-24 | Gen Motors Corp | Universal joint cage |
DE2252827C3 (de) * | 1972-10-27 | 1976-01-08 | Loehr & Bromkamp Gmbh, 6050 Offenbach | Gleichlaufgelenk |
JPS5622026Y2 (fr) * | 1977-12-16 | 1981-05-25 | ||
JPS5572921A (en) * | 1978-11-28 | 1980-06-02 | Honda Motor Co Ltd | Outer wheel of equal-velocity universal joint |
DE3114290C2 (de) * | 1981-04-09 | 1984-04-19 | Löhr & Bromkamp GmbH, 6050 Offenbach | "Gleichlaufdrehgelenk" |
DE3209596C2 (de) * | 1982-03-17 | 1985-10-03 | Uni-Cardan Ag, 5200 Siegburg | Gleichlaufdrehgelenk |
US4756640A (en) * | 1983-08-19 | 1988-07-12 | Gkn Automotive Components Inc. | Axial retaining member |
-
1990
- 1990-05-16 CA CA002016894A patent/CA2016894A1/fr not_active Abandoned
- 1990-05-23 CN CN90103893A patent/CN1028665C/zh not_active Expired - Lifetime
- 1990-06-07 ES ES9001580A patent/ES2024838A6/es not_active Expired - Lifetime
- 1990-06-22 EP EP19900911767 patent/EP0484420A4/en not_active Withdrawn
- 1990-06-22 JP JP2510988A patent/JPH05501905A/ja active Pending
- 1990-06-22 BR BR909007553A patent/BR9007553A/pt not_active IP Right Cessation
- 1990-06-22 KR KR1019920700167A patent/KR920704031A/ko not_active Application Discontinuation
- 1990-06-22 WO PCT/US1990/003654 patent/WO1991001453A1/fr not_active Application Discontinuation
- 1990-06-22 AU AU60611/90A patent/AU644806B2/en not_active Ceased
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1975758A (en) * | 1933-09-25 | 1934-10-02 | Bernard K Stuber | Universal joint |
DE2522670B1 (de) * | 1975-05-22 | 1976-05-06 | Loehr & Bromkamp Gmbh | Hinterschnittfreies Gleichlaufdrehgelenk |
GB2206949A (en) * | 1987-07-09 | 1989-01-18 | Spicer Hardy Ltd | Outer member for constant velocity ratio universal joint |
FR2623579A1 (fr) * | 1987-11-25 | 1989-05-26 | Uni Cardan Ag | Joint homocinetique |
Non-Patent Citations (1)
Title |
---|
See also references of WO9101453A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO1991001453A1 (fr) | 1991-02-07 |
CA2016894A1 (fr) | 1991-01-25 |
AU644806B2 (en) | 1993-12-23 |
KR920704031A (ko) | 1992-12-19 |
ES2024838A6 (es) | 1992-03-01 |
EP0484420A1 (fr) | 1992-05-13 |
AU6061190A (en) | 1991-02-22 |
CN1049050A (zh) | 1991-02-06 |
BR9007553A (pt) | 1992-06-23 |
CN1028665C (zh) | 1995-05-31 |
JPH05501905A (ja) | 1993-04-08 |
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