U.S. patent application number 09/904678 was filed with the patent office on 2002-01-31 for fluid heating methods and devices.
Invention is credited to Hoshino, Tatsuyuki, Moroi, Takahiro, Niwa, Masami, Suzuki, Shigeru.
Application Number | 20020011524 09/904678 |
Document ID | / |
Family ID | 18711678 |
Filed Date | 2002-01-31 |
United States Patent
Application |
20020011524 |
Kind Code |
A1 |
Suzuki, Shigeru ; et
al. |
January 31, 2002 |
Fluid heating methods and devices
Abstract
A heating pump 10 includes a rotor 20 having a plurality of
blades 21. A dividing wall 15 radially extends within an interior
portion of the heating pump 10. The dividing wall 15 has a width W.
A distance L is defined along a circular arc between adjacent
blades 21 in an intermediate position 21a along the radial
direction of the blades 21. A ratio W/L is preferably about 0.07 to
0.36, more preferably about 0.11 to 0.30 and most preferably, about
0.20.
Inventors: |
Suzuki, Shigeru;
(Kariya-shi, JP) ; Hoshino, Tatsuyuki;
(Kariya-shi, JP) ; Niwa, Masami; (Kariya-shi,
JP) ; Moroi, Takahiro; (Kariya-shi, JP) |
Correspondence
Address: |
MORGAN & FINNEGAN, L.L.P.
345 Park Avenue
New York
NY
10154
US
|
Family ID: |
18711678 |
Appl. No.: |
09/904678 |
Filed: |
July 13, 2001 |
Current U.S.
Class: |
237/19 |
Current CPC
Class: |
B60H 1/03 20130101; F01P
3/20 20130101; F01P 2060/18 20130101; F24V 40/00 20180501 |
Class at
Publication: |
237/19 |
International
Class: |
F24D 003/08 |
Foreign Application Data
Date |
Code |
Application Number |
Jul 17, 2000 |
JP |
2000-216410 |
Claims
1. A fluid heating apparatus comprising: a housing defining an
interior, a suction port and a discharge port, a rotor rotatably
disposed within the housing interior, the rotor comprising a
plurality of radially extending blades disposed on the peripheral
surface of the rotor and a plurality of channels disposed between
the plurality of blades, wherein the respective blades are each
separated by a distance L that is defined as a circular arc length
between adjacent blades taken at intermediate position along the
radial direction of the blades and a dividing wall radially
disposed along the housing interior between the suction port and
the discharge port and having a width W, the dividing wall
preventing a direct flow of fluid between the suction port and the
discharge port when a rotor blade is aligned with the dividing
wall, wherein the ratio W/L is within a range of about 0.07 to
0.36.
2. A fluid heating apparatus as in claim 1, wherein the ratio W/L
is within a range of about 0.11 to 0.30.
3. A fluid heating apparatus as in claim 1, wherein the ratio W/L
is about 0.20.
4. A fluid heating apparatus as in claim 1, further comprising a
fluid regulator in communication with the discharge port, wherein
the fluid regulator is arranged and constructed to restrict a flow
of fluid exiting from the discharge port.
5. A fluid heating apparatus as in claim 1, wherein the channels
have a substantially semi-circular cross-section.
6. A fluid heating apparatus as in claim 1, further comprising an
engine supplying rotational power to the rotor and a heating
system, wherein fluid discharged from the discharge port is
utilized to heat the heating system.
7. A fluid heating apparatus as in claim 6, further comprising a
fluid regulator in communication with the discharge port, wherein
the fluid regulator is arranged and constructed to restrict a flow
of fluid exiting from the discharge port, the channels have a
substantially semi-circular cross-section and the ratio W/L is
within a range of about 0.11 to 0.30.
8. A fluid heating apparatus as in claim 7, wherein the ratio W/L
is about 0.20.
9. A regenerative pump comprising: a housing defining an interior,
a suction port and a discharge port, an impeller rotatably disposed
within the housing interior, the impeller comprising a plurality of
radially extending impeller vanes disposed on the peripheral
surface of the impeller and a depressions formed between each two
adjacent impeller vanes, wherein the impeller vanes are separated
by a distance L and the distance L is defined as a circular arc
length between adjacent impeller vanes taken at a middle position
of the impeller vane along the radial direction of the impeller
vane and a dividing wall disposed along the housing interior
between the suction port and the discharge port and having a width
W, the dividing wall preventing a direct flow of fluid between the
suction port and the discharge port when one impeller vane is
aligned with the dividing wall, wherein the ratio W/L is within a
range of 0.07 to 0.36.
10. A regenerative pump as in claim 9, wherein the ratio W/L is
within a range of 0.11 to 0.30.
11. A regenerative pump as in claim 9, wherein the ratio W/L is
0.20.
12. A method of heating a fluid comprising: rotating an impeller of
a regenerative pump in order to draw the fluid into the
regenerative pump, the impeller comprising a plurality of radially
extending impeller vanes disposed on the peripheral surface of the
impeller, wherein the impeller vanes are separated by a distance L
and the distance L is defined as a circular arc length between
adjacent impeller vanes taken at a middle position of the impeller
vane along the radial direction of the impeller vane and wherein a
dividing wall of the regenerative pump has a width W and a ratio
W/L is within a range of 0.07 to 0.36; and regulating fluid
pressure within the regenerative pump in order to restrict a flow
of pressurized fluid from the regenerative pump, whereby the fluid
is heated.
13. A method as in claim 12, wherein the ratio W/L is within a
range of 0.11 to 0.30.
14. A method as in claim 12, wherein the ratio W/L is 0.20.
Description
BACKGROUND OF THE INVENTION
[0001] 1. Field of the Invention
[0002] The present invention relates to turbine-type pump, which
can be utilized as fluid heating devices. The present invention
also relates to methods for heating fluids.
[0003] 2. Description of the Related Art
[0004] A known turbine or regenerative pump that is utilized as a
fluid heating device is disclosed in U.S. Pat. No. 3,720,372. The
fluid heating device includes a fluid regulating means connected to
the outlet of a pressurizing pump 110. The fluid temperature is
raised (heated) by means of the fluid regulating means. As shown in
FIG. 5, the pump 110 includes a rotor (impeller) 120 that rotates
within housing 111 in the direction of arrow 130. The rotor 120 has
a plurality of radially extending walls (blades) 121 that are
disposed on both side surfaces (peripheral surfaces) and radially
extend from rotational axis 122. The rotor 120 also includes
channels 123 that are disposed between the blades 121. A dividing
wall 115 divides the interior of the housing 111 between a suction
port 113 and a discharge port 114. When the rotor 120 rotates,
fluid is drawn into the pump 110 via section port 113 and the fluid
pressure increases due to the flow of fluid within the channels 123
that are disposed between the blades 121. By increasing the number
of impacts of the channels 123 on the fluid, the fluid pressure
increases. The pressurized fluid is then discharged through the
discharge port 114. A regulating valve (not shown) is disposed
downstream of the discharge port 114 and the regulating valve
regulates the fluid pressure generated by the pump 110. By
restricting the flow of pressurized fluid discharged from the
discharge port 114, a portion of the work of the pump 110 is
converted into an increase in the internal energy of the fluid, and
the temperature of the fluid increases. Thus, by increasing the
number of impacts of the channels 123 on the fluid, the fluid can
be heated more rapidly. However, the discharge flow rate will
naturally be decreased when the regulating valve restricts the flow
of pressurized fluid.
SUMMARY OF THE INVENTION
[0005] It is, accordingly, one object of the present invention to
teach improved turbine-type pumps that can be utilized as fluid
heating devices.
[0006] In one embodiment of the present teachings, fluid heating
devices (pumps) may include a suction port and a discharge port
separated by a dividing wall disposed within a housing. A rotor or
impeller is rotatably disposed within the housing and preferably
comprises a plurality of blades or impeller vanes (i.e. radially
extending walls) on both side surfaces. The dividing wall
preferably prevents the direct flow of fluid from the suction port
to the discharge port when a blade is aligned with the dividing
wall. A fluid regulator optionally communicates with the discharge
port. When the fluid heating device operates, the fluid regulator
regulates the fluid pressure and restricts the flow of pressurized
fluid discharged from the fluid heating device. As a result, the
internal energy of the fluid increases and thus the fluid
temperature also increases.
[0007] In a preferred aspect of the present teachings, the width
(W) of the dividing wall and the distance (L) between the rotor
blades (radially extending walls) can be adjusted in order to
efficiently heat the fluid. For example, the ratio (W/L) preferably
falls within the range of about 0.07-0.36. More preferably, the
ratio (W/L) falls within the range of about 0.11-0.30 and most
preferably, the ratio is about 0.20. The fluid may be a coolant,
such as cooling water, lubricating oil, or other similar liquid
substances, and/or a hydraulic fluid. In fact, any type of fluid
that is capable of conducting heat can be utilized with the present
teachings. Further, the "width of the dividing wall" is preferably
defined as the thinnest width of the dividing wall, if the width of
the dividing wall is not uniform.
BRIEF DESCRIPTION OF THE DRAWINGS
[0008] FIG. 1 shows a schematic view of a representative coolant
circulation circuit utilized in an automobile air conditioning
system.
[0009] FIG. 2 is a cross-sectional view of a representative heating
pump (fluid heating device).
[0010] FIG. 3 is a sectional view taken along the line III-III
shown in FIG. 3.
[0011] FIG. 4 is a graph illustrating the correlation between
(Q/Qmax) and (W/L).
[0012] FIG. 5 is a cross-sectional view of a known heating
pump.
DETAILED DESCRIPTION OF THE INVENTION
[0013] Representative fluid heating devices preferably provide a
ratio (W/L) of the dividing wall width (W) to the distance (L)
between impeller or rotor blades along a circular arc that is about
0.07 to 0.36. More preferably, the ratio is about 0.11 to 0.30 and
most preferably, the ratio is about 0.20.
[0014] Representative fluid heating devices may include, for
example, a housing defining a suction port and a discharge port. A
dividing wall is preferably disposed within an interior portion of
the housing between the suction port and the discharge port and has
a prescribed width (W). A rotor or impeller may be rotatably
disposed within the housing and may include a plurality of blades
(impeller vanes) or radially extending walls that are disposed on
the peripheral surface of the rotor. Optionally, a regulator may be
disposed in a manner to communicate with the pressurized fluid
discharged from the discharge port.
[0015] Representative methods for heating a fluid may be performed,
for example, utilizing the representative fluid heating devices,
although naturally other fluid heating devices also may be
utilized. For example, representative methods for heating a fluid
may include rotating a rotor or impeller with respect to a fluid.
The rotor may include blades or radially extending walls that are
separated along a circular arc by a distance L. The blades may pass
by a dividing wall having a width W and preferably the ratio (W/L)
is about 0.07 to 0.36. The pressure of the fluid is increased by
the work of the rotor and a fluid pressure regulator may regulate
the fluid. For example, the pressure regulator may restrict the
flow of the pressurized fluid exiting from the rotor. Consequently,
the fluid temperature may be increased.
[0016] In more preferred methods, the ratio (W/L) may be about 0.11
to 0.30 and most preferably the ratio (W/L) is about 0.20.
[0017] Additional representative examples of the present teachings
will be described in further detail with reference to the attached
drawings. This detailed description is merely intended to teach a
person of skill in the art further details for practicing preferred
aspects of the present teachings and is not intended to limit the
scope of the invention. Only the claims define the scope of the
claimed invention. Therefore, combinations of features and steps
disclosed in the above detail description may not be necessary to
practice the invention in the broadest sense, and are instead
taught merely to particularly describe some representative examples
of the invention. In addition, the present teachings naturally may
be combined in ways that are not specifically enumerated in order
to provide additional useful embodiments of the present
teachings.
[0018] As shown in FIG. 1, an automobile engine E may include a
water pump 52 that supplies a coolant (e.g. engine coolant) to a
water jacket 50. The coolant is preferably antifreeze, e.g. a
mixture of water and ethylene glycol, although naturally other
fluids may be utilized with the present teachings. A coolant
circulating circuit may include the engine E, a radiator 6, a
thermostat valve 7, a heater core 8, an electromagnetic valve 8a, a
check valve 9, a fluid heating device H, and a plurality of pipes
1-5 connecting the respective parts. In this embodiment, three
pipes 1, 2, 3 are located downstream of water jacket 50 and two
pipes 4, 5 are located upstream of the water jacket 50. Pipe 4
defines a return path to the water pump 52 via the radiator 6 and
the thermostat valve 7. Pipe 5 defines a return path to the water
pump 52 via the electromagnetic valve 8a and the heater core 8.
Pipe 1 define a path from the water jacket 50 to the thermostat
valve 7, which is disposed at the branch point of pipe 1 and pipe
4. Pipe 2 defines a path connecting the water jacket 50 to both
pipes 4, 5 via the check valve 9. Pipes 2 and 3 are disposed in a
parallel relationship between the water jacket 50 and pipes 4,
5.
[0019] The water pump 52 is linked to a crankshaft (output shaft)
of the engine E via a V-belt or other energy transmitting means and
is driven by the engine E. The water pump 52 is disposed in the
vicinity of the inlet opening of the water jacket 50 and increases
the pressure of the coolant that has returned via pipes 1, 4, 5
into the water jacket 50. The coolant moves through the circulating
circuit as a result of the pressure applied by the water pump
52.
[0020] The radiator 6 functions as a heat exchanger in order to
radiate heat from the coolant to the outside air. The thermostat
valve 7 detects the temperature of the coolant flowing from the
engine E via pipes 1 or 4 and connects either pipe 1 or pipe 4 to
the water pump 52 according to the detected temperature. If the
coolant temperature detected by the thermostat valve 7 is lower
than a pre-selected temperature (for example, 80.degree. C.), pipe
1 is connected to the water pump 52. Therefore, the coolant
circulating circuit is shortened and the waste heat from the engine
will increase the coolant temperature. On the other hand, if the
coolant temperature detected by the thermostat valve 7 is higher
than the pre-selected temperature, pipe 4 is connected to the water
pump 52. Therefore, coolant circulation via pipe 1 is stopped and
the coolant temperature decreases by passing through radiator 6.
Thus, the radiator 6, the thermostat 7, the pipe 4, and other
circuit elements and other pipes are utilized in order to
selectively cool the coolant.
[0021] The heater core 8 functions as a heat exchanger and warms up
the air inside the vehicle cabin by using the heat from the coolant
supplied through pipe 5. The electromagnetic valve 8a is an ON/OFF
valve (open/close valve) that controls the supply of coolant from
the engine E to the heater core 8 according to the cooling/warming
condition of the automobile air conditioning system. A
representative heating circuit may include the heater core 8, the
electromagnetic valve 8a, pipe 5, and other circuit elements and
other pipes.
[0022] The check valve 9 permits unidirectional flow of coolant
from the water jacket 50 to pipes 4 and 5, but does not permit the
coolant to flow in the opposite direction. If the flow of coolant
via pipe 1 is blocked by the thermostat valve 7 (i.e., the radiator
is operating), the check valve 9 is opened and maintains a constant
flow of coolant to pipe 4 and/or pipe 5.
[0023] As shown in FIG. 1, the turbine-type or regenerative pump
(fluid heating device) H includes a heating pump 10 disposed in
series with pipe 3 and a regulating valve 40, which may be a fluid
regulating means. The heating pump 10 and the regulating valve 40
cooperatively operate so that both pumping and heating functions
are provided at the same time (or selectively), while maintaining a
balance of both functions.
[0024] As shown in FIGS. 2 and 3, the heating pump 10 preferably
includes a rotor (impeller) 20 rotatably disposed within housing
11. The housing 11 defines a suction port 13 that is adapted to
draw the coolant into the housing 11 and a discharge port 14 that
is adapted to discharge coolant from the housing 11. A dividing
wall 15 separates the suction port 13 from the discharge port 14.
Preferably, the dividing wall 15 has a uniform, or substantially
uniform, width (W) with respect to the rotor 20. Further, the
dividing wall 15 preferably prevents the direct flow of coolant
between the suction port 13 and the discharge port 14. Instead, as
shown in FIG. 2, the coolant will move counterclockwise within the
substantially cylindrical chamber 25 from the suction port 13 to
the discharge port 14. The chamber 25 is connected to (communicates
with) the upstream of pipe 3 via the suction port 13 and is
connected to (communicates with) the downstream (or the regulating
valve 40) of pipe 3 via the discharge port 14. The rotor 20
preferably includes an integrally formed drive shaft 22 and both
are rotatably disposed inside the chamber 25. A pulley 16 is
fixedly mounted on the end of the drive shaft 22 outside the
housing 11. The pulley 16 is operationally linked to the crankshaft
(output shaft) of engine E via a V-belt (see FIG. 1) or other
energy transmitting means.
[0025] The rotor 20 preferably has a disk-like shape and includes a
plurality of blades (radially extending walls) 21 that are
equidistantly disposed on both side surfaces (peripheral surfaces)
of the rotor body 24. For example, fourteen (14) blades 21 may be
utilized. The blades 21 may be substantially rectangular-shaped
pieces having a length t in the radial direction and the blades 21
may radially extend from the rotational axis of the rotor body 24.
Concave channels 23 are formed between the blades 21, which
channels 23 are substantially semi-circular in cross-section. The
channels 23 also may be, for example, depressions or recesses. If
blades 21 are disposed on both sides of the rotor body 24, the
total number of blades 21 can be reduced.
[0026] When the drive shaft 22 and the rotor 20 of the heating pump
10 rotate due to the driving force of engine E, the coolant is
drawn through the suction port 13, flows inside the chamber 25 and
is discharged from the discharge port 14. Because the rotor 20
rotates, an eddy flow (secondary vortex) as shown by the arrows in
FIG. 3 is generated in the area formed by a channel 11a having a
semicircle cross section in the housing 11 that is opposite the
rotor 20 and channels 23 of the rotor 20. The coolant pressure
gradually increases by repeatedly joining or converging the eddy
flow generated within the channels 23 and the main flow inside the
chamber 25. The heating pump 10 thus provides a fluid transport
function that is similar to the water pump 52 and can be used as an
auxiliary pump to support the water pump 52.
[0027] When the dividing wall 15 is aligned with a channel 23
during operation of the heating pump 10, a space S is defined
between the inner surface of the dividing wall 15 and the surface
of the channel 23, as shown in FIG. 3. The moving blades 21 act on
the coolant to cause a complete revolution of the coolant. The
coolant is then diverted to the discharge port 14 by the dividing
wall 15. As a result of this action, the heating pump 10 increases
the coolant pressure. As a result of the space S, the coolant can
leak directly from the relatively high-pressure discharge port 14
to the relatively low-pressure suction port 13 via the space S when
the dividing wall 15 is aligned with a channel 23.
[0028] As noted above, the heating pump 10 also provides a fluid
heating function in addition to the fluid transport function. As
shown in FIG. 2, a small gap G is defined between the peripheral
edge of the rotor 20 and the inner surface of the chamber 25.
Pressurized fluid flows along this gap G from the suction port 13
to the discharge port 14. When the rotor 20 rotates, the energy of
the pump 10 acts on the coolant in the chamber 25 and the coolant
temperature increases due to the increased the internal energy of
the coolant. Therefore, the force applied to the drive shaft 22 and
the rotor 20 via the pulley 16 is converted into both pressurizing
work of the rotor 20 and the heat generated as a result of the
power loss.
[0029] The regulating valve 40 can restrict the flow of the coolant
from the discharge port 14. The regulating valve provides a braking
force that acts on the pressurized coolant supplied by the rotor 20
and thereby increases the coolant temperature. Therefore, the
heating pump 10 can heat the coolant.
[0030] Since the fluid transport function and the fluid heating
function are contrary to each other, the coolant can be heated to a
higher temperature if regulating valve 40 greatly restricts the
flow of coolant from the discharge port 14. However, in this case,
the amount of coolant that is discharged from the discharge port 14
is decreased. On the other hand, if the regulating valve 40 is
adjusted to permit a greater amount of coolant to discharge from
the discharge port 14, more coolant naturally can be discharged.
However, in this case, the coolant temperature increases less.
[0031] The present inventors have determined that the heat
generated by heating pump 10 is influenced by the nature of the
internal leak of the coolant from the discharge port 14 to the
suction port 13 via the space S between the dividing wall 15 and
channels 23 of the rotor 20. In particular, a correlation exists
between the ratio (W/L) of the width (W) of the dividing wall 15 to
the circular arc length (L) between the blades 21 in the
intermediate position 21a along the radial direction of the blades
21, as shown in FIG. 2. As shown in FIG. 4, the amount of heat (Q)
generated as the cooling fluid temperature is raised is influenced
by the ratio (W/L). In FIG. 4, "Qmax" represents the maximum amount
of heat generated by the pump 10. Thus, the ratio (Q/Qmax)
represents a ratio of the amount of heat generated at each
measurement point of W/L in relation to Qmax.
[0032] As shown in FIG. 4, when (W/L) is set within the range of
0.about.1, the amount of heat generated by the coolant reaches a
maximum (Qmax) at (W/L)=0.20. Thus, (Q/Qmax) is 1 when (W/L) is
0.20. When (W/L) is increased or decreased with respect to this
reference point, the value (Q/Qmax) decreases. However, when (W/L)
is set within the range of 0.07.about.0.36, (Q/Qmax) is greater
than or equal to 0.92. Furthermore, when (W/L) is set within the
range of 0.1.about.0.30, (Q/Qmax) is greater than or equal to
0.95.
[0033] To the contrary, the inventors have determined that the
ratio (W/L) of the pump disclosed in U.S. Pat. No. 3,720,372, which
is shown in FIG. 5 is about 0.41. Thus, the present teachings
provide heating pumps that are capable of more efficiently
generating heat.
[0034] Naturally, the above-described embodiments may be modified
in various ways without departing from the scope of the present
invention. For example, the ratio (W/L) according to the above
embodiment can be set to various values within the range of
0.07.about.0.36. Further, although the blades 21 have been
described as being disposed on both side surfaces of the rotor body
24, the blades 21 can also be disposed only on one side surface of
the rotor body 24. In addition, although a coolant comprising water
and ethylene glycol was utilized in the representative embodiment,
various other fluids that are capable of conducting heat can be
used instead of this coolant.
[0035] Preferably, each blade may be made of steel and may be
inserted to the rotor body. Each blade may preferably have a
thickness of 1.2 mm or less than 1.2 mm. Relatively thin blade can
increase the space defined by the mutually neighboring blades and
thus, contributing the effective heat generation, while the steel
blade can increase the strength of the blade.
[0036] With respect to the structure of the actuation chamber, a
fluid introducing passage may preferably connect the high-pressure
area (discharge area) to the low-pressure area (suction area).
Preferably, the fluid introducing passage may be formed within the
dividing wall. Further, a fluid release valve that opens and closes
the fluid introducing passage may be adapted in order to release
the high-pressure fluid to the low-pressure area. By releasing the
high-pressure fluid to the low-pressure area, excessive heat
generation can be alleviated. For example, a rotary valve, a ball
valve or a lead valve can be utilized for the release valve.
Further, a pilot valve for opening the release valve may be
installed. The pilot valve may open the release valve with
relatively small amount of the fluid and thus, the alleviation
control of the heat generation can quickly and precisely be
performed. Preferably, the pilot valve may include a spool that can
actuate the release valve.
[0037] Further, each groove of the pump housing may include a
plurality of shield blades at the inner circumferential side that
corresponds to the rotor body (inner circumferential side just
close to the drive shaft). The height of the shield blade measured
from the inner circumferential surface of the groove in the
direction of the outer circumferential surface of the groove may be
approximately 1/8 (one eighth) of the height of the actuation
chamber measured from the inner circumferential surface of the
groove to the outer circumferential surface of the groove. By such
structure, heat generating effect can be effectively
controlled.
[0038] The thickness of the dividing wall in the rotational
direction of the rotor can be selected from the various dimensions
in relation to the width of the space defined by the mutually
neighboring blades with respect to the rotational direction of the
rotor. On the other hand, in order to secure the heat generating
efficiency and to reduce the noise in operating the fluid heating
device, the thickness of the dividing wall in the rotational
direction of the rotor may preferably be equal to or wider than the
width of the space defined by the mutually neighboring blades with
respect to the rotational direction of the rotor. Further, the
dividing wall may have groove. Preferably, multiple grooves may be
provided on the surface of the dividing wall that faces the rotor
blade.
[0039] Further techniques for making and using fluid heating
devices are taught in a U.S. patent application Ser. No.
09/576,355, a U.S. patent application filed on even date herewith
entitled "Fluid Heating Devices" naming Takahiro Moroi, Masami Niwa
and Shigeru Suzuki as inventors and claiming Paris Convention
priority to Japanese patent application serial number 2000-216412
and a U.S. patent application filed on even date herewith entitled
"Fluid Heating Devices" naming Takahiro Moroi, Masami Niwa and
Shigeru Suzuki as inventors and claiming Paris Convention priority
to Japanese patent application serial number 2000-214602, all of
which are commonly assigned and are incorporated by reference as if
fully set forth herein
* * * * *