U.S. patent number 3,665,725 [Application Number 05/107,246] was granted by the patent office on 1972-05-30 for capacity control for compression expansion refrigeration systems.
This patent grant is currently assigned to Thermo King Corporation. Invention is credited to John W. Barlass, Lowell B. Naley.
United States Patent |
3,665,725 |
Barlass , et al. |
May 30, 1972 |
CAPACITY CONTROL FOR COMPRESSION EXPANSION REFRIGERATION
SYSTEMS
Abstract
A compression expansion refrigeration system is provided with a
hot gas line to connect hot gas from the compressor directly to the
expansion coil for reducing its capacity and a servo operated
suction pressure modulation valve is provided in the intake line to
the compressor to vary the capacity of the system to obtain a
controlled load temperature. Thermostatic control means disables
the servo operated modulation valve in the open position and
maintains closed a valve in the hot gas line to provide maximum
capacity so long as the controlled temperature is above a
predetermined amount above the desired controlled temperature and
when the controlled temperature falls below the predetermined
amount the valve in the hot gas line is opened to provide a direct
step reduction in capacity and the suction modulation valve is
activated to vary the lowered capacity to obtain the desired
controlled load temperature.
Inventors: |
Barlass; John W. (Excelsior,
MN), Naley; Lowell B. (St. Louis Park, MN) |
Assignee: |
Thermo King Corporation
(Minneapolis, MN)
|
Family
ID: |
22315642 |
Appl.
No.: |
05/107,246 |
Filed: |
January 18, 1971 |
Current U.S.
Class: |
62/196.4; 62/217;
62/278 |
Current CPC
Class: |
F25B
47/022 (20130101); F25B 41/20 (20210101); F25B
41/22 (20210101) |
Current International
Class: |
F25B
41/04 (20060101); F25B 47/02 (20060101); F25b
041/00 () |
Field of
Search: |
;62/196,217,278 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Perlin; Meyer
Claims
We claim as our invention:
1. A capacity control for a compression refrigeration system having
a compressor connected in a refrigerant circuit with a condensing
coil to an expansion device and an evaporator coil comprising, a
suction modulation valve in the suction line between said
evaporator coil and said compressor, servo means to be activated to
variably close said modulation valve to change the capacity of the
system, a hot gas injection line connected between said compressor
and said evaporator to bypass said condenser and inject hot
refrigerant gas directly from said compressor into said evaporator
to reduce the capacity of the system, a normally closed hot gas
valve in said hot gas line to be opened when the capacity of the
system is to be reduced from maximum capacity, and thermostatic
control means to inactivate the servo control of said modulation
valve in the open position and to cause said hot gas valve to be in
the closed position when maximum capacity is desired and the
controlled refrigerated load temperature is above a predetermined
amount above the desired controlled load temperature, said
thermostatic control means being responsive to open said hot gas
valve and activate the servo means for said modulation valve when
the temperature falls below the predetermined amount above the
desired load temperature whereby the capacity of the refrigeration
system is directly reduced a predetermined amount by the opening of
the hot gas valve and is gradually reduced beyond the predetermined
amount by the operation of said modulation valve to obtain the
desired load temperature.
2. The invention of claim 1 in which said servo operated suction
valve is normally open and is provided with a servo mechanism
powered by compressed refrigerant liquid supplied from the
refrigerant circuit to variably close the valve for capacity
control, and said thermostatic control means to inactivate said
suction valve in the open position is comprised of a normally
closed valve in the supply of liquid refrigerant to the suction
valve servo mechanism that is operated to be opened when the
controlled temperature drops below the predetermined amount above
the desired controlled temperature.
3. The invention of claim 1 in which said thermostatic control
means is effective to open said hot gas valve when the controlled
temperature is below one predetermined amount above the desired
temperature and is effective to activate the servo controlled
suction valve when the controlled temperature is below another
predetermined amount above the desired temperature.
4. The invention of claim 2 in which said thermostatic control
means is effective to open said hot gas valve when the controlled
temperature is below one predetermined amount above the desired
temperature and is effective to activate the servo controlled
suction valve when the controlled temperature is below another
predetermined amount above the desired temperature.
5. The invention of claim 4 in which said normally closed valve in
the supply of liquid refrigerant to the suction valve servo
mechanism and the normally closed hot gas valve in said hot gas
line are solenoid operated valves, said thermostatic control means
including respective thermostatic switches connected to energize
the respective solenoid valves when they are required to be opened
for controlling the capacity of the system.
Description
CROSS REFERENCES TO RELATED PATENT APPLICATIONS
So far as is known, this application is not related to any
copending patent applications.
BACKGROUND OF THE INVENTION
There are many known arrangements for varying the capacity of a
compression expansion refrigeration system. For example, it is
known that the capacity of the system may be reduced by injecting
hot refrigerant gas directly from the compressor into the expansion
coil. Also, it is known that a throttle valve may be interposed in
the suction line to the compressor to be variably closed or
modulated to vary the suction pressure and the capacity of the
system to thereby obtain a desired controlled refrigerated
temperature. The known arrangements for capacity control such as
just described have well known limitations and problems which
prevent their being effective to give a very wide range of capacity
control down to as low as three to five percent of total capacity.
Therefore, a system using the known capacity controls cannot have
an excess of capacity or large capacity relative to the normal load
because of the limited range of operation of such capacity
controls. Transportable refrigeration systems for trucks, railroad
cars and the like can be more effectively used if the refrigeration
system can be provided with a large or excess capacity for rapidly
cooling a new load and can then have the capacity controllably
reduced over a large range to as low as three percent of the
maximum capacity while operating continuously to maintain the load
at the desired controlled refrigerated temperature.
PRIOR ART
The U.S. Pat. to Long No. 3,088,291 issued May 7, 1963 may be of
interest in disclosing a compression expansion refrigeration system
having both hot gas injection and suction line pressure modulation
for capacity control but the control arrangements for the hot gas
injection and suction line pressure modulation are not such as to
provide the large range of capacity control in the manner provided
by the present invention.
SUMMARY
In accordance with the invention, a compression refrigeration
system is provided with a hot gas line between the discharge of the
compressor and the evaporator coil to bypass the condenser and feed
a predetermined amount of hot gas directly into the expansion coil
to reduce the capacity of the system. A normally closed hot gas
valve is provided in the hot gas line to enable the system to
function with maximum capacity when the valve is closed. A servo
operated suction line pressure modulating throttle valve is
provided in the suction line of the system to be controllably
closed when it is desired to vary the capacity of the system to
maintain a desired refrigerated load temperature. The servo
operated suction valve is arranged to be normally open when its
servo mechanism is inactivated or disabled. Thermostatic control
means is provided to maintain the hot gas valve closed and to
inactivate the servo mechanism of the suction pressure modulation
valve in the valve open position when the load temperature is above
a predetermined amount above the desired controlled refrigerated
temperature and the maximum refrigeration capacity is therefore
required. The thermostatic control means is effective to open the
hot gas valve to provide a direct and immediate step reduction in
capacity when the load temperature drops below the predetermined
amount above the desired controlled load temperature. The
thermostatic control is also arranged to activate the servo
mechanism for the suction pressure modulation valve after the hot
gas valve has been opened when the load temperature falls below a
predetermined amount above the desired load temperature so that the
lowered capacity may be further reduced to as low as three percent
of the total capacity in order to maintain the desired load
temperature. The hot gas injection as described above is effective
to provide a step reduction in capacity that enables the system
capacity to be further lowered to about 3 percent of the maximum
capacity by the operation of the suction pressure modulation valve
without fully closing the valve to such an extent as would create a
vacuum into the compressor or would starve the compressor of
cooling gas to be compressed. This also assures a sufficient gas
flow to provide return of lubricating oil to the compressor.
Further features and advantages of the invention will be apparent
with reference to the following specification and drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a block diagram of the refrigeration system embodying the
capacity control of the invention; and
FIG. 2 is a graphical showing of the operation of the
invention.
DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring to FIG. 1 of the drawings, a refrigerant gas compressor
10 is shown to have its outlet connected to the hot gas line 11 and
to the condensing coil 12. The condensed liquid refrigerant from
the condensing coil 12 is connected by the liquid line 13 to the
expansion device 14 and the expansion coil 15. Expanded refrigerant
gas from the expansion coil 15 is connected by the suction line 16
to the inlet of the refrigerant gas compressor 10 thus completing
the refrigerant circuit.
A hot gas bypass line 20 is connected from the hot gas discharge
line 11 to the outlet side of the expansion device 14 and thus to
the expansion coil 15. When the solenoid operated hot gas valve 21
is opened, the bypass line 20 functions to continuously connect a
quantity of hot refrigerant gas directly from the compressor 10
into the expansion coil 15 thus providing a step reduction in
refrigeration capacity for the system. The hot gas line valve 21 is
a form of normally closed solenoid operated valve well known in the
art which may be opened when the solenoid coil of the valve is
energized upon the closing of the thermostatic switch contacts 22
as will be further described in some detail.
A suction pressure modulating or throttle valve 30 is interposed in
the suction line 16 and such valve is of the servo operated type
that will be normally opened when its servo mechanism 31 is
inactivated as is well known in the art. The servo mechanism 31 is
arranged to be operated by the pressure of liquid refrigerant in
the line 33. A solenoid valve 34 is connected in the liquid
refrigerant line 33 to be normally closed except when its solenoid
coil is energized upon the closing of the thermostatic switch 35.
When the valve 34 is closed, the servo mechanism 31 for the suction
pressure modulating valve 30 is inactivated with the valve in the
full open position. On the other hand, when the solenoid valve 34
is open, the liquid refrigerant under pressure in line 33 is
connected to the servo mechanism 31 which functions responsive to
the temperature sensing coil 32 to variably close the suction
pressure modulating valve 30 and vary the suction pressure in the
line 16 to the compressor 10 to obtain a desired controlled load
temperature from the evaporator coil 15.
Referring now to both FIGS. 1 and 2 of the drawing, the preferred
operation of the capacity control system of the invention will be
described. It should first be remembered that the refrigeration
system of the invention is provided with a very high or excess of
capacity to thereby obtain a rapid cooling of a load such as might
be desired in a refrigerated truck or railroad car compartment.
When the system is first operated, both the hot gas bypass solenoid
valve 21 and the liquid line solenoid valve 34 are closed so that
no hot gas is injected directly into the expansion coil and the
suction pressure modulation valve is full open thus assuring the
operation of the system at maximum capacity as indicated by the
point CX on FIG. 2 of the drawing. Thus the system operates at
maximum capacity to rapidly cool a new load until the temperature
of the load drops as shown by FIG. 2 of the drawing to the
temperature T1 which is a predetermined temperature above the
desired load temperature T2. When the temperature T1 is reached,
both thermostatic switches 22 and 35 may be closed. The closure of
thermostatic switch 22 causes the energization of the solenoid
valve 21 in the hot gas bypass line 20 to thus open the valve 21
and cause a predetermined quantity of hot refrigerant gas to be
continuously injected directly into the expansion coil 15. This
immediately produces a stepped reduction of capacity of the
refrigeration system as indicated from the point C to the point C1
in the curve of FIG. 2. At the same time, with the thermostatic
switch 35 closed to energize and open the solenoid valve 34, the
servo mechanism 31 for the hot gas suction line valve 30 is
activated. Servo mechanism 31, functioning in connection with the
temperature sensing coil 32, thus causes the suction valve 30 to
variably close until the desired controlled temperature T2, at a
very low capacity C3 of the refrigeration system, is reached.
Thereafter the suction modulation valve 30 will operate in a known
manner to maintain the desired low temperature T2 by varying the
capacity of the refrigeration system as required about the low
capacity point C3.
Although the invention has been described as employing two
thermostatic switches 22 and 35, it should be obvious to those
skilled in the art that a single thermostatic switch may be used in
place of the two switches and the electric current connected by the
single thermostatic switch would be connected in parallel to both
of the solenoid valves 21 and 34. Such an arrangement, of course,
would require that both valves 21 and 34 open at the same time. It
may be desirable to open valve 21 and inject hot gas directly into
the evaporator coil 15 before the servo mechanism 31 for the
suction pressure modulation valve 30 is activated. In such case,
the separate thermostatic switch 35 could be differently adjusted
from the thermostatic switch 22 so that the solenoid valve 34 would
be opened at a different time from the opening of the solenoid
valve 21. Depending upon the desired operating parameters of the
system, either valve 21 or 34 may be opened before the other, it
being understood, however, that when the valve 21 is opened, an
immediate step reduction in capacity of the refrigeration system
will be obtained and that when the valve 34 is opened, the
graduated or modulated change in capacity of the system would be
obtained as the servo operating suction pressure modulation valve
30 is variably closed or opened.
Various modifications will occur to those skilled in the art.
* * * * *