U.S. patent application number 10/313725 was filed with the patent office on 2003-05-01 for variable speed drive.
Invention is credited to Hammerbeck, John Philip Roger.
Application Number | 20030083167 10/313725 |
Document ID | / |
Family ID | 10839521 |
Filed Date | 2003-05-01 |
United States Patent
Application |
20030083167 |
Kind Code |
A1 |
Hammerbeck, John Philip
Roger |
May 1, 2003 |
Variable speed drive
Abstract
A variable speed drive comprising two drives, an output drive
wheel and an endless, extendible member that is driven by the
drives and extends around and rotates the output drive wheel. The
drives are operable to move the endless member around an endless
path at a first speed at a first driving position and at a second
speed at a second position. This causes local expansion or
contraction of the endless member around the output drive wheel and
so varies its speed.
Inventors: |
Hammerbeck, John Philip Roger;
(London, GB) |
Correspondence
Address: |
PRICE HENEVELD COOPER DEWITT & LITTON
695 KENMOOR, S.E.
P O BOX 2567
GRAND RAPIDS
MI
49501
US
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Family ID: |
10839521 |
Appl. No.: |
10/313725 |
Filed: |
December 6, 2002 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
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10313725 |
Dec 6, 2002 |
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09815821 |
Mar 23, 2001 |
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6508733 |
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09815821 |
Mar 23, 2001 |
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PCT/GB99/03198 |
Sep 24, 1999 |
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Current U.S.
Class: |
474/239 ;
474/144; 474/148 |
Current CPC
Class: |
F16H 19/06 20130101;
F16H 9/02 20130101 |
Class at
Publication: |
474/239 ;
474/144; 474/148 |
International
Class: |
F16D 001/00; F16H
057/02; B62J 013/00; F16G 009/00 |
Foreign Application Data
Date |
Code |
Application Number |
Sep 25, 1998 |
GB |
9820984.4 |
Claims
The invention claimed is:
1. A variable speed drive comprising an output drive, a driver and
an endless, extendible member that extends around and is driven by
the driver and drives the output drive, wherein the first driver is
operable to drive the endless, extendible member at a first speed
at a driving position, and a driven brake system for changing a
second speed or stopping movement of the endless, extendible member
at a driven position, thereby to cause local expansion or
contraction of the endless, extendible member around the driver
without extending the overall length of the endless, extendible
member.
2. A drive as claimed in claim 1, wherein the driven brake system
is operable to reduce the speed of the endless, extendible member
to substantially zero at the driven position, so that the endless,
extendible member is substantially prevented from moving past the
driven position.
3. A drive as claimed in claim 1, wherein the endless, extendible
member is an endless coil or spring or a belt or tube.
4. A variable speed drive as claimed in claim 3, wherein the
endless, extendible member is an endless spring or coil, and the
output drive comprises two hollow driven shafts.
5. A variable speed drive as claimed in claim 4, wherein the hollow
driven shafts power a generator.
6. A variable speed drive as claimed claim 4, wherein at least one
lug depends from an inner peripheral surface of each hollow driven
shaft for placement between adjacent windings of the spring or
coil, so that when the endless spring or coil is propelled forward,
each hollow driven shaft is rotated by engagement of successive
windings of the endless spring or coil with the at least one
lug.
7. A variable speed drive as claimed in claim 6, wherein the at
least one lug is a pair of lugs, each lug of the pair of lugs being
between adjacent windings of the endless spring or coil but offset
from each other in such a manner that a first one of the pair of
lugs contacts a forward one of the adjacent windings and a second
one of the pair of lugs contacts a rearward one of the
windings.
8. A variable speed drive as claimed in claim 6, wherein two or
more lugs are provided opposite each other.
9. A variable speed drive as claimed in claim 4, wherein sets of
lugs are provided at opposing ends of at least one of the two
hollow driven shafts.
10. A variable speed drive as claimed in claim 4, wherein the two
hollow driven shafts each comprise an inner hollow cylindrical
shaft that is releasably coupled to an outer hollow cylindrical
shaft that drives a generator.
11. A variable speed drive as claimed in claim 10, wherein the
driven brake system is operable to de-couple one of the inner
hollow cylindrical shafts from a corresponding one of the outer
hollow cylindrical shafts.
12. A variable speed drive as claimed in claim 11, wherein the
driven brake system is hydraulically driven.
13. A variable speed drive as claimed in claim 11, wherein the
driven brake system comprises a braking mechanism for braking
movement of the one of the inner hollow cylindrical shafts, thereby
to de-couple the one of the inner hollow cylindrical shafts from
the corresponding one of the outer hollow cylindrical shafts so
that one of the speeds of the endless spring or coil through the
one of the inner hollow cylindrical shafts is reduced or brought to
zero.
14. A variable speed drive as claimed in claim 11, wherein the
driven brake system comprises a compression spring that is mounted
between one end of the one of the inner hollow cylindrical shafts
and one end of the one of the outer hollow cylindrical shafts,
wherein the compression spring is operable to pull the one of the
inner hollow cylindrical shafts into driven engagement with the one
of the outer hollow cylindrical shafts up until a pre-determined
tension of the endless spring or coil is reached, at which stage
the one of the inner hollow cylindrical shafts is moved out of
engagement with the one of the outer hollow cylindrical shafts.
15. A variable speed drive as claimed in claim 14, comprising an
actuator that is operable to sense when to switch off the output
drive and move the one of the inner hollow cylindrical shafts
against an action of the compression spring and out of engagement
with the one of the outer hollow cylindrical shafts, thereby to
de-couple the one of the inner hollow cylindrical shafts from the
one of the outer hollow cylindrical shafts.
16. A variable speed drive as claimed in claim 15, wherein a
detector is provided to detect a loosening of the endless spring or
coil and switch off a generator driven by the outer shaft, thereby
to return the output drive to a starting position.
17. A variable speed drive as claimed in claim 10, wherein the one
of the inner hollow cylindrical shafts has two separate but
interlocking parts that can move longitudinally apart from each
other, each of the parts being releasably mounted in driven
engagement with one of the outer hollow cylindrical shafts, wherein
the driven brake system includes a driven component for moving the
parts of the one of the inner hollow cylindrical shafts from a
driven position to a de-coupled position in which the parts of the
one of the inner hollow cylindrical shafts are de-coupled from the
one of the outer hollow cylindrical shafts.
18. A variable speed drive as claimed in claim 17, wherein the
driven component is hydraulically driven.
19. A variable speed drive as claimed in claim 17, wherein the
driven component comprises elliptical wheels that are rotatable
into engagement with the parts of the one of the inner hollow
cylindrical shafts, thereby to push the parts of the one of the
inner hollow cylindrical shafts away from each other and out of
driven engagement with the one of the outer hollow cylindrical
shafts.
20. A variable speed drive as claimed in claim 1, wherein a drive
member is provided on the input drive, the endless, extendible
member being wound around the drive member.
21. A variable speed drive as claimed in claim 20, wherein the
drive member is circular.
22. A variable speed drive as claimed in claim 20, wherein the
drive member is pear shaped.
23. A variable speed drive as claimed in claim 1, wherein at least
one detector is provided for detecting an expansion or contraction
of the endless, extendible member, and thereby changes in a driver
speed of the driver.
24. A variable speed drive as claimed in claim 23, wherein when the
endless, extendible member is a spring, the at least one detector
is operable to monitor separation of adjacent windings to thereby
gain a measure of expansion or contraction of the spring and a
spring speed of the spring.
25. A variable speed drive as claimed in claim 24, wherein the at
least one detector is two detectors on opposing sides of the
driver, and further including a comparator for comparing the
separation of the windings to thereby calculate a rate of power
transmitted.
26. A variable speed drive comprising a driver, an output drive and
an endless, extendible member that extends around and is driven by
the driver and drives the output drive, wherein the driver is
operable to drive the endless, extendible member at a first speed
at a driving position, and a driven brake system for changing a
second speed or stopping movement of the endless, extendible member
at a second position, thereby to cause local expansion or
contraction of the endless, extendible member around the driver,
wherein the output drive comprises a hollow drive shaft on which is
provided a lug for interacting with the endless, extendible member
thereby to be moved by it.
27. A variable speed drive comprising a driving system, an output
drive and an endless, extendible member that extends around and is
driven by the driving system and drives the output drive, wherein
the driving system comprises a first driver operable to drive the
endless, extendible member at a first speed at a first position and
a second driver operable to drive the endless, extendible member at
a second speed at a second position, thereby to cause local
expansion or contraction of the endless, extendible member around
the first driver.
28. A variable speed drive comprising an input drive, a movable
member, an output drive and an endless, extendible member that is
driven by the input drive and extends around the input drive and
the movable member, wherein movement of the endless, extendible
member over the output drive causes the output drive to move and
movement of the moveable member expands or contracts the endless,
extendible member, thereby varying an overall length of the
endless, extendible member to vary a speed at which the output
drive is driven, wherein the output drive comprises a hollow driven
shaft on which is provided a lug for interacting with the endless,
extendible member to move the hollow driven shaft.
29. A variable speed drive as claimed in claim 28, wherein the
movable member comprises two spaced apart moveable locating
members, the endless, extendible member being located between the
locating members, the locating members being fixedly mounted
relative to each other and movable relative to the output drive
such that when the locating members are moved in one direction, the
endless, extendible member is caused to engage a first one of the
locating members and is able to move a driven shaft in a first
direction, and when moved in another direction, the endless,
extendible member is caused to engage a second one of the locating
members and is able to move the driven shaft in a second direction,
thereby to provide a reversible drive.
30. A variable speed drive as claimed in claim 28, wherein the
movable member comprises a wheel.
31. A variable speed drive as claimed in claim 28, wherein the
endless, extendible member is a spring or coil.
32. A variable speed drive as claimed in claim 31, wherein the lug
depends from an internal wall of the hollow drive shaft for
placement between windings of the spring or coil, so that when the
spring or coil is propelled forward, the hollow drive shaft is
rotated by engagement of successive windings with the lug.
33. A variable speed drive as claimed in claim 32, wherein two or
more lugs are provided.
34. A variable speed drive as claimed in claim 33, wherein the lugs
are provided with a roller bearing that provides a surface for
engagement with the windings of the spring or coil, thereby to
reduce friction.
35. A variable speed drive as claimed in claim 31, wherein a drive
wheel is provided on the input drive, the endless, extendible
member being wound around the drive wheel.
36. A variable speed drive as claimed in claim 31, wherein a
detector is provided for detecting any expansion or contraction of
the endless, extendible member, and thereby changes in the speed of
the output drive and rate of transmission of power to the output
drive.
37. A variable speed drive as claimed in claim 36, wherein the
detector is operable to monitor separation of adjacent windings of
the spring or coil, thereby to gain a measure of expansion or
contraction of the spring or coil.
38. A variable speed drive as claimed in claim 28, wherein the
endless, extendible member is an elastic belt or tube.
39. A variable speed drive as claimed in claim 38, wherein the
output drive is a linear electric generator.
40. A variable speed drive as claimed in claim 39, wherein material
is mounted at regularly spaced intervals along a length of the belt
or tube, wherein the material is capable of being attracted and/or
repelled magnetically.
41. A variable speed drive comprising an input drive, a movable
member, an output drive and an endless, extendible member that is
driven by the input drive and extends around the input drive and
the movable member, wherein movement of the endless, extendible
member over the input drive causes the input drive to move and
movement of the moveable member expands or contracts the endless,
extendible member, thereby varying an overall length of the
endless, extendible member, and so varying a speed at which the
endless, extendible member is driven, wherein the endless,
extendible member is an elastic belt or tube with material mounted
at regularly spaced intervals along the elastic belt or tube
wherein the material is capable of being attracted and/or repelled
magnetically and the output drive is a linear electric
generator.
42. A drive comprising an input drive, an output drive and an
endless extendible member driven by the input drive and driving the
output drive, in which the extendible member extends around one of
the input drive and the output drive, and in which the extendible
member extends through the other of the input drive and the output
drive such that said other of the input drive and output drive
rotates around a circumference of the extendible member.
43. A drive comprising an input drive, an output drive and an
endless, extendible member extending around and driven by the input
drive, in which the endless extendible member extends through the
output drive and drives the output drive to rotate around a
circumference of the extendible member.
44. A generator comprising an input drive, an output drive and an
endless, extendible member extending around and driven by the input
drive, in which the endless extendible member extends through the
output drive and drives the output drive to rotate around a
circumference of the extendible member.
Description
CROSS-REFERENCE TO RELATED APPLICATIONS
[0001] This application is a continuation of copending patent
application Ser. No. 09/815,821, filed on Mar. 23, 2001 entitled
VARIABLE SPEED DRIVE, which is a continuation of PCT International
Application No. PCT/GB99/03198 filed in the United Kingdom on Sep.
24, 1999 designating the United States of America, which was
published in English on Apr. 6, 2000 and which claims priority to
British Patent Application No. 9820984.4 filed Sep. 25, 1998.
BACKGROUND OF THE INVENTION
[0002] The present invention relates to a variable speed drive.
[0003] One known variable speed drive comprises a motor for driving
a continuous drive belt that is wound around and movable along an
external surface of a circular pyramid. Mounted on the pyramid is
the drive's output shaft. In this arrangement, when the belt is
driven around a wide end of the pyramid it causes the pyramid, and
so the output shaft, to rotate at a particular speed. By moving the
belt towards the apex of the pyramid, the speed at which the
pyramid rotates increases. Hence, by suitably positioning the belt
relative to the surface of the pyramid, the speed of the output
shaft can be varied.
[0004] A problem with this drive is that it is not efficient.
Another problem is that it is bulky in three dimensions and complex
in operation. Whilst various other, more efficient variable speed
drives are available, they tend to be complex and expensive.
SUMMARY OF THE INVENTION
[0005] An object of the present invention is to provide a low cost,
low weight and energy efficient variable speed drive.
[0006] According to one aspect of the present invention, there is
provided a variable speed drive comprising a drive, a movable
member, an output drive and an endless, extendible, member that
extends around the output drive and the movable member, and is
driven by the drive, wherein movement of the endless member around
the output drive causes said output drive to move and movement of
the movable member causes the endless member to expand or contract,
thereby varying its overall length, and so varying the speed at
which the output drive is driven.
[0007] Preferably, two spaced apart movable members are provided,
the endless member being located between them, the two members
being fixedly mounted relative to each other and movable relative
to the drive, such that when the movable members are moved in one
direction the endless member is caused to engage a first one of the
movable members and is able to move the output drive in a first
direction, and when the movable members are moved in another
direction the endless member is caused to engage a second one of
the members and is able to move the output drive in a second
direction, thereby to provide a reversible drive. Preferably, the
or each movable member comprises a wheel.
[0008] Preferably, the drive comprises a hollow drive shaft.
Preferably, the hollow drive shaft is driven by an electric motor.
Drive means may be mounted on the hollow drive shaft for
interacting with the endless, flexible member, thereby to move
it.
[0009] Preferably, the endless, extendible member is an endless
coil or spring. The endless member may comprise a belt or tube.
[0010] When the endless member is a spring or coil, the drive means
preferably comprises a lug that depends from an internal wall of
the hollow drive shaft for locating between adjacent windings of
the spring or coil, so that when the hollow drive shaft is rotating
the spring is propelled forward by engagement of successive
windings with the rotating lug. Preferably, a pair of lugs is
provided, each lug of the pair being between adjacent windings of
the spring but offset from the other in such a manner that a first
one of the pair contacts a forward one of the adjacent windings and
the second one of the pair contacts a rearward one of the
windings.
[0011] Preferably, two or more lugs are provided opposite each
other. This is advantageous because it keeps the spring positioned
centrally in the hollow drive shaft. The opposing lugs are
preferably positioned so that the angle of incidence of each lug to
a winding of the spring or coil can be prevented from becoming too
steep. Preferably, each lug is provided with a roller bearing that
provides a surface for engagement with the windings of the spring,
thereby to reduce the effects of friction.
[0012] Preferably, sets of lugs are provided at opposing ends of
the hollow drive shaft. This is advantageous because the part of
the spring that is between the lugs is substantially unaffected by
movement of the or each movable member so that the part that is
effected is reduced. This means that the movable member does not
need to be moved as far as would otherwise be necessary.
[0013] Preferably, a drive wheel is provided on the output shaft,
the flexible member being wound around the drive wheel.
[0014] Preferably, a detector is provided for detecting expansion
or contraction of the endless member, and thereby changes in the
speed of the output drive. When the endless member is a spring,
preferably the detector is operable to monitor separation of its
adjacent windings, thereby to gain a measure of the expansion or
contraction of the spring and so its speed. By comparing the
separation of the windings of the spring or coil on either side of
the output drive, the actual rate of power transmitted can be
calculated.
[0015] Preferably, a controller is provided for controlling
movement of the movable member. Preferably the controller is in
communication with the detector so that information relating to a
measured speed can be fed back to the controller.
[0016] According to another aspect of the present invention there
is provided a variable speed drive comprising drive means, an
output drive and an endless, extendible member that is driven by
the drive means and extends around and drives the output drive,
wherein the drive means is operable to drive the endless member at
a first speed at a first driving point and means are provided for
changing the speed or stopping movement of the endless member at a
second point, thereby to cause expansion or contraction of the
endless member around the output drive.
[0017] The means for changing the speed or stopping movement of the
endless member may be operable to reduce the speed of the endless
member to substantially zero at the second drive point, so that the
endless member is substantially prevented from moving past that
point.
[0018] Preferably, the endless, extendible member is an endless
coil or spring. The endless flexible member may comprise a belt or
tube.
[0019] When the endless member is a spring or coil, preferably the
drive means comprises two hollow drive shafts located on opposing
sides of the output drive. Preferably the hollow drive shafts are
driven by the same motor.
[0020] Preferably, a lug depends from each hollow inner shaft for
locating between adjacent windings of the spring or coil, so that
when each hollow drive shaft is rotating, the spring is propelled
forward by engagement of successive windings with the rotating lug.
Preferably, a pair of lugs is provided, each lug of the pair being
between adjacent windings of the spring but offset from the other
in such a manner that a first one of the pair contacts a forward
one of the adjacent windings and the second one of the pair
contacts a rearward one of the windings.
[0021] Two or more lugs may be provided on opposing sides of the
hollow drive. This is advantageous because it keeps the spring
positioned centrally in the hollow drive shaft. The opposing lugs
are preferably positioned so that the angle of incidence of each
lug to a winding of the spring or coil can be prevented from
becoming too steep. Preferably, the or each lug is provided with a
roller bearing that provides a surface for engagement with the
windings of the spring, thereby to reduce the effects of
friction.
[0022] Preferably, sets of lugs are provided at opposing ends of
the hollow drive shaft. This is advantageous because the part of
the spring that is between the lugs is substantially unaffected by
movement of the or each movable member so that the part that is
effected is reduced. This means that the movable member does not
need to be pulled as far as would otherwise be necessary.
[0023] Preferably, the hollow drive shafts each comprise an inner
hollow cylindrical shaft that is releasably coupled to an outer
hollow cylindrical shaft, which is driven by a motor. Preferably,
the motor is a constant output motor.
[0024] Preferably, the means for changing the speed or stopping
movement of the extendible member are operable to decouple the
inner shaft from its outer shaft, so that the inner shaft no longer
rotates and the spring is substantially prevented from moving past
that point. Preferably, both of the hollow drive shafts are driven
by the same motor.
[0025] The means for changing the speed or stopping movement of the
extendible member may comprise a braking mechanism for braking
movement of at least one of the inner shafts, thereby decoupling it
from the corresponding outer shaft, so that the speed of the
endless spring through that shaft can be reduced or even brought to
zero.
[0026] The means for changing the speed or stopping movement of the
extendible member may comprise a compression spring that is mounted
between one end of the inner drive shaft and the same end of the
outer drive shaft, wherein the compression spring is operable to
pull the inner shaft into driving engagement with the outer shaft
until a pre-determined tension of the endless member is reached, at
which stage the pulling action of the member overcomes the pulling
action of the compression spring, so that the inner shaft is moved
out of engagement with the outer shaft.
[0027] Preferably, there is provided an actuator that is operable
to sense when it is time to switch off the drive and move one of
the inner shafts against the action of the compression spring and
out of engagement with the outer shaft, thereby to decouple that
inner shaft from the outer shaft in order to loosen off the spring.
A detector may be provided to detect a loosening of the spring and
switch off the motor that drives the outer shafts, thereby to
return the drive to a starting position.
[0028] The inner shaft may have two separate but interlocking parts
that can move longitudinally apart from each other, each of the
parts being releasably mounted in driving engagement with the outer
drive shaft, wherein the means for changing the speed or stopping
movement of the endless member past the second point comprises
means for moving the parts of the inner shafts from their driven
position to a position in which they are de-coupled from the outer
shaft. Preferably, the means for moving the parts of the inner
shaft comprise elliptical wheels that are rotatable into engagement
with the parts of the inner shaft and thereby push the parts away
from each other and out of driving engagement with the outer
shaft.
[0029] Preferably, a drive member is provided on the output drive,
the flexible member being wound around the drive member, which
drive member may be circular or, for example "pear" shaped or
elliptical.
[0030] Preferably, a detector is provided for detecting the
expansion or contraction of the flexible member, and thereby
changes in the speed of the output drive. When the flexible member
is a spring, the detector is preferably operable to monitor
separation of its adjacent windings, thereby to gain a measure of
the expansion or contraction of the spring and so its speed. By
comparing the separation of the windings of the spring or coil on
either side of the output drive, the actual rate of power
transmittal can be calculated.
[0031] Preferably, a controller is provided for controlling
movement of the movable member. Preferably the controller is in
communication with the detector so that information relating to a
measured speed can be fed back to the controller.
BRIEF DESCRIPTION OF THE DRAWINGS
[0032] Various systems in which the above mentioned aspects of the
invention are embodied will now be described by way of example only
and with reference to the following drawings:
[0033] FIG. 1 is a diagrammatic, partially sectioned,
representation of a variable speed drive system;
[0034] FIG. 2 is a side view of the drive system of FIG. 1, in the
direction of arrow A;
[0035] FIGS. 3a and 3b are exploded and sectioned views of the
portion of FIG. 1 marked B;
[0036] FIG. 4 is similar to FIG. 1 but shows the drive in a
different configuration;
[0037] FIG. 5 is a diagrammatic, partially sectioned,
representation of a modified version of the variable speed drive
system of FIG. 1;
[0038] FIG. 6 is a schematic, partially sectioned, representation
of a variable speed drive that can be reversed;
[0039] FIG. 7 is a side view of the drive system of FIG. 6 in the
direction of arrow C;
[0040] FIG. 8 is a schematic view similar to that of FIG. 8 in
which the drive is shown in its reversed position;
[0041] FIG. 9 is a diagrammatic plan view of another variable speed
drive system;
[0042] FIG. 10 is a section on the line D-D of the drive system of
FIG. 9;
[0043] FIG. 11 is a view taken from the line E-E of FIG. 9;
[0044] FIG. 12 shows the effects of braking the inner shaft of the
drive system of FIG. 9;
[0045] FIG. 13 is a diagrammatic plan view of yet another variable
speed drive system;
[0046] FIG. 14 is a section on the line F-F of FIG. 13;
[0047] FIG. 15 is a top view of the shaft of FIG. 14 in a neutral
position;
[0048] FIG. 16 is similar to that of FIG. 15 except in a thrust
position;
[0049] FIG. 17 is a section through yet another variable speed
drive;
[0050] FIG. 18 is a section on the line G-G of FIG. 17;
[0051] FIG. 19 is a plan view of a "pear" shaped drive shaft;
[0052] FIG. 20 is a plan view of a guide wheel/output drive wheel
arrangement that can be used in the drive systems;
[0053] FIG. 21 is a section through another specific guide
wheel/output drive wheel arrangement, and
[0054] FIG. 22 is a top view of the arrangement of FIG. 21.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
[0055] FIGS. 1, 2 and 4 show an electric motor 10 with a hollow
drive shaft 12 that is operable to be rotated at a constant speed.
Extending from an internal wall 14 of the hollow drive shaft 12 are
opposing drive lugs 16. Each lug 16 comprises a cylindrical member
18 around which extends a roller bearing 20 (see FIG. 3a) to
provide a bearing surface for limiting friction. The lugs 16 are
typically provided in pairs, each lug of the pair being in close
proximity to the other, but offset along the axis of the shaft, as
shown in FIG. 3(b).
[0056] At opposing ends of shaft 12 and laterally offset from its
axis, are a drive wheel 20 that is mounted on a drive shaft 22 and
a movable tension wheel 24 that is rotatably mounted on a support
26 that is movable relative to shaft 12 and drive wheel 20 using a
drive mechanism 27.
[0057] Extending through shaft 12 is an endless spring or coil 28
that winds around the movable tension wheel 24 and drive wheel 20.
The shaft 12, the movable tension wheel 24 and the drive wheel 20
are arranged so that the spring 28 lies in substantially a single
plane. Extending between adjacent windings of the spring are the
pairs of lugs 16.
[0058] Spring 28 can be made of any suitable material, for example
steel, and is arranged so that when the motor 10 is not switched on
it is only lightly in contact with the drive lugs 16, the drive
wheel 20 and the tensioning wheel 24.
[0059] When the motor 10 is running, i.e., the hollow drive shaft
12 is rotating, the movable tensioning wheel 24 is moved away from
the motor 10 so that the spring 28 is stretched and gradually
tensioned until it comes into contact with the drive wheel 20, as
shown in FIG. 1. At this stage, a first one of the pair of lugs 16
contacts a forward one of the windings F and a second one of the
pair contacts a rearward one of the windings R, as shown in FIG.
3b. Because the lugs 16 rotate with the hollow drive shaft 12, the
spring 28 is propelled through the hollow shaft, with minimal
frictional contact with the lugs 16, and each winding engages in
turn with the roller bearing 19 of the drive lugs 16. In this way,
the spring 28 is driven in an endless path through the shaft 12 and
around tension wheel 24 and drive wheel 20. Given that the speed of
rotation of the lugs 16 is constant, the spring 28 is advanced at a
constant speed.
[0060] As will be appreciated, feeding the spring 28 around its
endless path in this way causes rotation of the drive wheel 20,
which in turn imparts torque to the drive shaft 22 causing it to
rotate. In this way, the motor 10 drives the drive shaft 22 via the
spring 28. It should be noted that the speed of the drive shaft 22
as it rotates is slightly higher than that of the spring 28 as it
moves through hollow shaft 12.
[0061] In order to vary the speed at which the drive shaft 22 is
rotating, the movable tension wheel 24 is moved relative to the
motor 10. When the tension wheel 24 is moved away from the motor
10, as shown in FIG. 4, this causes the endless spring 28 to
expand. The lengthening of the spring 28 causes it to move around
its endless path faster, which in turn causes the drive wheel 20,
and so shaft 22, to rotate at a faster rate. Hence, the speed of
the drive 22 can be varied by increasing or reducing the length of
spring 28.
[0062] On each of opposing sides of the drive wheel is a detector
30 for monitoring the separation of adjacent windings of the spring
28. Each of these could be, for example, a simple photo-detector or
a detector that generates magnetic pulses each time a winding
passes it. Alternatively, the passing of windings of the spring
could be monitored mechanically using, for example, a movable wheel
that engages the spring and is moved by varying the spring's
tension. Because increases in the output of the drive cause the
winding separation to vary on either side of the drive wheel 20,
this allows the torque output to be automatically monitored.
[0063] Connected to each detector 30 is a controller 32 that is
connected to the mechanism 27 for driving the movable tension wheel
24. Signals indicative of the torque of the drive wheel 20 are sent
from the detector 30 to the controller 32. The measured torque is
then compared to a desired torque. If the measured torque and the
desired torque are not the same, then the controller 32 sends a
signal to the drive mechanism 27 to move the tension wheel 24
thereby to vary the speed of the spring 28 and so the drive wheel
20 accordingly. In this way, the output torque can be varied.
[0064] Using a standard industrial, steel, spring coil, the
variable speed drive system of FIGS. 1 and 2 can provide a drive
wheel/spring speed ratio of typically six. Higher ratios can be
achieved by linking together a plurality of the drives of FIGS. 1
and 2. For example, linking three of these drives would provide a
ratio of two hundred and sixteen, i.e. six times six times six.
[0065] FIG. 5 shows a modified version of the drive of FIGS. 1 and
2. In this, opposing pairs of drive lugs 16 are provided at each
end of drive shaft 12. In use, when the movable wheel is moved from
its at rest position (indicated by the dotted line in FIG. 5) to an
extended position, the portion of the spring between the lugs at
either end of shaft 12 is substantially unaffected. In this way,
the effective length of the spring is reduced and the movable wheel
24 does not have to be moved as far to provide the same output
speed as would be the case were the spring to be expanded over its
entire length. This can be advantageous where, for example, a
compact drive is desired.
[0066] FIG. 6 shows another variable speed drive system. In this
case, the system is reversible so that torque can be imparted to
the drive shafts in opposite directions. As with the system
described with reference to FIGS. 1 and 2, the system of FIG. 6
comprises an electric motor 10 with a hollow drive shaft 12 from
which depends drive lugs 16 and through which extends an endless
spring 28.
[0067] At opposing ends of the hollow drive shaft 12 are provided
two pairs of symmetrically placed drive wheels 34 and 36 and 38 and
40. The wheels of each pair 34, 36 and 38, 40 are located on
opposite sides of the axis of the hollow drive shaft 12. Extending
from each wheel is a shaft 41 at the end of which is a smaller
unifying wheel 42, 44. The unifying wheels 42, 44 of each pair are
connected using a drive belt 46 that combines their output to
produce a combined output torque.
[0068] Mounted above the motor and the drive wheels 34, 36, 38 and
40 is a movable gantry 48 that carries a pair of opposing movable
tension wheels 50 and 52 on a single support 54, as shown in FIG.
7. In this way, the movable wheels 50 and 52 are fixedly mounted
relative to each other and can be moved together relative to the
motor. The gantry 48 is positioned so that the tension wheels 50
and 52 can be moved transversely back and forwards above the level
of the motor 10 and drive wheels 34, 36, 38 and 40 and generally
perpendicular to the axis of the hollow drive shaft 12. Extending
around one of the movable tension wheels 50 and 52 in FIG. 4 is the
spring 28.
[0069] When the drive 10 is in the configuration shown in FIG. 6,
feeding the spring 28 around its endless path causes rotation of
drive wheels 36 and 40, which imparts torque to their respective
shafts 41 causing them to rotate in a first direction. As before,
the speed of the drive shafts 41 is slightly higher than that of
the spring 28 as it moves through hollow shaft 12.
[0070] In order to vary the speed at which shafts 41 are rotating,
the gantry 48 and so movable tension wheels 50 and 52 are moved
relative to the motor 10. When the tension wheel 50 is moved away
from the motor 10, this causes the endless spring 28 to expand
causing it to move around its endless path faster, which in turn
causes the drive wheels 36 and 40 to rotate at a faster rate.
Hence, the speed of the drive can be varied by increasing or
decreasing the length of the spring 28.
[0071] If it is desired to reverse the direction of operation, the
movable tension wheels 50 and 52 are moved towards the motor 10
from their extended position, over the motor 10 and towards its
opposing side. This causes the spring 28 to move out of engagement
with the first movable tension wheel 50 and into engagement with
the second moveable tension wheel 52 as shown in FIG. 8. Once in
this position, feeding the spring 28 around its endless path causes
rotation of the drive wheels 34 and 38, which in turn imparts
torque to their respective shafts 41 causing them to rotate in a
second direction opposite to the first direction. In this way, the
direction of rotation of the output shafts 41 is reversed.
[0072] Between the forward and reverse positions, there is a
neutral position in which neither of the tensioning wheels 50 and
52 is in contact with the spring 28.
[0073] FIG. 9 shows another variable speed drive system that
includes two opposing and substantially parallel hollow drive
shafts A and B. Between the drive shafts A and B is a braking
mechanism 60 that can, for example, be actuated hydraulically, and
is adapted to act on either one of the shafts A or B as and when
desired. At one end of the drive shafts A and B is provided an
output drive wheel 62 and at the other end a guide wheel 64.
Extending through each of the hollow shafts, around the output
drive wheel and the guide wheel is an endless extendible member 66,
in this case a spring. The arrangement is such that the portions of
the spring that extend through the hollow drive shafts A and B are
substantially parallel.
[0074] Each of the hollow drive shafts A and B is driven by a
single motor 68, as shown in FIG. 10. Each comprises a hollow inner
shaft 70 that extends through a similarly hollow outer shaft 72
(FIG. 11), each shaft being movable relative to the other. As with
the previously described embodiments, provided on an inner
peripheral surface of the inner shafts of drive shafts A and B are
lugs 74 that engage with the windings of the spring in use to drive
it through the shaft. These lugs 74 are preferably provided in
pairs, as shown in FIGS. 3a and 3b.
[0075] On an outer surface of each of the outer shafts 72 are
provided cogs 76 that are adapted to engage with an endless toothed
belt 78 that is connected to the driving motor 68. This toothed
belt 78 extends around the drive of the motor 68 towards a guide
wheel 80, which guides it towards a lower end of the drive shaft B,
as can be seen from FIG. 11. The belt extends partially around
shaft B, partially around a lower end of the other drive shaft A
and from there back to the driving motor 68. When the motor 68
drives its output shaft in a clockwise direction, shaft B is
rotated clockwise but shaft A is rotated anti-clockwise. Hence,
both of the outer shafts A and B are driven by a single motor 68
but in opposite directions.
[0076] On opposing sides and in the vicinity of the output wheel 62
are provided spacing detectors 82 for detecting the separation of
adjacent windings of the spring 66. As before, each of these could
be, for example, a simple photo-detector or a detector that
generates magnetic pulses each time a winding passes it.
Alternatively, the passing of windings of the spring could be
monitored mechanically using, for example, a movable wheel that
engages the spring and is moved by varying the spring's tension.
Because increases in the output of the drive cause the winding
separation to vary on either side of the drive wheel 20, detecting
the separation of the windings on opposite sides of the output
drive allows the torque output to be automatically monitored.
[0077] In use, the motor 68 drives the outer shaft 72 of both of
the hollow drive shafts. Frictional engagement between the inner
and outer shafts 70 and 72, respectively, causes the inner shafts
70 to rotate with the outer shafts 72, as shown in FIG. 12a. This,
in turn, causes the lugs 74 to rotate. Engagement of the lugs 74
with the endless spring 66 causes the spring 66 to be driven at one
point by the hollow drive shaft A and simultaneously at another
point by the second shaft B. If the speed of each shaft A, B is the
same, this means that the speed at which the spring 66 moves is
constant and the output wheel drive 62 is driven at a constant
speed by its engagement with the spring 66. If, however, the brake
60 is applied to one of the inner shafts of the drives A or B, this
creates a difference in the speeds at which the spring 66 is being
driven at the two points. This causes a local expansion or
contraction of the spring 66, which in turn causes a variation in
the speed at which the output drive wheel 62 is driven.
[0078] For example, if the spring 66 of FIG. 9 were to be driven in
a clockwise manner, application of the brake 60 to the flange 73 of
the inner shaft of drive B would slow down or even stop movement of
the inner shaft 70 as shown in FIG. 12b. This prevents movement of
the spring 66 through shaft B. Since the rate of movement of the
spring 66 through shaft A is unchanged, however, this causes a
shortening of the spring 66 on the drive wheel 62 and so a local
increase in the tension of the spring 66, thus causing an increase
in the speed of the drive wheel 62. When the brake 60 is removed
from the flange 73 of the inner shaft 72 of drive B, the hollow
drive shafts A and B again run synchronously and the spring 66
returns to its equilibrium position, as shown in FIG. 12c.
[0079] In contrast, were the brake 60 to be applied to the flange
73 of shaft A, as shown in FIG. 12d, this would prevent rotation of
its inner shaft 70. Since the rate of movement of the spring 66
through shaft B would be unchanged, however, this causes a
lengthening of the spring 66 on the output drive wheel 62 and so a
local decrease in the tension of the spring 66. In this way, the
speed of the wheel 62 is decreased.
[0080] By driving the spring 66 at a given speed at one point on
one side of the output drive wheel 62 and changing its speed or
stopping movement on the other side of the wheel, it can be seen
that the output speed of the drive system of FIG. 9 can be
varied.
[0081] FIG. 13 shows an alternative arrangement to that of FIG. 9.
This has a similar overall layout, but does not include the braking
mechanism. The specifics of the hollow drive shafts A and B are
also different.
[0082] FIG. 14 shows a section through one of the drive shafts of
FIG. 13. This has an outer hollow cylindrical drive shaft 84 that
extends around an inner shaft 86 that has two parts 88 and 90, each
part 88, 90 comprising a hollow cylindrical shaft that has a lip 92
extending from one end. Projecting from an inner peripheral surface
of each part 88 and 90 of the inner shaft, and at an end thereof,
is a set of lugs 94 that is used for moving the spring 66.
[0083] The parts of the inner shaft 88 and 90 are mounted so that
the cylindrical portions extend through the hollow outer shaft 84
and the lips 92 abut and extend beyond the ends of that shaft 84.
The two parts 88 and 90 are interlocked so that they can move apart
from each other but cannot rotate relative to the other. By
installing the spring 66 so as to be permanently in tension between
the opposing sets of lugs 94, the two parts 88 and 90 are held
together in frictional engagement. This tension additionally forces
the lips 92 of those parts into frictional engagement with the
outer shaft 84 so that under normal circumstances when the outer
shaft 84 is driven, the inner and outer shafts rotate together.
[0084] Mounted around the outer periphery of the outer shaft 84 and
near the lips 92 of the inner shafts are two opposing elliptical
wheels 96. These are selectively rotatable, for example, by means
of small impulses from electromagnets, from a neutral position, as
shown in FIG. 15, in which they do not engage either the inner or
outer shafts, to a thrust position in which they engage the lips 92
of the inner shafts, as shown in FIG. 16. When in the thrust
position, the elliptical wheels 96 touch the inner part of the lips
92 of the inner shafts, thereby frictionally binding the surfaces.
Subsequent rotation of the elliptical wheels 96 forces the inner
shafts out of engagement with the outer shaft 84. Further rotation
returns the elliptical wheels 96 to the normal, neutral position,
at which point the inner shafts are moved back into engagement with
the outer shaft 84.
[0085] As before, the motor 68 drives the outer shaft of both of
the hollow drive shafts A and B. When the elliptical wheels 96 of
each drive are in their neutral position, frictional engagement
between the inner and outer shafts causes the inner shafts 88 and
90 to rotate with the outer shafts 84, as shown in FIG. 12a, which
in turn causes the endless spring 66 to be driven at one point by
the hollow drive shaft A and simultaneously at another point by the
second shaft B. Since the speed of each shaft is the same, this
means that the speed at which the spring 66 moves is constant along
its length and the output wheel drive 62 is driven at a constant
speed by its engagement with the spring 66. If, however, the
elliptical wheels are moved to their thrust position on one of the
drive shafts A or B, this disengages the inner and outer shafts of
that drive and stops rotation of the inner shaft, which in turn
prevents further movement of the spring 66 through the shaft. This
creates a difference in the speeds at which the spring is being
driven at the two points, which causes a local expansion or
contraction of the spring 66, which in turn causes a variation in
the speed at which the output drive wheel 62 is driven.
[0086] For example, if the spring of FIG. 13 were to be driven in a
clockwise manner, movement of the elliptical wheel 96 of shaft B to
the thrust position would disengage the inner and outer shafts and
prevent movement of the inner shaft. This prevents movement of the
spring 66 through shaft B. Since the rate of movement of the spring
66 through shaft A is unchanged, however, this causes a shortening
of the spring 66 on the drive wheel 62 and so a local increase in
the tension of the spring. In this way, the speed of the drive
wheel 62 is increased. When the elliptical wheels of shaft B are
moved to their neutral position, the hollow drive shafts again run
synchronously and the spring 66 returns to its equilibrium
position.
[0087] In contrast, were the elliptical wheels 96 of drive A to be
moved to the thrust position, this would prevent rotation of the
inner shaft of drive A and so would slow or stop movement of the
spring 66 at that point. Since the rate of movement of the spring
66 through shaft B is unchanged, however, this causes a lengthening
of the spring 66 on the output drive wheel and so a local decrease
in the tension of the spring. In this way, the speed of the wheel
is decreased.
[0088] Use of the elliptical wheels 96 to move the inner shafts
relative to the outer shaft 84 avoids the need to use high power
actuators. This is advantageous. As an alternative, however, it
would be possible to cause movement of the inner shafts away from
the outer shaft using some form of hydraulic actuator.
[0089] Each of the drive systems previously described provides the
possibility of continuously variable speed. There are, however,
some applications in which it would be useful to have a simple
automatic gear that can accelerate to a particular speed for a few
moments and then stop, as for example in a car starter motor. One
way to provide such a system is to have two drives connected by
geared wheels of different sizes, the relative sizes depending on
the time necessary to accelerate to the desired speed.
[0090] FIG. 17 shows a drive system that includes two opposing and
substantially parallel hollow drive shafts A and B. At one end of
the drive shafts A and B is provided an output drive wheel 62 and
at the outer end a guide wheel 64. In operable engagement with
drive A is a hollow shaft electric motor 97, which is arranged to
drive shaft A. Extending through each of the hollow shafts A and B,
around the output drive wheel 62 and the guide wheel 64 is an
endless extendible member 66, in this case a spring. The
arrangement is such that the portions of the spring that extend
through the hollow drive shaft are substantially parallel. As
before, extending from inner peripheral surface of the inner shafts
are sets of lugs 94 for driving the spring 66.
[0091] Extending around each drive shaft A, B and attached thereto
is a cog 98 and 100, which is adapted to mesh with the cog on the
other shaft (see FIG. 18). The cog 98 that extends around shaft A
has a smaller diameter than that which extends around shaft B.
Since shaft A is connected to the electric motor 97, the smaller of
the two cogs 98, i.e., the drive cog, can be driven, which in turn
drives the larger one 100, i.e., the slave cog. Since the diameters
of the cogs 98 and 100 are different, this means that the hollow
drive shafts are rotated at different speeds. This gradually causes
the coil 66 to be extended over the output drive wheel 62 causing
it to run faster.
[0092] In order to prevent the spring extending indefinitely, each
drive shaft A, B is provided with means for automatically stopping
further extension when a particular spring tension is reached. To
this end, each drive shaft A, B comprises a cylindrical outer shaft
102 that extends around a longer cylindrical inner shaft 104 that
is flanged at both ends. At one end of the inner shaft 104 are
compression springs 105 that bear against its flange 106 and
additionally the end of the outer shaft 102. At the other end of
the inner shafts 104 are provided interlocking means 108 that
interlock with like means on the end of the outer shaft 102, in
such a way that the inner shaft 104 is longitudinally movable away
from the outer shaft 102 and rotatable therewith thereto.
[0093] In the starting position, the outer and inner shafts 102 and
104 are interlocked so that rotation of the outer shaft 102 causes
rotation of the inner shaft 104 and the spring 66 is evenly
tensioned along its length. When the motor 97 is started, the drive
cog 98 rotates at a first speed and drives the slave cog 100 at a
second lower speed. This gradually causes the spring 66 to extend,
which in turn causes the output drive wheel to move faster. When
the spring 66 reaches a particular tension, the engagement of the
spring 66 with the lugs 94 is sufficient to overcome the pulling
action of the compression springs 105, which allows the inner shaft
104 to move forward out of engagement with the outer shaft 102. The
inner shaft 104 gradually stops rotating and stops driving the
spring 66 forward. This causes a reduction in the tension of the
spring 66, until such time as the compression spring 105 is able to
draw the inner shaft 104 back into engagement with the outer shaft
102, at which stage the process begins again. In this way, the
extension of the spring 66 is automatically limited so that it does
not become overly stressed and a drive is provided that accelerates
and then maintains a constant speed.
[0094] Once the drive system has reached its desired speed and is
no longer required, it can be switched off. It is however important
that it be returned to the starting position for later use. In
order to ensure this, an actuator 108 is provided. This actuator
108 is stimulated by the rising output of the main motor's
generator (for example the dynamo of a car). It acts on the end of
the inner shaft 104 of drive A nearest the compression spring 103
and pushes against the action of the compression spring 105, in
order to de-couple the inner shaft 104 from its outer shaft 102.
Connected to the actuator 108 and indeed to the electric motor 94
is a return to start detector 110, which is positioned adjacent to
the output drive wheel 62. When drive A is de-coupled, drive B
continues to feed the spring 66 around its closest path, which
causes the tension of the spring 66 to loosen around the output
drive wheel 62 until eventually the spring 66 is lifted off the
output wheel 62. When this happens, the spring 66 abuts the return
to start detector 110, which sends a signal that causes the
actuator 108 and the motor 97 to switch off. In this way, the drive
system is automatically returned to its start position.
[0095] Whilst the arrangement of FIG. 17 has a mechanical means,
i.e., a spring, for decoupling the inner and outer shafts, it will
be appreciated that a hydraulic actuator could be used.
[0096] The speed of the output drive wheels 62 of the systems shown
in FIGS. 9, 13 and 17 is varied by driving the endless member 66 at
one point on one side of the output wheel and either increasing or
decreasing its speed, or stopping its movement altogether, at
another point on the opposite side of the output wheel. This
creates a local extension or contraction of the member and so
varies its tension around the output drive shaft. This causes a
variation in the output speed.
[0097] Whilst the output drive shafts of the previously described
systems carry circular wheels, it will be appreciated that they may
carry members of any suitable shape. For example, the output shaft
may carry a "pear" shaped member 112, as shown in FIG. 19. This
type of shaft would be useful for applications in which a
non-uniform output power cycle is required, for example, in a high
compression engine. In addition, whilst the output drive wheel 62
and the guide wheel 64 are shown as being of the same size, they
could, of course, be different, as shown in FIG. 20. It may also be
useful, particularly in the case where the guide wheel 64 and the
output drive wheel 62 are different sizes, to use each as a drive
depending on the speed requirements for particular applications. In
this way, the drive system could have a low speed mode when the
larger of the two wheels is used as the drive and a high speed
output mode when the smaller of the two wheels is used as the
drive. This would be useful, for example, for washing machine
motors, which have to operate in a high "spin" mode and a lower
speed normal mode.
[0098] When the guide wheel 64 and the drive wheel 62 are each used
as a drive, they may be coupled together using, for example,
inter-meshing cogged wheels 114 and 166 that are mounted on their
respective output shafts C and D respectively, as shown in FIG. 21.
As will be appreciated, the cogged wheels are coupled together in
such a manner that they rotate in opposite directions, as shown in
FIG. 22. In this example, the ultimate output is only taken from
shaft E. When the drive wheel 62 is being driven directly, the
output on shaft E is rotated in a first direction. When the guide
wheel 64 is driven directly, this causes rotation of cogged wheel
116, which in turn drives the other cogged wheel 114, but in the
opposite direction to that when the output drive wheel is used as
the main drive. In this way, the drive is fully reversible.
[0099] As will be appreciated, in each of the drives described
above, the performance of a spring 28 varies depending on the
profile of the steel used, the pitch and the diameter, as well as
by the quality and thickness of the material used. The particular
spring characteristics will depend on the desired application. For
example, if the drive has to be very compact, the length of spring
used should be relatively short. The spring 28, however, may be
wound so that there is a sufficient gap between adjacent windings
to receive the lugs of the motor. In addition, the spring 28 should
preferably be circular in section before its ends are joined to
form an endless path, in order to minimize energy loss through
flexing in operation and decrease the torsion in the spring.
[0100] The drive wheels used in the variable speed drives described
above could have slots formed in the surface that contacts with the
spring 28. This reduces the likelihood of the spring slipping. This
is more important at low drive wheel speed/spring speed ratios. At
higher ratios, the increased spring tension is sufficient to avert
slippage and the windings of the spring merely ride over the slots,
or the angle at which the coil engages with the drive wheel is
varied.
[0101] One application for the drive systems described above is a
starter motor for use in conventional internal combustion engines.
Such combustion engines have to be turned sufficiently fast to
produce continuous firing of the cylinders. Considerable torque is
required with modern high compression engines to achieve this.
Conventionally, a powerful electric starter motor is used that
requires solenoid switching of power to it and a heavy duty battery
to provide the current fast enough. Electric motors provide
mechanical output most efficiently at high revolutions per minute.
However, in conventional systems, the starter engages with a large
gear wheel in the engine and so the number of revolutions is
reduced so that the engine is accelerated a little above its
minimum revolutions per minute. In practice, however, more
efficient and quicker starting would be achieved by accelerating
the engine to a much higher revolutions per minute.
[0102] If a variable speed drive in which the invention is embodied
were used as a starting motor, the size of that motor could be
reduced, probably without the necessity for solenoid switching.
This is because the spring drive acts as a reduction gear at low
ratios so that the large gear wheel in the engine would not be
required and the battery could also be greatly reduced in size. It
is estimated that the variable speed drive in which the invention
is embodied would be typically half the weight of a conventional
starting motor. This is advantageous because it reduces the overall
weight of the engine and the overall cost.
[0103] Because the variable speed drive in which the present
invention is embodied is lighter than like prior art drives, this
reduces vibration. This is highly advantageous. Another advantage
of the invention is that friction is lower than in conventional
drives. This improves the overall efficiency.
[0104] The drive in which the invention is embodied is suitable for
use in many domestic machines, such as driers and washing machines
that currently use electric motors with unnecessarily high power so
that the speed can be controlled electrically. The drive in which
the invention is embodied allows use of a less powerful motor.
[0105] It will be appreciated that the drive described above could
be reversed to provide a generator, each of these machines
operating on the same principle that speed is variable by varying
the length of the flexible member or by driving the member at
different rates at two different points, thereby to create a local
extension or contraction of the member.
[0106] Whilst the motor described above is rotary, it will be
appreciated that a linear or tubular motor could be used to drive
the flexible member around its endless path. Furthermore, the
flexible member could be a belt or a tube rather than a spring or
coil. In this case, when a pulse phased linear or tubular electric
motor is used as the drive, material (for example iron slugs) is
provided at spaced intervals along the length of the member, which
material is capable of being attracted or repelled magnetically by
the motor. In this way, by pulsing the drive, the flexible member
can be driven around its endless path. By measuring the separation
of adjacent slugs in the vicinity of the output drive, the speed at
the output can be determined. By comparing the separation of the
slugs of the belt or tube on either side of the output drive, the
actual rate of power transmitted can be calculated.
[0107] As will be appreciated, the principles of the invention,
which have been disclosed by way of example only, can be
implemented in various ways. Those skilled in the art will readily
recognize that modifications and changes can be made and it is not
necessary to follow strictly the exemplary applications illustrated
and described herein.
* * * * *