[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.
