U.S. patent application number 10/760566 was filed with the patent office on 2004-08-05 for variable speed transmission and electronic speed control therefor.
Invention is credited to Johnson, Kevin L., Ruebusch, Richard T., Voyles, Jason D..
Application Number | 20040152546 10/760566 |
Document ID | / |
Family ID | 26912801 |
Filed Date | 2004-08-05 |
United States Patent
Application |
20040152546 |
Kind Code |
A1 |
Johnson, Kevin L. ; et
al. |
August 5, 2004 |
Variable speed transmission and electronic speed control
therefor
Abstract
A variable speed transmission including a housing, a drive shaft
having an axis of rotation and rotatably supported in the housing,
an output shaft having an axis of rotation and rotatably supported
in the housing, a first pulley and a second pulley both having a
common axis of rotation, a third pulley having an axis of rotation
and rotatably attached to the drive shaft, and a belt. The output
shaft is operatively connected to the drive shaft. The first pulley
and the second pulley each have a variable pitch diameter and
changes in the first and second pulley variable pitch diameters
being inversely proportional. The third pulley and one of the first
and the second pulleys are in engagement though the belt.
Inventors: |
Johnson, Kevin L.; (Douglas,
GA) ; Ruebusch, Richard T.; (New Albany, IN) ;
Voyles, Jason D.; (Salem, IN) |
Correspondence
Address: |
BAKER & DANIELS
111 E. WAYNE STREET
SUITE 800
FORT WAYNE
IN
46802
|
Family ID: |
26912801 |
Appl. No.: |
10/760566 |
Filed: |
January 20, 2004 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
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10760566 |
Jan 20, 2004 |
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09902412 |
Jul 10, 2001 |
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6705961 |
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60218332 |
Jul 14, 2000 |
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Current U.S.
Class: |
474/33 ; 474/35;
474/70 |
Current CPC
Class: |
F16H 61/66259 20130101;
F16H 2009/166 20130101; F16H 63/062 20130101 |
Class at
Publication: |
474/033 ;
474/035; 474/070 |
International
Class: |
F16H 009/16; F16H
063/00 |
Claims
What is claimed is:
1. A variable speed transmission, comprising: a housing; a drive
shaft having an axis of rotation and rotatably supported in said
housing; an output shaft having an axis of rotation and rotatably
supported in said housing, said output shaft operatively connected
to said drive shaft; a first pulley and a second pulley both having
a common axis of rotation, said first pulley and said second pulley
each having a variable pitch diameter, changes in said first and
second pulley variable pitch diameters being inversely
proportional; a third pulley having an axis of rotation and
rotatably attached to said drive shaft; and a belt, said third
pulley and one of said first and said second pulleys being in
engagement though said belt.
2. The transmission of claim 1, wherein said output shaft is an
axle, said axle axis of rotation being perpendicularly disposed to
said drive shaft axis of rotation, said axle being selectively
operatively connected to said drive shaft.
3. The transmission of claim 2, further comprising a clutch
mechanism, said axle being selectively operatively connected to
said drive shaft through said clutch mechanism.
4. The transmission of claim 1, further comprising a pivot pulley
assembly which comprises said first and said second pulleys, said
pivot pulley assembly further comprising a pivot arm pivotably
attached to said housing, said first and second pulleys being
rotatably attached to said pivot arm.
5. The transmission of claim 4, wherein said axes of rotation of
said first and third pulleys are parallel but separated.
6. The transmission of claim 5, wherein said pivot arm is manually
pivoted relative to said housing, the distance between said axes of
rotation of said first and third pulleys is changed in response to
movement of said pivot arm.
7. The transmission of claim 6, wherein said first and said second
pulley pitch diameters are varied in response to movement of said
pivot arm, whereby a drive ratio between said first and said second
pulleys is varied.
8. The transmission of claim 5, further comprising an electric
linear actuator operatively connected to said pivot arm, said
linear actuator having a first position and a variable second
position.
9. The transmission of claim 8, wherein said pivot arm has a first
position when said linear actuator is in its said first position,
and said pivot arm has a second position when said linear actuator
is in its said second position.
10. The transmission of claim 9, wherein said first and said second
actuator positions are variable and said first and second pivot arm
positions are variable, whereby the drive ratio between said first
and second pulleys is variable.
11. The transmission of claim 1, wherein said third pulley has a
variable pitch diameter which is varied in response to changes in
the pitch diameter of said one of said first and second
pulleys.
12. The transmission of claim 11, further comprising a spring in
engagement with said third pulley, said third pulley variable pitch
diameter being biased into its smallest sized diameter by said
spring, whereby engagement of said third pulley and said one of
said first and second pulleys through said belt is maintained.
13. The transmission of claim 11, wherein a drive ratio between
said third pulley and said one of said first and second pulleys is
variable.
14. An implement comprising: a deck; an engine attached to said
deck and having a pulley; an axle rotatably supported by said deck;
a ground engaging wheel driven by said axle; and a variable speed
transmission attached to said deck and comprising: a housing, a
drive shaft having an axis of rotation and rotatably supported in
said housing, said drive shaft being operatively connected to said
axle, a first variable pitch diameter pulley and a second variable
pitch diameter pulley, said first variable pitch diameter pulley
and said second variable pitch diameter pulley having a common axis
of rotation, said first variable pitch diameter pulley having a
first variable pitch diameter and said second variable pitch
diameter pulley having a second variable pitch diameter, said first
and said second variable pitch diameters being in an inversely
proportional relationship, a third pulley rotatably attached to
said drive shaft, and a transmission belt, said third pulley
assembly and one of said first and said second variable pitch
diameter pulleys being in engagement though said belt; and a drive
belt extending between said engine pulley and the other of said
first and second pulleys.
15. The implement of claim 14, further comprising a pivot pulley
assembly which comprises said first and said second pulleys, said
pivot pulley assembly further comprising a pivot arm pivotably
attached to said housing, said first and second pulleys being
rotatably attached to said pivot arm.
16. The implement of claim 15, wherein said first and said second
pulley pitch diameters are varied in response to movement of said
pivot arm, whereby a drive ratio between said first and said second
pulleys is varied.
17. The implement of claim 16, wherein said engine maintains a
substantially constant speed, and said third pulley has a speed
which is varied in response to variation of said first and said
second variable pitch diameters.
18. The implement of claim 17, wherein said third pulley has a
variable pitch diameter, said third pulley having a speed which is
varied in response to variation in said third pulley pitch
diameter.
19. The implement of claim 15, further comprising a linear actuator
operatively connected to said pivot arm, said linear actuator being
electronically moved, wherein said pivot arm is pivoted by said
linear actuator and said pivot pulley assembly is moved in response
to rotational movement of said pivot arm.
20. An electronic ground speed regulator for an implement,
comprising: a variable speed transmission having a speed control
mechanism; an electric linear actuator in communication with said
speed control mechanism, said actuator having a first position and
a second position and being moved therebetween in response to
changes in an electrical input to said actuator, said speed control
mechanism being varied in response to movement of said actuator
from one of said first and second positions to the other of said
first and second positions; an electronic control circuit in
electrical communication with said actuator, said electronic
circuit having a first condition wherein said electronic control
circuit maintains said actuator in one of its said first and second
positions and a second condition wherein said electronic control
circuit controls movement of said actuator between its said first
and second positions; and an operator-manipulated switch in
electrical communication with said electronic control circuit,
movement of said actuator being controlled through manipulation of
said switch.
21. The electronic speed regulator of claim 20, wherein said first
and second positions are variable positions.
Description
CROSS REFERENCE TO RELATED APPLICATIONS
[0001] This application is related to and claims the benefit under
35 U.S.C. .sctn. 119(e) of U.S. Provisional Application Serial No.
60/218,332, entitled VARIABLE SPEED TRANSMISSION, filed on Jul. 14,
2000.
BACKGROUND OF THE INVENTION
[0002] 1. Field of the Invention
[0003] This invention relates to belt drive systems for vehicles
and, more particularly, to a belt drive system for lawn and garden
tractors, walk-behind mowers and other vehicles which utilize a
constant engine drive speed to propel the vehicle at variable
speeds.
[0004] 2. Description of the Related Art
[0005] Variable speed transmission assemblies for lawn and garden
tractors and self-propelled walk-behind mowers allow for the ground
speed to be varied while maintaining a constant engine speed.
Constant engine speed facilitates, for example, effective cutting
by mower blades. Previous variable speed transmission designs, such
as those disclosed in U.S. Pat. No. 6,142,898 (Miyata), have
incorporated various planetary gear arrangements. Other variable
speed transmission designs, such as those disclosed in U.S. Pat.
No. 4,484,901 (Toti et al.) and U.S. Pat. No. 4,934,989 (Furukawa
et al.), include multiple drive belt and multiple pulley systems to
propel a mower or tractor while still maintaining a constant engine
speed.
[0006] Planetary gear arrangements usually include a series of
intermeshed gears to provide a suitable mower axle speed when the
engine is operating at a relatively fast engine shaft speed. A
problem with such planetary gear arrangements is that they
considerably increase mower costs. Multiple drive belt and pulley
systems, such as that disclosed in U.S. Pat. No. 4,934,989
(Furukawa et al.), typically include at least one belt tensioner or
idle pulley which is merely used to maintain tension on the belts.
However, these systems generally require more space and, like
planetary gear arrangements, increase the mower costs since the
systems require more expensive assembly operations.
[0007] An inexpensive infinitely variable speed transmission which
includes a declutching mechanism and allows for greater ease of
control by the operator would be highly desirable.
SUMMARY OF THE INVENTION
[0008] The present invention provides a variable speed transmission
which overcomes the disadvantages of prior transmissions and/or
speed controls therefor by providing an inexpensive variable speed
transmission that requires less space through the use of
self-adjusting pulleys. Additionally, a clutch mechanism is
provided on the transmission for clutching and declutching the
transmission. Furthermore, the operator need only move the pivot
arm of the transmission to cause a change in the speed of the
transmission, thereby providing ease of control of the
transmission. The variable speed transmission may include an
electronic speed control to prevent the varying the speed setting
of the transmission while the engine is not running and to
facilitate easy ground speed changes to an implement, such as a
walk-behind mower, having the inventive transmission. Furthermore,
the electronic speed control allows the operator to select the
desired speed by tapping a switch, thereby providing additional
eases of control of the transmission.
[0009] The present invention provides a variable speed transmission
including a housing, a drive shaft having an axis of rotation and
rotatably supported in the housing, an output shaft having an axis
of rotation and rotatably supported in the housing, a first pulley
and a second pulley both having a common axis of rotation, a third
pulley having an axis of rotation and rotatably attached to the
drive shaft, and a belt. The output shaft is operatively connected
to the drive shaft. The first pulley and the second pulley each
have a variable pitch diameter and changes in the first and second
pulley variable pitch diameters being inversely proportional. The
third pulley and one of the first and the second pulleys are in
engagement though the belt.
[0010] The present invention further provides an implement
including a deck, an engine attached to the deck and having a
pulley, an axle rotatably supported by the deck, a ground engaging
wheel driven by the axle, a variable speed transmission attached to
the deck, and a drive belt. The variable speed transmission
includes a housing, a drive shaft having an axis of rotation and
rotatably supported in the housing, a first variable pitch diameter
pulley and a second variable pitch diameter pulley having a common
axis of rotation, a third pulley rotatably attached to the drive
shaft, and a transmission belt. The drive shaft is operatively
connected to the axle. The first variable pitch diameter pulley has
a first variable pitch diameter and the second variable pitch
diameter pulley has a second variable pitch diameter and the first
and the second variable pitch diameters are in an inversely
proportional relationship. The third pulley assembly and one of the
first and the second variable pitch diameter pulleys are in
engagement though the transmission belt. The drive belt extends
between the engine pulley and the other of the first and second
pulleys.
[0011] The present invention further provides an electronic ground
speed regulator for an implement including a variable speed
transmission having a speed control mechanism, an electric linear
actuator in communication with the speed control mechanism, an
electronic control circuit in electrical communication with the
actuator, and an operator-manipulated switch in electrical
communication with the electronic control circuit. The actuator has
a first position and a second position and is moved therebetween in
response to changes in an electrical input to the actuator, and the
speed control mechanism is varied in response to movement of the
actuator from one of the first and second positions to the other of
the first and second positions. The electronic circuit has a first
condition wherein the electronic control circuit maintains the
actuator in one of its first and second positions and a second
condition wherein the electronic control circuit controls movement
of the actuator between its first and second positions. Movement of
the actuator is controlled through manipulation of the switch.
BRIEF DESCRIPTION OF THE DRAWINGS
[0012] The above mentioned and other features and objects of this
invention will become more apparent and the invention itself will
be better understood by reference to the following description of
embodiments of the invention taken in conjunction with the
accompanying drawings, wherein:
[0013] FIG. 1A is a first embodiment of an implement having a
variable speed transmission in accordance with the present
invention, the transmission being manually actuated;
[0014] FIG. 1B is a second embodiment of the implement of FIG. 1 A,
the transmission being electronically actuated;
[0015] FIG. 2 is an upper rear perspective view of a first
embodiment variable speed transmission in accordance with the
present invention;
[0016] FIG. 3 is a lower rear perspective view of the variable
speed transmission of FIG. 2;
[0017] FIG. 4 is a top plan view of the variable speed transmission
of FIG. 2;
[0018] FIG. 5 is a sectional view of the variable speed
transmission of FIG. 4 along line 5-5;
[0019] FIG. 6A is an exploded view of the variable speed
transmission of FIG. 2;
[0020] FIG. 6B is a portion of the exploded view of FIG. 6A showing
an alternative embodiment of the pivot pulley assembly;
[0021] FIG. 7 is a sectional view of the variable speed
transmission of FIG. 4 along line 7-7;
[0022] FIG. 8 is a top plan view of the variable speed transmission
of FIG. 2 showing engagement of the drive belt with the output
pulley of a power source and corresponding to a pivot arm position
which provides the greatest axle speed;
[0023] FIG. 9 is a top plan view of the variable speed transmission
of FIG. 2 showing engagement with the output pulley of a power
source and corresponding to a pivot arm position which provides the
lowest axle speed;
[0024] FIG. 10 is a sectional view of the variable speed
transmission of FIG. 8 taken along line 10-10, the belts sectioned
for clarity;
[0025] FIG. 11 is a sectional view of the variable speed
transmission of FIG. 9 taken along line 11-11, the belts sectioned
for clarity;
[0026] FIG. 12 is an enlarged view of encircled area 12 of FIG. 11,
showing the worm drive and axle support structure;
[0027] FIG. 13 is a top plan view of a second embodiment of a
variable speed transmission in accordance with the present
invention;
[0028] FIG. 14 is a sectional view of the variable speed
transmission of FIG. 13 taken along line 14-14;
[0029] FIG. 15 is a top plan view of a third embodiment of a
variable speed transmission in accordance with the present
invention, including the transmission of FIG. 13 having an
alternative pivot arm assembly;
[0030] FIG. 16 is an elevational view of the variable speed
transmission of FIG. 13 partially in section;
[0031] FIG. 17 is an elevational view of a fourth embodiment of a
variable speed transmission in accordance with the present
invention partially in section and showing a modified pivot pulley
assembly; and
[0032] FIG. 18 is a circuit schematic of an electronic shift
control for a variable speed transmission in accordance with the
present invention.
[0033] Corresponding reference characters indicate corresponding
parts throughout the several views. The exemplifications set out
herein illustrate embodiments of the invention and such
exemplifications are not to be construed as limiting the scope of
the invention in any manner.
DETAILED DESCRIPTION
[0034] For the purposes of promoting an understanding of the
principles of the invention, reference will now be made to the
embodiments illustrated in the drawings and specific language will
be used to describe the same. It will nevertheless be understood
that no limitation of the scope of the invention is thereby
intended.
[0035] Referring first to FIGS. 1A and 1B, implement, or lawnmower,
2 is shown as having engine 5 mounted on deck 9 and handle 3
attached to deck 9. Attached to the ends of axle 20 (FIG. 2) are
ground engaging wheels 4; however, ground engaging wheels 4 may be
rotatably attached to deck 9 and driven by axle 20 through
reduction gearing (not shown). Bail 7 is attached to handle 3 and
has cable linkage 11 to move actuator lever 50 and engage a clutch
in transaxle housing assembly 12, thereby allowing movement of
implement 2, as described hereinbelow. As shown in FIG. 1A, handle
3 may include a manual control mechanism 6 which is used by the
operator to move cable 8, thereby moving pivot arm 26 (FIG. 2).
Alternatively, as shown in FIG. 1B, handle 3 may include switch 166
connected to linear actuator 168, which is then used to move cable
8 and pivot arm 26.
[0036] Referring to FIGS. 2 and 3, first embodiment variable speed
transmission 10 includes housing assembly 12 comprising two halves,
14 and 16, which are fastened together by a plurality of bolts 18
at interface 17. Axle 20 has axis of rotation 19 and is rotatably
supported within housing 12 by a pair of roller bearings 13 and 15
provided respectively in sleeve assemblies 22 and 23 (FIGS. 5, 6A
and 12), which are fixed between housing halves 14 and 16.
Cylindrical boss 24 is integrally attached to external surface 25
of housing half 14 and extends vertically relative to housing half
14. Pivot post 28 is rotatable within a through hole (not shown)
formed in boss 24, and supports pivot arm 26 which is fixed to an
end of pivot post 28. Pivot arm 26 includes pulley post 30, upon
which is rotatably supported pivot pulley assembly 32, which is
retained on post 30 by retaining ring 34 engaged within a groove
formed within post 30. Washer 36 is positioned between pivot pulley
assembly 32 and retaining ring 34 to allow non-binding rotation of
pulley assembly 32.
[0037] Engagement and disengagement of transmission 10 is exercised
selectively through operator control of cable linkage 11 (FIGS. 1A
and 1B) linked to actuator lever 50, which is fixed to actuator rod
54 and includes slot 52 that conforms to and is engaged with flats
55 and 57 of rod 54. Actuator rod 54 is rotatably supported within
housing 12 and includes a pair of flats 55 and 57 extending through
slot 52 to prevent lever rotation relative to actuator rod 54 (FIG.
4). Actuator lever 50 is prevented from being detached from
actuator rod 54 by retaining ring 56 which is engaged within a
groove positioned at an upper end of actuator rod 54. Spring 58 is
attached between actuator lever 50 and post 48 (FIG. 2) to return
actuator lever 50 to a position corresponding to disengagement of
drive shaft 44 from axle 20 (FIG. 6A) when actuator lever 50 is not
selectively engaged. Notch 60 is provided at an end of actuator
lever 50 to accommodate cable linkage 11 (FIGS. 1A and 1B) to
rotate actuator rod 54, which in turn, engages and disengages drive
shaft 44 from axle 20 as further described hereinbelow.
[0038] Pivot pulley assembly 32 and transmission pulley assembly 42
are externally positioned relative to housing 12 of transmission
10, and pivot pulley assembly 32 is engaged by both first
mechanical linkage, or transmission belt, 40 and second mechanical
linkage, or drive belt, 38, respectively (FIGS. 2-6A, 8-11). Pivot
pulley assembly 32 includes axis of rotation 61 and transmission
pulley assembly 42 includes axis of rotation 62 (FIGS. 10-11). It
may be seen that selective rotation of pivot arm 26 effectuates
movement of rotational axis 61 relative to rotational axis 62, such
as in the direction of arrow 35, as shown in FIG. 8. Pivot pulley
assembly 32, as best seen in FIGS. 2, 6A, 10 and 11, includes
pulley end 64 integrally attached to hexagonally shaped hub 66 and
rotatably supported by pulley post 30. Second pulley end 68
includes hexagonally shaped hole 69 axially and slidably engaged
with hub 66 (FIG. 6A) to prevent rotational movement of pulley end
68 relative to hub 66. Pulley end 68 is retained on post 30 by
circumferentially engaged retaining ring 74, and thrust washer 72
is placed between retaining ring 74 and pulley end 64 to prevent
rotational binding therebetween. Pulley center section 70 is
arranged intermediate pulley ends 64 and 68 respectively, and
includes inner hexagonally shaped hole 75 through which hub 66
slidably extends to provide movement of center section 70 axially
along hub 66. Having center section 70 arranged in this manner
provides a first pulley and a second pulley, each having variable
pitch diameters, which are in an inversely proportional
relationship.
[0039] Referring now to FIGS. 2, 3, 6A and 7, transmission pulley
assembly, or third pulley, 42 includes pulley end 80 rotatably
supported upon retaining ring 79 (FIGS. 6A and 7). Retaining ring
79 is engaged within a circumferentially formed groove provided in
drive shaft 44. Pulley end 80 is integrally attached to a first end
of hexagonally shaped hub 82 (FIGS. 2 and 6A) and a second end of
hub 82 slidably extends through hexagonally shaped through hole 85
(FIG. 6A) of pulley end 84. As best seen in FIGS. 2 and 5,
compression spring 86 is positioned between pulley end 84 and
retaining ring 90 to impart a continuous axial force upon pulley
end 84. This axial force is transferred to transmission belt 40 to
maintain continuous operative engagement between transmission
pulley assembly 42 and transmission belt 40 (FIGS. 8 and 10).
Compression spring 86 may be any suitable compression spring, such
as a SMALLEY.RTM. spring manufactured by the Smalley Steel Ring
Company of Wheeling, Ill. Retaining ring 90 is engaged within a
circumferential groove provided in hub 82, and thrust washer 88 is
positioned between compression spring 86 and retaining ring 90.
Second retaining ring 92 is received in a circumferential groove
provided in drive shaft 44 and abuts an axial end of hub portion 84
to retain pulley end 80 and hub 82 relative to drive shaft 44.
[0040] In an alternative embodiment of pivot pulley assembly 32,
shown in FIG. 6B, pivot pulley assembly 32' includes pulley end 64'
integrally attached to cylindrical hub 66' and rotatably supported
by pulley post 30. Pulley end 68' is affixed to cylindrical hub 66'
by hole 69' and is retained on post 30 in a manner similar to that
of pulley end 68. Pulley center section 70' is arranged
intermediate pulley ends 64' and 68', similar to pulley center
section 70, and is mounted on bushing 71. Bushing 71 includes hole
75' through which hub 66' extends such that center section 70'
moves axially along hub 66'. In operation, pivot pulley assembly
32' operates in a manner similar to pivot pulley assembly 32 and
may replace pivot pulley assembly 32.
[0041] With reference to FIGS. 10 and 11, drive belt 38 is engaged
with pivot pulley assembly 32, and transmission belt 40 is engaged
with both pivot pulley assembly 32 and transmission pulley assembly
42. As drive belt 38 continuously rotates, so does transmission
belt 40. With reference to FIG. 10, transmission belt 40 engages
pivot pulley assembly 32 at first variable radial position of
engagement R.sub.1 and transmission pulley assembly 42 at third
variable radial position of engagement R.sub.3. Drive belt 38
engages pivot pulley assembly 32 at second variable radial position
of engagement R.sub.2.
[0042] Belts 38 and 40 are positioned on pulley assemblies 32 and
42, such that first variable radial position of engagement R.sub.1,
located between pulley end 68 and pulley center section 70, is
measured radially from axis of rotation 61 of pivot pulley assembly
32. Drive belt 38 is engaged with pivot pulley assembly 32 at
second variable radial position of engagement R.sub.2, located
between pulley end 64 and pulley center section 70. Similar to the
first variable radial position of engagement R.sub.1, second
variable radial position of engagement R.sub.2 is measured radially
from axis of rotation 61 of pivot pulley assembly 32. Since drive
belt 38 and transmission belt 40 share axial moveable center
section 70, the position of center section 70 axially along hub 66
varies and is generally dependent on the positions and tension of
belts 38 and 40. For instance, if drive belt 38 is at its maximum
tension and transmission belt is at an intermediate tension, their
positions and corresponding tensions then place center section 70
axially closer to pulley end 68.
[0043] Rotational speed of transmission pulley 42 may be expressed
in terms of R.sub.1, R.sub.2 and R.sub.3. Generally, linear belt
velocity, relative to a circular revolving pulley, may be expressed
as: V=2B*T*R, where V=belt velocity, T=angular pulley speed in
revolutions per minute (RPM) and R=radial distance of the
engagement between the belt and pulley from the respective pulley
axis of rotation. With reference to FIGS. 8 and 10, a set of four
equations may be identified relating to the speed of the drive and
transmission belts. The equations are expressed as follows:
V.sub.drivebelt=2B*T.sub.drive pulley*R.sub.drive pulley/belt
V.sub.drivebelt=2B*T.sub.pivot pulley*R.sub.2
V.sub.transmission belt=2B*T.sub.pivot pulley*R.sub.1
V.sub.transmission belt=2B*T.sub.transmission pulley*R.sub.3
[0044] where:
[0045] V.sub.drivebelt=velocity of drive belt 38.
[0046] V.sub.transmission belt=velocity of transmission belt
40.
[0047] T.sub.drive pulley=angular speed of drive pulley 41.
[0048] T.sub.pivot pulley=angular speed of pivot pulley 32.
[0049] T.sub.transmission pulley=angular speed of transmission
pulley 42.
[0050] R.sub.drive pulley/drive belt=radial position of engagement
between drive pulley 41 and drive belt 38.
[0051] R.sub.2=radial position of engagement between pivot pulley
32 and drive belt 38.
[0052] R.sub.1=radial position of engagement between pivot pulley
32 and transmission belt 40.
[0053] R.sub.3=radial position of engagement between transmission
pulley 42 and transmission belt 40.
[0054] The aforesaid equations may be combined to form a single
expression: 1 T transmission pulley = R drive pulley / drive belt *
T drive pulley * R 1 R 2 * R 3
[0055] Since drive pulley 41 remains generally constant in radial
position relative to drive belt 38 and the angular speed of drive
pulley 41 remains generally constant, it should be noted that the
angular speed of transmission pulley 42 is generally dependent on
R.sub.1, R.sub.2 and R.sub.3. It may be seen, in view of the above
equation, that the fastest rotation of transmission pulley 42 is
obtained when R.sub.1 is at its largest radial position, or far
from hub 66, and R.sub.2 and R.sub.3 are at their smallest radii of
engagement with the respective belts, or close to hub 66 and hub
82, (FIGS. 8 and 10). Conversely, the slowest rotation of
transmission pulley 42 is obtained when R.sub.1' is at its smallest
radial position, or close to hub 66, and R.sub.2' and R.sub.3' are
at their largest radii of engagement with the respective belts, or
far from hub 66 and hub 82 (FIGS. 9 and 11). It will be understood
by those having ordinary skill in the art that this variable speed
transmission not only operates in conformity with the fastest and
slowest speed setting, as set forth above, but also provides
infinitely variable speed settings therebetween. Selective rotation
of pivot arm 26 by operator engagement of manual control mechanism
6 connected to hole 63 of pivot arm 26, provides varying axle
speeds ranging from slowest (FIGS. 9 and 11) to fastest (FIGS. 8
and 10).
[0056] It may be seen that movement of pivot arm 26 in the
direction indicated by arrow 35 (FIG. 8) causes immediate loosening
or "slack" in both belts 38 and 40. The aforesaid slack in
transmission belt 40 immediately dissipates as pulley end 84 is
urged toward pulley end 80 by spring 86, which causes an increase
in radial position of engagement R.sub.3 of transmission belt 40.
The slack in drive belt 38 immediately dissipates as drive belt 38
conforms to a new, larger radial position of engagement R.sub.2 of
drive belt 38 engaged with pivot pulley assembly 32. Both center
section 70 of pivot pulley assembly 32 and pulley end 84 of
transmission pulley assembly 42 are "responsive" (i.e., provide an
equilibrium position for belts 38 and 40 relative to pulley
assemblies 32 and 42) to selective rotation of pivot arm 26.
[0057] As shown in FIGS. 8 and 9, transmission pulley 42 is located
to the left of pivot pulley assembly 32. As such, drive belt 38
rotates in the clockwise direction, thus creating position of
radial engagement R.sub.2 at the point where drive belt 38 contacts
pivot pulley assembly 32. The distance between R.sub.2 and pivot
post 28 is equivalent to a moment arm D.sub.2 of the pivot pulley
assembly 32. As shown, moment arm D.sub.2 is relatively long,
thereby enabling a greater control of transmission 10 through
easier movement of pivot arm 26 and pivot pulley assembly 32 when
manually actuated due to a decrease in the amount of force required
to rotate pivot arm 26. Additionally, using the structure shown
allows for the usage of a smaller electronically controlled linear
actuator, since less force is needed to rotate pivot arm 26. The
structure shown is advantageous over a structure in which
transmission pulley 42 would be located to the right of pivot
pulley assembly 32. In that structure, the distance between pivot
post 28 and R.sub.2, or moment arm D.sub.1, is much less, thereby
making movement of pivot pulley assembly 32 more difficult since a
larger amount of force would be necessary to rotate pivot arm 26
whether using manual or electronic means.
[0058] Referring to FIG. 7, housing 12 of transmission 10 includes
sealed internal cavity 102, provided with lubrication oil (FIGS. 7
and 12). Shaft seal 100 is captured within a recessed portion of
housing half 14 to seal surface 95 of drive shaft 44 and enclose
lubrication oil provided in cavity 102 of housing 12 (FIG. 7).
Referring to FIG. 12, a pair of seals 107 and 109 provide a
lubrication barrier between axle 20 and housing 12 and are included
in each respective sleeve assembly 22 and 23 to prevent oil within
cavity 102 from escaping housing 12. Housing seal 104 is provided
between housing halves 14 and 16 to seal housing cavity 102 at
interface 17 (FIG. 7). Oil fill plug 111 is removably attached to
housing 12 to allow for introduction or removal of oil (FIG.
6A).
[0059] Transmission 10 includes external actuator lever 50 which
when rotated by an operator through cable linkage 11 (FIGS. 1A and
1B), causes the transmission drive shaft 44 to operatively engage
axle 20. Referring to FIGS. 6A and 7, drive shaft 44 includes worm
portion 94 located on outer surface 95 thereof, and intermeshed
with worm gear 96. A pair of ball bearing assemblies 103 and 105
are respectively fitted within respective housing halves 14 and 16
to rotatably support drive shaft 44. Referring to FIGS. 6A and 12,
a pair of cone clutches 97 and 98 are rotationally fixed on axle 20
by having notches 106 and 108 provided therein and engaged with
Woodruff key 110 (FIGS. 7 and 12). Woodruff key 110 is engaged
within notch 112 machined into axle 20 by a broaching operation,
for example, as is customary. Cone clutches 97 and 98 respectively
include frustoconical surfaces 114 and 116 which engage
complementary frustoconical surfaces 118 and 120 provided on
lateral sides of worm gear 96 (FIG. 12). A first pair of washers
122 and 124 are in contact with respective outer lateral surfaces
of cone clutches 97 and 98 and a pair of thrust bearings 126 and
128 contact respective washers 122 and 124. A second pair of
washers 134 and 136 contact respective thrust bearings 126 and 128.
Additionally, a pair of spacers 130 and 132 are positioned on
outermost lateral surfaces of washers 134 and 136 and an actuator
plate 138 is positioned intermediate spacer 130 and sleeve assembly
23. Actuator plate 138 is engaged by cam portion 140 (FIG. 6A) as
actuator rod 54 is selectively rotated by an operator through cable
linkage 11 (FIGS. 1A and 1B) attached to actuator lever 50.
[0060] In operation, an inward axial force, provided by actuator
plate 138, is transmitted to cone clutches 97 and 98 causing
frustoconical surfaces 114 and 116 of respective cone clutches 97
and 98 to respectively engage frustoconical surfaces 118 and 120 of
worm gear 96. Rotation of the actuator rod operatively engages the
worm gear and axle 20, through the clutch/worm gear interface, and
axle 20 is thus driven by rotating drive shaft 44. As an
alternative to disengagement of transmission 10, via selective
rotation of actuator lever 50, it is envisioned that pivot arm 26
may be rotated to a position corresponding to a fully slack belt 40
effectively producing insubstantial rotation of belt 40, and thus
insubstantial rotation of transmission pulley 42.
[0061] FIGS. 13, 14, and 16 illustrate a second embodiment of
variable speed transmission 10 wherein elements, which are similar
to the first embodiment, are denoted with the letter "a".
Transmission 10a differs from the first embodiment transmission in
several respects, one of which includes pivot arm 26a having a pair
of arm members 142 and 144 each pivotally attached to boss 24. Bolt
143 extends through arm members 142 and 144 and hole 145 of boss 24
to rotatably support pivot arm 26a (FIG. 16). Lock-nut 147 is
threaded upon bolt 143 to retain bolt 143 within boss 24. Sleeve
146 is rigidly attached to pivot arm 26a by, for example being
welded to arm members 142 and 144 and includes through hole 148. A
pair of bearing assemblies 150 and 152 are located within hole 148
of sleeve 146 to rotatably support shaft 154, which extends
outwardly from sleeve 146 and is rigidly attached to hub 66.
Positioned between a butt end of sleeve 146 and pulley end 64 is
thrust bearing 156 which affords additional rotatable support of
transmission pulley assembly 32.
[0062] Referring to FIG. 14, transmission 10a includes modified
transmission pulley 42a which, relative to transmission pulley 42
(FIGS. 1-3), is inverted. Pivot pulley assembly 32 is driven by
drive belt 38, at an upper portion 158 of pivot pulley assembly 32
and transmission belt 40 is positioned between center section 70
and pulley end 64 (FIG. 16). Axle speed is selected, through
operator rotation of pivot arm 26a, as described above, via cable 8
(FIGS. 1A and 1B). Pivot arm 26a includes a pair of holes 160 and
162 which accommodate connection with the cable linkage.
[0063] Referring to FIG. 15, a third embodiment of a variable speed
transmission is shown having lengthened pivot arm 26b relative to
pivot arm 26a and shown superimposed thereover. Pivot arm 26b
provides an increased range of axle speed control over pivot arm
26a by simply having an increased length.
[0064] A fourth embodiment of a variable speed transmission is
shown in FIG. 17 and includes modified pivot pulley assembly 32b.
Generally, pivot pulley assembly 32b includes smaller diameter
pulleys, relative to pivot pulley assembly 32a, which provides
greater axle speeds corresponding to a maximum radial position of
engagement between belt and respective pulley. For example, when
used with reduced speed power sources, the smaller diameter pivot
pulley assembly 32b, in combination with transmission pulley
assembly 42b, would provide an acceptable range of axle speeds.
Thus, it is envisioned that a variety of somewhat simple
modifications to variable speed transmission 10a, will allow a
manufacturer a variety of power source and transmission
combinations using a single housing and axle assembly.
[0065] Referring now to FIG. 18, electronic speed control mechanism
163 for transmission 10 is shown as including electric control
circuit 164 in communication with a coil (not shown) on engine 5,
switch 166 connected to linear actuator 168, and battery 170.
Linear actuator 168 is used to move pivot arm 26 to vary the speed
of transmission 10, as described above. Linear actuator 168
includes a rod (not shown) which may be either extended or
retracted between variable first and second positions to create the
movement at pivot arm 26. Linear actuator 168 may be any suitable
design for moving a pivot arm, such as, for example, the Electrak
E050 Linear Actuator, manufactured by Warner Electric of South
Beloit, Ill.
[0066] Switch 166 provides electrical communication between
electronic control circuit 164 and linear actuator 168, and is of
any suitable design, such as, for example, those manufactured by
EATON Cutler-Hammer. As shown, switch 166 is a double-pole, single
throw switch, although switch 166 may be any other type of switch
which would provide a connection between circuit 164 and linear
actuator 168. In addition to providing electrical communication
between circuit 164 and linear actuator 168, switch 166, when
closed, allows an operator to change the polarity of linear
actuator 168 in order to extend or retract the rod.
[0067] Electronic control circuit 164 includes relay 172, such as,
for example, OEG relay part number OUDH-S-112D manufactured by Tyco
Electronics of Japan; rectifier 174, such as, for example, a
Kimball-Elka model KBL02 rectifier; transistor 176, such as, for
example, the Motorola 2N3904, diode 178, resistors 180, 182, and
184, and capacitor 186. It should be noted that transistor 176 is
depicted as a Bipolar Junction Transistor (BJT), and terminology
describing the same is used; however, transistor 176 may be a Field
Effect Transistor (FET), such as a MOSFET or JFET. Additionally,
light-emitting diode (LED) 188 is included to provide a display to
the operator that electronic control circuit 164 is being powered.
Battery 170 is provided to power relay 172 and transistor 176. A
cover (not shown) may be used to cover many of the components of
electronic control circuit 164 with LED 188 being mounted in such a
manner as to allow the operator to easily view LED 188.
[0068] In operation, an alternating current signal is sent from
engine 5 by an electrical connection to the coil on the associated
electric motor. When the engine is operating, such a signal will be
generated, whereas when the engine is not operating, there will be
no signal. From the engine, the signal passes through second
resistor 182 and is sent to terminal 3 of rectifier 174, where it
is rectified, in a known manner. From the rectifier, the signal is
sent to capacitor 186 where the signal is filtered for noise. Both
the filtered signal from capacitor 186 and the unfiltered signal
from rectifier 174 are then sent to the base of transistor 176. At
the same time, current is flowing through first resistor 180 and is
being provided to the collector of transistor 176, and input
terminals 2, 5, and 1 of relay 172. From the emitter of transistor
176, current is provided to the negative side of switch 166 and to
ground.
[0069] Output 3 of relay 172, with the current flowing through
diode 178, provides current to the positive side of switch 166 to
allow full operation of switch 166. Additionally, a portion of the
current is provided to third resistor 184 and LED 188 to light LED
188 to notify the operator that electronic control circuit 164 is
in working order. Once both the positive and negative side of
switch 166 are powered, then the operator may operate switch 166
and linear actuator 168 in a manner consistent with the operation
of the variable transmission, as described above.
[0070] When the engine is not operating, there is no signal being
provided, thus there is no power to switch 166, and linear actuator
168 may not be operated, thereby preventing an operator from
attempting to vary the pulley diameters and preventing variation of
the speed in the transmission. As such, binding of the variable
speed mechanism is prevented, thereby eliminating potential damage
to the variable speed transmission upon starting the implement.
[0071] While this invention has been described as having exemplary
designs, the present invention can be further modified within the
spirit and scope of this disclosure. This application is therefore
intended to cover any variations, uses, or adaptations of the
invention using its general principles. Further, this application
is intended to cover such departures from the present disclosure as
come within known or customary practice in the art to which this
invention pertains and which fall within the limits of the appended
claims.
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