CA1125043A - Double cardan universal joint with improved centering means - Google Patents
Double cardan universal joint with improved centering meansInfo
- Publication number
- CA1125043A CA1125043A CA351,891A CA351891A CA1125043A CA 1125043 A CA1125043 A CA 1125043A CA 351891 A CA351891 A CA 351891A CA 1125043 A CA1125043 A CA 1125043A
- Authority
- CA
- Canada
- Prior art keywords
- yoke
- end yoke
- circular
- gear teeth
- teeth
- 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.)
- Expired
Links
- 239000004519 grease Substances 0.000 claims description 4
- 230000002730 additional effect Effects 0.000 claims 1
- 239000000306 component Substances 0.000 description 7
- 238000006073 displacement reaction Methods 0.000 description 4
- 238000005096 rolling process Methods 0.000 description 2
- 101000701876 Homo sapiens Serpin A9 Proteins 0.000 description 1
- 102000050111 human SERPINA9 Human genes 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 229920000136 polysorbate Polymers 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
- F16D3/26—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected
- F16D3/30—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected in which the coupling is specially adapted to constant velocity-ratio
- F16D3/32—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected in which the coupling is specially adapted to constant velocity-ratio by the provision of two intermediate members each having two relatively perpendicular trunnions or bearings
- F16D3/33—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected in which the coupling is specially adapted to constant velocity-ratio by the provision of two intermediate members each having two relatively perpendicular trunnions or bearings with ball or roller bearings
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Arrangement And Driving Of Transmission Devices (AREA)
- Steering Controls (AREA)
- Mutual Connection Of Rods And Tubes (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
A double Cardan universal joint is provided with improved centering means. One end joke of the joint has a plurality of cir-cular ridges or gear teeth facing the other end yoke with the center line of the gear teeth being coaxial with the axis of rotation of the one yoke. The other end yoke has a plurality of circular ridges or gear teeth facing the one end yoke with the center line of those gear teeth coaxial with the axis of rotation of that yoke. The teeth are positioned so that one tooth extends between two teeth of the other yoke for any position of the end yokes and the drive and driven mem-bers or shafts to which they are attached. One of the end yokes has a gear-tooth shaped projection at the center line and the other has a gear-tooth shaped recess at its center line. The sets of teeth are in patterns of sphere segments so that any longitudinal cross section taken centrally through the gear teeth has the same appear-ance as a spur gear segment. The tooth profile is such that points of contact are always on the pitch radii at the intersection with a line through the center of the sphere segments of the gear teeth.
A double Cardan universal joint is provided with improved centering means. One end joke of the joint has a plurality of cir-cular ridges or gear teeth facing the other end yoke with the center line of the gear teeth being coaxial with the axis of rotation of the one yoke. The other end yoke has a plurality of circular ridges or gear teeth facing the one end yoke with the center line of those gear teeth coaxial with the axis of rotation of that yoke. The teeth are positioned so that one tooth extends between two teeth of the other yoke for any position of the end yokes and the drive and driven mem-bers or shafts to which they are attached. One of the end yokes has a gear-tooth shaped projection at the center line and the other has a gear-tooth shaped recess at its center line. The sets of teeth are in patterns of sphere segments so that any longitudinal cross section taken centrally through the gear teeth has the same appear-ance as a spur gear segment. The tooth profile is such that points of contact are always on the pitch radii at the intersection with a line through the center of the sphere segments of the gear teeth.
Description
This invention relates to a double Cardan universal joint with improved centering means.
Double Cardan universal joints are well known in the art and have the advantage of producing constant velocity between the drive and drlven members or shafts which they connect. A double Cardan universal joint includes a first end yoke connected to a drive mRmber or shaft and having two arms rotatably receiving two opposite trunnions of a first cross. A second end yoke is connected to a driven member or shaft and has two arms rotatably receiving two opposite trunnions of a second cross. A connecting yoke extends between the end yokes and has arms receiving opposite trunnions of both crosses, the latter trunnions being mutually perpendicular to the trunnions received in the arms of the end yokes.
In order to provide constant velocity between the drive and driven shafts, it is essential that their-angles of displacement, when out of alignment, be equal. Stated another way, the angles formed between the axes of rotation of t.he shafts and the axis of rotation of the connecting yoke must be equal. To accomplish this, centering means are provided between the two end yokes and located within the connecting yoke. Heretofore, such centering means usually have been in a form of a socket carried by one end yoke and a ball extending into the socket and carried by the other end yoke.
To achieve true constant velocity, the point of engagement of the ball and socket must be equally spaced from the axes of the cross trunnions held by the arms of the connecting yoke.
With the centering means heretofore employed, the compo-nents thereof must necessarily move apart as the drive and driven shafts move out of alignment to angular positions. The greater ~he angle, the more the components separate. With a ball and socket centering device, for example, the ball moves outwardly relative to the socket with the result that the point of contact or engagement therebetween no longer is equally spaced from the aforesaid trunnion axes. As a result, the angles of displacement of the drive and driv-en shafts are no longer precisely equal and, consequently, precise constant velocity is not achieved between the drive and driven shafts.
The present invention provides a double Cardan universal joint with centering means, the components of which are always en-gaged equally from the axes of the trunnions carried by the connect-ing yoke. Accordi~gly, one end yoke has a plurality of circular ridges or gear teeth facing the other end yoke with the center line of the gear teeth being coaxial with the axis of rotation of the one yoke and the drive or driven shaft to which it is connected. Simi-larly, the other end yoke has a plurality of circular ridges or gear teeth facing the one end yoke with the center line of those gear teeth being coaxial with the axis of rotation of the other yoke and the drive or driven shaft to which it i5 connected. The sets of teeth are displaced one-half gear tooth so that one gear tooth is en-gaged between two other gear teeth for cmy position of the end yokes and the drive and driven shafts. The gear teeth are also shaped in spherical segment arcuate patterns, the centers of which are located at the intersections of the axes of the trunnions of the two crosses.
Thus, any longitudinal cross section taken centrally through the gear teeth appears the same as a section through a spur gear se~ent.
The gear teeth are of a profile or shape such that the efEective points of engagement therebetween are always on the pitch radii of the gears, at the intersection with a line taken through the centers of the sets of gear teeth, such a profile being involute or other similar shape.
The new centering means not only provides more precise con-stant velocity between the drive and driven shafts but also provides more of a rolling contact and less of a sliding contact so that less frictional loss and probably less wear will result. The centering means also enables the crosses of the double Cardan joint to be closer together to achieve greater angularity. Further, there are no moving parts in the new centering device.
It is, therefore, a principal object of the invention to provide a double Cardan universal joint with improved centering means.
Another object of the invention is to provide a double Cardan universal joint achieving more precise constant velocity be-tween drive and driven members which are connected by the joint.
A further object of the invention is to provide centering lQ means for a double Cardan universal joint, the components of which are always in engagem~nt at equal distances from the intersections of axes of trunnions of crosses held by the yokes of the jloint.
Yet another object of the invention is to provide cen-tering means for a double Cardan universal joint in which the points of engagement of the centering components are on lines of action which intersect on a line extendin~ between axes of trunnions of crosses held by the yokes of the joint.
~ et a further object of the invention is to provide a double Cardan universal joint with centerin~ means in the form of 2Q circular gear teeth engaged with one another for any angular position of drive and driven shafts which the ~oint connects.
Still another object of ~he invention is to provide a universal joint with centering means having no moving parts.
Still a further object of the invention is to provide a universal joint with centering means having less frictional loss and wear.
Many other objects and advantages of the in~ention will be apparent from the following detailed description of a preferred em-bodiment thereof, reference being made to the accompanying drawings, 30in which:
Fig. 1 is a view in perspective of a double Cardan univer-sal ~oint embodyiny the ;nvention;
Fig. 2 is a side view, with parts broken away and with parts in section, of the universal joint of Fig. l;
Fig. 3 is a view similar to Fig. 2 with the universal joint rotated ninety degrees;
Fig. 4 is an enlarged, fragmentary view in cross section of centering means oE the universal joint; and Figs. 5 and 6 are enlarged face views of centering compo-nents of the universal joint.
Referring to the drawings, and particularly to Fig. 1, adouble Cardan universal joint embodying the invention is indicated at 10 and connects drive and driven shafts or members 12 and 14.
The universal joint 10 includes a first end yoke 16, a second end yoke 18, and a connecting yoke or member 20.
In this instance, the first end yoke 16 has a base or flange 22 which is affixed directly to 1~he shaft 12. However, the flange 22 can be separate and bolted to a flange on the shaft 12, if desired. A pair o~ arms 24 and 26 extend from the flange 22 and have bearing cups 23 and 30 mounted therein and held by retaining rings 32. A first cross 34 has opposite trunnions 36 and 38 ro-tatably held by the yoke arms 24 and 26. Speci~ically, the trunnions 36 and 38 are recei~ed in the bearing cups 28 and 30 which contain needle bearings 40 and have seals 42, as usual.
The cross 34 also has two opposite trunnions 44 and 46 which are mutually perpendicular to the trunnions 36 and 38 and also have an axis of rotation which is mutually perpendicular to an axis of rotation of the trunnions 36 and 38. The trunnions 44 and 46 are rotatably received in arms 48 and 50 of the connecting yoke 20 f the arms extending from a common ring 52 of the connecting yoke 20.
Specifically, the trunnions 44 and 46 are held in bearing cups 54 and 56, again having the needle bearings 40 and the seals 42.
At the opposite end, the connecting yoke 20 has arms 58 and 60 having bearing cups 62 and 64 with the usual needle bearings 40 and the seals 42. The arms rotatably receive trunnions 66 and 68 of a second cross 70, the trunnions rotating on an axis parallel to the axis of the trunnions 44 and 46 of the first cross 34.
The second cross 70 also has opposite trunnions 72 and 74 which are mutually perpendicular to the trunnions 66 and 68 and have mutally perpendicular axes of rotation. These trunnions are rotatably held in bearing cups 76 and 78 having the needle bearings 40 and the seals 42, with the cups received in arms 80 and 82 ex-tending from a base or flange 84 of the second end yoke 18. Like the flange 22, the flanye 8~ can be affixed directly ta the shaft 14 or it can be bolted to a separate flange on the shaft 14.
For the double Cardan joint 20 to achieve constant veloci-ty between the drive and driven shafts 12 and 14, the angle of displace-ment of the shafts must be equal. More specifically, the axis of rotation of the shaft 12 must form an angle with the axls of rotation of the connecting yoke, or a line drawn through the intersections of the axes of rotation of the trunnions~ of the first cross 34 and of the second cross 36, which angle is equal to -the angle formed by the axis of rotation of the shaft 14 with the same axis or line.
Stated another way, the connecting yoke must rotate on an axis which is perpendicular to a plane which bisects the angle formed by the two shafts. To maintain -the equal angular relationship and the constant velocity, centering means indicated at 86 is provided. Accordingly, an arcuate bridging member or web 88 extends from the ends of the arms 24 and 26 of the end yoke 16, being cast integrally with the arms. A simiiar bridging member or web ~0 similarly extends from the ends of the arms 80 and 82 of the end yoke 18. A replaceable centering member 92 has a threaded shank (Fig. 4) received in a threaded opening 96 in the web 8~ and a centering member 98 similarly has a shank 100 threadedly received in an opening 102 in the web 90.
A plurality of circular ridges or gear teeth 104 and 106 are formed on the member 92, there being just two circular teeth in this instance. An outer circular groove 108 is formed between them and a central tooth 110 is located within an inner circular groove 112.
Circular ridges or gear teeth 114 and 116 are also formed on the member 98, with an outer tooth 118 being a partial one. A
groove 120 is formed between the -teeth 116 and 118 and an inner groove 122 is formed between the teeth 114 and 116. A central xecess 124 which receives the central tooth 110 is formed by the tooth 116.
The circular teeth of the member 92 are offset one-half tooth from the teeth of the member 98 so that they can intermesh similar to teeth of conventional spur gears. The teeth have an involute profile or shape in cross section, or other suitable profile, such that the teeth of one web will engage the teeth of the other web substantially on lines of action which intersect on a line extending through the in-tersections of the trunnion rotational axes of the crosses 34 and 70.
The pitch radius of the teeth 102, 106, and 110 have the center at the intersection of the axes of rotr~tion of the trunnions ~4 and 46 and the pitch radius of the teeth 114, 116, and 118 have the center at the intersection of the axes of rotation of the trunnions 66 and 68. The teeth may not engage exact]y in the above manner r depending on the degree of precision in the machining of the teeth. Where precise con-stan-t velocity and quiet operation are not so important, the tooth pro-file can be rougher so that the teeth are more in the nature of ci~cular ridges ~ith circular grooves therebetween.
The teeth on each web are formed in the pattern or configu-ration of a segment of a sphere, the center of which coincides with the intersection of the axes of rotation of the trunnions of the respective croSs 34 or 70. In -this manner, the point of effective engagement of the teeth, where the lines of action intersect, will always be equi-distant from the aforesaid axes of rotation. This assures that the angles of displacement of the rotational axes of the shafts 12 and 14 will always be equal and that the shafts will rotate with precise constant velocity. This centering design also takes less room so that the crosses can be closer together. Not only is the universal joint -thus more compact but the shafts can rotate with greater angularity, about 45 versus 18, for example.
In addition, the gear teeth engage with a rolling motion and essentially no sliding motion than previous centering components to reduce frictional loss and probably result in less wear. Finally, the centering means has no moving parts.
The centering means 38 can be equipped with a grease boot or enclosure 126, if desired. This has two spaced bands 128 and 130 which are received in annular grooves 132 and 134 in the peripheries of the centering members 92 and 98.
Double Cardan universal joints are well known in the art and have the advantage of producing constant velocity between the drive and drlven members or shafts which they connect. A double Cardan universal joint includes a first end yoke connected to a drive mRmber or shaft and having two arms rotatably receiving two opposite trunnions of a first cross. A second end yoke is connected to a driven member or shaft and has two arms rotatably receiving two opposite trunnions of a second cross. A connecting yoke extends between the end yokes and has arms receiving opposite trunnions of both crosses, the latter trunnions being mutually perpendicular to the trunnions received in the arms of the end yokes.
In order to provide constant velocity between the drive and driven shafts, it is essential that their-angles of displacement, when out of alignment, be equal. Stated another way, the angles formed between the axes of rotation of t.he shafts and the axis of rotation of the connecting yoke must be equal. To accomplish this, centering means are provided between the two end yokes and located within the connecting yoke. Heretofore, such centering means usually have been in a form of a socket carried by one end yoke and a ball extending into the socket and carried by the other end yoke.
To achieve true constant velocity, the point of engagement of the ball and socket must be equally spaced from the axes of the cross trunnions held by the arms of the connecting yoke.
With the centering means heretofore employed, the compo-nents thereof must necessarily move apart as the drive and driven shafts move out of alignment to angular positions. The greater ~he angle, the more the components separate. With a ball and socket centering device, for example, the ball moves outwardly relative to the socket with the result that the point of contact or engagement therebetween no longer is equally spaced from the aforesaid trunnion axes. As a result, the angles of displacement of the drive and driv-en shafts are no longer precisely equal and, consequently, precise constant velocity is not achieved between the drive and driven shafts.
The present invention provides a double Cardan universal joint with centering means, the components of which are always en-gaged equally from the axes of the trunnions carried by the connect-ing yoke. Accordi~gly, one end yoke has a plurality of circular ridges or gear teeth facing the other end yoke with the center line of the gear teeth being coaxial with the axis of rotation of the one yoke and the drive or driven shaft to which it is connected. Simi-larly, the other end yoke has a plurality of circular ridges or gear teeth facing the one end yoke with the center line of those gear teeth being coaxial with the axis of rotation of the other yoke and the drive or driven shaft to which it i5 connected. The sets of teeth are displaced one-half gear tooth so that one gear tooth is en-gaged between two other gear teeth for cmy position of the end yokes and the drive and driven shafts. The gear teeth are also shaped in spherical segment arcuate patterns, the centers of which are located at the intersections of the axes of the trunnions of the two crosses.
Thus, any longitudinal cross section taken centrally through the gear teeth appears the same as a section through a spur gear se~ent.
The gear teeth are of a profile or shape such that the efEective points of engagement therebetween are always on the pitch radii of the gears, at the intersection with a line taken through the centers of the sets of gear teeth, such a profile being involute or other similar shape.
The new centering means not only provides more precise con-stant velocity between the drive and driven shafts but also provides more of a rolling contact and less of a sliding contact so that less frictional loss and probably less wear will result. The centering means also enables the crosses of the double Cardan joint to be closer together to achieve greater angularity. Further, there are no moving parts in the new centering device.
It is, therefore, a principal object of the invention to provide a double Cardan universal joint with improved centering means.
Another object of the invention is to provide a double Cardan universal joint achieving more precise constant velocity be-tween drive and driven members which are connected by the joint.
A further object of the invention is to provide centering lQ means for a double Cardan universal joint, the components of which are always in engagem~nt at equal distances from the intersections of axes of trunnions of crosses held by the yokes of the jloint.
Yet another object of the invention is to provide cen-tering means for a double Cardan universal joint in which the points of engagement of the centering components are on lines of action which intersect on a line extendin~ between axes of trunnions of crosses held by the yokes of the joint.
~ et a further object of the invention is to provide a double Cardan universal joint with centerin~ means in the form of 2Q circular gear teeth engaged with one another for any angular position of drive and driven shafts which the ~oint connects.
Still another object of ~he invention is to provide a universal joint with centering means having no moving parts.
Still a further object of the invention is to provide a universal joint with centering means having less frictional loss and wear.
Many other objects and advantages of the in~ention will be apparent from the following detailed description of a preferred em-bodiment thereof, reference being made to the accompanying drawings, 30in which:
Fig. 1 is a view in perspective of a double Cardan univer-sal ~oint embodyiny the ;nvention;
Fig. 2 is a side view, with parts broken away and with parts in section, of the universal joint of Fig. l;
Fig. 3 is a view similar to Fig. 2 with the universal joint rotated ninety degrees;
Fig. 4 is an enlarged, fragmentary view in cross section of centering means oE the universal joint; and Figs. 5 and 6 are enlarged face views of centering compo-nents of the universal joint.
Referring to the drawings, and particularly to Fig. 1, adouble Cardan universal joint embodying the invention is indicated at 10 and connects drive and driven shafts or members 12 and 14.
The universal joint 10 includes a first end yoke 16, a second end yoke 18, and a connecting yoke or member 20.
In this instance, the first end yoke 16 has a base or flange 22 which is affixed directly to 1~he shaft 12. However, the flange 22 can be separate and bolted to a flange on the shaft 12, if desired. A pair o~ arms 24 and 26 extend from the flange 22 and have bearing cups 23 and 30 mounted therein and held by retaining rings 32. A first cross 34 has opposite trunnions 36 and 38 ro-tatably held by the yoke arms 24 and 26. Speci~ically, the trunnions 36 and 38 are recei~ed in the bearing cups 28 and 30 which contain needle bearings 40 and have seals 42, as usual.
The cross 34 also has two opposite trunnions 44 and 46 which are mutually perpendicular to the trunnions 36 and 38 and also have an axis of rotation which is mutually perpendicular to an axis of rotation of the trunnions 36 and 38. The trunnions 44 and 46 are rotatably received in arms 48 and 50 of the connecting yoke 20 f the arms extending from a common ring 52 of the connecting yoke 20.
Specifically, the trunnions 44 and 46 are held in bearing cups 54 and 56, again having the needle bearings 40 and the seals 42.
At the opposite end, the connecting yoke 20 has arms 58 and 60 having bearing cups 62 and 64 with the usual needle bearings 40 and the seals 42. The arms rotatably receive trunnions 66 and 68 of a second cross 70, the trunnions rotating on an axis parallel to the axis of the trunnions 44 and 46 of the first cross 34.
The second cross 70 also has opposite trunnions 72 and 74 which are mutually perpendicular to the trunnions 66 and 68 and have mutally perpendicular axes of rotation. These trunnions are rotatably held in bearing cups 76 and 78 having the needle bearings 40 and the seals 42, with the cups received in arms 80 and 82 ex-tending from a base or flange 84 of the second end yoke 18. Like the flange 22, the flanye 8~ can be affixed directly ta the shaft 14 or it can be bolted to a separate flange on the shaft 14.
For the double Cardan joint 20 to achieve constant veloci-ty between the drive and driven shafts 12 and 14, the angle of displace-ment of the shafts must be equal. More specifically, the axis of rotation of the shaft 12 must form an angle with the axls of rotation of the connecting yoke, or a line drawn through the intersections of the axes of rotation of the trunnions~ of the first cross 34 and of the second cross 36, which angle is equal to -the angle formed by the axis of rotation of the shaft 14 with the same axis or line.
Stated another way, the connecting yoke must rotate on an axis which is perpendicular to a plane which bisects the angle formed by the two shafts. To maintain -the equal angular relationship and the constant velocity, centering means indicated at 86 is provided. Accordingly, an arcuate bridging member or web 88 extends from the ends of the arms 24 and 26 of the end yoke 16, being cast integrally with the arms. A simiiar bridging member or web ~0 similarly extends from the ends of the arms 80 and 82 of the end yoke 18. A replaceable centering member 92 has a threaded shank (Fig. 4) received in a threaded opening 96 in the web 8~ and a centering member 98 similarly has a shank 100 threadedly received in an opening 102 in the web 90.
A plurality of circular ridges or gear teeth 104 and 106 are formed on the member 92, there being just two circular teeth in this instance. An outer circular groove 108 is formed between them and a central tooth 110 is located within an inner circular groove 112.
Circular ridges or gear teeth 114 and 116 are also formed on the member 98, with an outer tooth 118 being a partial one. A
groove 120 is formed between the -teeth 116 and 118 and an inner groove 122 is formed between the teeth 114 and 116. A central xecess 124 which receives the central tooth 110 is formed by the tooth 116.
The circular teeth of the member 92 are offset one-half tooth from the teeth of the member 98 so that they can intermesh similar to teeth of conventional spur gears. The teeth have an involute profile or shape in cross section, or other suitable profile, such that the teeth of one web will engage the teeth of the other web substantially on lines of action which intersect on a line extending through the in-tersections of the trunnion rotational axes of the crosses 34 and 70.
The pitch radius of the teeth 102, 106, and 110 have the center at the intersection of the axes of rotr~tion of the trunnions ~4 and 46 and the pitch radius of the teeth 114, 116, and 118 have the center at the intersection of the axes of rotation of the trunnions 66 and 68. The teeth may not engage exact]y in the above manner r depending on the degree of precision in the machining of the teeth. Where precise con-stan-t velocity and quiet operation are not so important, the tooth pro-file can be rougher so that the teeth are more in the nature of ci~cular ridges ~ith circular grooves therebetween.
The teeth on each web are formed in the pattern or configu-ration of a segment of a sphere, the center of which coincides with the intersection of the axes of rotation of the trunnions of the respective croSs 34 or 70. In -this manner, the point of effective engagement of the teeth, where the lines of action intersect, will always be equi-distant from the aforesaid axes of rotation. This assures that the angles of displacement of the rotational axes of the shafts 12 and 14 will always be equal and that the shafts will rotate with precise constant velocity. This centering design also takes less room so that the crosses can be closer together. Not only is the universal joint -thus more compact but the shafts can rotate with greater angularity, about 45 versus 18, for example.
In addition, the gear teeth engage with a rolling motion and essentially no sliding motion than previous centering components to reduce frictional loss and probably result in less wear. Finally, the centering means has no moving parts.
The centering means 38 can be equipped with a grease boot or enclosure 126, if desired. This has two spaced bands 128 and 130 which are received in annular grooves 132 and 134 in the peripheries of the centering members 92 and 98.
Claims
5. In a double Cardan type universal joint for connecting two shafts, said. universal joint comprising a first end yoke, a second end yoke, a connecting yoke between said first end yoke and said second end yoke, a first cross having two aligned trun-nions rotatably held by said first end yoke and having two addi-tional aligned trunnions rotatably held by said connecting yoke, a second cross having two aligned trunnions rotatably held by said second end yoke and having two additional aligned trunnions rotat-ably held by said connecting yoke, and centering means between said first yoke and said second yoke, the improvement comprising said centering means being two concentric, circular ridges with a circular groove therebetween, a recess within the inner circular ridge, an outer partial ridge with a circular groove between the outer partial ridge and the outer circular ridge carried by said first end yoke and located on a center line coaxial with the axis of rotation of said first end yoke, said ridges and said grooves also being arcuately disposed in transverse cross section with the center of the arc being on the point where the axes of the trun-nions of said first cross intersect, and two concentric ridges with a circular groove therebetween, a central tooth, and a cir-cular groove between the central tooth and the inner circular ridge carried by said second end yoke and located on a center line coaxial with the axis of rotation of said second end yoke, and said ridges, tooth and grooves of said second end yoke being arcuately disposed in transverse cross section with the center of the arc being on the point where the axes of the trunnions of said second cross intersect.
6. The improvement according to claim 5 characterized by said ridges being in the shape of gear teeth.
7. The improvement according to claim 5 characterized by said ridges of each of said members being disposed in the shape of a segment of a sphere with the center at the intersection of the respective trunnion axes.
8. In a double Cardan type universal joint for connecting two shafts, said universal joint comprising a first end yoke, a second end yoke, a connecting yoke between said first end yoke and said second end yoke, a first cross having two aligned trunnions rotatably held by said first end yoke and having two additional aligned trunnions rotatably held by said connecting yoke, a second cross having two aligned trunnions rotatably held by said second end yoke and having two additional aligned trunnions rotatably held by said connecting yoke, and centering means between said first yoke and said second yoke, the improvement comprising said centering means being two concentric, circular gear teeth with a circular groove therebetween, and a recess within the inner circular gear tooth carried by said first end yoke and located on a center line coaxial with the axis of rotation of said first end yoke, said gear teeth and grooves also being disposed in the shape of a segment of a sphere with the center being on the point where the axes of the trunnions of said first cross intersect, and two concentric, circu-lar gear teeth with a circular groove therebetween, a central tooth, and a central groove between the central tooth and the inner circu-lar gear tooth carried by said second end yoke and located on a center line coaxial with the axis of rotation of said second end yoke, and being disposed in the shape of a segment of a sphere with the center being on the point where the axes of the trunnions of said second cross intersect.
9. The improvement according to claim 8 characterized by an outer partial circular gear tooth with a circular groove between the outer partial tooth and the outer circular tooth carried by said first end yoke.
10. The improvement according to claim 8 wherein said teeth having profiles such that the teeth on one yoke will always engage the teeth on the other yoke on lines of action which intersect on a line extending through the intersections of the trunnion rotational axes of the crosses.
11. The improvement according to claim 8 characterized by said first circular gear teeth and grooves being on a web which ex-tends between the outer ends of said first end yoke and said second circular gear teeth and grooves being on a web which extends between the outer ends of said second end yoke.
12. The improvement according to claim 11 characterized by the first circular gear teeth and grooves being formed in a center-ing member which is threadedly engaged with said first web and the second circular gear teeth and grooves being formed in a second centering member which is threadedly engaged with said second web.
13. The improvement according to claim 12 characterized by said centering members having annular grooves in portions extending beyond said webs, and a grease boot having two spaced circular bands received in said centering member grooves.
14. The improvement according to claim 11 characterized by said webs being cast integrally with their corresponding end yokes.
15. The improvement according to claim 11 characterized by said first circular gear teeth and grooves being formed in a center-ing member which is removably carried by said first web and said second circular gear teeth and grooves being formed on a second centering member which is removably carried by said second web.
16. The improvement according to claim 15 characterized by said first centering member being threadedly engaged with said first web and said second centering member being threadedly engaged with said second web.
17. The improvement according to claim 15 characterized by a grease boot extending between said first and second centering mem-bers and engaged with both.
18. The improvement according to claim 17 characterized by a grease boot having two spaced circular bands and said centering mem-bers having annular grooves receiving said bands.
6. The improvement according to claim 5 characterized by said ridges being in the shape of gear teeth.
7. The improvement according to claim 5 characterized by said ridges of each of said members being disposed in the shape of a segment of a sphere with the center at the intersection of the respective trunnion axes.
8. In a double Cardan type universal joint for connecting two shafts, said universal joint comprising a first end yoke, a second end yoke, a connecting yoke between said first end yoke and said second end yoke, a first cross having two aligned trunnions rotatably held by said first end yoke and having two additional aligned trunnions rotatably held by said connecting yoke, a second cross having two aligned trunnions rotatably held by said second end yoke and having two additional aligned trunnions rotatably held by said connecting yoke, and centering means between said first yoke and said second yoke, the improvement comprising said centering means being two concentric, circular gear teeth with a circular groove therebetween, and a recess within the inner circular gear tooth carried by said first end yoke and located on a center line coaxial with the axis of rotation of said first end yoke, said gear teeth and grooves also being disposed in the shape of a segment of a sphere with the center being on the point where the axes of the trunnions of said first cross intersect, and two concentric, circu-lar gear teeth with a circular groove therebetween, a central tooth, and a central groove between the central tooth and the inner circu-lar gear tooth carried by said second end yoke and located on a center line coaxial with the axis of rotation of said second end yoke, and being disposed in the shape of a segment of a sphere with the center being on the point where the axes of the trunnions of said second cross intersect.
9. The improvement according to claim 8 characterized by an outer partial circular gear tooth with a circular groove between the outer partial tooth and the outer circular tooth carried by said first end yoke.
10. The improvement according to claim 8 wherein said teeth having profiles such that the teeth on one yoke will always engage the teeth on the other yoke on lines of action which intersect on a line extending through the intersections of the trunnion rotational axes of the crosses.
11. The improvement according to claim 8 characterized by said first circular gear teeth and grooves being on a web which ex-tends between the outer ends of said first end yoke and said second circular gear teeth and grooves being on a web which extends between the outer ends of said second end yoke.
12. The improvement according to claim 11 characterized by the first circular gear teeth and grooves being formed in a center-ing member which is threadedly engaged with said first web and the second circular gear teeth and grooves being formed in a second centering member which is threadedly engaged with said second web.
13. The improvement according to claim 12 characterized by said centering members having annular grooves in portions extending beyond said webs, and a grease boot having two spaced circular bands received in said centering member grooves.
14. The improvement according to claim 11 characterized by said webs being cast integrally with their corresponding end yokes.
15. The improvement according to claim 11 characterized by said first circular gear teeth and grooves being formed in a center-ing member which is removably carried by said first web and said second circular gear teeth and grooves being formed on a second centering member which is removably carried by said second web.
16. The improvement according to claim 15 characterized by said first centering member being threadedly engaged with said first web and said second centering member being threadedly engaged with said second web.
17. The improvement according to claim 15 characterized by a grease boot extending between said first and second centering mem-bers and engaged with both.
18. The improvement according to claim 17 characterized by a grease boot having two spaced circular bands and said centering mem-bers having annular grooves receiving said bands.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US4077479A | 1979-05-21 | 1979-05-21 | |
| US040,774 | 1979-05-21 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1125043A true CA1125043A (en) | 1982-06-08 |
Family
ID=21912871
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA351,891A Expired CA1125043A (en) | 1979-05-21 | 1980-05-14 | Double cardan universal joint with improved centering means |
Country Status (4)
| Country | Link |
|---|---|
| CA (1) | CA1125043A (en) |
| DE (1) | DE3019413A1 (en) |
| FR (1) | FR2457411A1 (en) |
| GB (1) | GB2052681B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4352276A (en) * | 1980-12-15 | 1982-10-05 | Borg-Warner Corporation | Constant velocity universal joint with improved centering device and boot seal |
| GB2096736B (en) * | 1981-04-15 | 1984-12-19 | Zeller Corp | Double universal joint |
| CN102913560A (en) * | 2011-08-01 | 2013-02-06 | 上海五同机械制造有限公司 | Universal coupler |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB377760A (en) * | 1931-03-09 | 1932-08-04 | Birger Ljungstroem | Improvements in or relating to deflectable power transmission mechanism |
| US2987896A (en) * | 1959-03-30 | 1961-06-13 | Ford Motor Co | Double universal joint |
| DE2105751A1 (en) * | 1970-04-13 | 1971-10-28 | Barkas Werke Veb | HOMOKINETIC LARGE-ANGLE JOINT |
| FR2061305A5 (en) * | 1970-09-11 | 1971-06-18 | Dba |
-
1980
- 1980-05-14 CA CA351,891A patent/CA1125043A/en not_active Expired
- 1980-05-20 FR FR8011271A patent/FR2457411A1/en active Pending
- 1980-05-21 GB GB8016842A patent/GB2052681B/en not_active Expired
- 1980-05-21 DE DE19803019413 patent/DE3019413A1/en not_active Withdrawn
Also Published As
| Publication number | Publication date |
|---|---|
| GB2052681B (en) | 1982-12-15 |
| DE3019413A1 (en) | 1980-11-27 |
| FR2457411A1 (en) | 1980-12-19 |
| GB2052681A (en) | 1981-01-28 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |