U.S. patent number 3,785,163 [Application Number 05/179,854] was granted by the patent office on 1974-01-15 for refrigerant charging means and method.
Invention is credited to William Wagner.
United States Patent |
3,785,163 |
Wagner |
January 15, 1974 |
**Please see images for:
( Certificate of Correction ) ** |
REFRIGERANT CHARGING MEANS AND METHOD
Abstract
Means and method for introducing an optimum charge of
refrigerant into a refrigeration or air conditioning system. When
the system is charged to optimum capacity there is a melting of
frost, which indicates when the charging operation is to be
stopped. This is accomplished by converting a liquid refrigerant to
a saturated vapor and feeding the saturated vapor into the low side
of the refrigeration or air conditioning system.
Inventors: |
Wagner; William (Miami Beach,
FL) |
Family
ID: |
22658260 |
Appl.
No.: |
05/179,854 |
Filed: |
September 13, 1971 |
Current U.S.
Class: |
62/77; 62/149;
62/292; 62/511 |
Current CPC
Class: |
F17C
6/00 (20130101); F25B 45/00 (20130101); F17C
2227/04 (20130101); F17C 2227/0393 (20130101); F17C
2250/043 (20130101); F25B 2345/006 (20130101); F17C
2223/0153 (20130101); F25B 2345/001 (20130101); F17C
2205/0352 (20130101) |
Current International
Class: |
F17C
6/00 (20060101); F25B 45/00 (20060101); F25b
045/00 () |
Field of
Search: |
;62/77,149,292,160,511 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Perlin; Meyer
Attorney, Agent or Firm: Stoll and Stoll
Claims
I claim
1. A method of charging a refrigeration or air conditioning system
having a compressor, a condenser on the high pressure side of the
compressor, and an evaporator on the low pressure side of the
compressor, said method comprising the steps of:
a. providing a flow of liquid refrigerant by removing the
refrigerant in liquid phase and under pressure from a refrigerant
container,
b. converting all the removed liquid refrigerant to saturated vapor
refrigerant by passing it under pressure through a refrigerant
restrictor, and
c. directing the saturated vapor refrigerant under pressure into
the low pressure side of the refrigeration or air conditioning
system while said system is in operation,
d. thereby subjecting the saturated vapor refrigerant to the
suction of the compressor and distributing it throughout the
system.
2. The method of claim 1, wherein:
a. the saturated vapor is caused to flow into the suction line of
the system at a point of entry adjacent the low side of the
compressor,
b. whereby frost is caused to form on said suction line between the
point of entry and the compressor, and
c. stopping the flow of saturated vapor into the suction line when
the frost melts.
3. In combination with a refrigeration or air conditioning system
having a compressor, a condensor on the high pressure side of the
compressor, a refrigerant charging means comprising:
a. a flow source of liquid refrigerant under substantial pressure
and external to said refrigeration or air conditioning system, said
liquid refrigerant being normally gaseous at atmospheric pressure
and room temperature,
b. a refrigerant restricting means having an inlet end and an
outlet end,
c. connecting means between the flow source and the inlet end of
said refrigerant restricting means to provide a flow of liquid
refrigerant through said refrigerant restricting means under
pressure,
d. said refrigerant restricting means being adapted to convert all
the liquid refrigerant removed from the flow source to a saturated
vapor while passing through said refrigerant restricting means,
and
e. connecting means between the outlet end of the refrigerant
restricting means and the low pressure side of the refrigeration or
air conditioning system between the compressor and the evaporator
to provide a flow of saturated vapor refrigerant under pressure
into said system.
4. Refrigerant charging means in accordance with claim 4, wherein
the refrigerant restricting means comprises:
a. a hollow cylindrical body, and
b. a helically threaded screw mounted therein,
c. a helical channel being thereby provided between the screw and
the hollow cylindrical body to conduct the liquid refrigerant in a
helical path and restrict and meter its flow,
d. thereby converting the liquid refrigerant to a saturated
vapor.
5. Refrigerant charging means in accordance with claim 4, wherein
the refrigerant restricting means comprises:
a. a capillary tube which conducts the liquid refrigerant and
restricts and meters its flow,
b. thereby converting the liquid refrigerant to a saturated
vapor.
6. Refrigerant charging means in accordance with claim 4, wherein
the refrigerant restricting means comprises:
a. a hollow body having an inlet and an outlet end, and
b. a partition extending across the hollow body, internally
thereof,
c. an orifice being formed in said partition to provide
communication between said inlet and outlet ends of the hollow body
in order to conduct the liquid refrigerant therethrough and to
restrict and meter its flow,
d. thereby converting the liquid refrigerant to a saturated
vapor.
7. Refrigerant charging means in accordance with claim 4,
wherein:
a. a bypass and a check valve are provided in the refrigerant
restricting means,
b. said check valve being operative to close the bypass during a
charging operation and to open the bypass to permit a vacuum to be
drawn on the refrigeration or air conditioning system.
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention
Domestic and commercial refrigeration and air conditioning
systems.
2. Description of the Prior Art
One conventional procedure for charging or recharging a
refrigeration or air conditioning system is a two-phase or two-step
procedure involving both liquid and vapor refrigerant. In the first
phase, liquid refrigerant is introduced into the high (discharge)
side of the system. In this operation, the refrigerant container is
inverted to insure a liquid flow. When the pressure equlizes, the
refrigerant container is turned right side up. In the second phase
of the procedure, vaporized refrigerant is added to the low
(suction) side of the system until it is fully charged.
Referring to the practice of introducing liquid refrigerant into
the high side of the system, a standard textbook in the industry,
"Modern Refrigeration and Air Conditioning" by Althouse, Turnquist
and Bracciano (The Goodheart-Willcox Company, Inc., publisher,
copyright 1968, page 589) comments as follows:
"Although it is not usually recommended, some servicemen do put
liquid refrigerant into the high pressure side of the system. This
is a dangerous practice because dynamic hydraulic pressures are
possible which may rupture the lines, and cause considerable
damage. However, this system can be used to put the initial charge
into a system if done very carefully."
In the second phase of the procedure, as the liquid refrigerant
vaporizes in the refrigerant container and flows as a vapor into
the refrigeration of air conditioning system, the container
temperature lowers and freezing occurs. This reduces the pressure
in the container and results in a flow slow-down or stoppage. This
condition may be overcome by heating the refrigerant container.
However, unless great care is taken, excessive heat may be applied
(as with a torch) and the refrigerant container may be caused to
explode. Service manuals invariable contain strong warnings against
the application of excessive heat, e.g., "Never use a direct flame
or a heater to warm containers and never heat the containers to
more than 125.degree. F."
The second phase of the operation is slow and time consuming when
conducted in accordance with recommended technique, but servicemen
are frequently tempted to accelerate the operation by hazardous
methods. Thus, to increase the flow of vapor refrigerant into the
low side of the system, the upright refrigerant container is
sometimes rocked from side to side. Here too the service manuals
contain a cautionary note: "CAUTION - Never turn container into a
position where liquid refrigerant will flow into system."
In another conventional method of charging a refrigeration or air
conditioning system, the introduction of refrigerant is limited to
the low side of the system. The refrigerant container is held in
right-side-up position and the refrigerant is allowed to vaporize
and to flow only as a vapor into the system. As is the case with
the second phase of the first mentioned procedure, this is a slow
process. To discourage servicemen from adopting hazardous
alternatives to the prescribed technique, and to prevent damage to
the compressor and a dangerous rise in oil level, the service
manuals warn against improper use of the refrigerant container,
thus: "CAUTION - Container must not be inverted and care must be
taken that liquid refrigerant does not enter the [low side of the]
system. This would cause damage to reed valves in compressor." The
above-mentioned textbook, "Modern Refrigeration and Air
Conditioning", page 589, contains a more explicit warning: "IT IS
VERY IMPORTANT THAT LIQUID REFRIGERANT NOT BE ALLOWED TO REACH THE
COMPRESSOR. The liquid is not compressible and the compressor
valves, and even the bearings and rods, may be ruined if the
compressor should pump liquid."
SUMMARY OF THE INVENTION
The present invention provides a refrigerant charging means and
method for charging a saturated vapor refrigerant into the low
pressure side of a refrigeration or air conditioning system.
Basically, liquid refrigerant is conducted through a restrictor
device to convert it to a saturated vapor and the saturated vapor
is then fed into the low side of the system while the compressor is
operating. Since the refrigerant enters the compressor as a
saturated vapor (as distinguished from a liquid) it does not damage
the compressor. Since the refrigerant leaves the refrigerant
container as a liquid (as distinguished from a vapor or gas)
frosting and drop in container pressure are avoided. There is no
need, therefore, of heating the refrigerant container and no danger
that the container will explode.
The refrigerant charging procedure which is herein described and
claimed is a relatively fast procedure, since it is based on the
principle of handling the refrigerant as a liquid and as a
saturated vapor (as distinguished from an unsaturated vapor or gas)
and conducting it under pressure from the refrigerant container to
the refrigeration or air conditioning system. More specifically,
the claimed procedure entails the following steps: (a) removing the
refrigerant from the refrigerant container in its liquid phase and
under pressure, (b) converting it under pressure into a saturated
vapor, and (c) feeding the saturated vapor, still under pressure,
into the low side of the refrigeration or air conditioning system.
Tests conducted on fifteen refrigeration and air conditioning units
ranging in size from 1/12 HP to 5 HP showed a 50 to 80 percent
reduction in charging time over the conventional methods above
described.
An optimum charge is visibly indicated by the appearance and
disappearance of frost on the suction line of the refrigeration or
air conditioning system. Determination of the optimum charge for
each individual system is important, since the characteristics of
the same model compressor (and system as a whole) will vary from
one unit to another. This is true of new equipment direct from the
production lines. Clearances of the operating parts of the
compressors usually vary sufficiently, within tolerance ranges, to
vary their operating and efficiency (flow and thermal)
characteristics. This is equally true of other components of
refrigeration and air conditioning systems, e.g., capillary tube
restrictors and expansion valves. Moreover, the characteristics of
refrigeration and air conditioning systems which have been in
operation for extended periods of time will further vary, both by
reason of their use and by reason of occasional abuse. Thus, the
pumping capability of a compressor will change over a period of a
few years due to loss of compression because of wear or a decrease
in torque of the motor which drives the compressor. For example, a
compressor which is rated 2 H.P. and operates for a period of two
or three years suffers sufficient wear and deterioration of its
working parts to reduce its efficiency to a rating of only 11/2 -
13/4 H.P. As a result, the initial theoretical recommended
refrigerant charge for any specific unit can be as much as 10
percent higher than it actually requires for balanced
operation.
It is evident that the reduced efficiency of a compressor, by
reason of prolonged use or other causal or contributory factors,
will result in a refrigerant charge which is greater than the
capacity of the compressor, and hence a wet and relatively
ineffective evaporator, producing the effect of an overcharged
system. To correct this condition, the excess refrigerant should be
purged (or restriction added to the restrictor device), but however
this condition is corrected the unit no longer has its original
B.T.U. rating.
When a refrigeration or air conditioning system requires
recharging, the service engineer will charge the system in
accordance with the manufacturer's specifications. Frequently it is
discovered that the system appears overcharged, and excessive
refrigerant is therefore purged until the proper frost or balance
occurs. If weighed, the excess refrigerant may prove to be as much
as 10 percent of the original charge. This will also account for
the fact that sight glasses may show an undercharge when the system
is fully charged to the manufacturer's specification.
Using the visual indication means provided by the charging
procedure herein claimed, both partially charged and completely
evacuated systems can be charged properly for good operating
performance without otherwise measuring (weighing) the amount of
refrigerant which is added to the system.
The operation of the present invention may be briefly stated as
follows: Liquid refrigerant - for example, Refrigerant 12 - is
caused to flow through a restrictor device which converts the
liquid refrigerant to a saturated vapor and meters such saturated
vapor into the refrigeration or air conditioning system adjacent
the low pressure or suction side of the compressor. As the quantity
of refrigerant increases in the system, the flow of saturated vapor
refrigerant into the system will decrease. The restrictor device is
designed with greater resistance to flow than is encountered in the
return suction line from the evaporator, thereby causing this
decrease in the flow of saturated vapor refrigerant into the
system.
During the process of conducting saturated vapor refrigerant into
the system, expansion of the saturated vapor will occur and cause
frosting of the suction line between the low side of the compressor
and the point of energy of the saturated vapor refrigerant. Some
frost will also be in evidence on the restrictor device itself and
on the line or hose connection between the restrictor device and
the suction line of the system, depending upon ambient
conditions.
Initially, the quantity of saturated vapor refrigerant at the point
of entry into the refrigeration or air conditioning system and its
expansion within the system produce a greater thermal effect than
the refrigerant gas which returns from the evaporator through the
suction line. A properly designed system with proper charge for
efficient and safe operation provides for the suction line gas
coming from the evaporator to be approximately 15.degree. above the
saturated vapor temperature. The metering operation of the
restrictor device will result in a sufficiently low saturated vapor
temperature (relative to the temperature of the suction line gas
returning from the evaporator) to maintain the frost on the suction
line between the point of entry of the saturated vapor and the low
side of the compressor until the suction line gas reaches volume
adequate to satisfy the displacement of the compressor. When this
condition is attained, that is, when sufficient suction line gas
returns from the evaporator to satisfy the requirements of the
compressor, the introduction of saturated vapor refrigerant into
the system will be reduced by the restrictor device to a very small
quantity. At this phase of the charging procedure, the suction gas
returning from the evaporator becomes the dominant thermal factor
at the low side of the compressor, and this causes the frost to
melt on the section of suction line which lies between said low
side of the compressor and the point of entry of the saturated
vapor refrigerant. Concurrently with the defrosting of the suction
line, the flow of saturated vapor refrigerant into the system is
stopped manually, and the system will then have a full and optimum
charge of refrigerant for efficient and safe operation.
The invention is not limited to any particular types of restrictor
devices. Any conventional restrictor device or any device which is
capable of functioning as a restrictor to convert liquid
refrigerant to a saturated vapor may be used for the purposes of
this invention. Examples of restrictor devices which are suitable
for the invention are the screw, capillary and orifice types which
are illustrated in the drawing. Other devices capable of
restricting the flow of liquid refrigerant, such as a needle-type
valve, may also be used in connection with the present invention.
The sole test is whether the device is capable of restricting and
metering the flow of a liquid refrigerant and converting it to a
saturated vapor. For the purposes of the claims, a device capable
of performing these functions is designated "refrigerant
restrictor".
An important feature of the invention resides in the provision and
use of a check valve in or in connection with the restrictor
device. The purpose of the check valve is to by-pass the restrictor
device when a vacuum is drawn on the refrigeration or air
conditioning system prior to charging.
BRIEF DESCRIPTION OF THE DRAWING
FIG. 1 is a schematic view showing a conventional refrigeration or
air conditioning system and a charging mechanism connected thereto,
including the charging means which is herein described and
claimed.
FIG. 2 is a view of a screw-type restrictor device which may be
used in the charging means herein claimed.
FIG. 3 is an inside view of said restrictor device, its outer shell
being shown in longitudinal section.
FIG. 4 is a longitudinal section through the entire restrictor
device.
FIG. 5 is a transverse section on the line 5--5 of FIG. 4.
FIG. 6 is a transverse section on the line 6--6 of FIG. 4.
FIG. 7 is a transverse section on the line 7--7 of FIG. 4.
FIG. 8 is a longitudinal section through a capillary tube type
restrictor device which may be used in the charging means herein
claimed.
FIG. 9 is a transverse section therethrough on the line 9--9 of
FIG. 8.
FIG. 10 is a transverse section on the line 10--10 of FIG. 8.
FIG. 11 is a longitudinal section through an orifice-type
restrictor device which may be used in the charging means herein
claimed.
FIG. 12 is a transverse section on the line 12--12 of FIG. 11.
FIG. 13 is a transverse section on the line 13--13 of FIG. 11.
DESCRIPTION OF PREFERRED EMBODIMENTS OF THE INVENTION
Referring now to the details of the invention as illustrated in
FIG. 1, it will be seen that a container 10 containing a
refrigerant in a liquid state is connected to a restrictor device
12 through a conventional charging mechanism 14 and said charging
mechanism is connected through said restrictor device to the low
pressure side of a refrigeration or air conditioning system 16.
More particularly, container 10 is connected to a manually
controlled valve mechanism 18 which controls the flow of
refrigerant from the container to the charging mechanism 14 through
a charging line 20. This charging line is connected to a manifold
22 having two ports, 24 and 26 respectively, and two manually
controlled valves 28 and 30, respectively, which control the flow
through said ports. A line 32 connects port 24 to a valve 34
adjacent the high pressure side of compressor 36. Restrictor device
12 is connected to port 26 of the charging mechanism and a line 38
connects said restrictor device to a valve 40 adjacent the low
pressure side of said compressor. Also connected to manifold 22 is
a pair of pressure gauges 42 and 44, respectively, which measure
the pressures on the high and low sides of the system when valve 18
is closed.
Refrigeration or air conditioning system 16 comprises compressor
36, condenser 46 and evaporator 50, and all of the other
conventional components of a refrigeration or air conditioning
system, including a discharge line 52 between the high side of the
compressor and condenser 46, a liquid line 56 between said
condenser 46 and evaporator 50, a filter drier 48 and a capillary
tube restrictor device 58 in said liquid line, and a suction line
60 between the evaporator and the low side of the compressor. It
will be noted that valve 34 is connected to discharge line 52 and
valve 40 is connected to suction line 60. These valves may be of
the line-tap variety.
Charging mechanism 14 may be conventional and may be used in
conventional manner. With particular reference to the operation of
the present invention, this mechanism may be used to charge or
recharge, or replenish the charge of, a conventional refrigeration
or air conditioning system such as system 16 shown in the drawing.
In this operation valve 28 is closed, and valve 30 is opened as
indicated in FIG. 1. A flow of refrigerant from container 10 and
through valve 18 and charging line 20 would therefore enter
manifold 22 and pass through valve 30, port 26, restrictor device
12, line 38 and valve 40 into the low side (suction line 60) of the
system. To do this, in accordance with the principles of this
invention, refrigerant container 10 is inverted, as shown in FIG.
1, and valve 18 is opened. A flow of liquid refrigerant under
pressure is thereby assured, and the liquid refrigerant will flow
through the charging mechanism and into restrictor device 12, where
it will be converted into a saturated vapor. The saturated vapor
will then pass through line 38 and valve 40, into the low side of
the system (suction line 60).
As the saturated vapor enters the low side of the system, its
expansion causes frosting of the suction line between valve 40 and
the compressor. The flow will continue freely until the charge
builds up in the system and back pressure is applied to the
restrictor device through line 38. This back pressure increases in
direct proportion to the increased charge in the suction line and
as the back pressure continues to increase it ends to restrict and
decrease the flow from the restrictor device. When the pressure in
the suction line is stabilized in the system, the flow of
refrigerant into the system should be manually shut off. When the
flow of refrigerant from restrictor device 12 and line 38 into
suction line 60 diminishes relative to the flow from evaporator 50
to the compressor through said suction line, a point is reached
when the frost on the suction line between valve 40 and the
compressor begins to melt. Melting continues until the refrigerant
flow in the refrigeration system is stabilized, and at that point
the frost completely disappears, thereby visually signaling
completion of the charging operation and the existence of an
optimum charge in the system.
Restrictor device 12 shown in FIG. 1 of the drawing exemplifies the
three restrictor devices which are specifically illustrated in
FIGS. 2-13 of the drawing and also all other flow restrictor
devices (e.g., needle valve restrictor devices) which may be used
in the performance of this invention.
Referring now to screw-type restrictor device 70 shown in FIGS. 2-7
of the drawing, it will be observed that it comprises a generally
cylindrical shell 72 having a helically threaded element 74
disposed therein, an inlet fitting 76 at one end of the shell, an
outlet fitting 78 at the opposite end of the shell, and a check
valve 80 between the inlet fitting 76 and the threaded element
74.
As the drawing clearly shows, threaded element 74 comprises a
hollow cylinder, open at both ends, and helically threaded on its
outer surface. Threaded element 74 snugly fits within cylinder
shell 72 and its helical thread engages the inner wall of said
shell to form a helical channel 82 between said threaded element 74
and said shell 72. It will now be evident that communication
between inlet fitting 76 and outlet fitting 78 may take place
either through helical channel 82 or bore hole 84 which extends
axially through threaded element 74.
The function of check valve 80 is to close off bore hole 84 when it
is desired to limit communication between said inlet and outlet
fittings to said helical channel 82 and any conventional check
valve capable of performing this function may be used. However, in
the preferred form of the invention, check valve 80 is a magnetic
valve which consists of a magnetically responsive disc 86 serving
as the valve member proper, an annular seat 88 therefor formed at
the inlet end of threaded element 74 and a magnet 90 situated in or
adjacent said seat 88 to attract disc 86 and to hold it in closed
position against said seat. This prevents a flow through bore hole
84 from inlet fitting 76 to outlet fitting 78.
On the opposite side of disc 86 from magnet 90 is a disc retainer
92. This retainer may assume various forms, for example the form of
a ring 94 with stud elements 96 projecting therefrom in the
direction of disc 86. Shell 72 is crimped or rolled to form annular
external grooves 98 and 100, respectively, on opposite sides of
ring 94. Internally, these annular grooves form annular beads which
engage the opposite sides of ring 94 and hold it securely in place
within shell 72. Back pressure upon disc 86 will dislodge the disc
from magnet 90 and seat 88 and cause it to engage stud elements 96.
This will open threaded element 74 for an internal flow through
bore hole 84. This condition will (before charging) when a vacuum
is drawn on the refrigeration or air conditioning system 16.
Inlet fitting 76 is, of course, firmly secured to the inlet end 72a
of shell 72. Said inlet fitting has a bore hole 76a formed
therethrough, and at its inlet end, said bore hole is enlarged and
provided with screw threads 76b. Basket screen 102 is provided at
the outlet end of said fitting, extending across bore hole 76a. By
the same token, outlet fitting 78 is firmly secured to the outlet
end 72b of shell 72. A bore hole 78a is formed through fitting 78,
and a basket screen 104 is secured to said fitting at its inlet end
across said bore hole. It will be understood that inlet fitting 76
may be coupled to a complementary fitting secured to manifold 22 at
port 26, and outlet fitting may be joined to line 38 in
conventional manner.
In the operation of the restrictor device last above described,
refrigerant container 10 is inverted as shown in FIG. 1 to insure a
flow of liquid refrigerant (as distinguished from a vapor or a gas)
therefrom. The container is, of course, pressurized, since the
refrigerant is contained therein in liquid form, and its normal or
natural state at room temperature is that of a gas. A pound of
liquid Refrigerant 12 expands to 3.8 cubic feet of vapor at room
temperature, i.e., 68.degree. Fahrenheit. When valve 18 is opened,
the liquid refrigerant will flow under pressure from said container
10, through said valve, charging line 10, manifold 22, port 26 and
restrictor device 70. Since the pressure would now be on the
opposite side of valve disc 86 from magnet 90, said valve disc will
be held against the valve seat 88 both by magnetic attraction and
hydraulic pressure. This will close off bore hole 84 through the
threaded element 74 and communication between the inlet and outlet
ends of the restrictor device will be confined to helical channel
82. Since the liquid refrigerant will now be caused to flow through
said helical channel, its flow will be restricted and metered to
the extent dictated by the cross-sectional dimensions of said
helical channel and its length, and sufficient to convert the
liquid refrigerant to a saturated vapor.
As an illustration, threaded element 74 may be 1.055 inches in
over-all (thread crest) diameter, 1.875 inches long, with twelve
threads or convolutions per inch, the helical channel defined by
the thread describing a 60.degree. triangle in cross-section, with
a depth of 0.037 inch. These figures are, of course, purely
illustrative, and intended only to exemplify the dimensional
characteristics of a conventional restrictor device capable of
converting a liquid refrigerant such as Refrigerant 12 into a
saturated vapor. As the refrigerant flow through helical channel 82
under the pressure exerted by inverted pressurized container 10, it
will be transformed into a saturated vapor and will leave the
restrictor device through the outlet fitting 78 in that form.
After the saturated vapor refrigerant leaves restrictor 70, it will
flow through line 38 and valve 40 into the low side (suction line
60) of the refrigeration or air conditioning system 16.
Turning now to the second illustrative form of restrictor device
which may be used in practicing the present invention, restrictor
device 110, shown in FIGS. 8-10 of the drawing, is of the capillary
type, comprising a generally cylindrical shell 112, a helically
coiled capillary tube 114 encased within the shell, an inlet
fitting 116 at the inlet end of the shell, an outlet fitting 118
which may be integral with the outlet end of the shell, and a
magnetic check valve 120 mounted within the shell between the inlet
fitting 116 and the inlet end 122 of the capillary tube. Once
again, the use of a magnetic valve is purely illustrative and other
conventional check valves may be used in its place and stead.
It will be noted that the inlet end 122 of the capillary tube is
supported by an annular element 124 which is positioned between an
annular shoulder 126 in shell 112 and inlet fitting 116. Valve seat
128 of check valve 120 is formed on annular element 124 and magnet
130 of said check valve is supported by said annular element. A
basket screen 132 is mounted on inlet fitting 116, and valve disc
134 is disposed between said basket screen 136 is mounted between
the outlet end 138 of the capillary tube and the outlet fitting
118.
The operation of restrictor device 110 may be understood from the
foregoing description of the operation of restrictor device 70. The
liquid refrigerant passes under pressure from container 10, through
valve 18, into and through charging line 20, manifold 22, port 26
and inlet fitting 116 of restrictor device 110. It then passes
through basket screen 132 and capillary tube 114 and thence through
basket screen 136 and outlet fitting 118. As the liquid refrigerant
passes through the capillary tube it is converted into a saturated
vapor and it leaves the restrictor device in that form. It is also
in that form that the refrigerant is introduced through lines 38
and 60 into the low side of the refrigeration or air conditioning
system shown in FIG. 1.
The following specifications relating to capillary tube 114
illustrate a capillary tube restrictor device capable of
functioning to convert Refrigerant 12 from liquid to saturated
vapor form: Capillary tube 114 has an O.D. of 0.083 inch, and an
I.D. of 0.031 inch. It is 36 inches long and wound into 11 coils
having an O.D. of 1.050 inches.
The third illustrated form of restrictor device which may be used
in connection with the present invention is shown in FIGS. 11, 12
and 13. Restrictor device 140 is of the orifice type. It comprises
a generally cylindrical shell 143, a magnetic check valve 144
mounted therein, an inlet fitting 146 at the inlet end of said
shell, and an outlet fitting 148 at the outlet end of said shell. A
check valve, for example magnetic check valve 144, performs the
dual functions of a flow restrictor and back pressure relief
valve.
More particularly, magnetic check valve 144 includes an annular
member 150 which is secured by means of crimped formations 152 and
154 to the inner wall of shell 142. A valve seat 156 is formed on
one side of annular member 150, and a magnet 158 is secured to said
annular member within said valve seat. Valve disc 160 is disposed
between valve seat 156 and a disc retainer 162 which is held in
place in shell 142 by means of crimped formations 164 and 166
formed therein. It will of course be understood that valve disc 160
and disc retainer 162 are situated on the inlet side of annular
member 150, that is, between said annular member and inlet fitting
146. It will be noted that mounted on the outlet side of said
annular member 150, that is between said annular member and outlet
fitting 148, is a basket screen 170.
It will now be observed that valve disc 160 has a pinhole opening
172 formed therein. It is this opening which functions to restrict
the flow of liquid refrigerant sufficiently to convert the
refrigerant to a saturated vapor. Once again, the flow of
refrigerant follows the circuit indicated in FIG. 1 and described
in connection with the screw-type restrictor device 70 and the
capillary tube type restrictor device 110.
The foregoing is descriptive of preferred forms of the invention,
and they are not to be construed as limiting the invention. Any
form of flow restrictor device may be used, whether built into, or
separate from, the refrigeration or air conditioning system,
provided that a flow of saturated vapor refrigerant is directed
into the low side of the system.
For the purposes of the claims, the term "liquid refrigerant" is
intended to mean any conventional refrigerant which is in a gaseous
state at ordinary room temperature and under atmospheric pressure.
Such refrigerants are pressurized to reduce them to a liquid phase,
and they are under pressure when maintained in such phase.
Illustrative of such refrigerants are the various refrigerants made
and sold by E. I. duPont de Nemours under the trademark FREON.
Examples are the refrigerants which are designated R-11
(trichloromonofluoromethane) and R-12 (dichlorodifluoromethane).
R-12 has a boiling point of -21.7.degree. Fahrenheit at atmospheric
pressure. For the purpose of the claims the expression "substantial
pressure" is intended to indicate the flow pressure of liquid
refrigerant from an inverted container.
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