CA2451899A1 - A gear coupler with a controllable roller clutch - Google Patents
A gear coupler with a controllable roller clutch Download PDFInfo
- Publication number
- CA2451899A1 CA2451899A1 CA002451899A CA2451899A CA2451899A1 CA 2451899 A1 CA2451899 A1 CA 2451899A1 CA 002451899 A CA002451899 A CA 002451899A CA 2451899 A CA2451899 A CA 2451899A CA 2451899 A1 CA2451899 A1 CA 2451899A1
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- Canada
- Prior art keywords
- cage
- race
- inner race
- gear coupler
- ring
- 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.)
- Abandoned
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- 230000005540 biological transmission Effects 0.000 claims abstract description 11
- 239000002253 acid Substances 0.000 claims 1
- 238000006073 displacement reaction Methods 0.000 description 3
- 241001274197 Scatophagus argus Species 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000005096 rolling process 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
- F16D15/00—Clutches with wedging balls or rollers or with other wedgeable separate clutching members
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- 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
- F16D41/00—Freewheels or freewheel clutches
- F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
- F16D41/08—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action
- F16D41/086—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action the intermediate members being of circular cross-section and wedging by rolling
- F16D41/088—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action the intermediate members being of circular cross-section and wedging by rolling the intermediate members being of only one size and wedging by a movement not having an axial component, between inner and outer races, one of which is cylindrical
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
- Friction Gearing (AREA)
Abstract
A gear coupler for a power transmission comprises an outer race having an cylindrical inner surface and an inner race having a cylindrical outer surface with spaced apart ramped surfaces. A plurality of rollers are seated between the inner and outer race.
A controllable cage has a plurality of cage pins seated between adjacent pairs of rollers and engages the rollers with the ramped surfaces. A shifting ring is coupled to the cage for axial movement therealong for selectively aligning the rollers between the ramped surfaces to disengage the inner race from the outer race and allow relative rotation therebetween and for wedging the rollers against the ramped surface to engage the inner race with the outer race and prevent relative rotation therebetween in response to varying rotational speeds of the inner and outer race.
A controllable cage has a plurality of cage pins seated between adjacent pairs of rollers and engages the rollers with the ramped surfaces. A shifting ring is coupled to the cage for axial movement therealong for selectively aligning the rollers between the ramped surfaces to disengage the inner race from the outer race and allow relative rotation therebetween and for wedging the rollers against the ramped surface to engage the inner race with the outer race and prevent relative rotation therebetween in response to varying rotational speeds of the inner and outer race.
Description
A GEAR COUPLER WITH A CONTROLLABLE ROLLER CLUTCH
BACKGROUND OF THE INVENTION
1. I~eld of Invention The subject invention relates to a gear coupler for a powered automotive transmission_ 2. Description of the Related Art Automotive power transmissions typically include a dog clutch with $
synchroni2er for changing speeds in a manual transmission or a disk clutch with discs made of frictional materials for changing speeds in an automatic transmission. These dog clutches and disk clutches are widely applied to engage or disengage two power transmission gears or shafts.
These clutches are commonly referred to as gear couplers and are comparatively complicated in construction and expensive to manufacture. Therefore, it is desirable to provide a cost-effective, simplified and efficient gear coupler for power transmissions utilizing a roller clutch which can engage and disengage two power transmission shafts.
SUMMARY OF THE INVENTION
According to o~c aspect of the invention there is provided a gear coupler for a power transmission comprising an outer race having an cylindrical inner surface and an inner race having a cylindrical outer surface with spaced apart tamped surfaces. A
plurality of rollers arc seated between the inner and outer race. A controllable cage having a plurality of cage pins seated between adjacent pairs of rollers engages the rollers with the tamped surfaces. A shifting ring is coupled to the cage for axial movement therealong for selectively aligning the rollers lxtween the tamped surfaces to disengage the inner race frarn the outer race and allow relative rotation thcrebetween and for wedging the rollers against the tamped surface to engage the inner race with the outer race and prevent relative rotation therebetween in response to varying rotational speeds of the inner and outer race.
BRIEF DESCRIPTION OF THE DRAWINGS
3253916v3 Advantages of the present invention will be readily appreciated as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings wherein:
Figure 1 is an exploded view of a gear coupler according to one aspect of the invention;
Figure 2a is an end view of the gear coupler of l~gurc 1;
Pigure 2b is a crass-sectional view taken along line A-A of Figure 2a;
Figure 3a is a side view of the gear coupler, Figure 3b is a cross-sectional view taken along line B-B of Figure 3a;
Figure 4 is an assembled view of the controllable cage of Figure 1;
Figure S is a side view of the shifting ring of Figure 1;
Figure 6a is a side view of the inner race and outer race disengaged;
Figure 6b is a fragmentary view of the cage with the inner race and outer race disengaged;
Figure 7a is a side view of the inner race and outer race engaged; and Figure 7b is a fragmentary view of the cage with the inner race and outer race engaged.
DETAILTD DESCRIPTION OF TIC PREFERR)~D EMBODI1VIENT
lZeferrlng to Figure 1, the subject invention relates to a gear coupler generally shown at.
far uae with a rolling clutch and chifting mechanism of a power transmission.
The gear coupler 1Q comprises an inner race 12, an outer race 14, and a plurality of elongated rollers I6 far reducing friction between the inntr 12 and outer 14 races. In the preferred embodiment, the inner raec 12 includes a cylindrical outer surface 18, while the outer race 14 includes a cylindrical inner surface 20, as shown in Figures 6b and 7b. It should be noted, however, that she invention described herein could be practiced using an inner race 12 and an outer race 14 of other shapes. Additionally, while the preferred embodiment contemplates cylindrical rollers 16, the rollers 16 need not be cylindrical for the invention to operate. indeed, any type of friction reducing meehanisra known in the art may be used to accomplish the same inventive concept.
The inner race 12 comprises a slotted portion 22 and a support portion 24. A
slot 26 is formed in the slotted portion 22 for aligning the inner race 12 as described below. The support portion 24 includes a plurality of ramped surfaces 28 disposed about the cylindrical surface 18 in 3253916v3 the shifting ring 30, the cage 3$ and the inner race 12 are also unable to rotate. As the shifting ring 30, and thus the pins 32, are moved axially, the shifting ring 30 shifts in a longitudinal direction, allowing the pins 32 to travel along the cam notches 48 to the upper sections 52. The larger diameter of the upper sections 52 allows angular movement of the shifting ring 30, the cage 38 and the inner race 12.
Referring to Figunas 3a, 3b, 6a, 6b, 7a and 7b, the cage pins 44 and rollers 1b are alternatingly arranged between the inner race 12 and the outer race 14. A
disengaged condition, wherein the inner race 12 and the outer race 14 are not in engagement with one another, exists when the shifting pins 3Z are seated in the bottom section of the cam notches 4$. Yn this condition, the rollers 16 rest atop the cylindrical surface 18 between adjacent romped surfaces 28 and are free to rotate between the innor race 12 and the outer race 14. Since the pins 32 are unable to rntate, the shifting ring 30, the cage 38 and the inner race 12 are similarly restrained, and the rollers 16 maintain their position atop the cylindrical surface 1$.
An engaged condition is created by actuation of the shifting ring 30. When the shifting ring 30 is actuated into axial movement, the pins 32 follow along the cam notches 48 to reach the upper sections 52 of the cam notches 48, thereby translating the displacement of the shifting ring 30 into rotational displaeell~ent of the cage 38. The cage 38 than rotates freely about tho inner race 12. Rotation of the cage 38 may occur through inertia, through the application of a frictional drag torque from a wave spring, or through any other means known in the art. As the cage 38 rotates, the cage pins 44 attached thereto also rotate. As the cage pins 44 contact the rollers 16, and the rollers 16 move around the inner race 12 to contact the romped surfaces 28 an the cylindrical surface 1 $. The rollers 16 then become wedged between the cylindrical surface 20 and the romped surfaces 28, thereby engaging the inner race 12 and the outer race i4 when the races 12, 14 rotate at different speeds.
Therefore, by axially shifting the shifting ring 3a, the inner race 12 and the outer race 14 are trroved from a disengaged condition to an engaged condition, dependent upon the position of the shifting ring 30, for operation of the gear coupler i0. It should be appreciated that the shifting ring 30 can be actuated by mechanical or electro-.mechanical mechanisms.
32539t6v3 19343!'095206 a spaced arrangement such that a portion of the cylindrical surface 18 lies between each two adjacent ramped surfaces 28, as shown in Figures 6b and ?b.
The gear coupler 10 further comprises a shifting ring 30 for moving. the inner race 12 and the outer race 14 between an engaged condition and a disengaged condition. Two shifting pins 32, each pin 32 including an interior end 34 and an exterior end 36, extend through the shifting ring 30 for aligning the shifting ring 30 and the inner race 12. In the preferred embadiment, the interior ends 34 of the shifting pins 32 fit within the slots 26 on the slotted portion 22 of the inner race 12. However, any portion of the pins 32 may contact the inner race 12 to effect the alignment of the shifting ring 30 and the inner race 12.
The gear coupler 10 further comprises a controllable miler cage 3$ comprising a cage ring 40, a cage plate 42, and a plurality of elongated, cylindrical, spaced apart cage pins 44.
extending between the cage ring 40 and the cage plate 42. As with the rollers 4, the cage pins 44 need not be cylindrical for the invention to operate. As best shown in Figure 4, the roller c$ge 38 further comprises a pair of cam plates 46 longitudinally extending from the cage ring 40. each plate 46 includes a cam notch 48 for receiving one of the shifting pins 32 to align the cage 38 with the inner race 12 and the shifting ring 30. In the preferred. embodiment, the exterior ends 36 of the pins 32 scat within the cam notches 48. However, any portion of the pins 32 may scat within tho cam notches 48 to align tha cage 38 and the shifting sang 30. $ach cam notch 48 comprises a lower section SO having a diameter essenrially equal to the diameter of the pins 32.
and an upper section 52 having a diameter larger than the pins 32.
The gear coupler 10 finally comprises an end cap 54 greferably seated within the outer race 14 just beyond the cage place 42 and a retaining ring 36 seated between the shifting ring 30 and the cage ring 40.
As shown in Figure 5, the two shifting pins 32 are tightly fitted into the shifting ring 30, preferably through openings formed within the shifting ring 5, although the pins 32 may be continuous with the shifting ring 30. The shifting pins 32 acts a cam followers in the cam notches 48 to translate linear, or axial, displacement of the shifting ring 30 into angular, or rotational, displacement of the cage 38. Specifically, when the pins 32 are seated in the lower section 54 of the cam notches 48, the angular mavcmcnt of the pins 32 is limited, and therefore, 3253916v3 1 fl94S149r5~~06 The invention has been described hare in an illustrative manner, and it is to be understood that the terminology used is intended to be in the nature of words or description rather than limitation. For instance, the invention may be accomplished using only one pin 32, necessftating the use of only one cam plate 46 and associated cam notch 48, and only one slot 26.
Furthermore, it should be appreciated that the invention may be practiced using only one roller 1+i or anE cage pin 44.
Many modifications and variations of the present invention are possible in light of the above teachings. It is, therefore, to be understood that within the scope of the appended claims, the invention may be practiced other than as sgeeifieally described herein.
3253916v3 !93+3!093206
BACKGROUND OF THE INVENTION
1. I~eld of Invention The subject invention relates to a gear coupler for a powered automotive transmission_ 2. Description of the Related Art Automotive power transmissions typically include a dog clutch with $
synchroni2er for changing speeds in a manual transmission or a disk clutch with discs made of frictional materials for changing speeds in an automatic transmission. These dog clutches and disk clutches are widely applied to engage or disengage two power transmission gears or shafts.
These clutches are commonly referred to as gear couplers and are comparatively complicated in construction and expensive to manufacture. Therefore, it is desirable to provide a cost-effective, simplified and efficient gear coupler for power transmissions utilizing a roller clutch which can engage and disengage two power transmission shafts.
SUMMARY OF THE INVENTION
According to o~c aspect of the invention there is provided a gear coupler for a power transmission comprising an outer race having an cylindrical inner surface and an inner race having a cylindrical outer surface with spaced apart tamped surfaces. A
plurality of rollers arc seated between the inner and outer race. A controllable cage having a plurality of cage pins seated between adjacent pairs of rollers engages the rollers with the tamped surfaces. A shifting ring is coupled to the cage for axial movement therealong for selectively aligning the rollers lxtween the tamped surfaces to disengage the inner race frarn the outer race and allow relative rotation thcrebetween and for wedging the rollers against the tamped surface to engage the inner race with the outer race and prevent relative rotation therebetween in response to varying rotational speeds of the inner and outer race.
BRIEF DESCRIPTION OF THE DRAWINGS
3253916v3 Advantages of the present invention will be readily appreciated as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings wherein:
Figure 1 is an exploded view of a gear coupler according to one aspect of the invention;
Figure 2a is an end view of the gear coupler of l~gurc 1;
Pigure 2b is a crass-sectional view taken along line A-A of Figure 2a;
Figure 3a is a side view of the gear coupler, Figure 3b is a cross-sectional view taken along line B-B of Figure 3a;
Figure 4 is an assembled view of the controllable cage of Figure 1;
Figure S is a side view of the shifting ring of Figure 1;
Figure 6a is a side view of the inner race and outer race disengaged;
Figure 6b is a fragmentary view of the cage with the inner race and outer race disengaged;
Figure 7a is a side view of the inner race and outer race engaged; and Figure 7b is a fragmentary view of the cage with the inner race and outer race engaged.
DETAILTD DESCRIPTION OF TIC PREFERR)~D EMBODI1VIENT
lZeferrlng to Figure 1, the subject invention relates to a gear coupler generally shown at.
far uae with a rolling clutch and chifting mechanism of a power transmission.
The gear coupler 1Q comprises an inner race 12, an outer race 14, and a plurality of elongated rollers I6 far reducing friction between the inntr 12 and outer 14 races. In the preferred embodiment, the inner raec 12 includes a cylindrical outer surface 18, while the outer race 14 includes a cylindrical inner surface 20, as shown in Figures 6b and 7b. It should be noted, however, that she invention described herein could be practiced using an inner race 12 and an outer race 14 of other shapes. Additionally, while the preferred embodiment contemplates cylindrical rollers 16, the rollers 16 need not be cylindrical for the invention to operate. indeed, any type of friction reducing meehanisra known in the art may be used to accomplish the same inventive concept.
The inner race 12 comprises a slotted portion 22 and a support portion 24. A
slot 26 is formed in the slotted portion 22 for aligning the inner race 12 as described below. The support portion 24 includes a plurality of ramped surfaces 28 disposed about the cylindrical surface 18 in 3253916v3 the shifting ring 30, the cage 3$ and the inner race 12 are also unable to rotate. As the shifting ring 30, and thus the pins 32, are moved axially, the shifting ring 30 shifts in a longitudinal direction, allowing the pins 32 to travel along the cam notches 48 to the upper sections 52. The larger diameter of the upper sections 52 allows angular movement of the shifting ring 30, the cage 38 and the inner race 12.
Referring to Figunas 3a, 3b, 6a, 6b, 7a and 7b, the cage pins 44 and rollers 1b are alternatingly arranged between the inner race 12 and the outer race 14. A
disengaged condition, wherein the inner race 12 and the outer race 14 are not in engagement with one another, exists when the shifting pins 3Z are seated in the bottom section of the cam notches 4$. Yn this condition, the rollers 16 rest atop the cylindrical surface 18 between adjacent romped surfaces 28 and are free to rotate between the innor race 12 and the outer race 14. Since the pins 32 are unable to rntate, the shifting ring 30, the cage 38 and the inner race 12 are similarly restrained, and the rollers 16 maintain their position atop the cylindrical surface 1$.
An engaged condition is created by actuation of the shifting ring 30. When the shifting ring 30 is actuated into axial movement, the pins 32 follow along the cam notches 48 to reach the upper sections 52 of the cam notches 48, thereby translating the displacement of the shifting ring 30 into rotational displaeell~ent of the cage 38. The cage 38 than rotates freely about tho inner race 12. Rotation of the cage 38 may occur through inertia, through the application of a frictional drag torque from a wave spring, or through any other means known in the art. As the cage 38 rotates, the cage pins 44 attached thereto also rotate. As the cage pins 44 contact the rollers 16, and the rollers 16 move around the inner race 12 to contact the romped surfaces 28 an the cylindrical surface 1 $. The rollers 16 then become wedged between the cylindrical surface 20 and the romped surfaces 28, thereby engaging the inner race 12 and the outer race i4 when the races 12, 14 rotate at different speeds.
Therefore, by axially shifting the shifting ring 3a, the inner race 12 and the outer race 14 are trroved from a disengaged condition to an engaged condition, dependent upon the position of the shifting ring 30, for operation of the gear coupler i0. It should be appreciated that the shifting ring 30 can be actuated by mechanical or electro-.mechanical mechanisms.
32539t6v3 19343!'095206 a spaced arrangement such that a portion of the cylindrical surface 18 lies between each two adjacent ramped surfaces 28, as shown in Figures 6b and ?b.
The gear coupler 10 further comprises a shifting ring 30 for moving. the inner race 12 and the outer race 14 between an engaged condition and a disengaged condition. Two shifting pins 32, each pin 32 including an interior end 34 and an exterior end 36, extend through the shifting ring 30 for aligning the shifting ring 30 and the inner race 12. In the preferred embadiment, the interior ends 34 of the shifting pins 32 fit within the slots 26 on the slotted portion 22 of the inner race 12. However, any portion of the pins 32 may contact the inner race 12 to effect the alignment of the shifting ring 30 and the inner race 12.
The gear coupler 10 further comprises a controllable miler cage 3$ comprising a cage ring 40, a cage plate 42, and a plurality of elongated, cylindrical, spaced apart cage pins 44.
extending between the cage ring 40 and the cage plate 42. As with the rollers 4, the cage pins 44 need not be cylindrical for the invention to operate. As best shown in Figure 4, the roller c$ge 38 further comprises a pair of cam plates 46 longitudinally extending from the cage ring 40. each plate 46 includes a cam notch 48 for receiving one of the shifting pins 32 to align the cage 38 with the inner race 12 and the shifting ring 30. In the preferred. embodiment, the exterior ends 36 of the pins 32 scat within the cam notches 48. However, any portion of the pins 32 may scat within tho cam notches 48 to align tha cage 38 and the shifting sang 30. $ach cam notch 48 comprises a lower section SO having a diameter essenrially equal to the diameter of the pins 32.
and an upper section 52 having a diameter larger than the pins 32.
The gear coupler 10 finally comprises an end cap 54 greferably seated within the outer race 14 just beyond the cage place 42 and a retaining ring 36 seated between the shifting ring 30 and the cage ring 40.
As shown in Figure 5, the two shifting pins 32 are tightly fitted into the shifting ring 30, preferably through openings formed within the shifting ring 5, although the pins 32 may be continuous with the shifting ring 30. The shifting pins 32 acts a cam followers in the cam notches 48 to translate linear, or axial, displacement of the shifting ring 30 into angular, or rotational, displacement of the cage 38. Specifically, when the pins 32 are seated in the lower section 54 of the cam notches 48, the angular mavcmcnt of the pins 32 is limited, and therefore, 3253916v3 1 fl94S149r5~~06 The invention has been described hare in an illustrative manner, and it is to be understood that the terminology used is intended to be in the nature of words or description rather than limitation. For instance, the invention may be accomplished using only one pin 32, necessftating the use of only one cam plate 46 and associated cam notch 48, and only one slot 26.
Furthermore, it should be appreciated that the invention may be practiced using only one roller 1+i or anE cage pin 44.
Many modifications and variations of the present invention are possible in light of the above teachings. It is, therefore, to be understood that within the scope of the appended claims, the invention may be practiced other than as sgeeifieally described herein.
3253916v3 !93+3!093206
Claims (20)
1. A gear coupler for a power transmission comprising:
an outer race having a cylindrical inner surface;
an inner race having a cylindrical outer surface with spaced apart ramped surfaces;
a plurality of rollers seated between said inner and outer race;
a controllable cage having a plurality of cage pins alternately stated between adjacent pairs of rollers for engaging said rollers with said ramped surfaces; and a shifting ring coupled to said cage for axial movement therealong for selectively aligning said rollers between said ramped surfaces to disengage said inner race from said outer race and allow relative rotation therebetween and for wedging said rollers against said ramped surface to engage said inner race with said outer race and prevent relative rotation therebetween in response to varying rotational speeds of said inner and outer races.
an outer race having a cylindrical inner surface;
an inner race having a cylindrical outer surface with spaced apart ramped surfaces;
a plurality of rollers seated between said inner and outer race;
a controllable cage having a plurality of cage pins alternately stated between adjacent pairs of rollers for engaging said rollers with said ramped surfaces; and a shifting ring coupled to said cage for axial movement therealong for selectively aligning said rollers between said ramped surfaces to disengage said inner race from said outer race and allow relative rotation therebetween and for wedging said rollers against said ramped surface to engage said inner race with said outer race and prevent relative rotation therebetween in response to varying rotational speeds of said inner and outer races.
2. A gear coupler as set forth in claim 1 wherein said inner race includes a support portion defining said ramped surfaces and a slotted portion extending axially from said support portion and having a slot longitudinally disposed therealong.
3. A gear coupler as set forth in claim 2 wherein said shifting ring includes a cylindrical center opening for axially receiving said slotted portion of said inner therein and a shifting pin projected radially therefrom and received in said longitudinal slot of said inner race.
4. A gear coupler as set forth in claim 3 wherein said cage includes a cage ring spaced longitudinally from a cage plate and said rollers rotatably coupled therebetween and seated between said inner and outer race.
5. A gear coupler as set forth in claim 4 wherein said cage includes a cam plate projecting longitudinally from acid cage ring; said cam plate including a generally V-shaped cam notch for cooperating with said shifting pin as said shifting ring moves axially along said cage.
6. A gear coupler as set forth in claim 5 wherein said cam notch includes a lower section spaced to cage said shifting pin and prevent rotational movement therebetween and an upper contoured section spaced to allow rotation movement of said cage relative to said shifting ring, whereby said axial movement of said shifting ring relative to said cage to position said shifting pin in said lower section of said cam notch aligns said rollers between said ramped surfaces of said inner race to disengage and allow relative rotation between said inner and outer race and axial movement of said shifting ring to position said shifting pin in said upper section allows rotation of said cage to wedge said rollers against said ramped surface between said inner and outer race to prevent relative rotation therebetween.
7. A gear coupler for a power transmission, said gear coupler 10 comprising:
an inner race comprising a slotted section, said slotted section including a slot longitudinally disposed therealong;
an outer race rotatably coupled to said inner race:
a shifting ring for engaging said inner race and said outer race;
a cage longitudinally disposed between said inner race and said outer race, said cage comprising a cage ring and a cam plate extending longitudinally from said cage ring:
a cam notch disposed on said cam plate; and a shifting pin positioned through said shifting ring such that said pin seats within said slot and said cam notch, thereby selectively aligning said shifting ring, said inner race and said cage, wherein said shifting pin follows along said cam notch in response to axial movement of said shifting ring to show rotation of said cage about said inner race.
an inner race comprising a slotted section, said slotted section including a slot longitudinally disposed therealong;
an outer race rotatably coupled to said inner race:
a shifting ring for engaging said inner race and said outer race;
a cage longitudinally disposed between said inner race and said outer race, said cage comprising a cage ring and a cam plate extending longitudinally from said cage ring:
a cam notch disposed on said cam plate; and a shifting pin positioned through said shifting ring such that said pin seats within said slot and said cam notch, thereby selectively aligning said shifting ring, said inner race and said cage, wherein said shifting pin follows along said cam notch in response to axial movement of said shifting ring to show rotation of said cage about said inner race.
8. A gear coupler as set forth in claim 7 further comprising a roller disposed between said inner race and said outer race far reducing friction between said inner race and said outer race, said roller being freely tolerable when said inner race and said outer race are disengaged.
9. A gear coupler as set forth in claim 8 wherein said cage further comprises a cage pin extending longitudinally from said cage ring such that rotation of said cage rotates said cage pin around said inner race.
10. A gear coupler as set forth in claim 9 wherein said cage pin is disposed between said inner race and said outer race adjacent said roller such that rotation of said cage pin around said inner race causes rotation of said roller around said inner race.
11. A gear coupler as set forth in claim 10 wherein a plurality of said rollers and a plurality of said cage pins are alternatingly disposed between said inner race and said outer race.
12. A gear coupler as set forth in claim 11 wherein said inner race further comprises a support section, said support section having a ramped surface disposed thereon such that said roller wedges between said ramped surface and said outer race to engage said inner race and said outer race.
13. A gear coupler as set forth in claim 12 wherein a plurality of said ramped surfaces are disposed about said support section, said ramped surfaces being spaced apart.
14. A gear coupler as set forth in claim 13 wherein said cage further comprises a cage plate longitudinally spaced from said cage ring such that said cage pin extends longitudinally from said cage ring to said cage plate.
15. A gear coupler as set forth in claim 14 wherein said cage plate 14 rests within said outer race.
16. A gear coupler as set forth in claim 15 further comprising an end cap disposed adjacent said cage ring.
17. A gear coupler as set forth in claim 16 wherein said end cap rests within said outer race.
18. A gear coupler as set forth in claim 17 further comprising a retaining ring disposed between said shifting ring and said cage ring.
19. A gear coupler as set forth in claim 18 wherein said inner race further comprises a generally cylindrical outer surface.
20. A gear coupler as set forth in claim 19 wherein said outer race comprises a generally cylindrical inner surface.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US43236502P | 2002-12-10 | 2002-12-10 | |
| US60/432,365 | 2002-12-10 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2451899A1 true CA2451899A1 (en) | 2004-06-10 |
Family
ID=32507911
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002451899A Abandoned CA2451899A1 (en) | 2002-12-10 | 2003-12-02 | A gear coupler with a controllable roller clutch |
Country Status (2)
| Country | Link |
|---|---|
| US (1) | US6997296B2 (en) |
| CA (1) | CA2451899A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2008046738A1 (en) | 2006-10-19 | 2008-04-24 | Zf Friedrichshafen Ag | Device for rotationally fixedly connecting a shaft to a component which is rotatably mounted on the shaft |
| DE102006049283A1 (en) * | 2006-10-19 | 2008-04-30 | Zf Friedrichshafen Ag | Device for torque proof connection of shaft, has rotating component, supported on shaft to connect gearwheel, designed as idle wheel of gear step of transmission device with drive shaft, where actuating element slides in axial direction |
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| EP1704344A2 (en) * | 2004-01-14 | 2006-09-27 | Timken US Corporation | Four wheel drive system |
| DE102007051735A1 (en) | 2006-10-26 | 2008-04-30 | Schaeffler Kg | Bidirectional overrunning clutch with controlled locking |
| CA2669278C (en) * | 2006-10-31 | 2015-04-28 | Magna Powertrain Usa, Inc. | Synchronized gear shift system |
| US20100320054A1 (en) * | 2009-06-22 | 2010-12-23 | D Eredita Michael A | Low rpm, mechanical, one-way drive, two-way overrunning clutch |
| US20110278133A1 (en) * | 2010-05-12 | 2011-11-17 | Top Gearbox Industry Co., Ltd | Gapless main shaft locking apparatus |
| CN111466812B (en) * | 2020-05-11 | 2021-08-17 | 新疆华庭工贸有限公司 | Suction and discharge integrated environment-friendly toilet system |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5393241A (en) * | 1977-01-26 | 1978-08-16 | Aisin Seiki Co Ltd | Car free wheel hub |
| JPS5649771Y2 (en) * | 1977-07-27 | 1981-11-20 | ||
| US6173824B1 (en) * | 1998-12-07 | 2001-01-16 | General Dynamics Government Systems Corporation | Rolling-element clutch assembly |
| US6814198B2 (en) * | 2000-04-20 | 2004-11-09 | Tesma International Inc. | Multi-directional coupling |
| US6550594B1 (en) * | 2000-11-01 | 2003-04-22 | Gkn Automotive, Inc. | Active pin slot index system for a bidirectional clutch |
-
2003
- 2003-12-02 CA CA002451899A patent/CA2451899A1/en not_active Abandoned
- 2003-12-10 US US10/732,766 patent/US6997296B2/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2008046738A1 (en) | 2006-10-19 | 2008-04-24 | Zf Friedrichshafen Ag | Device for rotationally fixedly connecting a shaft to a component which is rotatably mounted on the shaft |
| DE102006049283A1 (en) * | 2006-10-19 | 2008-04-30 | Zf Friedrichshafen Ag | Device for torque proof connection of shaft, has rotating component, supported on shaft to connect gearwheel, designed as idle wheel of gear step of transmission device with drive shaft, where actuating element slides in axial direction |
| US8196725B2 (en) | 2006-10-19 | 2012-06-12 | Zf Friedrichshafen Ag | Device for the rotationally fixed connection of a shaft to at least one component mounted to rotate on the shaft |
| US8245828B2 (en) | 2006-10-19 | 2012-08-21 | Zf Friedrichshafen Ag | Device of a rotationally fixedly connecting a shaft to a component which is rotatably mounted on the shaft |
| CN101529110B (en) * | 2006-10-19 | 2013-09-18 | 腓特烈斯港齿轮工厂股份公司 | Device for rotationally fixedly connecting a shaft to a component which is rotatably mounted on the shaft |
| DE102006049283B4 (en) | 2006-10-19 | 2019-03-14 | Zf Friedrichshafen Ag | Device for non-rotatably connecting a shaft with at least one idler wheel rotatably mounted on the shaft |
Also Published As
| Publication number | Publication date |
|---|---|
| US20040144610A1 (en) | 2004-07-29 |
| US6997296B2 (en) | 2006-02-14 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FZDE | Discontinued |