GB2203807A - Epicyclic split-torque transmission - Google Patents
Epicyclic split-torque transmission Download PDFInfo
- Publication number
- GB2203807A GB2203807A GB08713396A GB8713396A GB2203807A GB 2203807 A GB2203807 A GB 2203807A GB 08713396 A GB08713396 A GB 08713396A GB 8713396 A GB8713396 A GB 8713396A GB 2203807 A GB2203807 A GB 2203807A
- Authority
- GB
- United Kingdom
- Prior art keywords
- cog wheel
- gear
- cog
- driving
- drive shaft
- 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- Withdrawn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
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
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
An input shaft (1) drives a ring gear (16) of a first epicyclic train whose sun gear (29) drives the output shaft (32) and whose carrier (24) is common with that of a second epicyclic train whose sun gear (70) also drives the output shaft through spur gearing (44, 42, 36, 34) and a disconnecting device (50). The disconnecting device may alternatively be on a shaft driven by the ring gear (16) driving the sun gear of the second train. <IMAGE>
Description
TITLE: "TRANSMISSION, common axis of rotation version"
FIRST copy of
Specification & BR<
Drawings
BRIEF SUMMARY OF THE DISCLOSURE
The transmission disclosed is an all-gear, common axis of rotation, bidirectional-driving transmission which recirculates and compounds rotary motion producing a progressively accelerating shift-free output for vehicular or machine propulsion throughout the entire operational speed range for both forward and reverse operation.
A variation of the transmission mechanism provides for a friction-free clutch to perform conventional clutching type functions.
The clutch mechanism can be used in tandem with the transmission to propel vehicles or machines throughout their entire operational speed range.
The primary objective of this invention is to provide a bidirectionally-driven, recirculating-compounding progressivelyaccelerating transmission where all components share a common axis of rotation. Additional objects are to provide a common axis transmission: (1) free from internal clutch or band friction; (2) free from any gear damage resulting from improper shifting; (3) allowing smaller drive engines which further function as a resistive brake during deacceleration; (4) adapted as a frictionfree clutch without pressure friction, torque loss during shifting, or drive train uncoupling.
BRIEF DESCRIPTION OF THE DRAWINGS
Fig. 1 is a schematic side view of the common axis of rotation version of the bidirectionally-driven, recirculatingcompounding, all-gear, progressively-accelerating transmission utilizing a ring gear for first stage rotary multiplication.
Fig. 2 is a cross-section of the bidirectionally driving component arrangement of Fig. 1 at AA.
Fig. 3 is a schematic side view of the transmission utilizing the second driver gear for first stage multiplication.
Fig. 4 is a side view of a sustaining disc adapted as a frictionless clutch driver connected in a driving relation to the clutch output gear and output drive shaft.
Fig. 5 is an alternate driving arrangement for the second stage multiplication gears.
BRIEF DESCRIPTION OF THE DRAWINGS NUMBERS 1. Input drive shaft 7; Input driving gear 9. Input receiving gear 10. Connecting ring 16. Driving ring 17. Satellite Pinion connecting shaft 18. First satellite pinion 20. Second satellite pinion 22. Unitary coupler 24. Sustaining disc 27. Sustaining driver disc.
29. Second driver gear 31. Ring second cog wheel 32. Main drive shaft 33. Alternate drive shaft 34. Second cog wheel 35. Fifth cog wheel 36. Third cog wheel 40. Connecting axle 42. Fourth cog wheel 44. First cog wheel 70. Output receiving gear 73. Output receiving/combin
ation ring first cog wheel
DETAILED DESCRIPTION OF THE INVENTION
During operation of the transmission, motor power is provided through rotating drive shaft 1 of Fig. 1. Optional reduction driver 7 drives input reduction receiver 9 attached to the ring gear driver 16. The edge flange of ring gear driver 16 contains cogs within the inner circumferential surface which drive one or more first satellite pinions to produce a first stage rotary multiplication product. The first satellite pinions 18 are rigidly connected to a second set of satellite pinions 20 with shaft 17.Each shaft 17 is rotatably connected to sustaining disc 24. Sustaining disc 24 is mounted for free rotation upon drive shaft 32. Thus, driving couplers 22 consisting of first satellite pinion 18, shaft 17, and second pinion 20 are free to rotate about their own axis, and further free to concurrently driven orbit and drive sustaining disc 24 about the central axis. Output receiving gear 70 is mounted for free rotation about drive shaft 32, and is connected in a driven relationship with all second satellite pinions 20 of couplers 22.
Thus couplers 22 transfer the first stage rotational product to receiving gear 70 during their driven rotation about their individual axis, and also during concurrently driven orbiting about the central axis with sustaining disc 24. First cog wheel 44 is rigidly connected to output receiving gear 70 and shares the contiguous bore for free rotation about driveshaft 32. Fourth cog wheel 42 is rigidly connected to the first end of connecting axle 42, and further connected in a driving relation with first cog wheel 44. Third cog wheel 36 is rigidly connected to the second end of connecting axle 40.
Second cog wheel 34 is rigidly connected to one end of drive shaft 32, and connected in a driving relation to the third cog wheel 36.
Drive shaft 32 freely rotates through the centers of (1) the first cog wheel 44 and attached output receiving gear 70, and (2) sustaining disc 24 and is rigidly connected to the second driver gear 29.
Drive shaft 32 next freely rotates through the first stage driver ring 16 and attached receiving gear 9. Thus, the second satellite pinions 20 transfer to the output receiving gear 70 a rotational output rate determined by the first stage rotary multiplication product. The output receiving gear 70 next produces through the main drive shaft 32, second cog wheel 34, third cog wheel 36, the connecting axle 40, the fourth cog wheel 42, and the first cog wheel 44, a second stage rotary multiplication product which establishes the rate of rotation for the secondary driver gear 29 which, in addition to the driving ring 16, concurrently drives the couplers 22 through their first satellite pinions 18. Thus satellite pinions 18 serve as a common multiplicand for the first and second stage multipliers.
During initial or slow speed transmission operation, motor input produces low multiplication factors from the first stage.
Increases in the transmission'rate will increase (1) the multiplication compounding factor of the second stage and (2) the combined sum of both stages, accelerating the transmission output.
Compounding is defined as the looping or recirculation of the accelerating sums to produce greater sums and concurrent transmission output. Continued input acceleration progressively increases these results.
Located upon the main drive shaft 32 is a mechanism 50 which divides shaft 32 between the side attached to the second cog wheel 34 and the side attached to the second driver gear 29.
In the alternative transmission arrangement shown in Fig. 3, mechanism 50 is located upon drive shaft 32 between fifth cog wheel 35 and second cog wheel 34. The purpose of mechanism 50 is to utilize individually or in tandem: (1) a sliding clutch and locking plate to temporarily disengage the equal driving relationship between both shaft 32 sides and terminate and lock the rate of rotation of second driver gear 29 where only the first stage product motivates transmission output with higher torque to provide the effect of a low gear; or (2) utilize a planetary rotary reduction mechanism to lower the rotational rate of one shaft 32 side to reduce the rate of second stage multiplication during any phase of transmission operation for temporary increases in transmission output torque, providing the effect of a passing gear.
Shown in Fig. 5 is an alternate method of creating second stage multiplier gears. In this alternative, combination output receiving gear and first cog wheel ring gear 73 replaces output receiving gear 70 and first cog wheel 44. Second cog ring wheel 31 replaces second cog wheel 34. During operation of this alternative, fourth cog wheel 42 is driven by the combination wheel 73. The third cog wheel, connected to the fourth cog wheel 42 through connecting axle 40, drives second cog ring wheel 31 rigidly attached to drive shaft 32.
Shown in Fig. 3 is an alternative arrangement for operation of the transmission with the position for the first and second stage multipliers reversed. In this arrangement, motor power rotates input drive shaft 1 and rigidly attached second driver gear 29.
Second driver gear 29 drives first satellite pinions 18 rigidly attached to couplers 22 to produce the first stage rotary multiplication product rate. This rotational rate is transferred to the output receiving gear 70 through couplers 22 spinning through revolving sustaining disc 24. The first cog wheel 44, rigidly attached to the output receiving gear 70, drives fourth cog wheel 42 rigidly coupled to third cog wheel 36 with alternate drive shaft 33. Third cog wheel 36 drives second cog wheel 34 rigidly attached to main drive shaft 32. Main drive shaft 32 is rigidly connected to fifth cog wheel 35 which drives driving ring 16. Driving ring 16 drives first satellite pinions 18 concurrently with driver gear 29 to produce the second stage of rotary multiplication.Thus, the couplers 22 transfer to the output receiving gear 70 a rotational output rate determined by the first stage rotary multiplication product. The output receiving gear next produces through the fifth cog wheel 35, the main drive shaft 32, the second cog wheel 34, the third cog wheel 36, the alternate shaft 33, the fourth cog wheel 42, and the attached first cog wheel 44, a second stage rotary multiplication product which establishes the rate of rotation for the driving ring 16 which, in addition to the second driver gear 29 concurrently drives the coupler 22 through their first satellite pinions 18. Thus also in this alternative, satellite pinions 18 serve as a common multiplicand for the first and second stage multipliers.
The common axis of rotation transmission is adaptable to function as a friction-free clutch mechanism by utilizing the differentially driven sustaining driver disc adapted as a cog wheel to drive an output gear attached to an alternate drive shaft.
Fig. 4 shows the centrally bored sustaining driver disc 27 with attached couplers 22. Driver disc 27 freely rotates upon the main drive shaft and is connected in a driving relation with clutch output gear 71. Couplers 22, rotatably mounted through sustaining driver disc 27, are connected in a driven relation with both the first stage driving ring 16 and the second driver gear 29. Clutch output gear 71 is rigidly connected to the alternate drive shaft 33 rotatably mounted to supporting framework. During operation of the friction free clutch, sustaining driver disc 27 does not rotate when the first and second stages differentially drive at the motor idle speed. However, differential first and second stage drive rates beyond the motor idle speed progressively rotates sustaining driver disc 27 in proportion to the rate of increases of the twostage differential driving rate. Driver disk 27 next drives clutch output gear 71, rotating the gear and attached alternate drive shaft 33. Alternate drive shaft 33 transfers rotary power to the vehicular transmission, or operational mechanism. During input speeds below the idle speed, the second stage driver gear 29 is uncoupled by mechanism 50 allowing sustaining driver disc 27 to remain in a fixed non-rotating position for motor starting and stopping sequences.
It is the intention to cover all equivalents of the invention above described together with all modifications and variations thereof that are within the scope of the appended claims.
Claims (6)
1. A transmission with a common component axis of rotation, comprising:
(a) a driving ring which rotates about a central axis and has a central bore;
(b) at least one unitary coupler, each coupler including:
(i) a satellite pinion with which the driving ring
is connected in a driving relation to produce
a first stage rotary multiplication product;
(ii) a transmitting pinion gear rotating upon an
axis parallel to that of the driving ring gear;
(iii) a connecting shaft which at one end is rigidly
connected to the satellite pinion and at another
end is rigidly connected to a second satellite
pinion so that the coupler transmits-rotary
multiplication products;
(c) one centrally bored output receiving gear with which all the second satellite pinions are connected in driving relation, the output receiving gear rotating about the central axis;;
(d) a centrally bored circular sustaining disc including equidistantly spaced bearing supports for the couplers, the connecting shaft of each coupler being rotatably connected to the disc through a bearing support; wherein each coupler can rotate about an axis of its own, and the circular sustaining disc and couplers are free to rotate about the central axis;
(e) a secondary driver gear rigidly connected at its central axis to the main drive shaft being rotatable around the central axis and connected in a driving relation to the first satellite pinions, and rotating within the driving ring;
(f) a first cog wheel integrally connected to the output receiving gear to rotate around the central axis, the first cog wheel having a central bore which is contiguous with the receiving gear bore;;
(g) a main drive shaft supportively mounted to supporting framework which is rigidly connected to the secondary driver gear and freely rotating through and beyond the driving ring on one end, and on the other end freely rotating through the sustaining disc and the contiguous bores of the receiving gear and first cog wheel so that the sustaining disc and the receiving gear with the first cog wheel are free to rotate about the main drive shaft;
(h) a second cog wheel which is rigidly connected to the main drive shaft to rotate around the central axis;
(i) a third cog wheel whith is connected in driving relation with the second cog wheel;
(j) a fourth cog wheel which is connected in driving relation with the first cog wheel; and
(k) a connecting axle which extends between the third and fourth cog wheels and which has ends which are rigidly connected to the third and fourth cog wheels, the connecting axle being parallel to the central axis and supportively mounted to a supporting framework; wherein the second satellite pinions transmit to the output receiving gear a rotational output rate determined by the first stage rotary multiplication product, and the output receiving gear producing through the main driveshaft, the second and third cog wheels, the connecting axle, and the fourth and first cog wheels a second stage rotary multiplication product which establishes the rate of rotation of the secondary driver gear which in addition to the driving ring, drives the coupler through their first satellite pinions.
2. The transmission as claimed in Claim 1, further comprising:
(a) an input shaft rotating at the central axis and rigidly connected to the driver gear and freely rotating through the driving ring, sustaining disc, output receiving gear, and attached first cog wheel;
(b) at least one satellite pinion which the driving gear is connected in a driving relation to produce a first stage rotary multiplication product;
(c) a fourth cog wheel connected in a driving relation with the first cog wheel and rigidly attached to an alternate drive shaft;
(d) a third cog wheel rigidly attached to the alternate drive shaft;
(e) a second cog wheel rigidly attached to the main drive shaft, and connected in a driving relation with the third cog wheel;
(f) a fifth cog wheel rigidly attached to the main drive shaft, and connected in a driving relation with the driving ring;; wherein the output receiving gear produces through the fifth cog wheel, the main drive shaft, the second cog wheel, the third cog wheel, the alternate shaft, the fourth cog wheel, and the first cog wheel to produce the second stage rotary multiplication product which establishes the rate of rotation for the driving ring, which in addition to the second driver gear, concurrently drives the first satellite pinions.
3. A friction-free clutching mechanism with a common component axis of rotation, comprising:
(a) a driving ring which rotates about a central axis and has a central bore;
(b) at least one unitary coupler, each coupler including:
(i) a satellite pinion with which the driving ring
is connected in a driving relation to produce a first
stage rotary multiplication product;
(ii) a transmitting pinion gear rotating upon an axis
parallel to that of the driving ring gear;
(iii) a connecting shaft which at one end is rigidly
connected to the satellite pinion and at another
end is rigidly connected to a second satellite
pinion so that the coupler transmits rotary
multiplication products;
(c) one centrally bored output receiving gear with which all the second satellite pinions are connected in driving relation, the output receiving gear rotating about the central axis;;
(d) a centrally bored circular sustaining disc driver cog wheel including equidistantly spaced bearing supports for the couplers, the connecting shaft of each coupler being rotatably connected to the disc through a bearing support; wherein each coupler can rotate about an axis of its own, and the circular sustaining disc and couplers are free to rotate about the central axis;
(e) a secondary driver gear rigidly connected at its central axis to the main drive shaft being rotatable around the central axis and connected in a driving relation to the first satellite pinions, and rotating within the driving ring;
(f) a first cog wheel integrally connected to the output receiving gear to rotate around the central axis, the first cog wheel having a central bore which is contiguous with the receiving gear bore;;
(g) a main drive shaft supportively mounted to supporting framework which is rigidly connected to the secondary driver gear and freely rotating through and beyond the driving ring on one end, and on the other end freely rotating through the sustaining disc and the contiguous bores of the receiving gear and first cog wheel so that the sustaining disc and the receiving gear with the first cog wheel are free to rotate about the main drive shaft.
(h) a rotating output drive shaft with an axis parallel to the central axis, and mounted to supporting framework;
(i) a sustaining disc driver output receiving gear rigidly attached to the output drive shaft, and connected in a driving relation to the sustaining disc driver cog wheel;
(j) a second cog wheel which is rigidly connected to the main drive shaft to rotate around the central axis;
(k) a third cog wheel which is connected in driving relation with the second cog wheel;
(1) a fourth cog wheel which is connected in driving relation with the first cog wheel; and
(m) a means for uncoupling the second stage driver gear; wherein motor starting or stopping does not rotate the output drive shaft;
(n) a connecting axle which extends between the third and fourth cog wheels and which has ends which are rigidly connected to the third and fourth cog wheels, the connecting axle being parallel to the central axis and supportively mounted to a supporting framework; wherein the second satellite pinions transmit to the output receiving gear a rotational output rate determined by the first stage rotary multiplication product, and the output receiving gear producing through the main driveshaft, the second and third cog wheels, the connecting axle, and the fourth and first cog wheels a second stage rotary multiplication product which establishes the rate of rotation of the secondary driver which in addition to the driving ring, drives the couplers through their first satellite pinions, wherein a certain driving ring/secondary driver gear counterrotation rate causes no rotation of the sustaining disc driver cog wheel, output receiving gear, or output drive shaft, while progressive differential driving of the driving ring/ secondary driver gear causes progressive drive rotation of the output receiving gear and attached output drive shaft by the sustaining disc driver cog wheel.
4. The transmission as claimed in Claim 1 further comprising an alternate method for driving the second stage multiplication gears, including:
(a) a combination output receiving gear and first cog wheel ring gear;
(b) a second cog ring wheel; wherein the fourth cog wheel is connected in a driven relation with the combination output receiving gear and first cog wheel, and the second cog ring wheel is connected in a driven relation with the third cog wheel.
5. The transmission as claimed in Claim 1 further comprising a selective planetary geared rotation reduction means attached to the connecting axle; wherein one connecting axle section rotates at a slower rate than the second axle section to increase transmission output torque producing a step-down or passing-gear effect.
6. The transmission as claimed in Claim 1 further comprising a selective means to disengage and lock one connecting axle section; wherein one connecting axle section is separated and locked to prevent its rotation and second stage driving while the second connecting axle section is free to rotate, increasing transmission output torque producing a step-down or passing gear effect.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US3759687A | 1987-04-13 | 1987-04-13 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB8713396D0 GB8713396D0 (en) | 1987-07-15 |
| GB2203807A true GB2203807A (en) | 1988-10-26 |
Family
ID=21895197
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB08713396A Withdrawn GB2203807A (en) | 1987-04-13 | 1987-06-08 | Epicyclic split-torque transmission |
Country Status (1)
| Country | Link |
|---|---|
| GB (1) | GB2203807A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113339473A (en) * | 2021-05-25 | 2021-09-03 | 武汉市精华减速机制造有限公司 | Periodic speed changing device for accurately positioning rotary disc |
-
1987
- 1987-06-08 GB GB08713396A patent/GB2203807A/en not_active Withdrawn
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113339473A (en) * | 2021-05-25 | 2021-09-03 | 武汉市精华减速机制造有限公司 | Periodic speed changing device for accurately positioning rotary disc |
Also Published As
| Publication number | Publication date |
|---|---|
| GB8713396D0 (en) | 1987-07-15 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| WAP | Application withdrawn, taken to be withdrawn or refused ** after publication under section 16(1) |