[0015]
FIG. 6 is a flat
layout illustration of a portion of the flow diverter of the
valve of FIG. 3, the flow diverter shown in a full open
position.
[0016]
FIG. 7 is a flat
layout illustration of the flow diverter of FIG. 6 shown in a
full closed position.
[0017]
FIG. 8 is side
view, partly in section, of a valve according to a third
exemplary embodiment of the invention.
[0018]
FIG. 9 is a side
view of a valve according to a fourth exemplary embodiment of
the invention.
[0019]
FIG. 10 is an
end view of the valve of FIG. 9.
[0020]
FIG. 11 is side
view of a valve according to a fifth exemplary embodiment of the
invention.
[0021]
FIG. 12 is a
side view, partly in section, of a valve according to an sixth
exemplary embodiment of the invention.
[0022]
FIG. 13 is a
flat layout illustration of a portion of the flow diverter of
the valve of FIG. 12, the flow diverter illustrated in a full
open position.
[0023]
FIG. 14 is a
flat layout illustration of the flow diverter of FIG. 13 shown
in a full closed position.
[0024]
FIGS. 15 and 16
are schematic illustrations of engine coolant systems
incorporating the valve of FIGS. 3 through 5.
[0025]
FIG. 17 is a
schematic illustration of an engine coolant system incorporating
the valve of FIGS. 9 and 10.
[0026]
FIG. 18
illustrates the rotary valve in combination with an electronic
water pump.
[0027]
FIG. 19
illustrates the rotary valve/water pump combination of FIG. 18
mounted to an engine.
DESCRIPTION OF THE INVENTION
[0028] Referring to the drawings, where like numerals identify
like elements, there is illustrated in FIGS. 1 and 2 a valve 10
according to an exemplary embodiment of the invention. The valve
10 includes a body 12 defining an interior for receiving a
fluid, such as a coolant for an engine of an automobile for
example. The body 12 includes an inlet 14 defining an inlet
passageway and first and second outlets 16, 18 defining outlet
passageways. The body 12 also includes a main junction 20 to
which each of the inlet 14 and the first and second outlets 16,
18 is connected such that an interior defined by the main
junction 20 communicates in common fashion with each interiors
of each of the inlet 14 and the outlets 16, 18. As shown, the
inlet 14 and the outlets 16, 18 of the depicted valve body 12
are tubular in form defining substantially cylindrical
interiors. The interior of the main junction 20 is also
substantially cylindrical.
[0029] The valve 10 includes a flow diverter 22 located within
the interior of the main junction 20 of the body 12 between the
inlet 14 and the outlets 16, 18. The flow diverter 22 includes a
tubular side wall 24 defining an interior. The outer surface of
the side wall 24 of flow diverter 22 is substantially
cylindrical to provide for sliding receipt of the flow diverter
22 within the interior of the main junction 20 of valve body 12.
The sliding receipt of the flow diverter 22 in this manner
provides for rotation of the flow diverter 22 with respect to
the valve body 12 about a central axis of the flow diverter 22.
[0030] The valve 10 includes a motor 26 having an output shaft
28 engaging the flow diverter 22 for drivingly rotating the flow
diverter 22 with respect to the valve body 12. In the
illustrated embodiment, the flow diverter 22 includes an end
wall 30 connected to the side wall 24 of the flow diverter 22 at
one end of the side wall 24. The flow diverter 22 also includes
a socket 32 on the end wall 30 extending from a surface of the
end wall 30 opposite the interior of the flow diverter 22. As
shown in FIG. 1, the socket 32 is adapted to receive an end
portion of the motor output shaft 28. To facilitate engagement,
and transfer of torque, between the motor 26 and the flow
diverter 22, the socket 32 and the end portion of the output
shaft 28 can include flattened surfaces (e.g., a hex-head,
non-circular, triangular or flat configurations).
[0031] Referring to FIG. 2, the first and second outlets 16, 18
are spaced apart from each other on the main junction 20 such
that an angle, .theta..sub.A, defined between central axes of
the outlets 16, 18 is equal to approximately 150 degrees. The
inlet 14 of the illustrated valve 10 is spaced between the
outlets 16, 18 on the main junction 20 such that angles,
.theta..sub.B and .theta..sub.C, defined between the inlet 14
and the first and second outlets 16, 18, respectively, are each
equal to approximately 105 degrees. An opening 34 is defined in
the side wall 24 of the flow diverter 22 extending around
approximately one-half (i.e., 180 degrees) of the circumference
of the tubular side wall 24. The opening 34 is located along the
length of the side wall 24 of the flow diverter 22 to position
the opening 34 adjacent the location of the inlet 14 and the
outlets 16, 18 on the main junction 20.
[0032] Arranged in this manner, the opening 34 in the flow
diverter 22 is adapted to provide communication between the
inlet 14 and either one of the first and second outlets 16, 18
as follows. The flow diverter 22 is shown in FIG. 2 in a first
flow position. In the first flow position, the flow diverter 22
is oriented rotationally with respect to the valve body 12 such
that the opening 34 provides communication between the first
outlet 16 and the interior of the flow diverter 22. As shown,
the opening 34 in the first flow position also provides
communication between the inlet 14 and the interior of the flow
diverter 22. As a result, a flow of a fluid directed into the
interior of valve body 12 will be directed in the first flow
position into the first outlet 16 via the interior of the flow
diverter 22 as illustrated by the flow arrow in FIG. 2. As
shown, the tubular side wall 24 of flow diverter 22 functions to
close the second outlet 18 from the interior of the main
junction 20 in the first flow position, thereby preventing fluid
from being directed into the second outlet 18. Those skilled in
the art will readily understand that a counter-clockwise
rotation of the flow diverter 22 (from the point of view shown
in FIG. 2) by an angle equal to approximately .theta..sub.A
(e.g., approximately 150 degrees) will position the flow
diverter 22 in a second flow position in which the fluid is
directed from the inlet 14 into the second outlet 18. In a
similar manner as the second outlet 18 in the first flow
position, the flow diverter 22 will function to close the first
outlet 16 from the interior of the main junction 20 in the
second flow position such that flow of the fluid into the first
outlet 16 is prevented.
[0033] The motor 26 is preferably adapted to provide two-way
travel of the flow diverter 22 between the first and second flow
positions. According to a presently preferred embodiment, the
motor 26 is a stepper motor and the valve 10 includes travel
stops (not shown) for limiting the rotational travel of the flow
diverter 22 between the first and second flow positions. Such a
construction provides for the use of a simple torque-limited
stepper motor for driving the flow diverter 22. The valve of the
present invention is not limited to stepper motor and could
include other types of motive force (e.g., DC motor, solenoid,
hydraulic, or mechanical force) for driving the flow diverter.
The use of a DC motor or a hydraulic or mechanical force for
driving the flow diverter would be desirable for higher capacity
valves (e.g., valves having capacity greater than approximately
200 gallons per minute).
[0034] The valve 10 includes a mounting plate 36 at one end of
the main junction 20 of the valve body 12. The mounting plate 36
is adapted to receive fasteners 38 for securing the valve body
12 to a housing of the motor 26. The valve 10 also includes an
annular flange 40 located at an end of the main junction 20 of
valve body 12 opposite the mounting plate 36. As shown in FIG.
1, the flange 40 defines a recessed shoulder on an inner surface
for receiving a closure plate 42 to enclose the flow diverter 22
within the interior of the main junction 20. The flange 40 and
the closure plate 42 facilitate placement of the flow diverter
22 into the interior of the valve body 12 during assembly of the
valve 10.
[0035] For smaller capacity valves (e.g., capacity less than
approximately 150 gals/minute), all components of the flow
diverter and valve body can molded from a thermoplastic material
(e.g., glass-filled nylon). This includes valves on most
passenger cars having operating temperatures ranging between
approximately 40 degrees Centigrade and approximately 130
degrees Centigrade. For valves used in HD diesel engines and for
larger capacity valves, the flow diverter and valve body would
both preferably be made from a metal (e.g., aluminum). The use
of similar materials (e.g., all plastic or all metal) for the
flow diverter and the valve body, desirably provides more
uniform thermal expansion to help prevent sticking between the
flow diverter and the valve body. The aluminum of the flow
diverter 22 can be coated with a polytetrafluoroethylene
material (e.g., Teflon.RTM.) to facilitate relative rotation
between the flow diverter 22 and the valve body 12. The
inclusion of a coating of polytetrafluorethylene on the diverter
22 would also help prevent sludge build-up on the diverter 22.
For valves having a valve body made from a thermoplastic
material, the closure plate 42 of valve body 12 is preferably
secured to the flange 40 using a thermoplastic welding process
(e.g., spin welding). It should be understood, however, that the
present invention is not limited to any particular material such
as aluminum or thermoplastics and that other materials (e.g.,
magnesium) could be used. Also, although preferred, it is not
required that a similar material be used to form both the flow
diverter and the valve body. It is conceived that the use of
mixed materials could have application in special circumstances.
[0036] As shown in FIG. 1, the main junction 20 of valve body 12
and the flow diverter 22 are preferably dimensioned such that a
controlled gap 44 is defined between the closure plate 42 and an
end of the flow diverter 22.
[0037] The flow diverter 22 of valve 10 includes apertures 45
defined in the end wall 30 of the flow diverter 22. The
apertures 45 in end wall 30 allow some of the fluid directed
into the interior of the flow diverter 22 to pass through the
end wall 30 into a space provided between the end wall 30 and
the mounting plate 36. The receipt of fluid via apertures 45
serves to prevent a pressure imbalance that could otherwise
develop on opposite sides of the end wall 30.
[0038] Although the flow diverter 22 has been described above as
directing flow to either the first outlet 16 or the second
outlet 18, it should be understood that the flow diverter 22
could be adapted to provide a position in which a flow of a
fluid is split between the first and second outlets 16, 18.
[0039] In the above-described valve 10 the flow of fluid is
directed into the interior of the flow diverter 22, and
discharged from the interior of the flow diverter 22, through
the opening 34 in the side wall 24. Thus, the fluid is directed
in lateral directions (i.e., perpendicular to the central axis
of the flow diverter 22) for both inlet and discharge. Referring
to FIGS. 3 through 5, there is illustrated a valve 46 according
to a second exemplary embodiment of the invention having a flow
diverter 48 in which the fluid is turned 90 degrees, either
axially to laterally with respect to the flow diverter 48, or
alternatively laterally to axially, between the inlet and
discharge of fluid.
[0040] The valve 46 includes a body 50 defining an interior and
including an inlet 52 and first and second outlets 54, 56 that,
similar to the inlets and outlets of valve 10 are substantially
cylindrical. The valve body 50 also includes a substantially
cylindrical main junction 58 located between the inlet 52 and
the outlets 54, 56. The outlets 54, 56 extend laterally from the
main junction 58 and are located on opposite sides of the main
junction 58 of the illustrated valve 46. The inlet 52 is located
at an end of the main junction 58 and is oriented such that a
central axis of the inlet 52 is substantially parallel to, and
aligned with, a central axis of the main junction 58. Although
the valve 46 is shown and described as including inlet 46 and
outlets 54, 56, the present invention is not so limited. It
should be understood that the direction of flow could be
reversed such that flow enters the valve 46 from a pair of
"inlets" (e.g., elements 54, 56) for discharge via a single
"outlet" (e.g., element 46).
[0041] The flow diverter 48, similar to the flow diverter 22 of
valve 10, includes a tubular side wall 60 defining an interior
and having an outer surface slidingly received by the main
junction 58 for relative rotation between the flow diverter 48
and the valve body 50. Also similar to flow diverter 22 of valve
10, the flow diverter 48 includes an end wall 62 and a socket 64
engagingly receiving an output shaft 68 of a motor 66 for driven
rotation of the flow diverter 48 by the motor 66. The socket 64
on flow diverter 48 extends inwardly with respect to the flow
diverter 48, in contrast to the socket 32 of flow diverter 22
which extends in an outward direction from the end wall 30 of
flow diverter 22. The valve 46 includes a mounting plate 70 at
an end of the main junction 58 of valve body 50 receiving
fasteners 72 to secure the valve body 50 to the motor 66. The
valve 46 includes a bushing 74 received in an opening defined in
the mounting plate 70 for rotatably supporting the output shaft
68 of motor 66. Also, in some applications a simple radial
O-ring shaft seal (not shown) can be utilized. According to a
presently preferred embodiment, the motor 66 is a stepper motor.
As shown, the motor 66 can include dual motor leads 75 to
provide protection against failure of the motor in the event
that one of the leads becomes inoperative. Preferably,
separation is provided between the leads 75 to limit the risk
that an event causing severance of one of the motor leads 75
result in severance of both motor leads 75. It is also
contemplated that in the event of a relatively high motor torque
(e.g., a torque above a design range for motor 66) the valve 46
could be adapted to send an alert signal for service identifying
a failure mode.
[0042] Similar to valve 10, the valve 46 includes a flange 76
located at an end of the main junction 58 opposite the mounting
plate 70 and defining a recessed shoulder on an inner surface of
the flange 76. The flange 76 on the main junction 58 is adapted
to receive a flange 78 located at an end of the inlet 52 for
connecting the inlet 52 to the main junction 58. The inlet 52 is
preferably secured to the main junction 58 by welding the
flanges 76, 78 to each other. According to one preferred
embodiment, the valve body 50 is made from a thermoplastic
material (e.g., glass-filled nylon) and the inlet 52 is secured
to the main junction 58 using a thermoplastic welding process
(e.g., spin welding).
[0043] The connection of the inlet 52 at the end of the main
junction 58 in the above-described manner results in fluid being
directed into the interior of the flow diverter 48 in an axial
direction with respect to the flow diverter 48 through an open
end 80 of the flow diverter 48. As shown in FIG. 3, at least one
opening 82 is defined in the side wall 60 of the flow diverter
48 for discharging fluid to one of the outlets 54, 56 depending
on the angular orientation of the flow diverter 48 with respect
to the valve body 50. Preferably, the flow diverter 48 includes
an opening on each of opposite sides of the side wall 60. As
described below in greater detail, the use of a pair of openings
in this manner limits the amount of rotation necessary to move
the flow diverter 48 between first and second flow positions for
respectively directing the flow to the first and second outlets
54, 56 of valve 46. As shown in the drawings and described below
in greater detail in the description of FIGS. 6 and 7, the
openings 82 are not circular in shape. Instead, the
configuration of the openings 82 has been empirically developed
to provide desired flow characteristics (e.g., to transition
flow during initial opening of the valve to prevent "gulps" of
cold coolant from entering an engine). The use of separate
discharge openings also allows for differing configurations for
the openings, as also described below, for more precise flow
control (e.g., a first configuration for a radiator outlet
versus a by-pass outlet).
[0044] The flow diverter 48 also includes apertures 84 defined
in the end wall 62 of the flow diverter 48. The apertures 84 in
end wall 62 allow some of the fluid directed into the interior
of the flow diverter 48 via the inlet 52 to pass through the end
wall 62 into a space 86 provided between the end wall 62 and the
mounting plate 70. The receipt of fluid within the space 86 via
apertures 84 serves to prevent a pressure imbalance that could
otherwise develop on opposite sides of the end wall 62.
[0045] As illustrated in FIG. 4, the rotary valve 46 is
configured such that the flow diverter 48, and the main junction
58 of body 50 in which the flow diverter 48 is housed, have
substantially uniform wall thickness about the valve body 50.
Uniformity in wall thickness in this manner facilitates
precision molding of both mating components of the valve 46 to
control all close tolerances features including roundness. Such
precision facilitates dimensional stability under all operating
conditions for the valve 46.
[0046] Referring to FIG. 5, the flanges 76, 78 of the valve body
50 of rotary valve 46 are adapted to receive fasteners 112
(e.g., nut and bolt connectors) in aligned openings for securing
the inlet of the valve body 50 to the main junction 58. As shown
in FIG. 5, the valve 46 preferably includes an O-ring face seal
between the flanges 76, 78. As also shown in FIG. 5, a taper is
preferably provided on the inner surface of the main junction 58
adjacent the flanges 76, 78 to facilitate assembly of the
diverter 48 with the O-ring component.
[0047] The interior volume provided by the construction of the
flow diverter 48 provides an ideal transition between the
axially inlet flow of fluid to the radially discharged flow (or
alternately, between a radially inlet flow and an axially
discharged flow in a reversed flow application of the valve 46).
Also, the rounded configuration of the rotary valve 46 of the
present invention allows the valve to operate freely regardless
of pressure differentials between various components of a fluid
control system (e.g., between radiator, engine, by-pass, etc. of
an engine coolant system) and without the need for extra torque
or special balancing passageways as disclosed in U.S. Pat. Publ.
2006/0005789. The construction of the valve also provides space
saving efficiencies for reduced package size.
[0048] Referring to FIGS. 6 and 7, a portion of the side wall 60
of flow diverter 48 of valve 46 is shown. The portion of the
substantially cylindrical side wall 60 has been illustrated in
FIGS. 6 and 7 in a flat layout form to facilitate description.
The flow diverter 48 is respectively shown in full open and full
closed positions in FIGS. 6 and 7. The inner diameter of the
associated outlet 56 is shown in dotted line in FIGS. 6 and 7 to
illustrate the relative positions between the opening 82 in the
figures to illustrate the relative positions between the opening
82 and the outlet 56 in the full open and full closed flow
positions. As described above, the flow diverter 48 preferably
includes a second opening (not shown) on an opposite side of the
flow diverter 48. As understood by one skilled in the art, the
inclusion of two openings in this manner limits the amount of
rotation necessary to move the flow diverter between first and
second flow positions in which fluid is directed to the first
and second outlets 54, 56, respectively.
[0049] The opening 82 in the flow diverter side wall 60 includes
a rounded end 116 at one end of the opening 82. As shown, the
rounded end 116 has a radius that is substantially equal to that
of the inner surface of the associated outlet 56. In this
manner, the opening 82 is configured such that no portion of the
flow diverter side wall 60 will block the outlet 56 in the full
open position shown in FIG. 6 (i.e., there is complete
communication between the interior of the flow diverter 48 and
the interior of the outlet 56). The opening 82 is
non-symmetrical including an opposite end 118 that is not
circular in configuration. Instead, as shown, the edge of the
flow diverter side wall 60 defining the opening 82 returns
inwardly with respect to the opening 82 at the second end 118
such that a portion of the side wall 60 forms a tongue-like
formation 120 projecting inwardly into the opening 82 at the
second end 118. As should be understood by one skilled in the
art, the inclusion of the tongue-like projection 120 at the
second end 118 of opening 82 provides for controlled transition
in the flow of fluid being directed from the flow diverter 48 to
the associated outlet 56 as the flow diverter 48 is moved from
the full open position towards the full closed position (i.e.,
downwardly in the point of view of FIG. 6). In addition to
limiting necessary rotation between the first and second flow
positions, the inclusion of separate openings on opposite sides
of the flow diverter 48 allows for customization of the
flow-controlling projection defined at the second end of the
opening (e.g., differently configured projection for a radiator
outlet of an automotive coolant system compared to that for a
by-pass outlet).
[0050] The flow diverter 48 also defines a substantially
circular O-ring groove 122 in an outer surface of the side wall
60 adapted for receiving an O-ring seal (not shown). As shown in
FIG. 7, the groove 122 is located with respect to the opening 82
to position the groove 122 in a substantially concentric
relationship with the associated outlet 56 in the full closed
condition to provide a closure seal between the diverter 48 and
the outlet 56. It should be understood that the O-ring feature
could be included on any of the various embodiments of the
rotary valve of the present invention.
[0051] Referring to FIG. 8, there is shown a valve 124 according
to a third exemplary embodiment of the invention. The valve 124
is adapted for relatively larger flow capacity compared to the
valve 46. The valve 124 includes a body 126 including and inlet
128 connected to a main junction 130 at an end of the main
junction 130. The body 126 also includes a pair of outlets 132,
133 connected in transverse manner to the main junction 130
similar to the outlets 54, 56 of valve 46 for example. In a
similar manner as valve 46, the inlet 128 and the main junction
130 respectively include flanges 134, 136 adapted for receiving
fasteners 138 (e.g., nut and bolt connectors) for securing the
inlet 128 to the main junction 130.
[0052] The valve 124 includes a flow diverter 140 rotatably
received within an interior of the main junction 130. The flow
diverter 140 includes a substantially cylindrical side wall 142
and an end wall 144 defining a socket 146 for receiving an
output shaft 150 of a drive motor 148. It should be understood
that the flow diverter 140 includes openings (not shown) in the
side wall 142 of the flow diverter as described above to provide
for respectively opening and closing the outlets of the valve
124 to fluid from the interior of the diverter 140. To
facilitate rotatable support of the flow diverter 140 within the
valve body 126, the valve 124 includes a pair of watertight
bearings 152 located at opposite ends of the flow diverter 140
within housing portions of the main junction 130. An
intermediate area of the valve 124 located between the bearings
152 is sized to minimize friction. According to a presently
preferred embodiment, the valve body 126 and the flow diverter
140 are both made from aluminum. The flow diverter 140 can be
coated with polytetrafluoroethylene to further limit friction
between the flow diverter 140 and the valve body 126.
[0053] As shown in FIG. 8, the valve 124 includes an O-ring seal
located between the outer surface of the flow diverter 140 and
the interior of the main junction 130 adjacent the outlet 132 to
provide a seal between the outer surface of the flow diverter
140 and the interior of the main junction 130.
[0054] Similar to the above-described valves 10, 46, the valve
124 includes a mounting plate at an end of the main junction 130
receiving fasteners to secure the valve body 126 to the motor
148 of valve 124. As discussed above, the flow diverter of each
of the valves 10, 46, 124 also includes an end wall defining a
socket engagingly receiving the output shaft of the motor. In
addition to facilitating valve assembly, these construction
features also facilitate subsequent access to interior
components of the valves, thereby promoting serviceability of
the valves (e.g., for repair or replacement of an interior
component of the valve). This serviceability feature is
particularly desirable in valves such as the higher capacity
valve 124 providing ready access for servicing interior
components of the valve 124 such as the watertight bearings 152.
Regarding the desired serviceability feature, certain large
capacity valves (e.g., capacity greater than approximately 400
gals/minute) are expected to incorporate preventive maintenance
provisions due to the initial high purchase cost.
[0055] Each of valves 46, 124, described above, includes a
single inlet and a plurality of outlets adapted for receiving a
fluid from the inlet via an intermediately located flow
diverter. The present invention, however, is not so limited.
Referring to FIGS. 9 and 10, there is shown a valve 154
according to a fourth exemplary embodiment of the invention. The
valve 154 includes a body 156 including a substantially
cylindrical main junction 158 and a flow diverter 160 rotatably
received within an interior of the main junction 158 in the
above described manner and having openings 162 in a side wall of
the flow diverter. The valve body 156 of valve 154 includes an
outlet 164 located at an end of the main junction 158 in an
axially aligned manner similar to the inlet 52 of valve 46 for
example. However, instead of directing fluid into the flow
diverter 160, the outlet 164 receives fluid from the flow
diverter 160 as indicated by the flow arrow in FIG. 9. The valve
154 includes a motor 166 to which the main junction 158 of body
156 is secured in the above-described manner for valves 46, 124.
[0056] The valve body 156 includes first, second and third
inlets 168, 170, 172 each connected to the main junction 158 in
transverse fashion for directing a fluid into the interior of
the flow diverter 160 through the openings 162 of the diverter
160. The inlets 168, 170, 172 are spaced about the main junction
158 such that angles, .theta..sub.D, .theta..sub.E,
.theta..sub.F, are respectively defined between the first and
third inlets 168, 172, between the first and second inlets 168,
170 and between the second and third inlets 170, 172. The
angles, .theta..sub.D, .theta..sub.E, .theta..sub.F, are
respectively equal to approximately 100 degrees, 130 degrees,
and 130 degrees, respectively, in the depicted embodiment.
[0057] According to one embodiment, the valve 154 could be
adapted to direct coolant fluid in an automotive engine and the
inlets 168, 170, 172 could respectively receive coolant fluid
from an engine bypass line, from the radiator, and from the
transmission (or engine oil pan) to direct the coolant fluid to
a coolant pump via the outlet 164. This valve concept is
illustrated in the layout drawing of FIG. 18. The bypass line
168 and the radiator inlet line 170 maintain the same open and
close features as explained above for valve 46 of FIGS. 3
through 5. However, the transmission line 172 is designed to
always remain opened. This allows for the cooling of the
transmission fluid during hot conditions and the heating of the
transmission fluid during cold conditions.
[0058] Referring to FIG. 11, there is shown a valve 176
according to a fifth exemplary embodiment of the invention.
Similar to valve 154, the valve 176 includes a body 178 having a
single outlet 180 connected to an end of a main junction 182 in
an axially aligned manner and a flow diverter 184 rotatably
received in an interior of the main junction 182. The main
junction 182 is secured to a motor 186 at an end of the main
junction 182 opposite the outlet 180.
[0059] The valve body 178 includes a plurality of inlets
arranged in two groups of inlets each including three inlets.
The inlets of the first group include first, second and third
inlets 188, 190, 192 and the inlets of the second group include
fourth, fifth and sixth inlets 194, 196, 198. The first group of
inlets 188, 190, 192 is spaced about the main junction 182 at a
first axial location of the main junction 182 and the second
group of inlets 194, 196, 198 is spaced about the main junction
182 at a second axial location of the main junction 182. In the
above-described manner, the flow diverter 184 of valve 176
includes openings, such as opening 200 for inlet 190, for
directing fluid into the interior of the flow diverter 184 from
the inlets. As shown, the opening 200 includes a
flow-controlling tongue 202. In an automotive application, the
inlets 188, 190, 192, 194, 196, 198 could respectively be
arranged to receive a coolant fluid from transmission, radiator,
bypass line, exhaust gas recirculation (EGR), charge air cooler
(CAC), and rear axle.
[0060] Referring to FIG. 12, there is shown a valve 228
according to a sixth exemplary embodiment of the invention. The
valve 228 includes a body 230 having a main junction 232 and an
inlet 234 secured to an end of the main junction 232 in an
axially aligned manner. The main junction 232 is secured to a
motor 236 at an end of the main junction 232 opposite the inlet
234. A flow diverter 238 is rotatably received in an interior of
the main junction 232 and includes an end wall 239 defining a
socket formation 240 engagingly receiving an output shaft 242 of
motor 236 for drivingly rotating the flow diverter 238. The
valve body 230 also includes outlets, such as outlet 244,
extending transversely from the main junction 232. The flow
diverter 238 includes a side wall 246 having openings, such as
opening 248, for directing fluid to one of the outlets, such as
outlet 244, from the inlet 234 via an interior of the flow
diverter 238. The flow diverter 238 also includes apertures 250
defined by the end wall 239 to provide for balanced pressure on
opposite sides of the end wall 239. As discussed with respect to
some of the other embodiments, this embodiment also includes the
taper in the main junction 232 to facilitate assembly, as well
as the O-ring component. Although these features are optional,
they are preferred.
[0061] Referring to FIGS. 13 and 14, a portion of the outer
surface of the flow diverter 238 is shown in flat layout in full
open and full closed positions, respectively. Similar to valve
46, the opening 248 in flow diverter 238 of valve 228 includes a
rounded first end 252 having a radius substantially matching
that of the outlet 244 and an opposite second end 254 forming a
flow controlling tongue 256. Also similar to valve 46, the flow
diverter 238 of valve 228 defines a circular groove 258 for
receiving an annular O-ring for creating a seal between the flow
diverter 238 and the outlet 244 when the flow diverter is moved
to the full closed position for outlet 244 shown in FIG. 14. The
valve body 230 also includes a reinforcing web 260 extending
across an interior of the outlet 244 adjacent the flow diverter
238. The web 260 provides reinforcing support for an O-ring
located at the intersection between the outlet 244 and the main
junction 232. This support prevents sagging of the O-ring that
might otherwise occur when the O-ring is heated. For relatively
larger flow capacity valves (e.g., capacity greater than
approximately 200 gals/minute) additional webs may be desired,
for example two webs arranged in an inverted V-shaped
configuration as shown in broken line in FIGS. 13 and 14.
[0062] Referring to the schematic illustration of FIG. 15, there
is shown an engine coolant system 262 incorporating the rotary
valve 46 of FIGS. 3 through 5. As illustrated by the flow
arrows, engine coolant fluid is directed to the valve 46 in
system 262 from a radiator 264 via line 266 and from a bypass
line 268. The coolant fluid is outlet from the valve 46 to
engine 270 via a water pump 272.
[0063] Referring to the schematic illustration of FIG. 16, there
is shown another engine coolant system 274 incorporating the
valve 46 of FIGS. 3 through 5. As shown, system 274 is arranged
such that engine coolant fluid is directed from the engine 270
to the valve 46 via the water pump 272. Depending on the
rotational position of the valve 46, the engine coolant is
outlet from the valve 46 either to the radiator 264 via line 276
or returned to the engine 270 via bypass line 278.
[0064] Referring to FIG. 17, there is illustrated an engine
coolant system 280 incorporating the valve 154 of FIGS. 9 and
10. The system 280 is arranged such that engine coolant is inlet
to the valve 154 from radiator 282 via line 284, from the engine
286 via radiator bypass line 288, or from transmission 290 via
line 292. The engine coolant fluid is outlet from the valve 154
to a water pump 294 via line 296. From the water pump 294, the
engine coolant is respectively directed to the engine 286 and
the transmission 290 via lines 298, 300.
[0065] The inlet to the valve 154 of system 280 from the
transmission 290 preferably always remains opened. This
arrangement allows bypass flow to heat the transmission 290
during cold weather conditions and to direct colder radiator
flow during relatively hot conditions. As should be understood,
the engine coolant could alternatively be directed to another
feature of an automobile rather than the transmission 290.
[0066] Referring to FIG. 18, there is shown a portion of an
engine coolant system 302 including an integral rotary valve 304
and electronic water pump 306. The electronic water pump 306 is
described in greater detail in U.S. Pat. No. 6,499,442, which is
incorporated herein by reference in its entirety. The rotary
valve 304, like rotary valve 154 of FIGS. 9 and 10, includes
inlets 308, 310, 312 directing a fluid to a flow diverter 314
rotatably received in an interior of a main junction 316. A
motor 318 includes a housing secured to one end of the main
junction 316. The valve 304 lacks the outlet pipe that was
included in the valve 154 of FIGS. 9 and 10. Instead, a housing
320 of the electronic water pump 306 is secured directly to the
main junction 316 of the valve 304 opposite the motor 318.
[0067] Referring to FIG. 19, there is illustrated a coolant
system 322 for an automobile engine incorporating the integral
valve 304 and water pump 306 assembly of FIG. 18. The coolant is
directed into the valve 304 in system 322 from radiator 324 via
line 326, from the engine 328 via a radiator bypass line 330,
and from an oil pan 332 via line 334. The fluid is output from
the valve 304 to the integral water pump 306 and, from there, is
directed to the engine 328 via line 336 and to the oil pan 332
via line 338. In terms of the coolant flow distribution, the
system 322 is arranged substantially similar to the system 280
shown in FIG. 17, except that the coolant is directed from the
water pump 306 to the oil pan 332 instead of the transmission of
the automobile. It should be understood that the coolant line
could conceivably be directed to any suitable component of the
automobile for conditioning by the coolant system. As was the
case for the valve inlet from the transmission of system 280,
the valve inlet from the oil pan 332 in system 322 is preferably
maintained in an opened condition. Some small engines, such as
hybrid engines, might incorporate a Y connection to combine both
transmission and oil pan cooling in a single electronic-water
pump and electronic control valve.
[0068] The foregoing describes the invention in terms of
embodiments foreseen by the inventor for which an enabling
description was available, notwithstanding that insubstantial
modifications of the invention, not presently foreseen, may
nonetheless represent equivalents thereto.
