U.S. patent application number 13/861930 was filed with the patent office on 2013-09-05 for planetary gear mechanism for a bicycle.
The applicant listed for this patent is Dean Schneider, Alexander Serkh. Invention is credited to Dean Schneider, Alexander Serkh.
Application Number | 20130228995 13/861930 |
Document ID | / |
Family ID | 43807109 |
Filed Date | 2013-09-05 |
United States Patent
Application |
20130228995 |
Kind Code |
A1 |
Serkh; Alexander ; et
al. |
September 5, 2013 |
PLANETARY GEAR MECHANISM FOR A BICYCLE
Abstract
A planetary gear mechanism for a bicycle, and more particularly
to a planetary gear mechanism comprising a first planetary
mechanism connected coaxially in series to a second planetary
mechanism, which second planetary mechanism is connected coaxially
in series to a third planetary mechanism, the second planetary
mechanism output is a step up in speed from the first planetary
mechanism output, the third planetary mechanism output is a step up
in speed from the second planetary mechanism output.
Inventors: |
Serkh; Alexander; (Troy,
MI) ; Schneider; Dean; (Washington, MI) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Serkh; Alexander
Schneider; Dean |
Troy
Washington |
MI
MI |
US
US |
|
|
Family ID: |
43807109 |
Appl. No.: |
13/861930 |
Filed: |
April 12, 2013 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
12660861 |
Mar 5, 2010 |
8439792 |
|
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13861930 |
|
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Current U.S.
Class: |
280/261 |
Current CPC
Class: |
B62M 11/145 20130101;
B62M 11/18 20130101; F16H 3/663 20130101; F16H 2200/003 20130101;
F16H 2200/2046 20130101; F16H 2200/2023 20130101; F16H 2200/201
20130101 |
Class at
Publication: |
280/261 |
International
Class: |
B62M 11/14 20060101
B62M011/14 |
Claims
1. A bicycle comprising: a frame (30); a planetary gear
transmission comprising an input member (22), a first planetary
mechanism, a second planetary mechanism and a third planetary
mechanism, and an output member (44); the first planetary
mechanism, second planetary mechanism and third planetary mechanism
are each connected in series; and a flexible drive member (50)
drivingly engaged between the output member (44) and a wheel
(34).
2. The bicycle as in claim 1, wherein: the input member is
connected to the first planetary mechanism; the second planetary
mechanism rotary output is a step up in speed from the first
planetary mechanism rotary output, the third planetary mechanism
rotary output is a step up in speed from the second planetary
mechanism rotary output; and the third planetary mechanism is
connected to the output member.
3. A bicycle comprising: a frame having a bottom bracket; a
planetary gear transmission comprising an input member, a first
planetary mechanism, a second planetary mechanism and a third
planetary mechanism, and an output member, the first planetary
mechanism, second planetary mechanism and third planetary mechanism
are each connected in series; the planetary gear transmission
disposed in the bottom bracket; and a flexible drive member
drivingly engaged between the output member and a rear wheel.
4. The bicycle as in claim 3, wherein the planetary gear
transmission comprises twelve output gear ratios.
5. The bicycle as in claim 3, wherein the flexible drive member
comprises a belt.
6. The bicycle as in claim 3, wherein the input member comprises a
crank.
7. The bicycle as in claim 5, wherein the output member comprises a
sprocket, the sprocket having a plurality of holes, each hole being
engagable by a belt tooth.
Description
REFERENCE TO RELATED APPLICATIONS
[0001] This application is a continuation of and claims priority
from U.S. non-provisional patent application Ser. No. 12/660,861
filed Mar. 5, 2010.
FIELD OF THE INVENTION
[0002] The invention relates to a planetary gear mechanism for a
bicycle, and more particularly to a planetary gear mechanism
comprising a first planetary mechanism connected coaxially in
series to a second planetary mechanism, which second planetary
mechanism is connected coaxially in series to a third planetary
mechanism, the second planetary mechanism output is a step up in
speed from the first planetary mechanism output, the third
planetary mechanism output is a step up in speed from the second
planetary mechanism output.
BACKGROUND OF THE INVENTION
[0003] It is known that bicycles may have internal geared
transmissions located in rear hubs. For example, the Shimano
Company provides a Shimano Nexus.TM. eight speed transmission. The
transmission comprises an internal geared planetary transmission
which is located in a bicycle rear wheel hub. Rohloff GmbH of
Germany provides a fourteen speed planetary gear transmission, also
for use in a bicycle rear wheel hub.
[0004] The prior art transmissions have common disadvantages
including heavy weight and that each is located in the bicycle rear
wheel hub.
[0005] Also representative of the art is U.S. Pat. No. 6,468,178
(2002) to Mohtasham which discloses a rear wheel hub and chainless
drive train gear assembly for use on a bicycle having an axle
bracket fixed to the frame of the bicycle, a spindle extending
axially through the axle bracket and left and right pedal crank
arms for rotating the spindle upon application of a pedaling force.
A primary drive gear fitted to the spindle drivingly engages
carrier gears which operate a planet gear cage housing and a
multiple planetary gear and sun gear arrangement according to
various gear ratios determined by selective operation of a clutch
assembly. Planetary gear groups each include an integral set of
planetary gears of varying size which mesh with corresponding sun
gear rings. Operation of the clutch assembly serves to selectively
engage pawl stops with a corresponding sun gear ring, thereby
engaging the corresponding sun gear ring with one of the planetary
gears of the planetary gear groups according to a selected gear
ratio. The planetary gear groups drive an annular gear ring and an
associated annular needle bearing which, in a forward clockwise
rotation, engages the hub body to rotate the rear bicycle wheel.
Reverse rotation of the annular gear, in a counter-clockwise
rotation, results in a freewheeling of the drive train gear
assembly relative to the hub body.
[0006] What is needed is a planetary gear mechanism comprising a
first planetary mechanism connected coaxially in series to a second
planetary mechanism, which second planetary mechanism is connected
coaxially in series to a third planetary mechanism, the second
planetary mechanism output is a step up in speed from the first
planetary mechanism output, the third planetary mechanism output is
a step up in speed from the second planetary mechanism output. The
present invention meets this need.
SUMMARY OF THE INVENTION
[0007] The primary aspect of the invention is to provide a
planetary gear mechanism comprising a first planetary mechanism
connected coaxially in series to a second planetary mechanism,
which second planetary mechanism is connected coaxially in series
to a third planetary mechanism, the second planetary mechanism
output is a step up in speed from the first planetary mechanism
output, the third planetary mechanism output is a step up in speed
from the second planetary mechanism output.
[0008] Other aspects of the invention will be pointed out or made
obvious by the following description of the invention and the
accompanying drawings.
[0009] The invention comprises a planetary gear mechanism
comprising an input member (22), a first carrier (100) having a
first carrier first pinion gear (P1) and a first carrier second
pinion gear (P2), each journalled to the first carrier, the first
carrier rotationally fixed to the input member (22), the first
carrier second pinion gear (P2) in meshing engagement with sun gear
S1 which is engaged with a first brake (Brake 1), a second carrier
(200) having second carrier first pinion gear (P4) and a second
carrier second pinion gear (P5), each pinion gear (P4) and (P5) is
journalled to the second carrier, the second carrier engaged with a
second brake (Brake 2), a first ring gear (R1) in meshing
engagement with the first carrier first pinion gear (P1), a second
ring gear (R2) in meshing engagement with the second carrier first
pinion gear (P4), the first ring gear and second ring gear comprise
a ring gear member (400), a third carrier (300) having a third
carrier first pinion gear (P6) and a third carrier second pinion
gear (P7), each pinion gear (P6) and (P7) is journalled to the
third carrier, a third ring gear (R3) in meshing engagement with
the second carrier second pinion gear (P5), the third ring gear
fixedly connected to the third carrier (300), a fourth ring gear
(R4) engaged with a third brake (Brake 3) and in meshing engagement
with the third carrier first pinion gear (P6), a first one-way
clutch (CL1) engaged between the first carrier (100) and the ring
gear member (400), a second one-way clutch (CL2) engaged between
the second carrier (200) and the ring gear member (400), a third
one-way clutch (CL3) engaged between the third carrier (300) and
the fourth ring gear (R4), and an output member (44) in meshing
engagement with the third carrier second pinion gear (P7).
BRIEF DESCRIPTION OF THE DRAWINGS
[0010] The accompanying drawings, which are incorporated in and
form a part of the specification, illustrate preferred embodiments
of the present invention, and together with a description, serve to
explain the principles of the invention.
[0011] FIG. 1 is a cross-sectional schematic view of the
transmission.
[0012] FIG. 2 is a table of gear ratios.
[0013] FIG. 3 is a table of brake and clutch positions for each
gear.
[0014] FIG. 4 is a partial side view of a bicycle.
[0015] FIG. 4A is a side view of a belt.
[0016] FIG. 5 is a cross-sectional view of the transmission.
[0017] FIG. 6 is a perspective view of a brake.
[0018] FIG. 7 is a cross-section at 7-7 in FIG. 5.
[0019] FIG. 8 is a cross-section at 8-8 in FIG. 5.
[0020] FIG. 9 is a cross-section at 9-9 in FIG. 5.
[0021] FIG. 10 is a cross-section at 10-10 in FIG. 5.
[0022] FIG. 11 is a cross-section at 11-11 in FIG. 5.
[0023] FIG. 12 is a cross-section at 12-12 in FIG. 5.
[0024] FIG. 13 is a cross-section at 13-13 in FIG. 5.
[0025] FIG. 14 is an exploded view of the transmission.
[0026] FIG. 15 is a detail of FIG. 14.
[0027] FIG. 16 is a detail of FIG. 14.
[0028] FIG. 17 is a detail of FIG. 14.
[0029] FIG. 18 is a detail of FIG. 14.
[0030] FIG. 19 is a detail of FIG. 14.
[0031] FIG. 20 is a detail of FIG. 14.
[0032] FIG. 21 is an end view of shift cam ring 600.
[0033] FIG. 22 is a side view of the shift cam ring 600.
[0034] FIG. 23 is an end view of shift cam ring 600.
[0035] FIG. 24 is a perspective view of shift cam ring 600.
[0036] FIG. 25 is an end view of shift cam ring.
[0037] FIG. 26 is a side view of the shift cam ring.
[0038] FIG. 27 is an end view of shift cam ring.
[0039] FIG. 28 is a perspective view of the shaft cam ring.
[0040] FIG. 29 is a perspective view of a shift dog.
[0041] FIG. 30 is a plan view of a shaft dog.
[0042] FIG. 31 is a side view of a shift dog.
[0043] FIG. 32 is a perspective view of a shift dog.
[0044] FIG. 33 is a perspective view of a shift dog.
[0045] FIG. 34 is a perspective view of a shift dog.
[0046] FIG. 35 is a perspective view of a shift dog.
[0047] FIG. 36 is a perspective view of a shift dog.
[0048] FIG. 37 is a detail of FIG. 18.
[0049] FIG. 38 is a detail of FIG. 19.
[0050] FIG. 39 is a detail of FIG. 19.
[0051] FIG. 40 is a detail of FIG. 6.
[0052] FIG. 41 is a detail of FIG. 6.
[0053] FIG. 42 is a detail of FIG. 6.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
[0054] FIG. 1 is a cross-sectional schematic view of the
transmission. The invention generally comprises a planetary gear
mechanism having an input member connected to a first planetary
mechanism, the first planetary mechanism connected coaxially in
series to a second planetary mechanism, which second planetary
mechanism is connected coaxially in series to a third planetary
mechanism, the second planetary mechanism output is a step up in
speed from the first planetary mechanism output, the third
planetary mechanism output is a step up in speed from the second
planetary mechanism output, and the third planetary mechanism
connected to an output member.
[0055] The proposed transmission is preferably located in a bicycle
bottom bracket, see FIG. 4. Crank arms (see FIG. 4) are attached to
each end of the input member 22. Carrier 100 is rigidly connected
to the member 22, and thereby rotates with member 22. Carrier 100
further comprises a carrier pin or shaft 101.
[0056] Three planet pinion gears are journalled to pin 101, namely,
P1, P2, P3. Each pinion gear P1, P2, P3 rotates together at the
same speed about pin 101. Pinions P1, P2, P3 preferably comprise a
single gear component having three different diameters, thereby
describing gears P1, P2, P3.
[0057] Ring gear member 400 comprises a first ring gear R1 and a
second ring gear R2. R1 is in meshing connection with pinion P1.
Sun gears S1 and S2 are in meshing engagement with pinion gears P2
and P3 respectively. Sun gears S1 and S2 are reaction gears with
brake 1 and brake 4. Brake 1 and brake 4 are connected to a bicycle
frame (see FIG. 4). The rotational speed of pinion P1 is a function
of whether brake 1 or brake 4 is engaged or disengaged, see FIG.
3.
[0058] Second planetary mechanism has two pinion gears P4 and P5
fixedly connected to a carrier shaft 201, and therefore gears P4
and P5 rotate together with shaft 201. Ring gear R2 is in meshing
engagement with pinion gear P4. Carrier shaft 201 is journalled to
carrier 200. Carrier 200 is a reaction member with and is engaged
with brake 2.
[0059] A third ring gear R3 is fixedly attached to the input member
of the third planetary mechanism which is carrier 300. The third
planetary mechanism pinion gear P6 is in meshing engagement with
fourth ring gear R4. Ring gear R4 is engaged with brake 3 and
one-way clutch CL3. One-way clutch CL3 is engaged with carrier 300
and ring gear R3.
[0060] Pinion gear P6 and P7 are each journalled to carrier pin
301, and therefore rotate together. Pinion gears P6 and P7
preferably comprise a single gear component having two different
diameters and hence define gears P6 and P7. Pinion gear P7 is in
meshing engagement with output sun gear S3. Output sun gear S3 is
fixedly attached to output sprocket 44.
[0061] All planetary carrier mechanisms are numbered as a function
of increasing speed of their respective output members, that is,
the third planetary mechanism causes rotation of sprocket 44, which
in turn rotates faster than the relative rotation of the second
planetary mechanism, which in turn rotates faster than the relative
rotation of the first planetary mechanism when each planetary
mechanism is operating with all one-way clutches dis-engaged, see
FIG. 3 gear 12. Further, each planetary carrier mechanism is
coaxial with the others and each of the planetary carrier
mechanisms are connected in series.
[0062] Each planetary mechanism further comprises a one-way clutch,
namely, CL1, CL2, CL3. When engaged each one-way clutch locks each
respective planetary carrier mechanism with a gear ratio of
1:1.
[0063] A low-friction bushing 50 is disposed between input member
22 and sun gear S1. A low-friction bushing 51 is disposed between
sun gear S1 and sun gear S2. A low-friction bushing 52 is disposed
between sun gear S3 and input member 22.
[0064] For ease of reference, the following assemblies may also be
generally referred to as the first planetary mechanism, second
planetary mechanism and third planetary mechanism. [0065] First
planetary mechanism: carrier 100; pinion gears P1, P2, P3; shaft
101; one-way clutch CL1; ring gear R1 [0066] Second planetary
mechanism: carrier 200; pinion gears P4, P5; shaft 201; one-way
clutch CL2; ring gear R2; ring gear R3 [0067] Third planetary
mechanism: carrier 300; pinion gears P6, P7; shaft 301; one-way
clutch CL3; ring gear R4
[0068] FIG. 2 is a table of gear ratios. Planetary mechanism
(carrier) 100 has gear ratios 1, 1.33, and 1.76. Planetary
mechanism 200 has gear ratios 1 and 1.15. Planetary mechanism 300
has gear ratios 1 and 2.30. The combined overall gear ratio is
noted in column i.
[0069] The inventive transmission results in very linear steps
between each gear ratio averaging approximately 15%. This allows
predictable power requirements for each shift as a rider shifts up
and down through the gears.
[0070] Since the inventive transmission increases the speed of the
output member front sprocket 44 compared to the speed of input
member 22, the ratio between the front sprocket 44 and a rear
sprocket 36 installed on the rear wheel 34 is adjusted accordingly.
Hence, for example, front sprocket 44 has 32 teeth and the rear
sprocket has 42 teeth. The number of teeth on the front sprocket
and rear sprocket may be adjusted as may be required by a user.
[0071] FIG. 3 is a table of brake and clutch positions for each
gear. For example, first gear, the slowest gear, has all planetary
mechanisms 100, 200, 300 at gear ratio 1:1 and all clutches CL1,
CL2, CL3, are locked. In first gear all brakes 1, 2, 3, 4 are
disengaged.
[0072] The inventive transmission is about 20%-30% lighter than
prior art transmissions. Another advantage of the transmission is
better clearance in a bicycle frame since front sprocket is much
smaller.
[0073] The following is provided as an example and is not intended
to limit the design parameters which may be used for each
component. The diameters are in mm.
TABLE-US-00001 Pinion Gear Ring Gear Diameter No. of Teeth P1 NA
13.6 17 P2 NA 18.4 23 P3 NA 10.4 13 P4 NA 11.2 14 P5 NA 13.6 17 P6
NA 16 20 P7 NA 10.4 13 NA R1 57.6 72 NA R2 45.6 57 NA R3 48 60 NA
R4 52.8 66
[0074] FIG. 4 is a partial side view of a bicycle. The inventive
transmission will be preferably installed in bottom bracket 20.
Crank arms 41 are connected to input member 22. A rider's feet
engage pedals 42. A flexible drive member 50 is engaged between
sprocket 44 and rear sprocket 36. Rear sprocket 36 is connected to
wheel 34. A rider (not shown) sits on seat 24. Wheel 34, crank arms
41, bottom bracket 20, seat 24 are connected to bicycle frame 30,
known in the art. Flexible drive member 50 may comprise a belt or
chain.
[0075] FIG. 4A is a side view of a belt. Belt 50 comprises a body
98. Teeth 99 extend from belt body 98. Teeth 99 extend across the
width of the belt and normal to a longitudinal or endless
direction. This style of belt is also referred to as a toothed,
cogged or synchronous belt as is known in the automotive arts.
[0076] FIG. 5 is a cross-sectional view of the transmission.
Planetary carrier mechanisms 100, 200, 300 are shown connected in
series within bottom bracket or a transmission housing 20. Carrier
100 is fixedly connected to input member 22. Carrier 200 is
rotatable about member 22 on bearings 1002, 1003. Carrier 300 is
rotatable about member 22 on bearings 1003, 1004, 1005. Member 22
rotates within bottom bracket 22 on bearing 1001. Member 22 may be
hollow to reduce weight of the transmission.
[0077] FIG. 6 is a perspective view of a brake. The figure shows
sun gears S1 and S2. Brake 1 engages sun gear S1. Brake 4 engages
sun gear S2. The brake mechanisms for shifting the planetary
transmission ensures that a compound planetary set cannot engage
two gear sets at once and thus become locked. The proposed
mechanism is located in the proximity of the sun gears of a
compound planetary gear set but could easily be applied to breaking
or shifting of a compound planetary gear set with multiple ring
gears.
[0078] The mechanism comprises two levers (701,702) (801,802)
configured in a manner such that one physically interferes or
prohibits the other lever from engaging its sun gear while the
other is engaged with its respective sun gear. When one sun gear is
stopped by a brake, the other sun gear will be forced to rotate
relative to the stopped sun gear. In the case of a compound set
with more than two sun gears, each sun gear will rotate at a
different speed than the others. However, if each brake is applied
to each sun at the same time the transmission would lock and not
rotate. Each lever limits the rotation or brakes their respective
sun gear by engaging with a stepped area of the sun gear such that
the lever engages the face of a step and limits the rotation of the
sun in one direction. The mechanism could engage the sun gears from
radially outside or radially inside depending on the configuration
required.
[0079] The shift levers are actuated by a roller 601 that engages a
profiled surface 601B. As the profile changes, the levers are moved
to either engage as a brake or open and allow free movement of the
respective sun gear.
[0080] Each brake 1 and brake 4 comprises a shift member 701 and
801 respectively. Shift cam 600 engages shift rollers 601. Each
shift roller 601 engages a compliant pad or member 602.
[0081] Each shift member 701 and 801 are pivotally mounted to end
cap 205. Each end 702, 802 of each shift member 701, 801 engages
sun gear teeth 210, 211 respectively.
[0082] In operation, shift cam 600 rotates enabling each shift
roller 601 to move radially outward, thereby releasing each
complaint pad 602. Releasing each complaint pad 602 enables each
shift member 701, 801 to pivot due to the biasing caused by springs
7001 thereby causing shift members 701, 801 to engage sun gear
teeth 210, 211 respectively. Engagement of each shift member 701,
801 with the respective sun gear teeth stops rotation of the
respective sun gear in a clockwise direction CW.
[0083] The reaction force caused by engagement of the shift members
701, 801 with teeth 210, 211 is transmitted through each shift
member 701, 801 to the end cap 205 and thereby to the bicycle
frame.
[0084] Brake 2 and brake 3 are identical in description and
operation to brake 1 and brake 4.
[0085] FIG. 7 is a cross-section at 7-7 in FIG. 5. Pinion gear P7
has a meshing engagement with sun gear S3. Brake 3 shift member 601
engages teeth 213. Teeth 213 are disposed on an outer perimeter of
ring gear R4. In the instant embodiment there are three sets of
pinion gears P6, P7.
[0086] FIG. 8 is a cross-section at 8-8 in FIG. 5. Pinion gear P6
is journalled to pin 301.
[0087] FIG. 9 is a cross-section at 9-9 in FIG. 5. Pinion gear P5
is journalled to pin 201. Pinion gear P5 has a meshing engagement
with ring gear R3. Brake 2 comprises shift member 901 which engages
teeth 212. Teeth 212 are disposed on an outer perimeter of carrier
200. In the instant embodiment there are three sets of pinion gears
P4, P5.
[0088] FIG. 10 is a cross-section at 10-10 in FIG. 5. Pinion gear
P4 has a meshing engagement with ring gear R2.
[0089] FIG. 11 is a cross-section at 11-11 in FIG. 5. Pinion gear 1
and P2 are journalled to pin 101. Pinion gear P1 has a meshing
engagement with ring gear R1. In the instant embodiment there are
four sets of pinion gears P1, P2, P3, each journalled to a pin
101.
[0090] FIG. 12 is a cross-section at 12-12 in FIG. 5. Sun gear S1
has a meshing engagement with pinion gear P2. Sun gear S2 has a
meshing engagement with pinion gear P3.
[0091] FIG. 13 is a cross-section at 13-13 in FIG. 5. Pinion gear
P3 has a meshing engagement with sun gear S2.
[0092] FIG. 14 is an exploded view of the transmission. Axis A-A is
the axis of rotation. A belt engages sprocket 44 and a rear hub,
see FIG. 4.
[0093] Transmission case 20 may be inserted into a bottom bracket
in a cartridge manner. Namely, case 20 is inserted into a
cylindrical receiver, the cylindrical receiver comprising the
bottom bracket. In an alternate embodiment, the seat stay, seat
tube and chain stays can be attached directly to case 20, for
example by welding, thereby making the transmission case 20 the
bottom bracket. The internals for the transmission would not be
changed for either embodiment. FIG. 15 is a detail of FIG. 14.
Shift cables 1, 2 (known in the art) are connected to the
transmission through adjusting grommets 81 and 82 respectively.
Shift cables 1, 2 are typically connected to shift mechanisms on a
bicycle handlebar for example (not shown). Grommets 81, 82 are
threadably engaged with case 20 at hole 21, 22 respectively.
Bearing 1006 is disposed between sun gear S3 and case 20.
[0094] Sprocket 44 comprises holes 440 which receive belt teeth
(not shown). Further, holes 440 allow dirt and debris thrown up by
the wheels to drop through the sprocket, thereby allowing the
sprocket to be self cleaning. This prevents debris from
accumulating between the belt and the sprocket which would
otherwise hinder performance.
[0095] Bushings 1007 and 1008 engage bearings 1005 and 1006
respectively.
[0096] Spacer 800 is disposed between bearing 1004 and bearing
1003. Spacer 801 is disposed between bearing 1003 and bearing
1002.
[0097] Nuts 42 attach sprocket 41 to a spider 51 on sun gear
S3.
[0098] FIG. 16 is a detail of FIG. 14. Each cable 1, 2 is fastened
to receiver 206. Receiver 206 is fixed to an end of shift cam ring
600. By extending or retracting each cable 1, 2 the shift cam ring
is thereby rotated within the transmission case 20. The range of
rotational movement of shift cam ring 600 is approximately
130.degree..
[0099] Surface 601A engages roller 603 which engages shift dog 702A
and 802A. Surface 602A engages roller 603 which engages compliant
member 601 and thereby shift dog 720, 721. Surface 603A engages
roller 603 which engages shift dog 702B, 802B. Surface 601B engages
roller 603 which engages shift dogs 820, 821.
[0100] Shift dogs 720 and 721 engage teeth 212. Shift dogs 820, 821
engage teeth 213.
[0101] Springs 8001A, 8001B, 8001C, 8001D bias each shift dog 720,
721, 820, 821 into engagement with teeth 212, 213 respectively.
Biasing the shift dogs causes the rollers 603 to maintain contact
with cam surfaces 601A, 602A, 603A and 601B.
[0102] FIG. 17 is a detail of FIG. 14. Bushing 1010 engages bearing
1002. Shift dogs 701A, 801A engage teeth 211. Shift dogs 701B, 801B
engage teeth 210.
[0103] FIG. 18 is a detail of FIG. 14. FIG. 19 is a detail of FIG.
14. FIG. 20 is a detail of FIG. 14. Threaded ring 23 attaches end
205 to case 20. Bushing 1009 engages bearing 1001. Cap 43 retains
crank arms (not shown) to axle shaft 22.
[0104] Springs 7001A, 7001B, 7001C, 7001D bias each shift dog 701A,
801A, 701B, 801B into engagement with teeth 211, 210
respectively.
[0105] FIG. 21 is an end view of shift cam ring 600. Shift cam ring
600 comprises member 600A and 600B for ease of manufacture and
assembly. Member 600A is cylindrical. Shift cam ring 600 is
disposed in the transmission and is radially outermost from the
planetary gear sets 100, 200, 300 and within the transmission case
20, see FIG. 5.
[0106] FIG. 22 is a side view of the shift cam ring 600. Member
600A is shown having a lattice structure in order to reduce weight
while maintaining strength. Shift cam ring 600 is rotatable within
transmission case 20.
[0107] FIG. 23 is an end view of shift cam ring 600.
[0108] FIG. 24 is a perspective view of shift cam ring 600. Each
shift circumferential surface 601A and 602A is disposed at opposite
ends of member 600A. Each surface 601A and 602A comprises a
radially inward surface of the shift cam ring 600.
[0109] Circumferential surface 601A comprises a plurality of
features each having a differing slope or radius. A radial position
of rollers 603 engaging compliant member 601 thereby shift dog 702A
and 802A is each determined according to which surface of 601A is
engaging rollers 603.
[0110] Circumferential surface 602A comprises a plurality of
features each having a differing slope or radius. A radial position
of rollers 603 engaging compliant member 601 and thereby shift dog
720 and 721 is each determined according to which surface of 602A
is engaging rollers 603.
[0111] Circumferential surface 603A comprises a plurality of
features each having a differing slope or radius. A radial position
of rollers 603 engaging compliant member 601 and thereby shift dog
702B and 802B is each determined according to which surface of 603A
is rollers 603.
[0112] Circumferential surface 601B comprises a plurality of
features each having a differing slope or radius. A radial position
of rollers 603 engaging compliant member 601 and thereby shift dog
820 and 821 is each determined according to which surface of 601B
is engaging rollers 603. 602. Each surface 603A and 601B comprises
a radially inward surface of the shift cam ring 600.
[0113] FIG. 25 is an end view of shift cam ring. Shift cam ring 600
comprises member 600A and 600B for ease of manufacture and
assembly. Member 600B is cylindrical.
[0114] Shift cam ring 600 is disposed in the transmission outermost
from the planetary gear sets and within the transmission case 20,
see FIG. 5. The transmission is shifted by rotation of the shift
cam ring 600 through extension and retraction of shift cables 1, 2
see FIG. 14.
[0115] FIG. 26 is a side view of the shift cam ring.
[0116] FIG. 27 is an end view of shift cam ring.
[0117] FIG. 28 is a perspective view of the shaft cam ring. Member
600B comprises extended members 601B and 602B. each member 601B and
602B engages a cooperating portion of 600A, namely, slots 603A and
604A.
[0118] FIG. 29 is a perspective view of a shift dog. Portion 7002
receives member 601. Member 601 comprises a resilient material
which can be compressed and will rebound when the compression is
released.
[0119] Each shift dog 701, 801 and 702, 802 is identical to the
others. For each shift dog 702, 802 a member 602 is fixed to
portion 7002.
[0120] FIG. 30 is a plan view of a shift dog. Receiving portion 760
receives a member 601. Each shift dog 720, 820, 721, 821 is
identical to the others. For each shift dog 720, 820, 721 and 821 a
member 602 is fixed to portion 760.
[0121] FIG. 31 is a side view of a shift dog. Receiving portion 760
receives a member 601.
[0122] FIG. 32 is a perspective view of a shift dog. Shift dog 820
is pivotally mounted to a dog mount 840. Dog mount 840 is fastened
to case 20 (not shown). A roller 603 is disposed between surface
601B and member 601.
[0123] FIG. 33 is a perspective view of a shift dog. Spring 8001A
biases shift dog 820 toward teeth 213.
[0124] FIG. 34 is a perspective view of a shift dog. Shift dog 840
is fastened to case 20.
[0125] FIG. 35 is a perspective view of a shift dog. Shift dog 720
is pivotally mounted to dog mount 740. Spring 8001A biases shift
dog 720 toward teeth 212. A roller 603 is disposed between a
surface 602A and a member 601.
[0126] FIG. 36 is a perspective view of a shift dog. Dog mount 740
is fastened to case 20.
[0127] FIG. 37 is a detail of FIG. 18. One way clutch dog 920 is
pivotally mounted to carrier 300. Spring 921 biases one way clutch
dog 920 against teeth 213 of ring gear R4. One way clutch dog 920
allows a reverse rotational movement of ring gear R4 by disengaging
teeth 213. Depending upon the particular gear that is engaged, the
one way clutch is the "free wheel" feature of the transmission
which allows a rider to stop pedaling and coast. A second identical
one way clutch dog is disposed opposite that shown in FIG. 37,
thereby forming a pair of one way clutch shift dogs.
[0128] FIG. 38 is a detail of FIG. 19. One way clutch dog 930 is
pivotally mounted to carrier 200. Spring 931 biases one way clutch
dog 930 against teeth 401 of ring gear R1. One way clutch dog 930
prevents a reverse rotational movement of ring gear R1 by engaging
teeth 401. One way clutch dog 930 allows a forward rotational
movement of ring gear R1 relative to carrier 200 by disengaging
from teeth 401. Depending upon the particular gear that is engaged,
the one way clutch is the "free wheel" feature of the transmission
which allows a rider to stop pedaling and coast. A second identical
one way clutch dog is disposed opposite that shown in FIG. 38,
thereby forming a pair of one way clutch shift dogs.
[0129] FIG. 39 is a detail of FIG. 19. One way clutch dog 901 is
pivotally mounted to carrier 100. Spring 902 biases one way clutch
dog 901 against teeth 401 of ring gear R1. One way clutch dog 901
allows forward rotational movement of ring gear R1 relative to
carrier 100 by disengaging teeth 401. One way clutch dog 901
prevents a reverse rotational movement of ring gear R1 by engaging
teeth 401. Depending upon the particular gear that is engaged, the
one way clutch is the "free wheel" feature of the transmission
which allows a rider to stop pedaling and coast. A second,
identical one way clutch dog is disposed opposite that shown in
FIG. 39, thereby forming a pair of one way clutch shift dogs.
[0130] FIG. 40 is a detail of FIG. 6. Roller 603 engages surface
601A, thereby pressing upon member 602 which in turn presses shift
dog 701, thereby disengaging shift dog 702 from teeth 210.
[0131] Use of resilient member 602 allows the shift cams to rotate
while the shift dog is still engaged with the teeth. The cams can
rotate and compress the resilient member while the dog is engaged
with the teeth and compressively loaded. When a bicycle rider
pedals a bicycle, the torque input into the transmission is cyclic
as the input shifts from one pedal to the other. Even for the very
best cyclists, the input torque drops to zero or near zero during
this transfer of input from one pedal the other. Due to the cyclic
input loading of a pedaling bicycle rider, when the torque
momentarily approaches or reaches zero, the force on the shift
dog/tooth interface also drops to zero or near zero, it is at this
moment that the shift dog will rotate out of engagement due to the
resilient member's desire to return to a relaxed state. This gives
the rider the impression of being able to shift under load while in
actuality the shift occurs under near no load conditions.
[0132] A duplicate set of shift dogs as described in this FIG. 38
are likewise mounted in area "A". All shift dogs 701, 702, 801, 802
are pivotally mounted to member 205 at mounting portions 2051,
2052, 2053, 2054 respectively.
[0133] FIG. 41 is a detail of FIG. 6. Shift dog 701 is allowed to
move radially outward by a movement of roller 601, which roller
follows surface 601A as surface 601A is rotated during a shift by a
rider. Shift dog 702 is shown fully engaged with teeth 210. Shift
dog 701 cooperatively engages protrusion 803, which in turn allows
shift dog 702 to pivot and thereby engage teeth 210. Spring 7001A
urges shift dog 801 into engagement with roller 601, and thereby
said roller 601 into surface 601A. Shift dogs 802 and 702 are able
to pivot independently of each other, but because of the
cooperative arrangement of protrusion 803 and shift dog 701, they
cannot both engage with the teeth of their respective sun gears at
the same time. If shift dog 702 is engaged with teeth 210, then the
relation of protrusion 803 and shift dog 701 prevents shift dog 802
from engaging teeth 211. Conversely, if shift dog 802 is engaged
with teeth 211, shift dog 702 cannot pivot to engage with teeth
210.
[0134] FIG. 42 is a detail of FIG. 6. Since shift dog 701 is fully
pressed by roller 603, shift dog 702 is fully disengaged from teeth
210. Shift dog 701 cooperatively engages protrusion 803, which in
turn prevents shift dog 702 from pivoting to engage teeth 210.
Protrusion 803 is positioned radially above shift dog 701. If shift
dog 701 rotates to engage teeth 210, shift dog 802 is held out of
engagement with teeth 211 as shown in FIG. 39. Shift dog 802 is
prevented from engaging teeth 211 by the cooperative arrangement of
protrusion 803 and shift dog 701.
[0135] When shift dog 802 is engaged with teeth 211 as shown in
FIG. 40 shift dog 702 is prevented from engaging teeth 210 by the
arrangement of protrusion 803 and shift dog 701. Both shift dogs
702 and 802 can be disengaged from teeth 210 and 211
simultaneously. Shift dogs 702, 802 are prevented from engaging the
teeth simultaneously by the cooperative arrangement of protrusion
803 and shift dog 701. Each protrusion 703, 803 is identical to the
other. Protrusion 703 extends from the end of shift dog 701.
Protrusion 803 extends from the end of shift dog 801.
[0136] Although a form of the invention has been described herein,
it will be obvious to those skilled in the art that variations may
be made in the construction and relation of parts without departing
from the spirit and scope of the invention described herein.
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