U.S. patent number 3,715,894 [Application Number 05/181,070] was granted by the patent office on 1973-02-13 for air conditioning bypass control.
Invention is credited to Richard E. Widdowson.
United States Patent |
3,715,894 |
Widdowson |
February 13, 1973 |
AIR CONDITIONING BYPASS CONTROL
Abstract
A vapor compression air conditioning system including defrost
control valve means between the compressor outlet and the
evaporator in bypass relationship to the condenser and expansion
valve for supplying hot refrigerant directly to the evaporator for
defrosting in response to a predetermined low temperature of
refrigerant in the evaporator which corresponds to frost
accumulation. The control valve includes a piston reciprocal in a
housing and having one end of the piston exposed to the compressor
outlet pressure and the second end exposed to a refrigerant
pressure within a variable volume control chamber between the
piston and the housing. A small diameter bleed port extending
through the piston equalizes the pressure forces acting on the ends
of the piston to normally maintain the piston in a closed position.
When a bimetal spring in an adjacent enclosure senses a low
refrigerant temperature which corresponds to frost accumulation on
the evaporator, a passage between the control chamber and the
enclosure is opened for rapidly reducing pressure in the control
chamber and causing the piston to move to its open position in
which hot refrigerant is directed to the evaporator.
Inventors: |
Widdowson; Richard E. (Dayton,
OH) |
Family
ID: |
22662787 |
Appl.
No.: |
05/181,070 |
Filed: |
September 16, 1971 |
Current U.S.
Class: |
62/196.4;
236/101D; 62/278; 236/101R |
Current CPC
Class: |
F25B
47/022 (20130101); F25B 41/20 (20210101) |
Current International
Class: |
F25B
41/04 (20060101); F25B 47/02 (20060101); F25b
041/00 () |
Field of
Search: |
;62/196,278 ;236/101
;73/363.9 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Perlin; Meyer
Assistant Examiner: Devinsky; Paul
Claims
What is claimed is as follows:
1. An air conditioning system comprising: an evaporator for cooling
air in a passenger compartment; a compressor for pressurizing
refrigerant discharged from said evaporator; a condenser for
cooling refrigerant discharged from said compressor; valve means
for expanding refrigerant discharged from said condenser to a low
pressure condition prior to its introduction into said evaporator;
a defrost control valve assembly fluidly connected between said
compressor and said evaporator and opened in response to a
predetermined evaporator refrigerant temperature to direct hot
refrigerant from said compressor directly into said evaporator for
defrosting; said defrost control valve including a housing with a
cylinder and a piston valve within said cylinder reciprocal between
closed and open positions; one end of said piston valve being
exposed to refrigerant pressure from said compressor outlet which
exerts an opening force upon said piston valve; the other end of
said piston valve forming a variable volume control chamber with
said housing; said piston having a small diameter bleed port
extending between said ends to said control chamber to transmit
refrigerant pressure from the compressor outlet to said control
chamber thus equalizing the pressure forces acting on the ends of
the piston which normally maintains said piston in its closed
position; said housing forming an enclosure connected to said
control chamber by a passage and having an inlet and an outlet
fluidly connected respectively to said evaporator and the inlet of
said compressor; valve means for blocking said passage when in a
closed position; bimetal spring means within said enclosure and
connected to said valve member for moving said valve member into an
open position in response to a predetermined evaporator refrigerant
temperature corresponding to frost accumulation on said evaporator
whereby said open passage decreases refrigerant pressure in said
control chamber to permit a pressure force on said first end of
said piston to move it into an open position permitting hot
refrigerant to pass directly to said evaporator for defrosting.
2. An air conditioning system comprising: an evaporator for cooling
passenger compartment air; a compressor for pressurizing
refrigerant discharged from said evaporator; a condenser for
cooling refrigerant discharged from said evaporator; a combination
expansion valve and defrost control valve assembly including a
housing with an expansion valve portion fluidly extending between
said condenser and said evaporator for expanding refrigerant to a
lower pressure condition; said housing further having a defrost
control valve portion opening in response to a low refrigerant
temperature corresponding to frost accumulation on said evaporator
to direct hot refrigerant from said compressor directly into said
evaporator for defrosting purposes; said defrost control valve
portion having a cylinder and a piston valve within said cylinder
reciprocal between closed and open positions; one end of said
piston valve being exposed to refrigerant pressure from said
compressor outlet to exert a fluid force upon said piston valve;
the second end of said piston valve forming a variable volume
control chamber with said housing; said piston having a small
diameter bleed port therethrough extending between said first and
second piston ends for transmitting refrigerant pressure from the
compressor outlet to said control chamber thereby equalizing
refrigerant pressures acting against said first and second ends;
said housing forming an enclosure connected by a passage to said
control chamber and having an inlet and an outlet fluidly connected
respectively to said evaporator and said compressor; a needle valve
member adapted to move between open and closed positions with
respect to said passage; bimetal spring means within said enclosure
operatively connected to said needle valve member for movement
between open and closed positions in response to changes in
refrigerant temperature of said evaporator corresponding to frost
accumulation on said evaporator whereby said bimetal spring means
moves in response to a predetermined low refrigerant temperature to
open said passage and change the refrigerant pressure within said
control chamber to move said piston into an open position for
directing hot refrigerant to said evaporator.
3. In an air conditioning system including an evaporator for
cooling air, a refrigerant compressor, a condenser, and an
expansion valve in refrigerant flow relation; a defrost control
valve assembly for melting frost on said evaporator comprising: a
valve housing with an inlet fluidly connected to said compressor,
an outlet fluidly connected to said evaporator and a cylindrical
bore between said inlet and outlet; a piston valve axially movable
within said cylindrical bore between closed and open positions to
regulate a flow of hot refrigerant from said compressor outlet to
said evaporator for defrosting; one end of said piston valve
exposed to refrigerant pressure from the compressor outlet; a
second end of said piston valve providing a movable wall of a
variable volume control chamber in said cylinder bore; said piston
valve having a small diameter bleed port extending therethrough
between said control chamber and said inlet for transmitting
refrigerant pressure to said control chamber thus equalizing
pressure forces on said piston valve; said housing forming an
enclosure with an inlet and an outlet fluidly connected
respectively to said evaporator and said compressor inlet for
refrigerant flow through said enclosure; said housing also having a
passage between said control chamber and said enclosure for
transmitting refrigerant pressure corresponding to said evaporator
to said control chamber; a needle valve member movable with respect
to said housing for opening and closing said passage; a bimetal
coil spring within said enclosure in heat transfer relationship to
refrigerant from said evaporator and axially movable with the
temperature changes to cause said needle valve member to open said
passage in response to a predetermined low refrigerant temperature
whereby said predetermined low refrigerant temperature corresponds
to frost accumulation on said evaporator and the opening of said
passage rapidly changes the control chamber pressure which produces
movement of said piston valve in said cylindrical bore for
directing hot refrigerant to said evaporator.
Description
This invention relates to vapor compression type air conditioning
systems and includes a bypass control valve between the compressor
outlet and the evaporator which opens in response to a
predetermined low evaporator temperature corresponding to frost
accumulation on the evaporator to direct hot refrigerant to the
evaporator for defrosting.
In air conditioning systems, there is an undesirable tendency for
frost to accumulate on the evaporator under some conditions. It is
a known practice to provide a throttling valve in air conditioning
systems to restrict refrigerant flow through the compressor's inlet
line which maintains refrigerant pressure in the evaporator above a
predetermined pressure level corresponding to an evaporator fin
temperature of more than 32.degree. F. Although this prevents frost
accumulation on the evaporator, it has the disadvantage of reducing
refrigerant flow and thus decreases the evaporator's capacity to
cool the passenger compartment of the automobile. The efficiency of
the system is also decreased.
The present defrost control valve for the refrigerating system uses
hot refrigerant directly from the compressor for defrosting
purposes. It includes a bimetal spring which moves in response to
evaporator refrigerant temperature to cause a piston valve to open
a passage which bypasses the condenser and expansion valve to
supply hot refrigerant directly to the evaporator for
defrosting.
The elimination of a throttling valve and the substitution of the
defrost control valve reduces the pressure differential between the
evaporator or low side of the system and the compressor outlet or
the high side of the system under some operating conditions. This
reduction increases the efficiency of the system since less work
input is needed to drive the compressor for a given amount of
cooling.
When the air conditioning system is first activated in warm ambient
temperatures, the present defrost control valve is closed since the
refrigerant temperature from the evaporator is relatively high due
to the amount of heat absorbed from the passenger compartment. The
absence of a flow restriction in the suction line decreases the
time necessary to pull down the temperature of the passenger
compartment to a comfortable level.
Another advantage of the present defrost control valve is the
prevention of subatmospheric pressures within the refrigerating
system which may be caused by restricting the suction line.
Subatmospheric pressures can induce air to leak into the system
which is very undesirable. The refrigerant pressure in the present
defrost control valve is above atmospheric pressure.
Therefore, it is an object of this invention to provide a defrost
control valve assembly responsive to a low refrigerant temperature
to direct hot refrigerant from the compressor outlet directly to
the evaporator for defrosting.
It is a further object of this invention to provide a defrost
control valve assembly including a bimetal type spring to sense a
predetermined low refrigerant temperature from the evaporator and
cause a passage to open which directs hot refrigerant from the
compressor outlet to the evaporator for defrosting.
It is a still further object of the invention to provide a defrost
control valve assembly including a housing with expansion valve
portion and a defrost control valve portion in which a piston is
reciprocated between closed and open positions for directing hot
refrigerant to the evaporator in response to movement of a
thermally responsive member which senses a predetermined low
refrigerant temperature downstream from the evaporator
corresponding to frost accumulation on the evaporator.
Further objects and advantages of the present invention will be
apparent from the following detailed description, reference being
had to the accompanying drawings in which preferred embodiments of
the invention are clearly shown.
IN THE DRAWINGS:
FIG. 1 is a diagrammatic view of an air conditioning system
including a sectional view of a combination expansion valve and
defrost control valve assembly; and
FIG. 2 is a diagrammatic view of a portion of an air conditioning
system including a fragmentary sectional view of another embodiment
of the expansion valve portion of the assembly shown in FIG. 1.
Referring now to FIG. 1, there is illustrated an air conditioning
system which includes a compressor 10 adapted to be driven by an
automobile engine (not shown). The compressor 10 draws refrigerant
through a suction or intake conduit 12 and passes compressed
refrigerant through a discharge conduit 14 into an air cooled
condenser 16, which is normally located in front of an automobile
radiator.
The compressed refrigerant is cooled and liquefied in condenser 16
from which it flows through a conduit 18 to the present combination
expansion valve and defrost control valve assembly 20. An expansion
valve portion 22 of assembly 20 includes a housing 24 which is
threadably supported within the main housing 26 of assembly 20. An
O-ring type seal 27 between members 24 and 26 prevents leakage
therebetween. The conduit 18 is threadably connected at 28 to the
housing member 24. A central bore 30 in housing 24 encircles a
stationary expansion valve member 32 which is secured by an annular
expansion member 34.
An O-ring seal 37 between members 24 and 32 prevents leakage
therebetween. Stationary valve member 32 has a central bore 36
which supports a movable valve member 38 having an annular seal 40.
A compression spring 42 normally maintains the member 38 in the
position against retainer 43 shown in FIG. 1. A passage 44 extends
axially through member 38 and connects the conduit 18 with interior
46 of housing member 32. After flowing through the passage 44 the
refrigerant enters a cavity 48 through ports 50. A second passage
52 which is centrally located in the end of the member 32 is
aligned with passage 44. An outlet 54 in housing 26 permits
refrigerant to flow from cavity 48 to an evaporator 58 through a
conduit 60.
Because of the restriction of passage 44, the refrigerant pressure
within the evaporator 58 and resultant pressure within the interior
46 is normally lower than the pressure within conduit 18. This
causes high pressure in conduit 18 to move valve member 38 to the
left in FIG. 1 and the left-hand end of member 38 to contact the
end of member 32. The combined restriction to refrigerant flow
through the passages 44 and 52 usually provides desirable
refrigerant quantities for the evaporator 58.
When the heat load on the evaporator 58 is great, refrigerant
pressure in the evaporator may increase due to superheating of
refrigerant. Superheating of refrigerant is the temperature of
refrigerant above its boiling point at a given pressure. The
resultant pressure in the evaporator is transmitted to cavity 48
and interior 46 and acts to force the valve member 38 to the right
into the position shown in FIG. 1 thus separating the passages 44
and 52. This movement reduces the flow restriction through the
expansion valve and increases the quantity of refrigerant passed
into the evaporator. The increased flow to the evaporator decreases
superheating and evaporator pressure. Refrigerant flows through the
evaporator 58 and conduit 62 into a chamber or enclosure 64 within
housing 26. After flowing through enclosure 64, refrigerant is
conducted by suction line 12 to the intake of compressor 10 to
complete the cycle.
Within the enclosure 64 a cup-shaped member 66 supports a
bimetallic coil spring 68 whose coils are composed of two different
metals with differing thermal coefficients of expansion. The
bimetal coil spring expands and contracts axially in response to
refrigerant temperature changes in the enclosure 64. Elongated
slots 70 in the side of member 66 pass refrigerant to the spring 68
and increase the heat transfer. One end of the bimetal spring 68
rests against the end 71 of member 66 and the other end of the
spring contacts an enlarged portion 72 of a needle valve members
74. The valve 74 includes an elongated body portion 76 extending
centrally through the center of spring 68 and bore 78 in the member
66. A lighter spring 80 engages the other side of the enlarged
portion 72 of needle valve 74 in opposition to the force produced
by the bimetal spring 68.
The coaction of springs 68 and 80 upon the enlarged portion 72 of
needle valve 74 locates the pointed end 82 of the valve 74 with
respect to a passage 84. A valve housing 86 is supported within a
bore 88 of housing 26 and is threadably connected at 90 to an inlet
fitting 92. An O-ring seal 93 prevents refrigerant leakage
therebetween. The fitting 92 threadably engages housing 26 at 94
and is fluidly connected to a conduit 96 which extends to the
outlet of compressor 10. An O-ring seal 97 prevents fluid leakage
therebetween. An inlet opening 98 extends centrally through the
fitting 92 into a cylindrical bore 100 in the valve housing 86. A
piston type valve 102 is supported for movement within bore 100. A
central passage 104 extends partially through the piston 102 and a
small diameter bleed passage 106 extends the remainder of the
distance through the piston 102. An O-ring seal 108 prevents fluid
leakage between the piston valve 102 and the housing 86.
The left end 109 of the piston valve 102 is exposed to refrigerant
pressure from the compressor outlet through conduit 96 and inlet
passage 98. The right end 110 of the piston 102 forms a wall of a
variable volume chamber 112 within member 86. The passage 84
extends from enclosure 64 to the control chamber 112. The chamber
112 also communicates with inlet 98 by bore 104 and bleed port 106.
When the passage 84 is closed by the needle valve 82, pressure from
the inlet 98 is transmitted through a filter 114, bore 104 and
bleed passage 106 into the chamber 112. This equalizes the pressure
in chamber 112 and in the inlet 98 and a light coil spring 116
maintains the piston 102 in the closed position in FIG. 1. In the
closed position, ports 118 are blocked by the piston to prevent
refrigerant flow through the bypass 120 to the evaporator.
When frost accumulates on the evaporator, heat transfer to air
passing through is lessened which causes refrigerant flowing
through the conduit 62 to decrease in temperature. The bimetal
spring 68 senses the temperature decrease and contracts to move the
needle valve 82 away from passage 84. The opening of passage 84
quickly reduces refrigerant pressure within the control chamber 112
which causes the piston 102 to move to the right in FIG. 1 which
align ports 118 with grooves 122 in the valve. Hot refrigerant then
flows from the compressor outlet through the conduit 96, inlet
passage 98, grooves 122, ports 118, bypass 120 and conduit 60 into
the evaporator 58. This raises the temperature of the evaporator
for melting frost.
When the bimetal spring 68 senses the warmer temperature output
from the evaporator the needle valve 82 blocks passage 84 and the
piston moves to the left to block ports 118.
In automotive air conditioning systems, operation of the compressor
10 during cool ambient temperatures may produce a low refrigerant
pressure within the evaporator corresponding to reduced
temperatures. At evaporator pressures below approximately 30 psig,
the temperature may fall below 32.degree. F. and frost may form.
The present defrost control valve will open under these temperature
conditions to flood the evaporator with sufficient hot refrigerant
to raise the evaporator temperature above 32.degree. F. Once the
temperature of refrigerant in the evaporator is above 32.degree. F.
and sensed by the bimetal operator, the supply of hot refrigerant
is cut off. Subsequently, if the evaporator temperature again falls
below 32.degree. F. the valve may open again.
The housing 26 is provided with a fitting 124 which threadably
engages bore 126 and includes a check valve 128. Fitting 124 is
utilized to initially fill the air conditioning system with
refrigerant and may be used to recharge the system as needed. An
O-ring seal 130 prevents refrigerant leakage between the fitting
124 and housing 26.
In FIG. 2, another embodiment of the combination expansion valve
and defrost control valve assembly 132 is illustrated. The assembly
132 includes a housing 134 similar to housing 24 in FIG. 1.
Assembly 132 is identical to that shown in FIG. 1 except for the
expansion valve portion 136 illustrated in the fragmentary view.
The expansion valve includes a housing 138 threadably secured to
the member 134 at 140 and is sealed by an O-ring 142. Conduit 18 is
connected to the housing 138 by a threaded fitting (not shown) at
144. Member 138 includes a central bore 146 which forms a cavity or
a chamber 148. A stationary valve member 150 is fixedly supported
within the cavity 148 at 152. An O-ring 154 prevents fluid leakage
around the valve member 150. Passages 156 extend from the inlet
opening 157 to cavity 148 through the side of the valve member 150.
A sleeve type valve member 158 encircles the stationary valve
member 150 and is movable axially along it. The movement of the
valve member 158 controls refrigerant flow through the passages
156. A cup-shaped member 160 surrounding the end of member 150 is
perforated by a plurality of ports 162 for refrigerant flow from
the passages 156 into cavity 148. A coil spring 164 between the
member 162 and the stationary member 150 normally maintains the
sleeve valve 158 in a position blocking the passages 156.
The sleeve valve 158 and member 160 are axially moved with respect
to stationary member 150 by contraction and expansion of a sealed
casing 166 with a bellows like configuration. The casing 166
includes a tubular thin-walled metal member 168 with corrugations
formed in its side surface. End members 170 and 172 seal the casing
interior 174. The end 172 is fixedly supported within the bore 146
by an expansion ring member 176 which has cut out portions around
its periphery to permit refrigerant flow from passages 156 to an
outlet port 155. The interior 174 of the casing 166 is evacuated so
as to expand and contract in response to pressure changes within
interior 148. A coil spring 178 extends between end members 170,
172 to normally maintain the casing 166 in an extended position. A
valve pin 180 is molded in the end member 170 and extends toward
the end member 172 which limit the contraction which the casing can
experience. The other end of the valve pin 180 extends through a
central portion of the cup-shaped member 160 to move the member 160
and sleeve valve 158 axially over the stationary valve member 150
as the sealed casing 166 expands. The casing 166 expands when the
refrigerant pressure within the cavity 148 decreases and contracts
when the pressure increases. This permits spring 164 to move the
sleeve valve 158 to close passages 156.
While the embodiments of the present invention as herein described
constitute preferred forms, it is to be understood that other forms
might be adapted.
* * * * *