US20040211195A1 - Refrigeration defrost system - Google Patents

Refrigeration defrost system Download PDF

Info

Publication number
US20040211195A1
US20040211195A1 US10420723 US42072303A US2004211195A1 US 20040211195 A1 US20040211195 A1 US 20040211195A1 US 10420723 US10420723 US 10420723 US 42072303 A US42072303 A US 42072303A US 2004211195 A1 US2004211195 A1 US 2004211195A1
Authority
US
Grant status
Application
Patent type
Prior art keywords
line
evaporator
refrigerant
refrigeration
refrigerant vapor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
US10420723
Other versions
US6807813B1 (en )
Inventor
Gaetan Lesage
Original Assignee
Gaetan Lesage
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B47/00Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02Defrosting cycles
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B5/00Compression machines, plant, or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02Compression machines, plant, or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2400/00General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07Details of compressors or related parts
    • F25B2400/075Details of compressors or related parts with parallel compressors
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2400/00General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/22Refrigeration systems for supermarkets
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B47/00Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02Defrosting cycles
    • F25B47/022Defrosting cycles hot gas defrosting

Abstract

A refrigeration defrost system including at least one frosted evaporator having an evaporator refrigerant vapor line and an evaporator refrigerant liquid line, comprises a first compressor having a suction inlet line and a discharge outlet line each connected to a discharge manifold, the discharge outlet being connected to said evaporator refrigerant vapor line. A first pressure regulator valve disposed in a refrigerant bypass passageway between the discharge manifold and the suction inlet line, feeds refrigerant vapor, when a defrost cycle is required, from the discharge manifold into the suction inlet line. The refrigerant vapor is fed from the first compressor into the discharge outlet line and into the frosted evaporator through the evaporator refrigerant vapor line, thereby defrosting said frosted evaporator. Also disclosed is a method of defrosting a frosted evaporator using a single, dedicated defrost compressor.

Description

    FIELD OF THE INVENTION
  • The present invention concerns refrigeration systems, more particularly refrigeration defrost systems for defrosting a frosted evaporator. [0001]
  • BACKGROUND OF THE INVENTION
  • Refrigeration systems are well known and widely used in supermarkets and warehouses to refrigerate, or maintain in a frozen state, perishable items, such as foodstuff. [0002]
  • Conventionally, refrigeration systems include a network of refrigeration compressors and evaporators. Refrigeration compressors mechanically compress refrigerant vapors, which are fed from the evaporators, to increase their temperature and pressure. High temperature refrigerant vapors, under high-pressure, are fed to an outdoor air-cooled refrigerant condenser whereupon air, at ambient temperature, absorbs the latent heat from the vapors, as a result the refrigerant vapors liquefy. The liquefied refrigerant is fed through expansion valves, to reduce the temperature and pressure, to the evaporators whereupon the liquefied refrigerant evaporates by absorbing heat from the surrounding foodstuff. [0003]
  • Since most evaporators operate at evaporating refrigerant temperatures that are lower than the freezing point of water (32° F., 0° C.), water vapor from ambient air freezes on the heat transfer surface of the evaporators, which creates a layer of frost on the surface. The frost layer decreases the efficiency of the heat transfer between the evaporator and the ambient air, which causes the temperature of the refrigerated space to increase above the required level. Maintaining the correct temperature of the refrigerated space is vitally important to maintain the quality of the stored food products. To do this, the evaporators must be defrosted regularly in order to re-establish their efficiency. During the defrosting period, the evaporator is out of service. It is therefore important to reduce the duration of the defrost period to avoid excessive rise of the refrigerated space temperature. [0004]
  • Several patents exist that have tried to solve the problem of defrosting a frosted evaporator, including: [0005]
  • U.S. Pat. No. 4,102,151, issued on Jul. 25, 1978, to Kramer et al, for “Hot Gas Defrost System with Dual Function Liquid Line”. [0006]
  • U.S. Pat. No. 5,575,158, issued on Nov. 19, 1996, to Vogel for “Refrigeration Defrost Cycles”. [0007]
  • U.S. Pat. No. 5,056,327, issued on Oct. 15, 1991, to Lammert for “Hot gas Defrost Refrigeration System”. [0008]
  • U.S. Pat. No, 5,050,400, issued on Sep. 24, 1991 to Lammert for “Simplified Hot Gas Defrost Refrigeration System”. [0009]
  • U.S. Pat. No. 6,286,322, issued on Sep. 11, 2001 to Vogel for “Hot gas Refrigeration System”. [0010]
  • The above systems suffer from a number of significant drawbacks such as the use of complex systems of pipes, valves, water tanks, all of which may be difficult to maintain. Disadvantageously, some of the above systems require the addition of a superheater to appropriately route the refrigerant during the defrost cycle, thereby adding to the complexity and cost of the system. [0011]
  • A common method for defrosting a frosted evaporator is the so-called hot refrigerant gas defrost method. Hot, high pressure refrigerant gas from a common discharge manifold or from an upper part of a refrigerant receiver, is fed backwards to the evaporator to be defrosted. The hot refrigerant gas is liquefied during its passage through the evaporator and its latent heat is used to melt the frost on the evaporator surface. The duration of the defrost period is directly proportional to the refrigerant mass flow. The higher the mass flow, the shorter the defrost period will be. [0012]
  • Disadvantageously, the refrigerant mass flow during a defrost cycle depends solely on the condensing pressure of the refrigeration system which, especially during the colder periods of the year, when the possibility to operate with lower condensing pressures and therefore more efficiently is readily available, is economically unacceptable. [0013]
  • Also, the liquid refrigerant obtained during the defrost is returned to the liquid line of the refrigeration system thus having a disruptive effect on the quality of the liquid refrigerant fed to the evaporators in normal operation, for example, so called “flash gas”, higher liquid temperature, and insufficient feeding of the most distant evaporators. [0014]
  • Thus there is a need for a refrigeration system that is simple and inexpensive to operate, and which can be used simultaneously with the normal refrigeration cycle. [0015]
  • SUMMARY OF THE INVENTION
  • The inventor has made a surprising and unexpected discovery that a single, dedicated compressor can be used to defrost a frosted evaporator in a refrigeration system. Moreover, during a defrost cycle, the single compressor operates with considerably higher suction pressure that the rest of the refrigeration compressor thus increasing efficiency and improving power consumption. Advantageously, the liquefied refrigerant is returned to the inlet of the refrigerant air cooled condenser, thus providing efficient cooling of the high pressure hot refrigerant gas before its entry into the refrigerant condenser, which increases the condenser efficiency during high ambient temperature periods of the year and reducing the condensing pressure. Another advantage is that during the cooler periods of the year, the refrigeration defrost system operates with low condensing pressures and provides efficient and rapid defrost cycle. [0016]
  • Also, the compressor avoids the fluctuations of the refrigeration system pressures. During a defrost cycle, a high-pressure refrigerant gas is fed to the suction of the dedicated defrost compressor thus increasing its suction pressure, mass flow and power consumption efficiency. Also during the defrost cycle, the liquid refrigerant is fed through a desuperheating expansion valve to the suction of the dedicated defrost compressor to maintain acceptable suction temperature. [0017]
  • In a first aspect of the present invention, there is provided a refrigeration defrost system including at least one frosted evaporator having an evaporator refrigerant vapor line and an evaporator refrigerant liquid line, said system comprising: a first compressor having a suction inlet line and a discharge outlet line each connected to a discharge manifold, said discharge outlet being connected to said evaporator refrigerant vapor line; and a first pressure regulator valve disposed in a refrigerant bypass passageway between said discharge manifold and said suction inlet line, for feeding refrigerant vapor, when a defrost cycle is required, from said discharge manifold into said suction inlet line, said refrigerant vapor being fed from said first compressor into said discharge outlet line and into said frosted evaporator through said evaporator refrigerant vapor line, thereby defrosting said frosted evaporator. [0018]
  • In another aspect, a refrigeration defrost system, as described above, further includes a condenser having a condenser refrigerant vapor line and a condenser liquid refrigerant line, said condenser liquid refrigeration line being connected to said evaporator liquid refrigeration line, said first pressure regulator valve, during a refrigeration cycle, stops said refrigerant vapor from entering said suction inlet line, said condenser feeding liquid refrigerant into said evaporator liquid refrigerant line and said evaporator refrigerant vapor line feeding refrigerant vapor into said suction inlet line. [0019]
  • In another aspect, a refrigeration defrost system as described above further includes a motorized ball valve disposed in a refrigerant defrost manifold between said discharge outlet line and said evaporator, in series connection with said first pressure regulator valve, for gradually feeding said refrigerant vapor into said evaporator refrigerant vapor line. [0020]
  • In another aspect, a refrigeration defrost system, as described above further includes a first check valve in series connection with said pressure regulator valve for stopping low pressure refrigerant vapor from said evaporator refrigerant vapor line from feeding into said suction inlet line. [0021]
  • Typically, in a refrigeration defrost system, as described above, a T-junction connects said refrigerant bypass passageway with said discharge manifold. The refrigerant bypass passageway further includes a solenoid valve and an expansion valve, in series connection between said suction inlet line and said condenser liquid refrigerant line, for feeding liquid refrigerant from said condenser liquid refrigerant line into said suction inlet line. The expansion valve is a desuperheating expansion valve. [0022]
  • Typically, in a refrigeration defrost system, as described above, in which said condenser further includes a liquid refrigerant return inlet line connected to said evaporator refrigerant liquid line for feeding liquefied refrigerant into said condenser during said defrost cycle. A second check valve is connected between said evaporator refrigerant liquid line and said liquid refrigerant return inlet line. [0023]
  • In another aspect, a refrigeration defrost system, as described above, further includes a second pressure regulator valve disposed in said discharge outlet line, said second pressure regulator valve regulating discharge outlet pressure during said defrost cycle. [0024]
  • Typically, a refrigeration defrost system, as described above, further includes a liquid refrigerant receiver connected between said condenser and said evaporator. [0025]
  • According to a second aspect of the present invention, the refrigeration defrost system further includes: first and second heat exchangers, said first heat exchanger being connected to said discharge manifold, said second heat exchanger being connected to said evaporator; a hot water tank connected to said first and second heat exchangers; and a three-way valve connected between said hot water tank and said first heat exchanger. [0026]
  • Typically, a three-way motorized valve is connected between said first heat exchanger and said discharge manifold, said three-way valve being closed during said defrost cycle, hot water from said hot water tank flowing into said second heat exchanger and into said frosted evaporator to defrost said frosted evaporator. [0027]
  • According to a third aspect of the present invention, there is provided a method of defrosting a frosted evaporator, said method comprising: feeding refrigerant vapor from a discharge manifold into a first compressor suction inlet line; and feeding said refrigerant vapor from said discharge outlet line into an evaporator suction inlet line, thereby defrosting said frosted evaporator. [0028]
  • In another aspect, a method of defrosting a frosted evaporator, as described above, further includes: stopping low pressure refrigerant vapor from entering said compressor suction inlet line.[0029]
  • BRIEF DESCRIPTION OF THE FIGURES
  • Further aspects and advantages of the present invention will become better understood with reference to the description in association with the following Figures, wherein: [0030]
  • FIG. 1 is a schematic diagram of an embodiment of a refrigeration defrost system having multiple evaporators and multiple compressors; [0031]
  • FIG. 2 is a schematic diagram of the refrigeration defrost system of FIG. 1 showing a dedicated defrost compressor; [0032]
  • FIG. 3 is a schematic diagram of a frosted evaporator from FIG. 2 connected to a dedicated compressor for defrosting; and [0033]
  • FIG. 4 is a schematic diagram of another embodiment of the refrigeration defrost system.[0034]
  • DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
  • With reference now to FIGS. 1 and 2, a refrigeration defrost system according to a first embodiment of the invention is generally illustrated at [0035] 10. Broadly speaking, the defrost system 10 includes one or more compressors 12, a refrigeration condenser 14, one or more evaporators 16, a liquid refrigerant receiver 18, a liquid refrigerant pump 20, one or more expansion valves 22, and a network, shown generally at 24 that includes a variety of passageways (or conduits), valves and manifolds, through which the liquid refrigerant pump 20, the evaporators 16, the compressors 12, and the condenser 14 are interconnected to circulate refrigeration fluid.
  • During a refrigeration cycle (or non-defrost cycle), the compressors [0036] 12 compress low-pressure refrigerant vapors from the evaporators 16. Each evaporator 16 includes an evaporator refrigerant vapor line 26 and an evaporator refrigerant liquid line 28. The evaporator vapor line 26 feeds the low-pressure refrigerant vapors through a pressure-regulating valve 30 into a suction manifold 32 and then into the compressors 12. The compressors 12 include a suction inlet line 34 and a discharge outlet line 36. The suction inlet line 34 receives the low pressure refrigerant vapor from the suction manifold 32 and the compressor 12 compresses the low-pressure refrigerant vapor thereby increasing its pressure and temperature and producing hot, high pressure refrigerant vapor. The condenser 14 receives the hot, high pressure refrigerant vapor from the discharge outlet line 36 through an electrically open second pressure regulator valve 37, disposed in the discharge outlet line 36, though a discharge manifold 38 and a conduit 40 which connect the compressors 12 to the condenser 14. The conduit 40 acts as a condenser refrigerant vapor line. In this embodiment, the condenser 14 is an outdoor air-cooled refrigeration condenser that is normally mounted on a roof of a building, although those skilled in the art will recognize that other types of condenser may be used to implement aspects of the invention. The condenser 14 condenses the hot, high pressure refrigerant vapors to produce high pressure liquid refrigerant that feeds through a condensate return conduit 42, which acts as a condenser refrigerant liquid line, to the liquid refrigerant receiver 18. A liquid refrigerant manifold 44 connects the liquid refrigerant pump 20 with the evaporators 16 through each expansion valve 22 and feeds the liquid refrigerant into evaporators 16 through the evaporator refrigerant liquid line 28, thereafter the refrigerant vapor feeds from the evaporator vapor line 26 into the suction manifold 32.
  • Referring now to FIGS. 2 and 3, when a defrosting cycle is required to defrost a frosted evaporator a signal from a refrigeration control system (not shown) isolates and dedicates a single compressor [0037] 11 to defrost a frosted evaporator 13, by energizing open a first pressure regulator valve 46, normally electrically closed during the refrigeration cycle. The valve 46 is disposed in a refrigerant bypass passageway 48 that is connected between the suction inlet line 34 and the discharge manifold 38. A T-junction 50 connects the bypass passageway 48 to the discharge manifold 38. The second pressure regulator valve 37, which is electrically open during the refrigeration cycle, now regulates the discharge outlet pressure. As best illustrated in FIG. 2, the open valve 46 feeds refrigerant vapor from the discharge manifold 38 (in the direction of the arrows) into the suction inlet line 34 along the bypass passageway 48. The refrigerant vapors then feed from the compressor 11 into the discharge outlet line 36. This increases the pressure to a level higher than the pressure in the suction manifold such that a first check valve 52, in series connection with the pressure regulator valve 46, closes to stop low pressure refrigerant vapor from the evaporator refrigerant vapor line 26 from feeding into the suction inlet line 34. The signal from the refrigeration control system causes a motorized ball valve 54 that is disposed in a refrigerant defrost manifold 56 between the discharge outlet line 36 and the evaporator refrigerant vapor line 26, to gradually open towards the manifold 56. This gradual opening of valve 54, in series connection with the valve 46 and the manifold 38, gradually feeds refrigerant vapor from the discharge outlet line 36 towards the frosted evaporator 13 through the evaporator refrigerant vapor line 26. The gradual opening of the valve 54 prevents the occurrence of thermal and mechanical stress in the evaporators during the defrost cycle. The increased suction pressure at the dedicated compressor 11 provides up to 70% higher mass flow, which ensures accelerated defrost cycles. The refrigerant defrost manifold 56 is in series connection with the pressure regulator valve 46 and the discharge outlet line 36.
  • As best illustrated in FIG. 3, the hot, high pressure refrigerant vapor feeds from the refrigerant defrost manifold [0038] 56 into the frosted evaporator 13 through a solenoid valve 58 and into the evaporator 13 through the evaporator vapor line 26. Normally, during the refrigeration cycle, the evaporator vapor line 26 feeds low pressure vapor into the suction inlet line 34 via the suction manifold 32. In the defrost cycle, the low pressure evaporator vapor line 26 receives the hot, high pressure refrigerant from the discharge outlet line 36. The hot, high pressure refrigerant vapor defrosts the frosted evaporator 13 and converts the high pressure vapor into liquid refrigerant which exits the evaporator 13 through a check valve 59 and the evaporator liquid refrigerant line 28.
  • Referring to FIGS. 1 and 2, normally during the refrigeration cycle, the evaporator liquid refrigerant line [0039] 28 receives liquid refrigerant from the liquid refrigerant receiver 18 along the liquid refrigerant manifold 44. During the defrost cycle, liquid condensate (liquid refrigerant) from the defrosted evaporator via the evaporator refrigerant liquid line 28 enters a defrost condensate return manifold 60 through a second solenoid valve 61 and into a liquid refrigerant return inlet line 62 with sufficient pressure to feed it into the condenser 14.
  • Referring to FIG. 2, when the refrigeration system control opens the valve [0040] 46, a solenoid valve 64 opens and feeds liquid refrigerant from the liquid refrigerant manifold 44 into the suction inlet line 34 via an expansion valve 66. The solenoid valve 64 and the expansion valve 66 are disposed in the refrigerant bypass passageway 48 and are in series connection between the suction inlet line 34 and the liquid refrigerant manifold 44. The expansion valve 66 is a so-called desuperheating expansion valve and is used to maintain the temperature at an acceptable level at the suction inlet line 34 by allowing liquid refrigerant to mix with hot, high pressure refrigerant vapor at the suction inlet line 34 of the compressor 11 during the defrost cycle.
  • After the frosted evaporator [0041] 13 is defrosted, the pressure regulator valve 46 closes to reestablish the compressor 11 as a non-defrost compressor 12 for normal refrigeration operation as described above.
  • One skilled in the art will recognize that the single dedicated compressor [0042] 11 may be used to defrost more than one frosted evaporator. This can be achieved by controlling the hot, high pressure refrigerant's pathway from the refrigerant defrost manifold 56 into multiple frosted evaporators via each frosted evaporator's vapor line.
  • In another embodiment, a source of heat may be used to increase the suction pressure of the single dedicated defrost compressor [0043] 11 during the defrost cycle. As best illustrated in FIG. 4, an additional circuit is added to the existing system 10 and includes a hot water tank 74, a three-way motorized valve 68, a pump 76 and two heat exchangers 72, 86, all interconnected by a number of conduits 70, 80, 82, 84, and 85. During the normal refrigeration cycle, the hot, high pressure refrigerant vapors flow from the compressors 11 and 12 though the three way valve 68 along the conduit 70 to the first heat exchanger 72. The pump 76 feeds water from the water tank 74 through a motorized valve 78 and along the conduit 80 to the heat exchanger 72. The hot water from the first heat exchanger 72 is fed through the conduit 82 back to water tank 74. The refrigerant leaving the heat exchanger 72 is fed through the conduits 38 and 40 to the external air-cooled condenser 14. When the water temperature in the water tank 74 reaches a predetermined value, the three-way valve 68 closes the conduit 70 and opens the conduit 38, which allows the hot, high pressure refrigerant vapors to flow to the air-cooled condenser 14, thereby by-passing the first heat exchanger 72.
  • When a defrost is required, the refrigeration control system signals the motorized valve [0044] 78 to close the conduit 80 and open the conduit 84, which allows the hot water to flow through the second heat exchanger 86. At this point, the pressure-regulating valve 37 will be de-energized and will maintain the discharge pressure of compressor 11 at higher level than the pressure in the discharge manifold 38. The motorized valve 54 will open the conduit 56 allowing the hot high-pressure refrigerant vapors from the compressor 11 to flow towards the refrigerant circuit and the evaporator to be defrosted. In this mode, the second heat exchanger 86 operates as an evaporator for the compressor 11, such that the heat from the hot water will be absorbed by the second heat exchanger 86 and then used to defrost the frosted evaporator. The amount of water in the water tank 74 and the temperature at which the water should be maintained will depend on the amount of heat required to defrost the frosted evaporator.

Claims (15)

    I claim:
  1. 1. A refrigeration defrost system including at least one frosted evaporator having an evaporator refrigerant vapor line and an evaporator refrigerant liquid line, said system comprising:
    a) a first compressor having a suction inlet line and a discharge outlet line each connected to a discharge manifold, said discharge outlet being connected to said evaporator refrigerant vapor line; and
    b) a first pressure regulator valve disposed in a refrigerant bypass passageway between said discharge manifold and said suction inlet line, for feeding refrigerant vapor, when a defrost cycle is required, from said discharge manifold into said suction inlet line, said refrigerant vapor being fed from said first compressor into said discharge outlet line and into said frosted evaporator through said evaporator refrigerant vapor line, thereby defrosting said frosted evaporator.
  2. 2. The refrigeration defrost system, according to claim 1, further includes a condenser having a condenser refrigerant vapor line and a condenser liquid refrigerant line, said condenser liquid refrigeration line being connected to said evaporator liquid refrigeration line, said first pressure regulator valve, during a refrigeration cycle, stops said refrigerant vapor from entering said suction inlet line, said condenser feeding liquid refrigerant into said evaporator liquid refrigerant line and said evaporator refrigerant vapor line feeding refrigerant vapor into said suction inlet line.
  3. 3. The refrigeration defrost system, according to claim 1, further includes a motorized ball valve disposed in a refrigerant defrost manifold between said discharge outlet line and said evaporator, in series connection with said first pressure regulator valve, for gradually feeding said refrigerant vapor into said evaporator refrigerant vapor line.
  4. 4. The refrigeration defrost system, according to claim 1, further includes a first check valve in series connection with said first pressure regulator valve for stopping low pressure refrigerant vapor from said evaporator refrigerant vapor line from feeding into said suction inlet line.
  5. 5. The refrigeration defrost system, according to claim 1, in which a T-junction connects said refrigerant bypass passageway with said discharge manifold.
  6. 6. The refrigeration defrost system, according to claim 5, in which said refrigerant bypass passageway further includes a solenoid valve and an expansion valve, in series connection between said suction inlet line and said condenser liquid refrigerant line, for feeding liquid refrigerant from said condenser liquid refrigerant line into said suction inlet line.
  7. 7. The refrigeration defrost system, according to claim 6, in which said expansion valve is a desuperheating expansion valve.
  8. 8. The refrigeration defrost system, according to claim 2, in which said condenser further includes a liquid refrigerant return inlet line connected to said evaporator refrigerant liquid line for feeding liquefied refrigerant into said condenser during said defrost cycle.
  9. 9. The refrigeration defrost system, according to claim 8, in which a second check valve is connected between said evaporator refrigerant liquid line and said liquid refrigerant return inlet line.
  10. 10. The refrigeration defrost system, according to claim 1, further includes a second pressure regulator valve disposed in said discharge outlet line, said second pressure regulator valve regulating discharge outlet pressure during said defrost cycle.
  11. 11. The refrigeration defrost system, according to claim 1, further includes a liquid refrigerant receiver connected between said condenser and said evaporator.
  12. 12. The refrigeration defrost system according to claim 1, further includes:
    a) first and second heat exchangers, said first heat exchanger being connected to said discharge manifold, said second heat exchanger being connected to said evaporator;
    b) a hot water tank connected to said first and second heat exchangers; and
    c) a three-way valve connected between said hot water tank and said first heat exchanger.
  13. 13. The refrigeration defrost system, according to claim 12, in which a three-way motorized valve is connected between said first heat exchanger and said discharge manifold, said three-way valve being closed during said defrost cycle, hot water from said hot water tank flowing into said second heat exchanger and into said frosted evaporator to defrost said frosted evaporator.
  14. 14. A method of defrosting a frosted evaporator, said method comprising:
    a) feeding refrigerant vapor from a discharge manifold into a first compressor suction inlet line; and
    b) feeding said refrigerant vapor from said discharge outlet line into an evaporator suction inlet line, thereby defrosting said frosted evaporator.
  15. 15. A method of defrosting a frosted evaporator, according to claim 14, further including:
    c) stopping low pressure refrigerant vapor from entering said compressor suction inlet line.
US10420723 2003-04-23 2003-04-23 Refrigeration defrost system Active US6807813B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US10420723 US6807813B1 (en) 2003-04-23 2003-04-23 Refrigeration defrost system

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US10420723 US6807813B1 (en) 2003-04-23 2003-04-23 Refrigeration defrost system
CA 2433955 CA2433955C (en) 2003-04-23 2003-07-11 Refrigeration defrost system

Publications (2)

Publication Number Publication Date
US6807813B1 US6807813B1 (en) 2004-10-26
US20040211195A1 true true US20040211195A1 (en) 2004-10-28

Family

ID=33159406

Family Applications (1)

Application Number Title Priority Date Filing Date
US10420723 Active US6807813B1 (en) 2003-04-23 2003-04-23 Refrigeration defrost system

Country Status (2)

Country Link
US (1) US6807813B1 (en)
CA (1) CA2433955C (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007069279A1 (en) * 2005-12-12 2007-06-21 Giuseppe Floris Energy saving chiller

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7610766B2 (en) * 2002-07-08 2009-11-03 Dube Serge High-speed defrost refrigeration system
US20050126198A1 (en) * 2003-12-12 2005-06-16 Marchand Jeffrey J. Refrigeration system with reverse flow defrost
US7197886B2 (en) * 2005-04-12 2007-04-03 Lesage Gaetan Heat reclaim refrigeration system and method
CN101248321A (en) * 2005-06-23 2008-08-20 卡里尔公司 Method for defrosting evaporator of refrigeration circuit
US7401473B2 (en) * 2005-09-26 2008-07-22 Systems Lmp Inc. Dual refrigerant refrigeration system and method
US8789380B2 (en) * 2009-07-20 2014-07-29 Systemes Lmp Inc. Defrost system and method for a subcritical cascade R-744 refrigeration system
GB0921315D0 (en) 2009-12-05 2010-01-20 Lemay Patrick An improved opened geothermal energy system
US9194615B2 (en) 2013-04-05 2015-11-24 Marc-Andre Lesmerises CO2 cooling system and method for operating same
EP3047218A1 (en) * 2013-09-19 2016-07-27 Carrier Corporation Refrigeration circuit with heat recovery module

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4158950A (en) * 1978-02-16 1979-06-26 General Electric Company Heat pump defrost system

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4009594A (en) 1975-06-02 1977-03-01 Whirlpool Corporation Hot gas defrosting apparatus
US4083195A (en) 1976-04-20 1978-04-11 Kramer Trenton Company Refrigerating and defrosting system with dual function liquid line
JPS6054578B2 (en) * 1978-02-02 1985-11-30 Sanyo Denki Kk
US4279129A (en) 1978-10-02 1981-07-21 Carrier Corporation Hot gas defrost system
US4318277A (en) 1978-10-02 1982-03-09 Carrier Corporation Non-reverse hot gas defrost system
US4602485A (en) 1983-04-23 1986-07-29 Daikin Industries, Ltd. Refrigeration unit including a hot gas defrosting system
US4914926A (en) 1987-07-29 1990-04-10 Charles Gregory Hot gas defrost system for refrigeration systems and apparatus therefor
US4949551A (en) 1989-02-06 1990-08-21 Charles Gregory Hot gas defrost system for refrigeration systems
US5056327A (en) 1990-02-26 1991-10-15 Heatcraft, Inc. Hot gas defrost refrigeration system
US5050400A (en) 1990-02-26 1991-09-24 Bohn, Inc. Simplified hot gas defrost refrigeration system
US5065584A (en) 1990-07-30 1991-11-19 U-Line Corporation Hot gas bypass defrosting system
US5315836A (en) 1993-01-15 1994-05-31 Mccormack Manufacturing Co., Inc. Air cooling unit having a hot gas defrost circuit
US5551250A (en) 1994-09-08 1996-09-03 Traulsen & Co. Inc. Freezer evaporator defrost system
US5575158A (en) 1994-10-05 1996-11-19 Russell A Division Of Ardco, Inc. Refrigeration defrost cycles
US5887440A (en) 1996-09-13 1999-03-30 Dube; Serge Refrigeration coil defrost system
US5867993A (en) 1997-09-08 1999-02-09 Dube; Serge Refrigerant reservoir and heat exchanger unit for a refrigerated counter system
US6286322B1 (en) 1998-07-31 2001-09-11 Ardco, Inc. Hot gas defrost refrigeration system

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4158950A (en) * 1978-02-16 1979-06-26 General Electric Company Heat pump defrost system

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007069279A1 (en) * 2005-12-12 2007-06-21 Giuseppe Floris Energy saving chiller

Also Published As

Publication number Publication date Type
CA2433955A1 (en) 2004-10-23 application
CA2433955C (en) 2009-01-27 grant
US6807813B1 (en) 2004-10-26 grant

Similar Documents

Publication Publication Date Title
US3332251A (en) Refrigeration defrosting system
US3392541A (en) Plural compressor reverse cycle refrigeration or heat pump system
US6343482B1 (en) Heat pump type conditioner and exterior unit
US5157933A (en) Transport refrigeration system having means for achieving and maintaining increased heating capacity
USRE29966E (en) Heat pump with frost-free outdoor coil
US4646539A (en) Transport refrigeration system with thermal storage sink
US5743102A (en) Strategic modular secondary refrigeration
US5406805A (en) Tandem refrigeration system
US4363218A (en) Heat pump using solar and outdoor air heat sources
US5435148A (en) Apparatus for maximizing air conditioning and/or refrigeration system efficiency
US6393851B1 (en) Vapor compression system
US5056324A (en) Transport refrigeration system having means for enhancing the capacity of a heating cycle
US20090120117A1 (en) Refrigeration system
US4711094A (en) Reverse cycle heat reclaim coil and subcooling method
US4903495A (en) Transport refrigeration system with secondary condenser and maximum operating pressure expansion valve
US5694782A (en) Reverse flow defrost apparatus and method
US6170270B1 (en) Refrigeration system using liquid-to-liquid heat transfer for warm liquid defrost
US5727393A (en) Multi-stage cooling system for commerical refrigeration
US6502412B1 (en) Refrigeration system with modulated condensing loops
US4912933A (en) Transport refrigeration system having means for enhancing the capacity of a heating cycle
US4748818A (en) Transport refrigeration system having means for enhancing the capacity of a heating cycle
US20080041079A1 (en) Refrigerant cycle device with ejector
US5692387A (en) Liquid cooling of discharge gas
US3766745A (en) Refrigeration system with plural evaporator means
US4197716A (en) Refrigeration system with auxiliary heat exchanger for supplying heat during defrost cycle and for subcooling the refrigerant during a refrigeration cycle

Legal Events

Date Code Title Description
FPAY Fee payment

Year of fee payment: 4

FPAY Fee payment

Year of fee payment: 8

FPAY Fee payment

Year of fee payment: 12