 |
Claims  |
|
|
I claim:
1. An apparatus for generating heat comprising:
(a) a compressor having an inlet and an outlet,
(b) a prime mover means operably coupled to drive the compressor,
(c) a conduit means connected to the compressor inlet and to the compressor
outlet,
(d) a heat exchange fluid charged in the apparatus at a pressure in the
range of 10 to 100 psig at 70.degree. F.,
(e) a heat exchanger means capable of transferring heat from the heat
exchange fluid to a second fluid for use outside the apparatus,
(f) a flow restricting means to restrict the volume of heat exchange fluid
reaching the compressor, and
(g) a fluid expansion means to cause the expansion of the heat exchange
fluid to be entirely in a gaseous state controlled such that no
significant heat transfer is made from ambient conditions
(h) wherein the conduit means interconnects elements (a), (c), (f) and (g)
in series to carry the heat exchange fluid from the compressor outlet
around the system through each element and back to the compressor inlet.
2. The apparatus of claim 1 wherein heat exchange fluid is maintained in a
gaseous state or flash liquid state throughout the circuit.
3. The apparatus of claim 1 wherein heat exchange means is a heat exchanger
provided with a first fluid path for the heat exchange fluid and a second
fluid path containing a second fluid, each path having an outlet and an
inlet for passage of the fluids therethrough in heat exchanging
relationship to each other.
4. The apparatus of claim 1 wherein flow restricting means is a capillary
tube of a size reducing the flow cross-section to no more than ten percent
of that of the conduit.
5. The apparatus of claim 1 wherein the flow restricting means is a
capillary tube which is no more than five percent of the cross-sectional
flow area of the conduit.
6. The apparatus of claim 1 wherein the fluid expansion means is a tank
controlled at or slightly higher temperature than ambient temperature.
7. The apparatus of claim 1 wherein an oil vapor drawing means is provided
in the fluid expansion means such that heat exchange fluid is drawn into
the conduit to the compressor inlet in close proximity to liquid oil as to
entrain oil in the vapor which enters the compressor.
8. The apparatus of claim 3 wherein a pulsator balance means is included in
the circuit in the heat exchanger in the fluid path for the heat exchange
fluid to create a pulsation flow of heat exchange fluid in a gaseous or
flash liquid state through system.
9. The apparatus of claim 1 wherein the flow restricting means is
constructed such that the major portion of the pressure drop of the heat
exchange fluid between the outlet and the inlet of the compressor occurs
passing through the flow restricting means.
10. The apparatus of claim 1 wherein the fluid expansion means is
constructed such that the major portion of the temperature drop of the the
heat exchange fluid between the outlet and inlet of the compressor is
during passage through the fluid expansion means.
11. The apparatus of claim 1 wherein the heat exchange fluid comprises at
least three chlorinated fluorinated substituted saturated hydrocarbon
having one to three carbon atoms with total halogen substitution in the
range of two to six.
12. The apparatus of claim 11 wherein the heat exchange fluid is charged in
the amount of 0.5 pound to 1.5 pounds per ton capacity of the compressor.
13. The apparatus of claim 1 wherein the heat exchange fluid is a miscible
selection of heat exchange fluids having condensation points in the range
of minus 160.degree. F. to 160.degree. F. at atmospheric pressure and
condensation points in the range of minus 40.degree. F. to 200.degree. F.
at 200 psig.
14. The apparatus of claim 1 wherein the heat exchange fluid is charged to
the apparatus at a pressure in the range of 25 to 80 psig at 70.degree. F.
15. The apparatus of claim 1 wherein the heat exchange fluid is charged in
the apparatus at a pressure in the range of 50 to 75 psig at 70.degree. F.
16. The apparatus of claim 1 wherein the pressure and temperature of the
heat exchange fluid is substantially increased during the passage through
the compressor and is decreased during passage through the fluid circuit
from the outlet to the inlet of the compressor.
17. An apparatus for generating heat comprising
(a) a compressor having an inlet and an outlet,
(b) a prime mover means operably coupled to the compressor,
(c) a heat exchange means capable of transferring heat from the heat
exchange fluid to a second fluid capable of transferring heat outside the
apparatus the heat exchange means having an inlet and an outlet for the
heat exchange fluid,
(d) conduit means connecting the outlet of the compressor to the inlet of
the heat exchange means,
(e) a flow restricting means having an inlet and an outlet to restrict the
volume of the heat exchange fluid reaching the compressor,
(f) conduit means connecting the heat exchange means outlet to the inlet of
the flow restricting means,
(g) a fluid expansion means having an inlet and an outlet, to cause the
heat exchange fluid to reach the gaseous state, being controlled that
there is not significant heat transfer from ambient conditions to the
fluid expansion means,
(h) conduit means connecting the outlet of the flow restricting means to
the fluid expansion means inlet and from the fluid expansion means outlet
to the compressor inlet, and
(i) a charge of heat exchange fluid in all of the above elements at a
pressure in the range of 10 to 100 psig at 70.degree. F.
18. An apparatus for generating heat comprising
(a) a compressor having an inlet and an outlet
(b) a prime mover means operably coupled to drive the compressor,
(c) a conduit means connected to the compressor inlet and to the compressor
outlet,
(d) a heat exchange fluid charged in the apparatus at a pressure in the
range of 10 to 100 psig at 70.degree. F.,
(e) a heat exchanger means capable of transferring heat from the heat
exchange fluid to a second fluid for use outside the apparatus,
(f) a flow restricting means to restrict the volume of heat exchange fluid
reaching the compressor, and
(g) a fluid expansion means to cause the expansion of the heat exchange
fluid to be entirely in a gaseous state controlled such that no
significant heat transfer is made from ambient conditions, and
(h) a pulsator balance means in the fluid path for the heat exchange fluid
to creat a pulsation flow of heat exchange fluid in a gaseous or flash
liquid state through the system,
(i) wherein the conduit means interconnects elements (f), (g) and (h) in
series to carry the heat exchange fluid from the compressor outlet around
the system through each element and back to the compressor inlet.
19. The apparatus of claim 18 wherein the pulsator balance means comprises
a primary pulsator accumulator comprising a container in the heat exchange
fluid circuit located inside the second fluid path in the cooler portion
of that path which causes the heat exchange fluid to be placed in a flash
liquid state and a secondary pulsator system, comprising a second
container in the heat exchange fluid circuit located inside the second
fluid path at the hottest portion of that path constructed such that the
flash liquid and/or gaseous heat exchange fluid fills only a portion of
the second container and causea a pulsation flow of the heat exchange
fluid out of the heat exchanger along the circuit.
20. An apparatus for generating heat comprising:
(a) a compressor having an inlet and an outlet
(b) a prime mover means operably coupled to drive the compressor,
(c) a conduit means connected to the compressor inlet and to the compressor
outlet,
(d) a heat exchange fluid charged in the apparatus at a pressure in the
range of 10 to 100 psig at 70.degree. F. and is maintained in a gaseous
state or flash liquid state throughout the apparatus,
(e) a heat exchanger means capable of transferring heat from the heat
exchange fluid to a second fluid for use outside the apparatus,
(f) a flow restricting means to restrict the volume of heat exchange fluid
reaching the compressor, and
(g) a fluid expansion means to cause the expansion of the heat exchange
fluid to be entirely in a gaseous state controlled such that no
significant heat transfer is made from ambient conditions,
(h) wherein the conduit means interconnects elements (a), (c), (f) and (g)
in series to carry the heat exchange fluid from the compressor outlet
around the system through each element and back to the compressor inlet. |
|
 |
|
 |
Claims |
|
|
|
Description |
|
|
BACKGROUND OF THE INVENTION
The apparatus of this invention falls into the general field of heat
generators and is most closely compared with the now common heat pump
system. There is an increasing need for heat generators which can convert
electricity to heat with increased efficiency.
The heat pump system utilizes three components, a compressor, an evaporator
and a condenser. A key element of the heat pump is the evaporator which
serves to absorb heat from a heat sump such as the outside air, well
water, a swimming pool or the ground. This heat is later transferred to
the area being warmed such as the interior of a house. The evaporator
must, of necessity, be located remote from the unit providing heat to the
interior of the house. The unit is sometimes installed in a window casing
or in a wall such that access to the external heat source and the area to
be warmed is provided. It is nearly impossible to make the heat pump
portable.
In addition, the efficiency of a heat pump decreases rapidly with the
temperature of the heat. For example, maximum efficiency is obtained when
the heat sump source is in the 40.degree. to 50.degree. F. range. The
efficiency may be about 2.5 but the efficiency drops rapidly as the sump
temperature is lowered until it reaches about 0.85 when the heat source is
at 0.degree. F. As a result, the heat pump is not practical in the winter
of many climates.
An object of this invention is to provide a heat generator which does not
draw heat from a heat sump.
Another object of this invention is to provide a heat generator which has
all of the advantages of the heat pump but avoids the inefficiency and
limitations of an evaporator external to the space being heated.
A particular object of this invention is to provide a heat generator which
is fully portable.
A further object of this invention is to provide a heat generator with its
operation and efficiency essentially independent of the outside
environment and of the ambient temperature where the heat generator is
located.
A specific object of this invention is to provide a heat generator with
increased efficiency utilizing only an energy source to operate a
compressor.
A specific object of this invention is to provide a heat generator which is
clean and does not affect the environment in any way whatsoever.
A specific object of this invention is to provide a heat generator which
may be easily controlled with a minimum of complexity since it is not
dependant upon or affected by the outside environment or the ambient
temperature.
Further objects will be apparent as the invention is further described in
detail.
DESCRIPTION OF PRIOR ART
The following patents all describe various heat pump devices: U.S. Pat. No.
2,241,070 to McLenegan; U.S. Pat. No. 2,483,896 to Gay; U.S. Pat. No.
2,619,326 to McLenegan; U.S. Pat. No. 2,723,083 to Bary; U.S. Pat. No.
3,992,876 to Wetherington, Jr., et al; U.S. Pat. No. 3,933,004 to Carter
et al; U.S. Pat. No. 3,984,050 to Gustafsson; U.S. Patent No. 3,989,183 to
Gustafsson; U.S. Pat. No. 4,012,920 to Kirschbaum; and U.S. Pat. No.
4,005,963 to Shoji, et al.
All of these patents utilize an evaporator/condenser and none satisfy the
above objects. None of the patents describe or suggest the present
invention.
SUMMARY OF THE INVENTION
The heating apparatus of this invention includes a compressor with an inlet
and an outlet driven by a prime mover such as electricity. Conduit
connecting all of the elements in series is attached to the inlet and
outlet of the compressor and forms a flow circuit to all of the components
of the apparatus to carry a heat exchange fluid from the compressor around
the circuit and back to the compressor. The heat exchange fluid is charged
to the apparatus at a pressure of 10 to 100 psig and is preferably
maintained in a gaseous or flash liquid state throughout the entire
circuit. The heat exchange fluid is confined within the conduit circuit. A
heat exchanger is provided to transfer heat from the heat exchange fluid
to a second fluid for use outside the apparatus. A flow restricting means
is interposed in the conduit circuit between the heat exchanger and an
expansion system to place the fluid in a gaseous state. The expansion
system is controlled so that there is no significant heat transfer from
the ambient to the expansion system.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a schematic diagram of the apparatus of this invention.
FIG. 2 is a partial cut-out perspective view showing the interior
construction of the heat exchanger.
FIG. 3 is a cross-sectional view along Lines 3--3 of FIG. 2 of the first
pulsator balance device.
FIG. 4 is a cross-sectional view along Lines 4--4 of FIG. 2 of the second
pulsator balance device.
FIG. 5 is a partial cut-out perspective of the expansion tank in the
apparatus of FIG. 1.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring to FIG. 1, compressor 10 is rated at 18,000 BTUs operated on full
load at 10.5 amps. This compressor is an open type belt driven direct
drive compressor and can receive heat exchange fluid at inlets 11 and 12
at 130.degree. F. or higher. The fluid leaving outlet 13 reaches in the
range of 250.degree. to 270.degree. F. and may reach as high as
500.degree. F. without damaging compressor 10. Compressor 10 is operating
at 8.5 amps on a 230 volt line and generates heat through heat exchanger
15 of about 33,000 BTUs per hour.
An alternative to compressor 10 is a hermetically sealed compressor with
internal windings commonly known as a refrigerant compressor used in air
conditioning. This type of compressor is typically rated at 5,000 BTUs per
hour and operates at full load at 7.5 amps. This type of compressor is
limited as to its temperature imput and is preferably operated with an
imput of heat exchange fluid in the temperature range of about 105.degree.
F. to a maximum of about 130.degree. F. Operated in the present apparatus,
it will compress the fluid to a temperature range of 200.degree. F. to
230.degree. F. at 225 psig operating at 5.1 amps from a 115 volt line.
The heat transfer fluid as it leaves outlet 13 is at about 250.degree. F.
and 225 psig traveling along 3/8 inch OD copper tubing 14, into heat
exchanger 15. The schematic of heat exchanger 15 is depicted in FIG. 1 and
the interior construction is shown in perspective view FIG. 2. Heat
exchanger 15 includes steel fifteen gallon tank 16 which contains water at
atmospheric pressure with opening 18 to the atmosphere. The heat exchange
fluid enters inlet 19 and passes through fifty feet of 3/8 OD copper
tubing 20 coiled to pass through in heat transfer mode with the water in
tank 16. Connected at the end of coiled tube 20 is first pulsator balancer
21. As shown in FIG. 3, balancer 21 is a twelve inch long cylinder 22 that
is 7/8 inch OD tubing with caps 23 and 24 welded on the ends of cylinder
22. Cap 24 has holes through which inlet tube 25 and outlet tube 26 pass
to a level about one inch inside surface of cap 24. The heat exchange
fluid travels along 3/8 inch copper tube 27 to secondary pulsator balancer
28, as more fully described in FIG. 4 which is again constructed of 7/8
inch copper OD tubing 29 with inlet tube 30 passing through and welded to
cap 31 and outlet tube 32 welded and passing through cap 33 close to the
bottom of tube 29 to 3/8 inch copper tube 34 which leads out of heat
exchanger 16 at outlet port 35. The heat exchange fluid travels along 3/8
inch copper tubing 40 to dryer and strainer 41 through sight glass 42
which is observed to be in the temperature range of 170.degree. to
200.degree. F. and essentially in a gaseous state and only partially in a
flash liquid state preferably being less than 20 percent flash liquid.
Connected to the sight glass is two feet of 1/4 inch copper tubing 43
connected to valve 44 from which reducing nipple 45 is used to weld to a
six inch length of 0.40 inch copper capillary tubing 46 which in turn is
welded to expansion nipple 47 connected to valve 48. Connected on the
other side of valve 48 is a two foot length of 1/4 inch copper tubing 49,
as a flow restrictor. The pressure in tube 49 is reduced to about 65 psig.
Tubing 49 is connected to expansion system 60 at inlet tube 50. Expansion
system 60 is pictured in perspective view in FIG. 4 and includes a five
gallon steel tank 61 with bottom 62. A small amount of oil will collect on
bottom 62 and be drawn into 1/2 inch OD copper outlet tubes 63 and 64
which are 1/2 inch OD copper. Tubes 63 and 64 reach almost to bottom 62
with bevel cuts 65 and 66 to prevent blockage should there by any
accumulation of liquid. Outlet tubes 63 and 64 are connected directly to
return tubes 67 and 68 which return the heat exchange fluid to inlets 11
and 12 of compressor 10. The heat exchange fluid in tank 61 is about
125.degree. F. and 65 psig as it is returned to compressor 10.
Heat is produced by the heat generator pictured in FIG. 1 by drawing the
water from outlet 71 of tank 17 at the rate of two gallons per minute at
about 180.degree. F. to produce 33,000 BTUs per hour for heating a
multi-room house returning the water along line 70 at approximately
120.degree. F.
The flow restrictor system design will depend upon the size of the
compressor and the temperature and pressure of the heat exchange fluid it
is capable of handling. When the 5,000 BTU compressor described above is
used in the apparatus, a 48 inch length of 0.040 copper capillary tubing
is effective to control the heat exchange fluid at about 30 psig and
105.degree. F. as it re-enters the small compressor. Since that compressor
is a hermetically sealed with internal winding type, the lower temperature
and pressure of the inlet fluid is necessary. The amount of the charge of
the heat exchange fluid is an element of this invention. For other heating
apparatuses such as the heat pump, it is common to charge about 10 pounds
of FREON refrigerant with a system utilizing a one ton compressor. In that
type of system it is necessary to charge the refrigerant under high
pressure. I have found that my heat generator operates more efficiently
with only a relatively small charge of heat exchange fluid. For example,
in the apparatus described in FIG. 1 through 5, a charge of a mixture of
FREON compounds at 65 psig or about 2 pounds by weight of FREON is very
effective. As a guide, it is preferred that the heat exchange fluid be
charged in an amount of about 0.5 pound to about 1.5 pounds per ton
capacity of the compressor. In my apparatus where the compressor is about
2 tons in capacity, 2 pounds of heat exchange fluid provides a good
balanced performance. It will be clear that the larger the compressor the
larger the overall system will generally be. As a consequence, it is
preferred that the heat exchange fluid be charged to a pressure of about
10 pounds to about 100 pounds psig. It is more preferred that the heat
exchange fluid be charged to a pressure range of 25 to 85 psig. It is most
preferred that the heat exchange fluid be charged to a pressure in the
range of 50 to 75 psig, all these pressure ranges being at 70.degree. F.
As the amount of the heat exchange fluid is reduced to the lower ends of
these ranges, the system will tend to slow down and stop as a result of
the heat exchange fluid collecting in one portion of the system and
failing to fill out the system and reach back to the compressor inlet. On
the other hand, as the amount of heat exchange fluid is increased to the
higher ends of these ranges, the inlet temperature of the compressor is
increased and the fluid concentration is increased such that the
compressor will ultimately heat up and burn out. In addition, as the
amount of heat exchange fluid charged is reduced and the efficiency of the
heating apparatus is also reduced. While an increase of the charge toward
the high end of the range and outside of the range tends to stall the
compressor.
The composition of the heat exchange fluid useful for this invention vary
widely, but are typically chosen from fluorinated and chlorinated
hydrocarbons commonly known in the field of FREON compounds, a registered
trademark of E.I. DuPont De Nemours & Co. (Inc.). Typically, the FREON
compounds have 1 to 3 carbon atoms with halogen substitutions in the range
of 2 to 6 atoms. The fluorine substitutions are one or more. Chlorine
substitutions are one or more except that it may be zero when there is
more than one fluorine substitution. Typical FREON compounds include
trichlorofluoromethane (F 11), dichlorodifluoromethane (F 12),
chlorotrifluoromethane, chlorodifluoromethane (F 22)
trichlorotrifluoroethane (F 113), dichlorotetrafluoroethane (F 114),
chloropentafluorothane, dichlorofluoromethane (F 21),
1-chloro-2,2,2,-trifluorothane (F 13), 2-chloroheptafluoropropane,
dichloromonofluoromethane; 1,2-dichloro-1,1,2trifluoroethane,
1,2-dilromo-1,1,2,2,-tetrafluoroethane; methyl fluoride,
monochlorofluoromethane, trifluoromethane, 1,1,1,2-tetrafluoroethane,
1,1,1,2,2,-pentafluoropropane, isomers, and the like. These compounds may
be used together in mixtures, including various azeotropic mixtures,
together on in combination with other heat exchange fluids including but
not limited to diethyl ether, dichloromethane, ethane, ethylane, propane,
nitrogen, air, ammonia, and the like. Azeotrope compositions of various
FREON compounds are effective in admixture with the above and include
FREON 500: dichlorodifluoromethane (F 112) and 1,1-difluoroethane; FREON
502: F 22 and F 115; FREON 503: F 13 and F 23; and azeotrope of F 22, F 13
and F 11, and the like. There are a large number of additional compounds
which provide a range of efficiency of the above compounds. While this is
not intended to limit the present invention, I have found that certain
mixtures of these compounds greatly increase the efficiency of the
apparatus. For example, a mixture of FREON compounds having condensation
points in the range of minus 160.degree. F. to 160.degree. F. at
atmospheric pressure and the compounds also having condensation points in
the range of minus 40.degree. F. to 200.degree. F. at 200 psig provide
excellent results. It will be clear that for compounds such as F 113 the
condensation point at 0 psig is about 118.degree. F. so that its
condensation point at 200 psig will essentially be off the scale. However,
by a selection of at least three FREON compounds spread across the range
described above, excellent results are obtained. The apparatus of Claim 1
gives good results with equal parts by weight of F 113, F 13, and F 22.
Substitutions and additions to the above compounds may be made into this
composition. An easy method of charging the heat exchange fluid to the
apparatus is to fill a drum with the proportion of the FREON compounds to
be used to a pressure of about 130 psig. The drum is connected by a hose
to expansion tank 61 and the pressure allowed to equalize to 65 psig, the
volume of the drum being chosen to be approximately equal to that of the
volume of the entire system of the apparatus.
It is preferred that the charge of the heat exchange fluid is such that
during normal operation there is less than 20 percent flash liquid at any
point in the circuit and it is more preferred that the amount of flash
liquid be in the range of one to ten percent. It is most preferred that
the heat exchange fluid be essentially all in the vaporized form which
will normally occur as long as the temperature is maintained about
120.degree. F.
Although not pictured, a circulating fan will generally be utilized in the
apparatus of FIG. 1 when the individual components are not fully insulated
from the ambient conditions. For example, when tank 61 is merely
maintained at a temperature above ambient, a circulating fan will carry
heat radiated from the exterior of tank 61 into the ambient air to further
heat the surroundings. It is preferred that all components be insulated
from ambient to eliminate the necessity of the fan.
The flow restricting system may take the form of a variety of individual
elements or a combination of elements to accomplish the same result. The
result to be accomplished is to restrict the amount of heat exchange fluid
passing through the system so as not to flood the compressor as the
temperature and pressure of the intake increase, and to cause it to flow
efficiently in the system. One system alone or in combination with other
elements of restricting the flow is to include a reduced charge of the
heat exchange fluid maintaining it at an undercharged amount as compared
to standard heat pumps, as described above. Another system alone, or in
combination with a limited charge is a flow restrictor placed in the
conduit after the heat exchanger and before there is a major drop in the
temperature and pressure of the fluid. An example of the flow restrictor
is a capillary tube of sufficient length and reduced cross-sectional area
to limit the flow returning to the compressor. The capillary tube is
preferably less than ten percent of the flow cross-sectional area of the
conduit and is more preferably less than five percent of the
cross-sectional area. It is most preferred that it is less than three
percent of the cross-sectional area of the conduit throughout the rest of
the apparatus. The larger the compressor, the larger and shorter the
capillary should be. For example, if the compressor size is doubled, a
general guide would be to double the capillary cross-sectional area or
decrease the length of the tube, according to instructions of the
manufacturer.
The condition of the expansion tank relative to ambient temperature is
important to the performance and control of the apparatus. In order to
control the apparatus and obtain the necessary efficiency, there shall be
no significant heat transfer from the ambient surrounding conditions to
the expansion system. It is preferred that the expansion system be
maintained at a temperature at or slightly higher than that of the ambient
condition. In that way, there cannot be a significant heat transfer from
the ambient to the expansion system. An alternative method of eliminating
heat transfer is to efficiently insulate the expansion system from the
ambient conditions.
It is preferred that the flow restrictor be in the form of a capillary tube
providing the major portion of the pressure drop along the heat exchange
circuit. For example, as the heat exchange fluid passes out of the
restrictor, it is possible for the fluid pressure to drop from about 200
psig to about 30 psig in the expansion system.
It is also preferred that the major temperature drop be in the fluid
expansion system. This is significant when it is realized that the purpose
of the apparatus is to heat a second heat exchange fluid so as to transfer
heat externally from the apparatus for other uses. For example, it is not
uncommon for the heat exchange fluid to drop from about 220.degree. to
about 180.degree. while passing through the heat exchanger, thus providing
that amount of corresponding heat outside the generator. On the other
hand, during the further flow inside the circuit, the temperature drop in
the fluid expansion system may be from about 180.degree. to about
110.degree. F. In the above example, the heat exchange fluid re-enters the
compressor at about 110.degree. F. and 30 psig.
To further compliment the flow restriction system of this invention, it is
preferred that a pulsating and balancing system be employed. This system
is at least one and preferably a series of expansion chambers in the
conduit inside the heat exchanger to maintain the gaseous or flash liquid
state of the fluid throughout the entire circuit.
The term "flash liquid" state as used throughout this specification refers
to a cloud of microscopic droplets as formed in a non-newtonian flow of
the gaseous mixture of the heat exchange fluid in my invention.
While this invention has been described with reference to the specific
embodiments disclosed herein, it is not confined to the details set forth
and the patent is intended to include modifications and changes which may
come within and extend from the following claims.
* * * * *
|
|
|
|
|
|
|
Description |
|
