U.S. patent application number 13/932852 was filed with the patent office on 2013-11-07 for balancing of a continuous variable clutch assembly.
The applicant listed for this patent is TEAM Industries, Inc.. Invention is credited to Brandon R. Bonham, Brandon J. Engen, Stephen J. Molde, Michael A. Mueller, Shane C. Okeson.
Application Number | 20130294856 13/932852 |
Document ID | / |
Family ID | 44558897 |
Filed Date | 2013-11-07 |
United States Patent
Application |
20130294856 |
Kind Code |
A1 |
Mueller; Michael A. ; et
al. |
November 7, 2013 |
BALANCING OF A CONTINUOUS VARIABLE CLUTCH ASSEMBLY
Abstract
A continuous variable clutch is provided. The continuous
variable clutch includes a first sheave member and a second sheave
member. The first sheave member includes a first central hub and a
first conical-faced surface extending radially from the first
central hub. The second sheave member includes a second central hub
and a second conical-faced surface that extends radially from the
second central hub. The second central hub of the second sheave
member is received in a cavity of the first central hub such that
the first conical-faced surface of the first sheave member facing
the second conical-faced surface of the second sheave portion. The
second central hub moving axially within the first central hub
based on an amount of torque on the continuous variable clutch. The
first sheave member and the second sheave member further forming a
central passage to receive an input shaft of a transmission.
Inventors: |
Mueller; Michael A.;
(Bemidji, MN) ; Engen; Brandon J.; (Clearbrook,
MN) ; Bonham; Brandon R.; (Bemidji, MN) ;
Okeson; Shane C.; (Bagley, MN) ; Molde; Stephen
J.; (Park Rapids, MN) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
TEAM Industries, Inc. |
Bagley |
MN |
US |
|
|
Family ID: |
44558897 |
Appl. No.: |
13/932852 |
Filed: |
July 1, 2013 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
12722919 |
Mar 12, 2010 |
8496551 |
|
|
13932852 |
|
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|
Current U.S.
Class: |
408/1R ;
29/407.01 |
Current CPC
Class: |
Y10T 408/03 20150115;
F16H 7/02 20130101; B23B 35/00 20130101; F16H 55/56 20130101; F16H
63/067 20130101; F16H 61/66272 20130101; Y10T 29/49764
20150115 |
Class at
Publication: |
408/1.R ;
29/407.01 |
International
Class: |
B23B 35/00 20060101
B23B035/00 |
Claims
1. A method of balancing a clutch, the method comprising: mounting
an assembled clutch on a test shaft; rotating the test shaft;
determining if the assembled clutch is balanced; and when the
assembled clutch is determined not to be balanced, balancing the
assembled clutch before engaging the assembled clutch with an input
shaft of a transmission.
2. The method of claim 1, wherein balancing the assembled clutch
further comprises: determining a location to remove material of the
clutch; determining an amount of material to be removed; and
removing the determined amount of material from the clutch at the
determined location.
3. The method of claim 1, wherein removing the determined amount of
material at the determined location further comprises: drilling out
the determined amount of material at the determined location.
Description
BACKGROUND
[0001] This application claims priority to and is a divisional
application of U.S. patent application Ser. No. 12/722,919, filed
Mar. 12, 2010, entitled CONTINUOUS VARIABLE CLUTCH, which is herein
incorporated by reference.
[0002] A typical driven clutch sheave includes two sheave members.
The first sheave member is called the stationary sheave member
because it is locked to a post or shaft. The other sheave member is
called moveable because it translates along the axis of the post or
shaft. Typically a cam having a cam angle profile is attached to or
incorporated into the moveable sheave member. The cam profile is
for torque sensing. As the moveable sheave member translates along
the shaft or post axis, the moveable sheave member rotates about
the post and slides linearly closer to or farther away from the
stationary sheave member due to the cam profile and a spring force
to form a sheave that is continuous variable clutch (CVC). A CVC
delivers torque by squeezing a belt tight enough to prevent
slipping. The cam profile allows for the CVC to be torque sensing.
The more torque that is put into the CVC the tighter the CVC
squeezes the belt. This will shift the CVC into a lower ratio.
Likewise when the torque drops, the CVC exerts less belt squeeze
because a reaction force in the cam allows the CVC to shift into a
higher ratio. Hence, the CVC has torque sensing capabilities.
[0003] For the reasons stated above and for other reasons stated
below which will become apparent to those skilled in the art upon
reading and understanding the present specification, there is a
need in the art for a more cost effective and efficient driven
CVC.
SUMMARY OF INVENTION
[0004] The above-mentioned problems of current systems are
addressed by embodiments of the present invention and will be
understood by reading and studying the following specification. The
following summary is made by way of example and not by way of
limitation. It is merely provided to aid the reader in
understanding some of the aspects of the invention.
[0005] In one embodiment, a continuous variable clutch is provided.
The continuous variable clutch includes a first sheave member and a
second sheave member. The first sheave member includes a first
central hub and a first conical-faced surface extending radially
from the first central hub. The first central hub forms a cavity.
The second sheave member includes a second central hub and a second
conical-faced surface that extends radially from the second central
hub. The second central hub of the second sheave member is received
in the cavity of the first central hub such that the first
conical-faced surface of the first sheave member faces the second
conical-faced surface of the second sheave portion. The second
central hub of the second sheave member is further configured to
move axially within the first central hub of the first sheave
member based on the amount of torque on the continuous variable
clutch to vary a gap distance between the first and second
conical-faced surfaces. In addition, the first sheave member and
the second sheave member further form a central passage to receive
an input shaft of a transmission.
BRIEF DESCRIPTION OF THE DRAWINGS
[0006] The present invention can be more easily understood and
further advantages and uses thereof more readily apparent, when
considered in view of the detailed description and the following
figures in which:
[0007] FIG. 1A is a front perspective view of a continuous variable
clutch of one embodiment of the present invention;
[0008] FIG. 1B is a back perspective view of the clutch of FIG.
1A;
[0009] FIG. 2 is a side perspective view of the unassembled clutch
of FIG. 1;
[0010] FIG. 3 is a side perspective partially unassembled view of
the clutch of FIG. 1;
[0011] FIG. 4 is another side perspective partially unassembled
view of the clutch of FIG. 1;
[0012] FIG. 5A is a cross-sectional side view of the assembled
clutch of FIG. 1, illustrating sheave roller clutch
positioning;
[0013] FIG. 5B is a cross-sectional side view of the assembled
clutch of FIG. 1, illustrating cam roller clutch positioning;
[0014] FIG. 5C is a cross-sectional side view of an assembled
clutch of FIG. 1, illustrating the clutch in high gear
positioning;
[0015] FIG. 6 is a balancing flow diagram of one embodiment of the
present invention;
[0016] FIG. 7A is a cross-sectional side view of an assembled
clutch of FIG. 1 and an input shaft of a transmission;
[0017] FIG. 7B is a cross-sectional side view of an assembled
clutch of FIG. 1 and an input shaft of a transmission engaged with
the clutch;
[0018] FIG. 8A is side perspective view of a cross-sectional side
view of an unassembled continuous variable clutch of another
embodiment of the present invention;
[0019] FIG. 8B and 8C are cross-sectional side views of the clutch
of FIG. 8A;
[0020] FIGS. 9A and 9B are cross-sectional side views of the clutch
of FIG. 8A engaged with an input shaft of a transmission; and
[0021] FIG. 10 is a cross-sectional side view of yet another
embodiment of a continuously variable clutch of another embodiment
of the present invention.
[0022] In accordance with common practice, the various described
features are not drawn to scale but are drawn to emphasize specific
features relevant to the present invention. Reference characters
denote like elements throughout Figures and text.
DETAILED DESCRIPTION
[0023] In the following detailed description, reference is made to
the accompanying drawings, which form a part hereof, and in which
is shown by way of illustration specific embodiments in which the
inventions may be practiced. These embodiments are described in
sufficient detail to enable those skilled in the art to practice
the invention, and it is to be understood that other embodiments
may be utilized and that changes may be made without departing from
the spirit and scope of the present invention. The following
detailed description is, therefore, not to be taken in a limiting
sense, and the scope of the present invention is defined only by
the claims and equivalents thereof.
[0024] Embodiments of the present invention provide continuous
variable clutches (CVCs) without a sheave member of the CVC being
coupled stationary to a center post. In embodiments, sheave members
are designed to be in direct rotational communication with a
transmission shaft. In particular, embodiments of the clutches form
a central passage that is designed to engage an input shaft of a
transmission. Benefits of this design include the use of smaller
central passages through the CVC. This provides better length to
diameter ratio of bushing used in the CVC, reduced costs since the
post is no longer needed, a reduction in weight of about 15% over a
typical CVC, less rotational inertia which results in a better
response and better overall performance than a typical CVC. A
further advantage of embodiments, as further discussed below, is
that embodiments of the CVC can be pre-balanced as a unit before
they are coupled to a transmission. Hence, they can be shipped
pre-balanced and then simply coupled to a transmission at a remote
location without the need for matched sets of balanced sheaves.
[0025] FIGS. 1A, 1B and 2 illustrate an embodiment of a CVC 100
with no relative motion. In particular, FIG. 1A is a front
perspective view of the CVC 100 and FIG. 1B is a back view of the
CVC 100. FIG. 2 is an unassembled side view of the CVC 100. With a
clutch 100 with no relative motion, the sheaves 102 and 104 of the
clutch are tied together to prevent rotation between the sheaves
102 and 104. If rotation is present, undesirable friction between
the faces of a belt engaging the sheaves 102 and 104 can be
present. This friction loss is called belt smear. This smearing is
detrimental to belt life and is a performance and efficiency
loss.
[0026] Clutch 100 includes a first sheave member 102 and a second
sheave member 104. In embodiments, the second sheave member 104
selectively moves longitudinally (axially) in relation to the first
sheave member 102 as discussed further below. The first sheave
member 102 includes a first central hub 102b having a first central
opening 102d to a chamber 102d and a first conical faced surface
102a. The first conical faced surface 102a extends radially from
the first central hub 102b about the central opening 102d.
Moreover, the first central hub 102b extends from the first central
opening 102d in generally a direction that is perpendicular in
relation to the first conical faced surface 102a. Further, the
first conical faced surface 102a faces a direction that is opposite
from the direction the first central hub 102b extends from the
first central opening 102d. The second sheave member 104 includes a
second central hub 104b having a first central opening 104e and a
second conical faced surface 104a. The second conical faced surface
104a extends radially from the first central opening 104e of the
second central hub 104b. Moreover, the second central hub 104b
extends from the first central opening 104e in generally a
direction that is perpendicular in relation to the second conical
faced surface 104a. Further the second conical faced surface 104a
of the second sheave member 104 faces the direction the second
central hub 104b extends from the first central opening 104e of the
second conical faced surface 104a. The second central hub 104b of
the second sheave member 104 is positioned in the first central hub
102b of the first sheave member 102 such that the first conical
faced surface 102a of the first sheave member 102 faces the second
conical faced member 104a of the second conical member 104.
[0027] Referring to FIG. 1A, the first central hub 102b of the
first sheave member 102 has a second hub central opening 102c. The
first central hub 102b of the first sheave member 102 further has
opposed first and second side slots 121a and 121b. A first sheave
roller 120a is received in the first side slot 121a and a second
sheave roller 120b is received in the second side slot 121b. The
first and second sheave rollers 120a and 120b are further discussed
below. As FIG. 1B illustrates, a cam cover 106d of a cam assembly
106 is coupled to the second sheave member 104. Referring to the
unassembled view of FIG. 2, the second central hub 104b of the
second sheave member 104 is designed to be received in a cavity
102e formed by the first central hub 102b of the first sheave
member 102 as discussed above. The second central hub 104b includes
opposed first and second bores 104d and 104g (104g is illustrated
in FIG. 5A). The bores 104d and 104g are aligned with slots 121a
and 121b of the first central hub 102b of the first sheave member
102. The first sheave roller 120a that is received in the first
side slot 121a of the first sheave member 102 includes a first
sheave roller central passage 117a. The second sheave roller 120b
that is received in the second side slot 121b of the first sheave
member 102a includes a second sheave roller central passage 117b. A
first sheave roller clutch fastener 118a passes through the first
sheave roller central passage 117a of the first sheave roller 120a
and into the first bore 104d in the second hub 104b of the second
sheave member 104. A second roller fastener 118b passes through the
second sheave roller central passage 117b of the second sheave
roller 120b and into the second bore 104g in the second hub 104b of
the second sheave member 104. Pins 122a and 122b are then inserted
through respective apertures in the fasteners 118a and 118b and
portions of the second central hub 104b to retain the fasteners
118a and 118b in the second sheave member 104 as further
illustrated in FIG. 5A. This operatively forms a connector that
connects the first sheave member 102 to the second sheave member
104 via the first and second sheave rollers 120a and 120b. This
connection allows longitudinal movement between the first and
second sheave portions 102 and 104 while preventing rotational
movement between the first and second sheave portions 102 and 104.
Hence the first and second sheave members 102 and 104 rotate
together without relative rotation as the second sheave member 104
moves longitudinally. This embodiment helps prevent belt smear.
[0028] An adjustment assembly 105 is used to selectively provide
the longitudinal (axial) movement of the second conical face
surface 104a of the second sheave member 104 in relation to the
first conical face surface 102a of the first sheave member 102. In
the embodiment illustrated in FIG. 2, the adjustment assembly 105
includes a cam assembly 106, a cylindrical spider 108 and a biasing
member 112. The cam assembly 106 includes a cylindrical cam portion
106e that extends from cam cover 106d. The cam portion 106e has
first and second cam slots 106a and 106b. The first and second cam
slots 106a and 106b have respective cam profile surfaces 302 and
304 (cam profiles) discussed further below. The cam cover 106d is
coupled to the second sheave member 104 by a plurality of fasteners
128. The cylindrical spider 108 has opposed first and second shafts
108a and 108b. The first and second shafts 108a and 108b extend
outward from an outer surface 107 of the spider 108. The spider 108
further includes a central spider passage 108c. An inner surface of
the spider 108 that defines the central spider passage 108c
includes a plurality of grooves that form internal gears (i.e.
internal splines) configured to engage exterior splines on an input
shaft of a transmission.
[0029] The adjustment assembly 105 further includes a first cam
roller 110a. The first cam roller 110a includes a first cam central
passage 111a (shown in FIG. 5B). The first shaft 108a of the spider
108 is received in the first cam central passage 111a of the first
cam roller 110a. The first cam roller 110a is further received in
the first cam slot 106a of the cam portion 106e of the cam assembly
106. A first cam roller fastener includes a first C-clip 126a and
washer 124a engages the first shaft 108a of the spider 108 to
retain the first cam roller clutch 110a on the first shaft 108. The
adjustment assembly 100 also includes a second cam roller 110b
(shown in FIG. 5B). The second cam roller 110b includes a second
cam central passage 111b. The second shaft 108b of the spider 108
is received in the second cam passage 111b of the second cam roller
110b. The second cam roller 110b further is received in the second
cam slot 106b of the cam portion 106e of the cam assembly 106. A
second cam roller fastener includes a second C-clip 126b and a
second washer 124b that engage the second shaft 108b of the spider
108 to retain the second cam roller 110b on the second shaft 108b
of the spider 108. A biasing member 112 is positioned between an
inner surface of the second hub 104b of the second sheave member
104 and a surface of the spider 108. The biasing member 112 exerts
a biasing force on the spider 108 to position the second conical
face surface 104a of the second sheave member 104 near the first
conical face surface 102a of the first sheave member 102. The
second hub 104b of the second sheave member 104 forms a chamber
104f. The cam portion 106e of the cam assembly 106, the spider 108,
the cam rollers 110a and 110b and the biasing member 112 are
received in chamber 104f of the second sheave member 104.
[0030] Referring to FIG. 3, a side perspective partially
unassembled view of the clutch with no relative motion 100 is
illustrated. As illustrated, the second hub 104b of the second
sheave member 104 is positioned to be received in chamber 102e of
the first hub 102a of the first sheave member 102. Also
illustrated, are the first cam roller 110a and the second cam
roller 110b of the spider 108 respectfully aligned with cam slots
106a and 106b of the cam assembly 106. In FIG. 4, the spider 108 is
illustrated as being inserted within the cam portion 106e of the
cam assembly 106 with roller clutches 110a and 110b respectively
positioned in cam slots 106a and 106b of the cam portion 106e of
the cam assembly 106. Each of the cam slots 106a and 106b includes
opposed cam slot surfaces 302 and 304 in which the respective cam
rollers 110a and 110b can engage. The first cam slot surface 304 is
engaged when an engine (not shown) is driving a vehicle (not shown)
containing clutch 100. The second cam slot surface 302 is engaged
when the vehicle is implementing engine braking. By changing the
cam slot surface 302 profile, the amount of engine braking can be
varied. Further discussion of the effect of the cam slot surfaces
302 and 304 are described in commonly assigned U.S. Pat. No.
6,743,129 which is incorporated in its entirety herein.
[0031] FIG. 5A illustrates a cross-sectional side view of an
assembled clutch with no relative motion 100. In particular, FIG.
5A illustrates pins 122a and 122b that retain fasteners 104d and
104g in the second sheave member 104. As discussed above, fasteners
104d and 104g retain the respective first and second sheave rollers
120a and 120b in the slots 121a and 121b of the first central hub
102b of the first sheave member 102 to slidably couple the first
sheave member 102 to the second sheave member 104. FIG. 5A also
illustrates the positioning of bearing 116 about opening 102c of
the first central hub 102b, bearing 114 in a second central opening
104g (shown in FIG. 3) of the second central hub 104b and bearing
115 in opening 106c of the cam 106. The bearings 116, 114 and 115
engage different portions of an input shaft 700 of a transmission
which is further discussed below in regards to FIGS. 7A and 7B.
FIG. 5A also illustrates a sheave pocket 131 that is designed to
receive a thrust bushing 154 and load washer 152 (illustrated in
FIG. 7B) that help retain the clutch 100 on a transmission shaft
due to axial forces.
[0032] FIG. 5B further illustrates the cross-sectional side view of
an assembled clutch with no relative motion 100. This view
illustrates the positioning of the first and second roller clutches
110a and 110b in the respective first and second cam slots 106a and
106b of the cam 106. In this position, the clutch 100 is set for
low gearing with the first and second conically faced surfaces 102a
and 104a of the first and second sheave members 102 and 104
positioned close to each other so a drive belt (not shown) will
ride high up on the respective first and second conical faced
surfaces 102a and 104a away from a central longitudinal axis 502 of
the clutch 100. The drive belt may be an endless V-shaped belt
known in the art that connects a drive element to a driven clutch
such as clutch 100. In the position illustrated in FIG. 5B, the
biasing member 112 is extended pushing the spider 108 away from an
inner front surface of the second central hub 104b of the second
hub 104 which in turn positions the first and second conical faced
surface next to each other. FIG. 5C illustrated the clutch 100 in a
high gearing configuration where a drive belt (not shown) would
ride low (closer to the longitudinal axis 502) on the first and
second conical faced surfaces 102a and 104a or even ride solely on
the second central hub 104b of the second sheave member 104. In
this position, the first and second rollers 110a and 110b have
moved in cam surfaces defined by the cam slots 106a and 106b of the
cam 106 thereby compressing biasing member 112. Rotational forces
delivered by the drive belt (not shown) move the first and second
rollers 110a and 110b in cam profile surfaces (cam profile) defined
by the cam slots 106a and 106b of the cam 106 to counter the
biasing force of the biasing member 112. The cam profile and the
biasing member 112 work together as a torque sensing unit. The
biasing member 112 in this embodiment is a spring.
[0033] In practice, once the clutch 100 has been assembled, it can
be balanced before it leaves the manufacture. Referring to FIG. 6 a
balancing flow diagram 600 of one embodiment is illustrated. The
clutch 100 is temporally mounted on a test shaft in balancing
machine 602. The conical-shaped faces 102a and 104a of the sheaves
102 and 104 are positioned a select distance away from each other
(almost a full open position). The rotational shaft holding the
clutch 100 is rotated (604). The balancing machine measures any
imbalance in single or multiple planes near each sheave 102 and 104
(606). If an imbalance is detected (606), the balancing machine
determines the location to remove material and the amount of
material to remove (608). Hence, the balancing machine calculates
the amount of mass required to be removed from a sheave 102 or 104
to create a clutch 100 that is within a balanced specification. In
one embodiment, the machine uses a drill bit to drill out the
calculated amount of material from the respective sheave member 102
or 104 (610) and then rechecks the value (606). Balancing of the
clutch 100 reduces vibration during use and premature failures.
Once the tied clutch 100 is balanced (606), it is removed from the
balancing machine and the rotation shaft. It is then ready to be
shipped to the customer assembled and pre-balanced (612).
[0034] FIG. 7A illustrates an input shaft 700 of a transmission
(not shown) that is aligned with a central passage 125 along the
longitudinal rotational axis 502 formed in the clutch 100 that is
accessed by the central opening 106c in the cover 106d of the cam
assembly 106. The input shaft 700 of the transmission further
includes exterior splines 702, a shoulder 706 and a central bore
704. The central bore 704 of input shaft 700 includes a threaded
bore portion that selectively engages external threads 156 of a
bolt 150 used to hold the shaft 700 in the clutch 100 via a load
washer 152 and a thrust bushing 154 that is received in recess 131
of the first sheave 102, as illustrated in FIG. 7B. FIG. 7B
illustrates the input shaft 700 of the transmission being received
in the tied clutch 100. The exterior spline 702 of the input shaft
700 of the transmission engages the internal splines in the central
passage 108c of the spider 108 such that rotation of the spider 108
rotates the transmission input shaft 700. As illustrated in FIG.
5B, the second central opening 102c in the first central hub 102b
of the first sheave member 102 is aligned with a central opening
104h in the second hub 104b of the second sheave member 104.
Further, the central opening 108c of the spider 108 and the central
opening to the cam central opening 106c of the cam cover 106d are
further aligned to form the central passage 125 to receive the
input shaft 700 of the transmission. In the embodiment illustrated,
bearings 116, 114 and 115 are used to engage surfaces of the input
shaft 700. In particular, bearings 116 in the second central
opening 102c of the first hub 102b engages a first surface portion
of the input shaft 700, bearing 114 in central opening 104h of the
second hub 104b of the second sheave member 104 engages another
surface portion of the input shaft 700 and bearing 115 in central
opening 106 to the cam cover 106d engages yet another surface
portion of the input shaft 700.
[0035] In operation, the second (moving) sheave member 104 and the
cam assembly 106 translates along a length of the input shaft 700
to either open up or close down a gap between the first and second
conical faces 102a and 104a of the first and second sheaves 102 and
104. The interior gears (splines) of the spider 108 engage the
splines 702 of the input shaft 700 therein locking rotation of the
spider 108 with rotation of the input shaft 700. In addition,
shoulder 706 of the input shaft 700 abuts an end surface of the
spider 108 thereby preventing the spider 108 from translating along
a length of the input shaft 700. As sheave 104 and the cam assembly
106 translate along the input shaft 700 there is a slight rotation
relative to the input shaft 700. The first sheave 102, the second
sheave 104 and the cam assembly 106 rotate together to the degree
of the profile surfaces (helix) 302, 304 on the cam assembly 106.
The faster the sheave 104 and cam assembly 106 rotates (i.e. the
more torque applied), the more the biasing member 112 is compressed
thereby increasing the force of the cam 108 on shoulder 706 of the
input shaft 700 and the gap between the first and second conical
faces 102a and 104a of the first and second sheaves 102 and 104 is
widened.
[0036] Referring to FIG. 8A an exploded side perspective view of
another embodiment of a CVC 200 is illustrated. In this embodiment,
a first (stationary) sheave member 202 is not tied together with a
second (movable) sheave member 204. However, like the embodiment
discussed above, this non-tied clutch 200 does not include a
central post. The first sheave member 202 includes a hub 202c with
a first opening 202d to a chamber 202e. A first conical-faced
surface 202a of the first sheave member 202 extends radially from
the first opening 202d. Opposite the first conical-faced surface
202a is a second surface 202b of the first sheave member 202. The
hub 202c of the first sheave member 202 extends centrally generally
in a perpendicular fashion from the second surface 202b of the
first sheave member 202. The second sheave member 204 includes a
second conical-faced surface 204a and a third surface 204b opposite
the second conical-faced surface. The second sheave member 204 of
this embodiment includes a cam assembly 204c. The cam assembly 206
extends centrally from the second conical-faced surface 204a in
generally a perpendicular fashion. Hence, unlike the embodiment
described above with a separate cam assembly 106, the cam assembly
206 in this embodiment is integrated into a hub of the second
sheave member 204. The cam assembly 204c includes cam profile
surfaces 205a and 205b similar to cam 106 described above.
[0037] Cam holding rods 206a and 206b are coupled to the first
sheave member 202 (this is further illustrated in FIGS. 8b and 8C).
The Cam holding rods 206a and 206b hold respective cam rollers 208a
and 208b. In particular, each cam roller 208a and 208b is posted on
portion of a respective holding rod 206a and 206b. A washer 210a
and 210b is then placed on the respective cam holding rod 206a and
206b. A C-clip 212a and 212b is then clipped in a respective groove
209a and 209b in the respective can holding rod 206a and 206b to
hold the respective cam roller 208a and 208b on the respective cam
holding rod 206a and 206b. Bearings 214 and 216 are positioned
around inner surfaces of the second sheave member 204 to engage an
input shaft of a transmission. Further illustrated in FIG. 8A are a
biasing member 218 and a bias cap 220. The bias retaining cap 220a
includes a central opening to receive an input shaft of a
transmission. The bias retaining cap 220 is designed to abut an end
of the biasing member 218. The cam holding rods 206a and 206b and
cam rollers 208a and 208b are assembled to the first sheave member
202 in one embodiment through the first opening 202d and into the
chamber 202e of the first sheave member 202.
[0038] FIGS. 8B and 8C illustrates a cross-sectional side view of
clutch 200. In particular, FIG. 8A illustrated the first and second
conical faced surfaces 202a and 202b of the first and second sheave
members 202 and 204 being positioned near each other. FIG. 8C
illustrates the first and second conical faced surfaces 202a and
202b of the first and second sheave members 202 and 204 being
positioned apart from each other (which would happen as torque on
the clutch 200 increases). In this embodiment, the clutch 200 comes
in four different parts that are assembled on an input shaft to a
transmission. The four parts are the bias retaining cap 220, the
bias member 218, the second (movable) sheave member 204 and the
first (stationary) sheave member 202. Similar to clutch 100
discussed above, this embodiment also forms a central passage 225
along a longitudinal axis 251 that is configured to receive an
input shaft of a transmission as illustrated in FIGS. 9A and 9B.
Referring to FIGS. 9A and 9B cross-sectional illustrations of the
clutch 200 coupled to an input shaft 230 of a transmission (not
shown) is illustrated. In particular, FIG. 9A illustrates, the
first and second conical faced surfaces 202a and 202b of the first
and second sheave member 202 and 204 being positioned near each
other. FIG. 9B illustrates the first and second conical faced
surfaces 202a and 202b of the first and second sheave member 202
and 204 being positioned apart from each other (which would happen
as the torque on the clutch 200 increases). As illustrated in FIGS.
9A and 9B, an end surface about the central opening 220a of the
bias retaining cap 220 abuts a shoulder 230a of the input shaft 230
to retain the bias retaining cap 220 in a static position in
relation to the input shaft 230. Splines 230b proximate an end of
the input shaft 230 engage interior gear (splines) of the first
sheave member 202 to lock rotation of input shaft 230 with rotation
of the clutch 200. Movement of the second (movable) sheave member
204 along the length of the input shaft 230 in relation to the
first (stationary) sheave member 202 is similar to that described
above in regards to clutch 100. In the clutch 200 embodiment, the
clutch 200 is balanced by first mounting the four pieces as
described above on a test input shaft and then balanced as
described above in FIG. 6. Once, the balancing is complete, the
clutch 200 is unassembled from the test input shaft and packaged
for sale.
[0039] FIG. 10 illustrates yet another embodiment of an untied CVC
300. Similar to clutch 200, clutch 300 includes a first
(stationary) sheave member 302 and a second (movable) sheave member
304 that has a cam assembly 304c for a hub. In particular, the
first sheave member 302 includes a first conical-faced surface
302a, a second surface 302b opposite the first conical-faced
surface 302a and a hub 302c centrally extending from the second
surface in generally a perpendicular fashion. Cam holding rods 306a
and 306b are coupled to the first sheave member 302. The Cam
holding rods 206a and 306b in turn rotationally hold cam rollers
308a and 308b. The cam rollers 308a and 308b engage respective cam
profiles in the cam assembly 304c of the second sheave member 302
that is received in the hub 302c of the first sheave member 302.
The second sheave member 304 further includes a second
conical-faced surface 304a that extends from the cam assembly 302c
and a third surface 304b that is opposite the second conical faced
surface 304a.
[0040] Clutch 300 further includes a tubular translate support 328
that holds the first sheave member 302, the second sheave member
304, the biasing member 318 and the bias retaining cap 320 together
as one unit. The translate support includes an outer surface 328c
and an inner surface 328d. In the embodiment of FIG. 10, bearings
312 and 316 are positioned between the second sheave member 304 and
the outer surface 328c of the translate support 328. A section of
the outer surface 328c of the translate support 328 near a first
end 328e of the translate support 328 includes external splines 332
that engage internal splines 330 of the hub 302c of the first
sheave member 302 to lock rotation of the translate support 328
with rotation of the first sheave member 302. A first groove 336 in
the outer surface 328c of the translate support 328 receiving a
protrusion in the hub 302c of the first sheave member 302 retains
the translate support 328 within the clutch 300. The first groove
336 in this embodiment is near the first end 328e of the translate
support 328. The outer surface 328c of the translate support 328
includes a second groove 326 that is proximate a second end 328f of
the translate support 328. A C-clip 324 fits in the second groove
326 to retain the bias retaining cap 324 in a static position on
the translate support 328. The translate support 328 further has an
opening 328b to a central passage 325 along a longitudinal
rotational axis 351 of the clutch 300 that is designed to receive a
transmission input shaft (not shown). Spines on the input shaft
engage interior spines 328a on the inner surface 328d of the
translate support 328 to lock rotation of the transmission input
shaft to the rotation of the translate support 328. Balancing of
clutch 300 is done similar to that described in regards to FIG. 6
above. Clutch 300 provides an untied clutch 300 that can be
pre-balance and be pre-assembled.
[0041] Although specific embodiments have been illustrated and
described herein, it will be appreciated by those of ordinary skill
in the art that any arrangement, which is calculated to achieve the
same purpose, may be substituted for the specific embodiment shown.
This application is intended to cover any adaptations or variations
of the present invention. Therefore, it is manifestly intended that
this invention be limited only by the claims and the equivalents
thereof
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