USRE29966E - Heat pump with frost-free outdoor coil - Google Patents
Heat pump with frost-free outdoor coil Download PDFInfo
- Publication number
- USRE29966E USRE29966E US05/831,032 US83103277A USRE29966E US RE29966 E USRE29966 E US RE29966E US 83103277 A US83103277 A US 83103277A US RE29966 E USRE29966 E US RE29966E
- Authority
- US
- United States
- Prior art keywords
- fins
- heating
- heat exchanger
- compressor
- indoor
- 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.)
- Expired - Lifetime
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
- F25D21/06—Removing frost
- F25D21/08—Removing frost by electric heating
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/006—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing frost
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
- F25D21/04—Preventing the formation of frost or condensate
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General 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
- F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started
Definitions
- compressed refrigerant is evaporated in an outdoor evaporation coil, the expanded refrigerant being thereafter compressed and passed through a condenser which extracts heat from the compressed refrigerant for heating the interior of a building.
- the refrigeration cycle is reversed and the system used as an air conditioner.
- Heat pumps of this type which are installed in cold climates must operate at outdoor air temperatures below 32° F. and sometimes as low as -20° F. Under these conditions, the evaporating temperature of the refrigerant in the outdoor coil drops to a point at which the coefficient of performance of the heating system is unreasonably low.
- a new and improved heat pump system which overcomes the disadvantages of prior art systems in that it allows continuous system operation at an economically practical coefficient of performance and completely eliminates the need for periodic reverse defrost operations regardless of outdoor ambient temperature or humidity. Additionally, the system of the invention incorporates means to permit the system to function immediately upon changeover to the heating cycle from a cooling cycle even though the pressure in the receiver of the system may initially exceed that in the indoor coil. A still further feature of the invention resides in the provision of means for protecting the compressor from liquid floodback when reversal occurs from the heating cycle to the cooling cycle.
- two outdoor heat exchangers are provided, one of which is used as a condenser (heat sink) during a summer cooling cycle while the other is utilized as the evaporator (heat source) for a heating cycle.
- a condenser heat sink
- evaporator heat source
- its surface temperature is always maintained above 32° F. by means of an electrical resistance heating element which is in intimate thermal contact with the fins of the coil whereby heat is transferred from the heating element or elements to the fins by conduction in contrast to prior art systems wherein radiation was relied upon.
- the electrical resistance heating coil can be controlled by means of a thermistor which senses the surface temperature of the outdoor coil fins or by means of a pressure switch which senses a drop in pressure at the output of the outdoor evaporator coil. In this manner, it is possible to operate at evaporating temperatures of +20° F. or higher so that a coefficient of performance of not less than 4.5 can be anticipated.
- refrigerant from the receiver is permitted to flow through the heat source outdoor coil for a short period of time, usually about 2 minutes, at the beginning of the heating cycle.
- condensing pressure in the indoor coil is permitted to build up while the liquid pressure in the receiver falls.
- a sufficient refrigerant charge is provided from the receiver to the active heating circuit.
- FIG. 1 is a schematic view of the entire heat pump system of the invention
- FIG. 2 illustrates one manner in which resistance heating elements may be disposed in intimate thermal contact with the fins of an outdoor evaporator
- FIG. 3 is a partial schematic diagram of the system of the invention showing the cooling cycle
- FIG. 4 is a partial schematic diagram of the system of the invention showing the heating cycle
- FIG. 5 is a schematic diagram showing the operation of the system of the invention immediately prior to changeover from a heating to a cooling cycle
- FIG. 6 is a schematic electrical circuit diagram showing the controls for the valves, fans, motors and other elements of the system of FIG. 1.
- the system shown includes a compressor 10 of conventional construction having an input or suction intake 12 and an output or discharge side 14.
- the compressor discharge 14 is connected through a conduit 16 to the inlet side of a first outdoor heat exchanger 20 which acts as a condenser during a normal refrigeration cycle.
- the heat exchanger 20 is provided with a motor-driven cooling fan 22 in accordance with usual practice.
- the exit side of the heat exchanger 20 is connected through a check valve 24 to a receiver 26.
- the receiver 26, in turn, is connected through a cut-off valve 28, a solenoid operated shut-off valve 30 and conduit 80 to an expansion device 32 connected to the inlet side of an indoor heat exchanger 34 again provided with a motor-driven fan 36.
- the outlet side of the indoor heat exchanger is connected through a three-way solenoid-operated valve 38 and through a pressure regulating valve 40 back to the inlet side 12 of the compressor 10. It will be appreciated that the system just described is a normal air-conditioning refrigeration system wherein the indoor heat exchanger 34 acts as an evaporator and the outdoor heat exchanger 20 acts as a condenser.
- the heat sink coil 20 is not used. Rather, a heat source outdoor coil 42 is employed. Coil 42 is again provided with a motor-driven fan 44 as shown, although it should be understood that a single fan may be used for both fans 22 and 44 shown herein.
- valve 38 is reversed so as to connect the pressure side 14 of the condenser 10 through a solenoid-operated valve 46, conduit 48 and valve 38 to the outlet side of the indoor heat exchanger 34.
- Refrigerant forced into the coil of heat exchanger 34 will now flow through a check valve 50 and a solenoid-operated valve 52, which is opened during a heating cycle, to an expansion valve 54 connected to the inlet of the heat source heat exchanger 42.
- the solenoid-operated valve 30 is initially maintained open at the beginning of a heating cycle to permit refrigerant to flow from the receiver 26 to the heat source coil 42; and is thereafter closed.
- the outlet side of the heat exchanger 42 is connected through a conduit 56 back to the inlet side 12 of compressor 10 through pressure-regulating valve 40.
- refrigerant will first flow through the indoor coil or heat exchanger 34 via valves 46 and 38; whereupon the heat of the refrigerant is transferred to the indoor atmosphere by the fan 36.
- the compressed refrigerant flows through check valve 50 and open solenoid valve 52 to the expansion device 54 at the second outdoor heat exchanger or heat source 42 where the refrigerant expands, thereby absorbing heat.
- the expanded refrigerant is then returned back to the inlet side of the compressor 10 via the conduit 56.
- an electrical resistance heating means 60 is provided in intimate contact with the fins 62 of the heat exchanger 42 whereby heat from the resistance heater will be transferred to the fins by conduction.
- the resistance heater 60 may be connected to a power source 64 through normally-open contacts 66 of a relay 68.
- the relay 68 is controlled by a thermistor 70 or the like in contact with the fins 62, the arrangement being such that when the temperature falls to 32° F., the current through the thermistor 70 will increase to the point where relay 68 is energized, thereby connecting the power source 64 to the heater 60.
- the thermistor 70 can be connected to additional control circuitry, not shown herein for purposes of simplicity, or can be used to control an SCR power supply for the heater 60.
- additional control circuitry not shown herein for purposes of simplicity, or can be used to control an SCR power supply for the heater 60.
- it instead of controlling the resistance heater 60 by means of the thermistor 70, it also can be controlled by means of a pressure switch 72 connected to the outlet side of the heat exchanger 42, the arrangement being such that when the pressure of the refrigerant falls as a result of falling ambient air temperature, the switch 72 will close to energize the heating element 60.
- FIG. 2 One possible arrangement for placing the heating element 60 in contact with the fins of the heat exchanger 42 is shown in detail in FIG. 2.
- Winding through the fins 62 is a serpentine coil 74.
- a plurality of electrical resistance heaters 76 is disposed throughout the length of the heat exchanger 42 in thermal contact with the surfaces of fins 62 and in-between the turns of the coil 74. These, then, are all adapted to be connected in parallel to the common power source 64 via lead 78.
- FIG. 3 The flow of refrigerant through the system during a normal cooling cycle is shown in FIG. 3. Valves 52 and 46 are closed at this time; solenoid valve 38 is in the position shown so as to connect the inlet side 12 of the compressor 10 to the outlet of the indoor coil 34; and valve 30 is open. Under these circumstances, refrigerant from the outlet side of the compressor 10 flows along the direction the arrows through the heat exchanger 20, which now acts as a condenser, the receiver 26, open valve 30, expansion device 32, and the indoor heat exchanger 34 which now acts as an evaporator back to the compressor through valves 38 and 40. This, of course, is a conventional and normal refrigeration cycle.
- the valve 30 is maintained open at onset of the heating cycles for a predetermined short period of time during which liquid refrigerant is permitted to flow from receiver 26 through open valve 52, expansion valve 54, heat source coil 42 and conduit 56 back to the inlet 12 of the compressor 10, thereby forming a complete cycle.
- this short period which typically may be set for 2 minutes, the condensing pressure in the indoor coil 34 is permitted to build up while the liquid pressure in receiver 26 falls. At the same time, a sufficient refrigerant charge is provided for the active heating circuit.
- the liquid solenoid valve 30 closes and liquid refrigerant condensed in the indoor coil 34 is now free to flow through check valve 50 and open valve 52 to the heat source coil 42.
- the suction pressure regulating valve 40 is provided and is adjusted for an outlet pressure not to exceed the maximum suction pressure for which the particular compressor is designed.
- the invention incorporates means for protecting the compressor from liquid floodback when changeover occurs from the heating cycle to the cooling cycle.
- Conditions which exist during the pump-down operation before changeover to cooling are illustrated in FIG. 5.
- the liquid solenoid valve 30 and the suction shut-off valve 38 are still in the position shown in FIG. 4 for the heating cycle.
- a changeover pressure switch hereinafter described, permits the hot gas solenoid valve 46 to close but prevents the liquid solenoid valve 30 from opening until the pressure in the indoor coil 34 has been reduced to a predetermined low value, indicating that no liquid has remained in the indoor coil 34.
- the electrical control for the refrigerant system just described is shown in FIG. 6. It includes two power leads 82 and 84 connected to a source of potential, now shown.
- the control operation will first be explained for the cooling cycle as shown in FIG. 3.
- the changeover pump-down switch CH is in the "low” position.
- Switch CH is in the low position when the pressure in indoor coil 34 is below a predetermined value and in the "hi" position when the pressure is above that value.
- a thermostat CT makes contact, thereby energizing the liquid line solenoid valve 30. This causes an increase in pressure in the evaporator 34, which is transmitted to a low pressure cutout LPC which closes, thereby energizing the compressor motor contactor C.
- An auxiliary interlock contact C-1 of contactor C energizes the condenser fan contactor CFC, thereby energizing the fan 22 of FIG. 1 providing that the condenser pressure switch FCC is closed.
- the switch FCC will be open upon start-up; however it will eventually close after the compressor has operated for a short period of time and an adequate condenser pressure has been built up to close the switch FCC.
- All other controls shown in FIG. 6 to the right of a heating thermostat MHS are deenergized and inactive during the cooling cycle.
- Suction shut-off valve 38 and solenoid valve 52 are deenergized and assume the positions shown in FIG. 3 since the changeover switch CH is in the low position and the contactor C3 is deenergized such that contacts C3-1 are open.
- heating thermostat MHS makes contact, thereby energizing contactor C3 which closes contacts C3-1. This reverses the position of suction cut-off valve 38 and energizes solenoid valve 52 to open the same.
- current is supplied to a time delay relay TD; however it is not actuated for a period of about 2 minutes.
- contacts C3-2 are closed to complete a circuit to solenoid valve 30 through normally-closed contacts TD-1 of the time delay relay TD and contacts C3-1.
- solenoid valve 30 remains open at this time and feeds liquid refrigerant through solenoid valve 52 which is also open at the same time to heat source coil 42 and back to the suction line, raising the suction pressure sufficiently to actuate the switch LPC which, in turn, energizes the compressor contactor C.
- Contactor FSC is also energized at the onset of the heating cycle so that the contactor CFD is energized to energize or start the motor for heat source fan 44 through contacts C-2 of contactor C and contacts FSC-1 of contactor FSC which is also energized.
- time delay relay TD deenergizes, thereby opening contacts TD-1 and deenergizing or closing the solenoid valve 30.
- the discharge pressure in indoor coil 34 has been raised sufficiently to condense liquid in this coil and feed it through check valve 50, open solenoid valve 52, expansion valve 54, outdoor heat source coil 42 and conduit 56 back to the compressor 10 from where the refrigerant is discharged through the open solenoid valve 46 and valve 38 back to the indoor coil 34, completing the cycle.
- Changeover switch CH has now switched to the high position since the refrigerant pressure in the indoor coil 34 has been raised sufficiently to cause this action. If the ambient temperature at the outdoor coil drops near 32°, thermostat LAT (schematically illustrated as thermistor 70 in FIG. 1) will make contact, thereby energizing heating contactor HC which will close contacts HC-1. Now, current flows from the heating thermostat MHS through an air-flow switch contact AFS which is maintained closed by the outdoor coil fan 44 to the contactor 68 for the heating coil 60 which transmits heat to the surface of the fins 62.
- thermostat LAT Schematically illustrated as thermistor 70 in FIG. 1
- the heating thermostat MHS breaks contact, thereby deenergizing the contactors HC and 68 for heating coil 60 as well as the hot gas valve 46 so that the supply of refrigerant to the indoor coil 34 is interrupted. Since the compressor 10 continues to operate temporarily, both the indoor coil 34 and the heat source coil 42 will shortly be evacuated, causing the pressure at the compressor suction intake to drop below the setting of low pressure switch LPC. This switch now breaks, deenergizing the compressor contactor C and through its interlock contacts C-2 the outdoor heat source fan contactor CFD.
- the changeover switch CH After the indoor coil 34 and heat source coil 42 are fully evacuated, the changeover switch CH will switch to its low position, deenergizing heat source solenoid valve 52 and suction line valve 38, restoring them to their positions shown in FIG. 3. If, on the other hand, the changeover from the heating cycle to the cooling cycle takes place suddenly and before the changeover pump-down switch has reached its low position, refrigerant flow temporarily will proceed through coils 34 and 42 as shown in FIG. 5 (since valves 38 and 52 are still energized) until the indoor coil has been fully evacuated and the changeover switch has been signaled to switch to its low position.
Abstract
Description
Claims (4)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US435673A US3918268A (en) | 1974-01-23 | 1974-01-23 | Heat pump with frost-free outdoor coil |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US435673A Reissue US3918268A (en) | 1974-01-23 | 1974-01-23 | Heat pump with frost-free outdoor coil |
Publications (1)
Publication Number | Publication Date |
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USRE29966E true USRE29966E (en) | 1979-04-17 |
Family
ID=23729321
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US435673A Expired - Lifetime US3918268A (en) | 1974-01-23 | 1974-01-23 | Heat pump with frost-free outdoor coil |
US05/831,032 Expired - Lifetime USRE29966E (en) | 1974-01-23 | 1977-09-06 | Heat pump with frost-free outdoor coil |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US435673A Expired - Lifetime US3918268A (en) | 1974-01-23 | 1974-01-23 | Heat pump with frost-free outdoor coil |
Country Status (1)
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US (2) | US3918268A (en) |
Cited By (24)
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US20050204757A1 (en) * | 2004-03-18 | 2005-09-22 | Michael Micak | Refrigerated compartment with controller to place refrigeration system in sleep-mode |
US20080209925A1 (en) * | 2006-07-19 | 2008-09-04 | Pham Hung M | Protection and diagnostic module for a refrigeration system |
US20090071175A1 (en) * | 2007-09-19 | 2009-03-19 | Emerson Climate Technologies, Inc. | Refrigeration monitoring system and method |
US20100077779A1 (en) * | 2006-12-16 | 2010-04-01 | Star Refrigeration Limited | Air-source heat pump |
US20100111709A1 (en) * | 2003-12-30 | 2010-05-06 | Emerson Climate Technologies, Inc. | Compressor protection and diagnostic system |
US7878006B2 (en) | 2004-04-27 | 2011-02-01 | Emerson Climate Technologies, Inc. | Compressor diagnostic and protection system and method |
US20110112814A1 (en) * | 2009-11-11 | 2011-05-12 | Emerson Retail Services, Inc. | Refrigerant leak detection system and method |
US20110132588A1 (en) * | 2009-11-23 | 2011-06-09 | Icecode, Llc | System and Method for Energy-Saving Inductive Heating of Evaporators and Other Heat-Exchangers |
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US20120291472A1 (en) * | 2009-11-30 | 2012-11-22 | Mitsubishi Electric Corporation | Air-conditioning apparatus |
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US9765979B2 (en) | 2013-04-05 | 2017-09-19 | Emerson Climate Technologies, Inc. | Heat-pump system with refrigerant charge diagnostics |
US9823632B2 (en) | 2006-09-07 | 2017-11-21 | Emerson Climate Technologies, Inc. | Compressor data module |
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US10914503B2 (en) | 2018-02-01 | 2021-02-09 | Johnson Controls Technology Company | Coil heating systems for heat pump systems |
Families Citing this family (25)
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SE395175B (en) * | 1975-08-05 | 1977-08-01 | Stal Laval Turbin Ab | ENERGY UNIT FOR SUPPLY OF DISTRICT HEATING SYSTEM |
US4065938A (en) * | 1976-01-05 | 1978-01-03 | Sun-Econ, Inc. | Air-conditioning apparatus with booster heat exchanger |
US4299095A (en) * | 1979-08-13 | 1981-11-10 | Robertshaw Controls Company | Defrost system |
JPS57202462A (en) * | 1981-06-05 | 1982-12-11 | Mitsubishi Electric Corp | Air conditioner |
US4409796A (en) * | 1982-03-05 | 1983-10-18 | Rutherford C. Lake, Jr. | Reversible cycle heating and cooling system |
US4493193A (en) * | 1982-03-05 | 1985-01-15 | Rutherford C. Lake, Jr. | Reversible cycle heating and cooling system |
US4553401A (en) * | 1982-03-05 | 1985-11-19 | Fisher Ralph H | Reversible cycle heating and cooling system |
US4785639A (en) * | 1986-05-20 | 1988-11-22 | Sundstrand Corporation | Cooling system for operation in low temperature environments |
DE3635604C2 (en) * | 1986-10-20 | 1998-07-02 | Leybold Ag | Method for carrying out maintenance work on a refrigerator, device and refrigerator for carrying out the method |
US4761964A (en) * | 1986-10-22 | 1988-08-09 | Pacheco Jerry J | Apparatus for enhancing the performance of a heat pump and the like |
US5109677A (en) * | 1991-02-21 | 1992-05-05 | Gary Phillippe | Supplemental heat exchanger system for heat pump |
US5163304A (en) * | 1991-07-12 | 1992-11-17 | Gary Phillippe | Refrigeration system efficiency enhancer |
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US11879673B2 (en) * | 2018-07-17 | 2024-01-23 | United Electric Company. L.P. | Refrigerant charge control system for heat pump systems |
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Cited By (64)
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US7152415B2 (en) | 2004-03-18 | 2006-12-26 | Carrier Commercial Refrigeration, Inc. | Refrigerated compartment with controller to place refrigeration system in sleep-mode |
US20050204757A1 (en) * | 2004-03-18 | 2005-09-22 | Michael Micak | Refrigerated compartment with controller to place refrigeration system in sleep-mode |
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