Information
-
Patent Grant
-
6490882
-
Patent Number
6,490,882
-
Date Filed
Tuesday, March 27, 200123 years ago
-
Date Issued
Tuesday, December 10, 200221 years ago
-
Inventors
-
Original Assignees
-
Examiners
Agents
- Howrey Simon Arnold & White LLP
-
CPC
-
US Classifications
Field of Search
US
- 062 498
- 062 467
- 062 3241
- 062 160
- 062 DIG 17
- 062 182
-
International Classifications
-
Abstract
A method of preventing refrigerant condensation in a discharge volume or discharge line of a compressor is disclosed. The method involves the application of one or more heaters to a cooling circuit to prevent condensed refrigerant from migrating into the discharge line and/or discharge volume of the compressor. In one embodiment, a heater is in thermal communication with the dome of the compressor. The heater may be a band heater. In another embodiment, a flexible strip heater is used on the discharge line of the cooling circuit. In another embodiment, both a heater on the discharge volume of the compressor and a heater on the discharge line may be used to prevent migration and condensation of refrigerant.
Description
BACKGROUND OF THE INVENTION
The present invention relates generally to a method of preventing refrigerant condensation in a discharge volume or discharge line of a compressor, and, more particularly to the application of one or more heaters to a cooling circuit to prevent condensed refrigerant from migrating into the discharge line and/or discharge volume of a compressor.
Electronic equipment in a computer or telecommunication room requires precise, reliable control of room temperature, humidity and airflow. Excessive heat or humidity can damage or impair the operation of critical computer systems and other components. For this reason, precision cooling systems are operated to provide cooling in these situations.
A typical cooling system
10
is schematically illustrated in FIG.
1
. The cooling system
10
includes compressor
20
, condenser
30
, expansion valve
50
and evaporator
60
. Refrigerant for use in the cooling system
10
may be any chemical refrigerant, such as chloroflourocarbons (CFCs), hydroflourocarbons (HFCS) or hydrochloroflourocarbons (HCFCs) such as R-22.
Operation of cooling system
10
is as follows. Refrigerant is compressed in a compressor
20
, which may be a reciprocating or scroll compressor or other compressor type. After the refrigerant is compressed, it travels through a discharge line
12
to a condenser
30
. A high head pressure switch
24
is attached to discharge line
12
. High head pressure switch
24
shuts down the compressor if the discharge pressure exceeds a predetermined level.
In condenser
30
, heat from the refrigerant is dissipated to an external heat sink, e.g., the outdoor environment. Upon leaving condenser
30
, refrigerant passes through a liquid line solenoid valve
40
and travels through a first liquid line
14
to expansion mechanism
50
. Expansion mechanism
50
may comprise a valve, orifice or other possible expansion apparatus known to those of ordinary skill in the art. The expansion mechanism
50
causes a pressure drop in the refrigerant, as the refrigerant passes through the mechanism.
Upon leaving the expansion mechanism, the refrigerant travels through second liquid line
16
, arriving at evaporator
60
, which comprises a heat exchanger coil. Refrigerant passing through evaporator
60
absorbs heat from the environment to be cooled. Specifically, air from the environment to be cooled circulates through evaporator coil, where it is cooled by heat exchange with the refrigerant. Refrigerant carrying the heat extracted from the environment then returns to compressor
20
by suction line
18
, completing the refrigeration cycle.
The precision cooling systems, such as that outlined above for a computer or telecommunications room, are typically operated year round, even when the outdoor ambient temperature is below 40° F. Certain operating conditions produce a high head pressure within the cooling system
10
and particularly in discharge line
12
. As a result, high head pressure switch
24
shuts down compressor
20
if the discharge pressure exceeds a predetermined level. In particular, when the environment in which the condenser is situated is 30° F. or cooler than the environment in which the evaporator is situated (i.e., the environment to be cooled), condenser
30
is significantly cooler than the evaporator.
With the cooling system
10
shut down for an extended period of time, refrigerant is in liquid line expands through evaporator
60
and draws through compressor
20
. The refrigerant then condenses in the cold condenser
30
. The condenser fills with liquid refrigerant, and refrigerant may begin to condense in discharge line
12
and compressor
20
. Starting compressor
20
with liquid refrigerant present in the discharge line
12
and/or the discharge volume of compressor
20
is likely to cause pressure excursion incidents. Condensation-induced shock (CIS) and vapor-propelled liquid slugging (VPLS) are phenomena that can produce dangerous high-pressure excursion incidents in the discharge lines.
To describe the occurrence of CIS and VPLS, operation of cooling system
10
is described after refrigerant has migrated from the liquid lines and condensed in the discharge line
12
and/or discharge volume of compressor
20
. During start up of compressor
20
, the refrigerant mass flow rate may increase from zero to the normal operating conditions in less than 10 seconds. To transfer momentum to the liquid in discharge line
12
, the refrigerant vapor being pumped by compressor
20
undergoes a pressure surge.
Any volume of liquid in discharge line
12
decreases the volume available for the vapor from compressor
20
. The less vapor volume available to absorb the pressure surge, the greater is the peak of the pressure surge to provide the necessary transfer of momentum. The condensation in line
12
or the discharge volume of compressor
20
induces a shock or pressure surge. If the vapor discharge volume is too small at startup, the peak of the pressure surge will exceed the predetermined setting of high head pressure switch
24
(which is chosen to prevent damage to the components of the cooling system).
High head pressure switch
24
will trip and shut down compressor
20
. Multiple attempts to restart cooling system
10
will eventually result in successful operation. With repeated starts of the compressor, the liquid slugging the line is eventually propelled by the vapor along the line
12
, and the volume available to the vapor increases. In other words, the liquid condensate in discharge line
12
can be forced through the line, allowing for enough volume in the discharge line to accommodate the compressed vapor without tripping high head pressure switch
24
.
Field reports indicate high-pressure pulses in discharge line
12
in close proximity to the location of pressure switch
24
. In some cases this pulse is high enough to peg and bend the needle on the gauge used to perform the measurement. Therefore, damage and wear to compressor
20
and other components of cooling system
10
can result from repeated occurrences of the high head pressure at startup.
It is to be understood that the formation of high-pressure excursion incidents can result from a number of other factors or conditions not listed herein. Furthermore, those conditions cited in the present disclosure as contributing to the possible occurrences of high-pressure excursion incidents may vary with the given design characteristics or installation conditions of a cooling system. The conditions cited are presented as exemplary of those conditions that may lead to high-pressure excursion incidents for a given cooling system in a conventional field setting.
One prior art solution to the refrigerant migration and condensation problem is to move liquid line solenoid valve
40
from the outdoor unit, i.e., condenser unit
30
, to the other end of the liquid line
14
just ahead of expansion mechanism
50
. Adding a liquid line solenoid valve to all evaporator units in production would prove costly. The circumstances associated with high-pressure excursion incidents as discussed herein occur in only a few installations of cooling system. Furthermore, the problems associated with liquid line slugging and high head pressures at startup are not usually discovered until after installation of a cooling system. Moving or inserting a liquid line solenoid
40
to just ahead of the expansion valve
50
involves a complicated retrofitting procedure. Typically, the procedure involves cutting the liquid line
14
and installing the liquid line solenoid
40
in the new location
42
, which can be cost prohibitive.
The present invention is directed to overcoming, or at least reducing the effects of, one or more of the problems set forth above.
SUMMARY OF THE INVENTION
In view of the foregoing and other considerations, the present invention relates to the application of one or more heaters to a cooling circuit to prevent condensed refrigerant from migrating into the discharge line and/or discharge volume of a compressor.
In accordance with one aspect of the present invention, there is provided a cooling system that includes a first and a second discharge section. The first discharge section includes a discharge volume of a compressor. The second discharge section includes a discharge line, where the discharge line runs from the discharge volume of the compressor to a condenser. The cooling system includes a heating element in thermal communication with at least one of the discharge sections.
In accordance with another aspect of the present invention, there is provided a cooling system. The cooling system includes a first means for collecting a discharge volume of a compressor and includes a second means for communicating the discharge volume of the compressor to a condenser. The cooling system includes a third means for applying heat to at least one of the first or second means.
In accordance with another aspect of the present invention, there is provided a compressor. The compressor includes a discharge section on the compressor and a heating element in thermal communication with the discharge section.
In accordance with another aspect of the present invention, there is provided a method for preventing high-pressure excursion incidents in a cooling system. The method includes the step of heating a compressor discharge volume of the cooling system.
In accordance with a further aspect of the present invention, the method further includes the step of heating a discharge line of the compressor.
In accordance with another aspect of the present invention, there is provided a cooling system having steps for preventing high-pressure excursion incidents in the cooling system. The cooling system includes steps for heating a compressor discharge volume of the cooling system.
In accordance with a further aspect of the present invention, the cooling system further includes steps for heating a discharge line of the compressor.
BRIEF DESCRIPTION OF THE DRAWINGS
The foregoing, the preferred embodiment, and other aspects of the present invention will be best understood with reference to the detailed description of specific embodiments of the invention, which follows, when read in conjunction with the accompanying drawings, in which:
FIG. 1
is a schematic diagram of a cooling system according to the prior art.
FIG. 2
is a schematic diagram of a cooling system in accordance with the present invention.
FIG. 3
illustrates a compressor according to the present invention.
FIG. 4
illustrates another compressor according to the present invention.
FIG. 5
illustrates yet another compressor according to the present invention.
FIG. 6
is an exterior view of a compressor according to the present invention.
FIG. 7
illustrates a discharge line having a heating element in accordance with the present invention.
FIGS. 8A-B
illustrate an embodiment of a heater according to the present invention that may be used to retrofit an installed cooling system in order to prevent high-pressure excursion incidents as discussed herein.
While the present invention is susceptible to various modifications and alternative forms, specific embodiments are shown by way of example in the drawings and are described in detail herein. However, it should be understood that the invention is not limited to the particular forms disclosed. Rather, the invention includes all modifications, equivalents and alternatives within the scope of the appended claims.
DETAILED DESCRIPTION OF THE INVENTION
Illustrative embodiments will now be described with reference to the accompanying Figures.
FIG. 2
is a schematic diagram of a cooling system
100
in accordance with the present invention. Cooling circuit
100
includes compressor
120
, condenser
140
, expansion mechanism
180
and evaporator
190
. Refrigerant used in cooling circuit
100
may be any chemical refrigerant, including chloroflourocarbons (CFCs), hydroflourocarbons (HFCs), or hydrochloro-flourocarbons (HCFCs) such as R-22.
Refrigerant enters compressor
120
through suction line
110
. Compressor
120
, which may be a reciprocating compressor, a scroll compressor, or other compressor type known to those of ordinary skill in the art, compresses the refrigerant. Compressor
120
is equipped with a crankcase heater
122
, which heats the compressor oil sump to prevent refrigerant condensation in the compressor oil during compressor off cycles. Compressor
120
also includes discharge section
124
, where compressed refrigerant is collected and discharged through discharge line
112
. A heater
126
is located at discharge section
124
of compressor
120
. Further details concerning the function of heater
126
are included below.
After the refrigerant is compressed, it travels through discharge line
112
to which high-pressure switch
128
is connected. High-pressure switch
128
protects cooling system
100
from damaging high pressures that may occur upon startup or during operation of the cooling system. Refrigerant exiting discharge line
112
enters condenser unit
130
. The condenser unit includes condenser
140
, which is a heat exchanger coil. In the condenser, heat from the refrigerant is dissipated to an external heat sink, i.e., an outdoor environment.
For the present, a detailed description of the components of condenser unit
130
is omitted. Upon leaving condenser unit
130
, refrigerant continues through liquid line
116
and liquid line solenoid valve
170
. Liquid line solenoid valve
170
is closed during off cycles to prevent refrigerant migration past the valve. The refrigerant then passes through expansion mechanism
180
, which may be a valve, orifice, or other expansion apparatus, which are well known to those of ordinary skill in the art. Expansion mechanism
180
subjects passing liquid refrigerant to a drop in pressure.
Exiting expansion mechanism
180
, refrigerant reaches evaporator
190
, which comprises a heat exchanger coil. Refrigerant passing through evaporator
190
absorbs heat from the environment to be cooled. Air from the environment to be cooled is circulated through evaporator coil, and is cooled by heat exchange with the refrigerant. Upon leaving evaporator
190
, refrigerant carrying the heat extracted from the environment returns to compressor
120
by suction line
110
, thereby completing the cooling cycle.
Cooling system
100
may be operated year round, even when the outdoor ambient temperature is approximately 30° F. or more below the indoor ambient temperature of the space to be cooled. For example, a typical indoor ambient temperature is about 70° F. In which case, cooling system
100
may be operated when the outdoor ambient temperature is about 40° F. With these conditions, condensing unit
130
is significantly cooler than evaporator
150
. To maintain adequate head pressure within condensing unit
130
, the capacity of condenser
140
must be reduced or restricted. The condensing unit
130
includes components for flooding condenser
140
with liquid refrigerant to maintain head is pressure. The components are 3-way head pressure control valve
150
, receiver
160
, heater
164
, and heater pressure switch
166
. The operation of these components is as follows.
Pressure line
114
connects discharge line
112
to 3-way pressure control valve
150
. Condenser
140
includes port
142
that connects to 3-way pressure control valve
150
. Pressure control valve
150
operates to maintain a minimum condensing pressure in condenser
140
. Upon leaving pressure control valve
150
, refrigerant is collected in receiver
160
, which includes pressure relief valve
162
and heater
164
. Receiver
160
aids in maintaining the condensing pressure in condenser
140
during low ambient temperature conditions.
Head pressure control valve
150
operates to maintain a minimum condensing pressure within condenser
140
. During low temperature operation, 3-way control valve
150
meters discharge gas into receiver
160
to maintain a discharge pressure operating against the dome of 3-way control valve
150
. The discharge pressure at valve
150
closes condenser port
142
, backing liquid refrigerant into condenser
140
. The presence of liquid refrigerant in condenser
140
reduces the condenser working volume. Receiver
160
is sized to hold the excess refrigerant that would otherwise flood condenser
140
.
Heater
164
on receiver
160
is temperature compensated. Heater
164
maintains the liquid refrigerant pressure within a specific range during off-cycles. Liquid pressure switch
166
turns heater
164
off during operation of the cooling system and/or when the pressure in receiver
160
is high. Heater pressure switch
166
may have a cut out of about 150 psig (1034 kPa) and a cut in of about 100 psig (690 kPa). For safety, the dome of receiver
160
includes a pressure relief valve
162
that may be set for about 450 psig (3103 kPa).
In low temperature conditions, the condenser will be only partially charged with refrigerant, and installations with significantly long liquid lines
116
, e.g., over 50 ft., may have as much or more refrigerant in liquid line
116
than in condenser
140
. This results in migration of refrigerant and the possibility of pressure excursion incidents as described in detail below.
During off cycles, condenser
140
will be the coldest part of cooling system
100
because of the low outdoor temperature. This results in a higher pressure in liquid line
116
than in condenser
140
. For example, assuming evaporator
190
is at the indoor temperature of 70° F. and condenser
140
is at the outdoor temperature of 40° F., the pressure in liquid line
116
may be as much as 50 psig greater than the pressure in condenser
140
. This pressure differential will induce refrigerant migration from liquid line
116
. Refrigerant expands through evaporator
190
and draws through suction line
110
and compressor
120
, finally condensing to liquid in condenser
140
.
During a prolonged off-cycle, condenser
140
fills with liquid refrigerant due to this migration. Refrigerant may also condense in discharge line
112
and eventually in discharge section
124
of compressor
120
. If liquid refrigerant is present in discharge line
116
and/or discharge section
124
, transient high pressures will occur when compressor
120
is started. Condensation-induced shock (CIS) and vapor-propelled liquid slugging (VPLS) produce these dangerous pressure excursions, which can cause significant damage to the cooling system.
To prevent pressure transients, it is necessary to prevent or minimize refrigerant migration and condensation in discharge line
112
and discharge section
124
. Applying a heater
126
to discharge section
124
provides one solution to prevent condensation in discharge section
124
of compressor
120
. Heater
126
may be a heater such as would be placed in thermal communication with the crankcase and may be mounted to the compressor top cap or dome. The compressor top cap or dome forms the discharge volume of the compressor, where pressurized vapor is first collected from the compression mechanism, be it a scroll or piston. Alternatively, heater
126
may be a flexible strip heater attached to discharge line
112
immediately adjacent to compressor
120
.
It is preferred to use only the heater attached to the compressor dome between the top plate and the top cap. Applying a heater to this location resembles the use of a heater on the crankcase of the compressor and is, therefore, easy to implement. Furthermore, the heater may be applied after a cooling system is installed and found to require prevention of high-pressure excursions. Thus, application of the heater according to the present invention, in the form of a kit or retrofitting package, obviates the need to modify all cooling systems before installation, which may be costly or may not require the prevention of high-pressure excursions.
Addition of heater
126
may eliminate the need to move the location of the liquid line solenoid to just upstream to expansion mechanism
180
, as described above. Furthermore, addition may completely eliminate the need for liquid line solenoid valve
170
altogether. Heater
126
may be powered continuously, as is normal practice for crankcase type heaters
122
used to prevent refrigerant condensation in the compressor oil sump.
FIG. 3
illustrates a sectional view of a compressor having additional heaters installed according to the present invention. Scroll compressor
200
is shown in isolation. For simplicity, the known prior art means for motor cooling, lubrication, thermal overload protection, refrigerant filtration, and for refrigerant flow, pressure, and temperature control are not shown. Scroll compressor
200
includes hermetically sealed enclosure
210
. Within enclosure
210
is an electric motor
212
having a rotor
213
and extended shaft
214
. Extended shaft
214
drives compression spiral
230
.
Scroll compressor
200
includes two spiral-shaped members
220
,
230
. Members
220
,
230
fit together forming a plurality of crescent-shaped gas pockets. Compression spiral
230
orbits within stationary scroll
220
. Refrigerant enters enclosure
210
through low-pressure intake
240
. When extended shaft
214
rotates by operation of electric motor
212
, orbiting spiral
230
forms pockets of gas with stationary spiral
220
. Orbiting spiral
230
continuously forces and presses the gas pockets against the inside surface of stationary scroll
220
so that sealed compartments
244
are formed. Sealed compartments
244
undergo a continuous decrease in volume. Consequently, the gas pressure increases starting from a low pressure chamber
242
at the outside of the spiral and ending at the high-pressure chamber at compressor discharge volume
250
. The vapor is then discharged through high-pressure discharge
254
.
Scroll compressor
200
is equipped with a crankcase heater
218
to prevent refrigerant condensation in oil sump
216
during off-cycles. This is particularly desirable when the compressor will be operated in a relatively cold environment, as the cold ambient air will condense the refrigerant, which will then dilute the oil. The presence of condensed refrigerant in the oil reduces its lubricating capabilities. A typical crankcase heater
218
is band heater that encompasses the compressor enclosure near oil sump
216
. It is desirable to heat oil sump
216
to vaporize any condensed refrigerant accumulated in oil sump
216
.
In accordance with the present invention, a second heater
252
is placed in thermal communication with vapor discharge volume
250
of the compressor. The second heater may be similar in construction to the band heater placed in thermal communication with oil sump
216
. A band heater has a plurality of coils formed in a band. Current is supplied to the coils, and the electrical resistance of the coils generates heat. The band heater may be placed in thermal communication with a surface that conducts heat, such as the dome of a scroll compressor. The heat generated by the coils conducts through compressor dome
251
and heats the area of vapor discharge volume
250
of the compressor.
Heater
252
maintains the vapor discharge volume
250
at a temperature that prevents refrigerant condensing to liquid within discharge volume
250
. Heater
252
may be operated continuously, even while the compressor is running without detrimental effect on the operational characteristics of compressor
200
. The amount of power supplied by the heater is typically in the range of 70 W, and this additional heat is negligible, when compared to the energy added to the refrigerant by the compressor. Heater
252
may add no more than 2° F. to the discharge temperature. Thus, the heater may operate continuously.
Alternatively, as illustrated in
FIG. 4
, a heater
354
may be placed in thermal communication with vapor discharge line
352
of compressor
300
. Heater
354
may be a flexible strip heater placed in thermal communication with discharge line
352
. It is preferable that heater
354
and discharge line
352
be enclosed within the tubular insulation for the refrigerant line. The insulation provides protection to the heater and acts to concentrate the application of heat to the discharge line. Heater
354
maintains the temperature of discharge line
352
above a temperature at which refrigerant will condense into a liquid. Heater
354
may run continuously, even while compressor
300
is running. The heat from second heater
352
has no detrimental effect on the operating characteristics of compressor
300
. The resulting heat applied to the system while the compressor is in operation is negligible and changes the discharge temperature by only a few degrees.
In yet another alternative, shown in
FIG. 5
, a heater
452
may be placed in thermal communication with vapor discharge volume
450
of compressor
400
. Heater
452
maintains vapor discharge volume
450
above a temperature at which refrigerant will condense into a liquid in volume
450
. Additionally, a third heater
456
is placed in thermal communication with high-pressure discharge line
454
. Third heater
456
may be a flexible strip heater placed in thermal communication with the discharge line
454
. Heater
456
and discharge line
454
are preferably enclosed within the tubular insulation for refrigerant line. Heaters
452
and
456
may run continuously, even while the compressor is running, as the additional heat produced by heaters
452
and
456
has no detrimental effect on compressor operation. The additional heat applied while the compressor is operating is negligible because it increases the discharge temperature by only a few degrees.
FIG. 6
illustrates an exterior view of a compressor with discharge heaters installed according to the present invention. Compressor
500
has an enclosure
502
. Within enclosure
502
are an electric motor, a compression mechanism and other necessary components (not shown). A suction line of the cooling system (not shown) connects to enclosure
502
via an intake line
504
. Uncompressed refrigerant enters the enclosure through intake line
504
to be compressed by compressor
500
. Once compressed, the refrigerant leaves compressor
500
through a discharge line
506
, which then connects to a discharge line of the cooling system (not shown).
Compressor
500
includes crankcase heater
508
encircling enclosure
502
of compressor
500
. The crankcase heater is a band heater that heats the oil in the oil sump of enclosure
502
. In addition to this crankcase heater
508
, the compressor includes a second heater
510
encircling enclosure
502
of the compressor. Second heater
510
is also a band heater as is used to heat the oil sump. Heater
510
encircles the enclosure around the top cap or dome
512
of the compressor.
The band heaters
508
and
510
have a plurality of coils formed in a band or circular belt. Current is supplied to the coils, and the electrical resistance of the coils generates heat. The band heaters
508
,
510
are applied directly to the surface of enclosure
502
. The heat generated by the coils of heaters
508
,
510
conducts through the material of enclosure
502
and heats the area of oil sump
509
and top cap
512
, respectively.
Top cap
512
contains the discharge volume or chamber, where compressed refrigerant is first collected after compression before leaving enclosure
502
. Second heater
510
prevents condensation of refrigerant in the discharge volume in top cap
512
. It is within capabilities of one of ordinary skill in the art to estimate and/or calculate the heater size required to sufficiently heat top cap
512
and prevent refrigerant condensation in the discharge volume.
FIG. 7
illustrates discharge line
520
having a heating element installed according to the present invention. Discharge line
520
is a high-pressure line that connects to a compressor (not shown) at end
522
. Compressed refrigerant leaving the compressor enters end
522
of discharge line
520
and travels along its length. A heater
524
is disposed around the discharge line
522
. Ideally, heater
524
is immediately adjacent to the compressor. The heater and the discharge line are enclosed by refrigerant line insulation
528
.
FIG. 8A
illustrates an embodiment of a heater
530
that may be used to retrofit an installed cooling system in order to prevent high-pressure excursion incidents as discussed herein. The heater resembles a crankcase heater such as provided by the Copeland Corporation. Heater
530
defines a band heater having a conductive wire
532
. The wire has wire leads
534
,
536
. Electrical current passing through wire
532
creates heat due to resistance of the wire. A first portion
540
of a mounting bracket attaches to one end of wire
532
. A second portion
542
of a mounting bracket attaches to the other end of wire
532
. Second portion
542
includes a snap lock
550
for connecting first portion
540
to second portion
542
. A ground wire
538
may also be attached to band heater
530
for safety. A series of tags
560
situate along the length of conductive wire
532
. A detail of a tag
560
is shown in a cross section A—A of FIG.
8
A. The tags include a ring
562
that wraps around wire
532
and deflecting ends
564
that contact a surface (not shown) such as a compressor dome.
FIG. 8B
illustrates the attachment of the band heater
530
of
FIG. 8A
to a compressor dome
570
according to the present invention. Conductive wire
532
bends around the contour of compressor dome
570
. Wire leads
534
,
536
bend in appropriate directions for attachment to electrical wiring. Snap lock
550
connects first portion
540
and second portion
542
of the mounting bracket to hold the band heater in place on the compressor dome
570
. Wire ends
534
,
536
may be provided with quick connectors (not shown) and conductive wire
532
may be sheathed with a metal protector (not shown).
While the invention has been described with reference to the preferred embodiments, obvious modifications and alterations are possible by those skilled in the related art. Therefore, it is intended that the invention include all such modifications and alterations to the full extent that they come within the scope of the following claims or the equivalents thereof.
Claims
- 1. A cooling system, comprising:a compressor having a discharge volume; a discharge line connecting said discharge volume to a condenser; and a heating element in thermal communication with said discharge volume or said discharge line.
- 2. The cooling system of claim 1, wherein said heating element is in thermal communication with said discharge volume of said compressor.
- 3. The cooling system of claim 2, wherein a second heating element is in thermal communication with said discharge line.
- 4. A cooling system, comprising:means for compressing refrigerant, said means for compressing having a discharge volume; a discharge line connecting said discharge volume to a condenser; and means for heating either said discharge volume or said discharge line.
- 5. The cooling system of claim 4, wherein said means for heating is in thermal communication with said discharge volume.
- 6. The cooling system of claim 5, further comprising means for heating said discharge line.
- 7. A compressor for use in a cooling system operated when an ambient temperature around a condenser of said system is an ambient temperature around an evaporator of said system, said compressor comprising:a discharge section; and a heating element in thermal communication with said discharge section.
- 8. A method for preventing high-pressure excursion incidents in a cooling system, said cooling system having a compressor discharge volume and a discharge line connecting said discharge volume to a condenser, said method comprising heating said compressor discharge volume.
- 9. The method of claim 8, further comprising heating said discharge line of said compressor.
- 10. A method for use with a cooling system operated when condensing unit ambient temperatures are less than evaporator ambient temperatures, comprising a step for preventing high-pressure excursion incidents in said cooling system by heating a discharge volume of a compressor.
- 11. The cooling system of claim 10, further comprising a step for preventing high-pressure excursion incidents in said cooling system by heating a discharge line of said compressor.
US Referenced Citations (4)