U.S. patent number 3,659,433 [Application Number 05/000,088] was granted by the patent office on 1972-05-02 for refrigeration system including a flow metering device.
This patent grant is currently assigned to Carrier Corporation. Invention is credited to David N. Shaw.
United States Patent |
3,659,433 |
Shaw |
May 2, 1972 |
REFRIGERATION SYSTEM INCLUDING A FLOW METERING DEVICE
Abstract
A refrigerant flow metering device for use in a refrigeration
system comprising a housing having an inlet and an outlet and
defining a bore disposed within its confines, the ends of which
communicate with the inlet and outlet, said bore being of a
variable cross section to form a variable passage. A valve element
positioned within the bore is capable of movement therein in
response to changes in pressure in the refrigeration system. A
spring associated with the valve element provides a force to move
the element toward the inlet of said housing.
Inventors: |
Shaw; David N. (Liverpool,
NY) |
Assignee: |
Carrier Corporation (Syracuse,
NY)
|
Family
ID: |
21689863 |
Appl.
No.: |
05/000,088 |
Filed: |
January 2, 1970 |
Current U.S.
Class: |
62/511; 137/504;
137/509; 137/517; 138/43; 138/45 |
Current CPC
Class: |
F25B
41/30 (20210101); Y10T 137/7869 (20150401); Y10T
137/7792 (20150401); Y10T 137/7835 (20150401) |
Current International
Class: |
F25B
41/06 (20060101); F25b 041/06 () |
Field of
Search: |
;62/196,222,223,511
;137/509 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Perlin; Meyer
Claims
I claim:
1. A refrigeration system including a compressor, a condenser, an
evaporator, and a flow metering device disposed between said
condenser and said evaporator, connected together to form said
system, said compressor and said flow metering device defining
therebetween a high pressure side and a low pressure side of said
system, said flow metering device comprising:
A. a valve housing having an inlet and an outlet and defining a
bore disposed within its confines, said bore providing a flow path
for refrigerant passing from said condenser to said evaporator
through said flow metering device; and
B. means operable to decrease the cross section of said bore as the
pressure differential between said condenser and said evaporator
increases, and being further operable to increase the cross section
of said bore as the pressure differential between said condenser
and said evaporator decreases.
2. A refrigeration system in accordance with claim 1 wherein said
last-mentioned means includes a valve element and a biasing member
associated therewith, said biasing member providing a force acting
on said valve element in opposition to a force provided by the
refrigerant flowing through said metering device.
Description
BACKGROUND OF THE INVENTION
This invention relates to a refrigeration system and more
particularly, to a refrigeration system including a refrigerant
flow metering device for regulating the flow of refrigerant from
the condenser to the evaporator.
The need for a device to meter the flow of refrigerant in
refrigeration systems is well known to those skilled in the art.
Most refrigeration systems employ either a thermostatic expansion
valve or a capillary tube as the required metering device. However,
each of the above-mentioned apparatus possesses disadvantages which
limit their utility.
Thermostatic expansion valves, while being highly efficient in
their operation and readily responsive to changes in load upon the
system to vary the flow of refrigerant to the evaporator, are also
relatively expensive. Therefore, they are generally not employed in
small applications such as room air conditioners.
Capillary tubes are generally employed in lieu of the thermostatic
expansion valves for such small applications, wherein ambient air
is almost universally utilized as the condensing medium. Although
capillary tubes are relatively inexpensive to manufacture and are
simple to install, when used in applications wherein ambient air is
employed as the condensing medium, certain problems generally
occur.
For example, at relatively high ambient temperatures, the pressure
differential between the condenser and evaporator is of a
relatively large magnitude, thus producing a substantial flow of
refrigerant through the capillary tube disposed between the
condenser and evaporator. At times, the refrigerant flow might
become excessive and a portion of the refrigerant flowing to the
evaporator will not be evaporated therein and will remain in its
liquid state as it passes to the compressor. The introduction of
liquid refrigerant into the compressor may produce serious
problems, such as breakage of valves, in addition to a decrease in
the efficiency of operation of the compressor.
An additional problem is found at relatively low ambient
temperatures wherein the pressure differential between the
condenser and the evaporator is of a relatively small magnitude,
whereby the flow of refrigerant through the capillary tube is
decreased. If the flow of refrigerant at low ambient temperatures
is insufficient, the compressor will reduce the pressure in the
evaporator coil below its designed operating point, and the
evaporator coil will begin to freeze, thereby reducing the transfer
of heat between the medium to be cooled, such as room air, and the
refrigerant flowing through the evaporator, thus reducing the
efficiency of the system operation.
The object of this invention is a refrigerant flow metering device
that will obviate the problems hereinbefore discussed.
SUMMARY OF THE INVENTION
This invention relates to a refrigeration system and, in
particular, to a novel refrigerant flow metering device which is
relatively inexpensive to manufacture and possesses none of the
disadvantages of the capillary tube hereinbefore noted. The novel
device operates to prevent excessive flow of refrigerant at
relatively high ambient temperatures and additionally operates to
prevent freezing of the evaporator coil at relatively low ambient
temperatures. In addition, the novel device herein disclosed
operates to permit rapid equalization of the pressure differential
between the condenser and evaporator when operation of the system
is discontinued. Rapid equalization permits utilization of a
low-starting torque motor to drive the compressor, thus eliminating
the need for expensive high-starting torque motors, or in the
alternative, eliminating the need for such devices as time delays
to prevent restarting of the compressor motor before a sufficient
period of time has elapsed, to enable the pressure in the
refrigeration system to equalize of its own accord.
The device includes a housing having an inlet and an outlet and
defining a bore disposed within its confines, the ends of which
communicate with the inlet and outlet. The bore is of a variable
cross section and thereby forms a variable restriction or passage.
The narrower portion of the variable cross section passage is
formed relatively close to the outlet of the housing, and the wider
portion of the variable cross section passage is formed relatively
close to the inlet of the housing. A valve element is positioned
within the bore and is capable of movement therein in response to
changes in pressure in the refrigeration system. A spring
associated with the valve element provides a force to move the
valve element toward the inlet of the housing. The valve element
moves toward the outlet of the housing upon an increase in the
pressure differential of the system and moves toward the inlet of
the housing upon a decrease in the pressure differential of the
system.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a schematic representation of a refrigeration system
including the novel refrigerant flow metering device; and
FIG. 2 is a cross-sectional view of the novel device.
DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring now to the drawings, and in particular to FIG. 1, there
is shown a refrigeration system including the novel refrigerant
flow metering device herein disclosed. In referring to the
drawings, like numerals shall refer to like parts.
The refrigeration system of FIG. 1 includes a compressor 10
connected to condenser 11 by conduit 12. Condenser 11 is connected
to evaporator 22 by conduits 13 and 13'. Refrigerant metering
device 14 is disposed between conduits 13 and 13' and operates to
regulate the flow of refrigerant from the condenser to the
evaporator. Conduit 15 connects the evaporator to the suction side
of the compressor.
Relatively high pressure refrigerant gas is discharged from the
compressor via conduit 12 and flows to condenser 11 where it passes
in heat transfer relation with a relatively cool medium such as
ambient air, passed thereover by means not shown, the refrigerant
gas rejecting heat to the cool medium and being condensed thereby.
The liquid refrigerant thus formed passes via conduit 13, through
device 14 and conduit 13', to evaporator 22. The refrigerant
absorbs heat in the evaporator from the medium to be cooled such as
room air which is passed over the evaporator (by means not shown)
in heat transfer relation with the refrigerant which is vaporized
thereby. The gaseous refrigerant thus formed is returned to the
compressor via conduit 15. The refrigeration system thus described
is typical of the type found in window mounted room air
conditioners, but it should be understood that such systems may be
employed in other applications. The compressor outlet and the inlet
to the refrigerant flow metering device define a high pressure side
of the refrigeration system, and the refrigerant flow metering
device outlet and compressor inlet define a low pressure side of
the system.
The refrigerant flow metering device disposed between the condenser
and the evaporator operates to regulate the flow of refrigerant in
response to the cooling load imposed on the system. Generally, such
device is sized so that a predetermined amount of refrigerant will
flow therethrough when the ambient temperature is within a range
generally referred to in the art as the design operating range.
For smaller applications, the refrigerant flow metering device
generally employed is a capillary tube. Although such device
generally functions as desired when the ambient temperature is
within its design range, such device does not function as desired
when the ambient temperature either exceeds or falls below the
desired range as heretofore noted. Although thermostatic expansion
valves may be employed to substantially increase the operating
range, such devices are relatively expensive. As will become more
apparent hereinafter, the novel refrigerant flow metering device
obviates the problems heretofore discussed without substantially
increasing the manufacturing costs as would occur by utilization of
a thermostatic expansion valve.
Referring now to FIG. 2 there is shown a cross-sectional view of
the novel refrigerant flow metering device employed in the
refrigeration system of FIG. 1. The device includes a main body
member or housing 16 having a threaded portion 17. Enclosing the
upper end of body member 16 is a cap member 18, connected to the
body member by means such as induction brazing indicated by
reference numeral 23. The refrigerant metering device has an inlet
thereto 24 and an outlet therefrom 25. The inlet and outlet are
connected together by a bore 19 disposed within the confines of
body member 16. The bore has a variable cross section as clearly
shown in FIG. 2, thus forming a variable passage.
Mounted within bore 19 is valve element 20, which is capable of
reciprocal movement in said bore relative to body member 16.
Associated with valve element 20 is spring 21 which provides a
biasing force moving the valve element toward the wider end of the
variable cross section bore, the wider end being relatively close
to the inlet of device 14. The narrower portion of bore 19 is
relatively close to the outlet of the device.
Threadably connected to portion 17 of body member 16 is calibrating
member 28. Calibrating member 28 includes seat portion 29, upon
which spring 21 is mounted. Calibrating member 28 is rotated
relative to body member 16 to provide a predetermined compressive
force on spring 21. This compressive force provides the desired
operating range for device 14. If desired, after calibration,
calibrating member 28 can be permanently affixed relative to body
member 16 by means such as induction brazing, represented by
reference numeral 27.
When assembled, device 14 is installed between conduits 13 and 13'
as shown in FIG. 1 and may be permanently affixed therein by means
such as induction brazing shown by reference numerals 30 and
31.
As noted hereinbefore, problems occur when capillary tubes are
employed in refrigeration systems utilizing ambient air as the
condensing medium. The novel refrigerant metering device will
properly control the flow of refrigerant even though the ambient
temperature has substantially increased or decreased from the
design operating point.
For example, assume the ambient temperature has increased above the
design point, thus increasing the magnitude of the pressure
differential between the condenser and the evaporator. The
refrigerant flow from the condenser to the evaporator will
correspondingly tend to increase. The increased pressure, caused by
the increase in ambient temperature, acting on the valve element 20
in bore 19 will force the element toward the narrower portion of
the bore, thus reducing the flow area about the valve element, and
acting to moderate the increased flow of refrigerant passing to the
evaporator due to the increase in pressure differential. Although
the flow area about valve element 20 has been reduced due to the
movement thereof toward the narrower portion of the bore, the total
flow of refrigerant passing to the evaporator will increase as
desired upon the increase in ambient temperature. The reduced flow
area operates to moderate the increase of refrigerant flow thereby
preventing the problems encountered with capillary tubes operating
at high ambient temperatures.
Assume now that the ambient temperature is relatively low as
compared to the design operating point. Thus, the pressure
differential between the condenser and the evaporator is of a
relatively small magnitude. At the relatively small magnitude
pressure differential, the flow of refrigerant from the condenser
to the evaporator is correspondingly decreased. As noted
hereinbefore, such a decrease in refrigerant flow where a capillary
tube is installed may cause freezing of the evaporator coil.
However, as shall be apparent, such a condition will not occur when
the novel refrigerant flow metering device is utilized.
The reduced ambient temperature operates to decrease the pressure
acting on valve element 20 of device 14. Spring 21 moves the valve
element toward the wider portion of bore 19, thus increasing the
flow area for the refrigerant through the device. Thus, the
reduction in the magnitude of the pressure differential between the
condenser and evaporator resulting from the decrease in ambient
temperature is compensated by the increase in flow area through the
device to maintain the flow of refrigerant to the evaporator at a
sufficient level to prevent the evaporator coil from freezing due
to refrigerant starvation. The increased flow area about valve
element 20 operates to moderate the reduction in refrigerant flow
caused by the decrease in ambient temperature.
The novel metering device further provides an additional advantage
upon shutdown of the refrigeration system. Upon shutdown, the
pressure differential between the condenser and the evaporator
decreases. With the standard capillary tube, refrigerant flow from
the condenser to the evaporator is reduced, thereby prolonging the
period of time in which equalization of the pressure differential
between the high pressure side and low pressure side of the system
will be obtained. If it is desired to restart the compressor motor
while the pressure differential is still relatively high,
high-starting torque motors are required, thus increasing the cost
of the refrigeration system. Alternatively, if it is desired to
prevent the restarting of the compressor motor until the pressure
differential has substantially equalized, such devices as time
delay apparatus must be included in the compressor motor circuitry,
also increasing overall cost.
By employing the novel device 14, as the pressure differential
decreases upon compressor shutdown, spring 21 moves valve element
20 to increase the flow area for the refrigerant through device 14.
Thus, device 14 promotes more rapid equalization, thus obviating
the need for either high-starting torque motors or devices to
provide time delay in restarting of the compressor motor.
It should be understood that devices such as accumulators, disposed
between the evaporator outlet and compressor suction, may be
required to prevent liquid refrigerant from flowing to the
compressor upon start-up of the system. Accumulators are generally
employed in refrigeration systems utilizing capillary tubes, and
their utilization may be similarly required for applications
employing the device of this invention.
While I have described a preferred embodiment of my invention, it
is to be understood that the invention is not so limited thereto
since it may be otherwise embodied within the scope of the
following claims.
* * * * *