US3068661A

US3068661A - Defrosting arrangement for heat pump

Info

Publication number: US3068661A
Application number: US40946A
Authority: US
Inventors: William L Mcgrath
Original assignee: Carrier Corp
Current assignee: Carrier Corp
Priority date: 1960-07-05
Filing date: 1960-07-05
Publication date: 1962-12-18
Anticipated expiration: 1979-12-18

Description

Dec. 18, 1962 INDOOR COIL w. L. MCGRATH 3,068,661

DEFROSTING ARRANGEMENT FOR HEAT PUMP Filed July 5. 1960 OUTDOOR l con.

INVENTOR. WILLIAM L. MC GRATH ATTORNEY.

ttes

Filed 3:15;] 5, 1961), Ser. No. 40,946 2 Claims. (Cl. 62-156) This invention relates broadly to air conditioning equipment. More particularly, this invention relates to air conditioning equipment employing a refrigeration system operable under the reverse cycle principle. Units of this type are generally known as heat pumps and are operable to supply either cooled or Warm air to an enclosure being served by the air conditioning unit.

In heat pumps of the air-to-air type, heat is extracted from one source of air and rejected to another. When the heat pump is employed to supply heated air to an enclosure, heat extracted from a source of air flowing over an outdoor heat transfer coil is rejected to a stream of air flowing over a heat transfer coil located inside the enclosure being treated. Under circumstances where the ambient temperature is substantially reduced, the amount of heat in the outdoor air is likewise relatively reduced. The heat pump operates, however, to lower the temperature of the outdoor coil sufficiently so that heat will flow from the outdoor air to the refrigerant within the coil. In reducing the temperature of the coil to a value such that a continued flow of heat will ensue, the outdoor coil may become frosted. This is true because the evaporator temperature is below the freezing point of water and moisture in the air stream flowing over the coil is deposited on the surface of the coil and frozen thereon.

Various arrangements have been suggested for periodically removing the coating of frost from the outdoor coil in a heat pump of the type under consideration so that efiicient operation of the outdoor heat exchanger will continue. One of the more common arrangements proposed involves reversing the refrigerant flow so that the unit temporarily reverts to cooling cycle operation. Thus hot gaseous refrigerant flows from the compressor to the outdoor coil while the indoor coil temporarily functions as an evaporator. Such an arrangement may cause inconvenience to occupants of the enclosure if the defrosting period is of considerable duration for the reason that relatively cool air is being supplied to the enclosure under circumstances where warm air is needed to maintain comfortable conditions.

The chief object of this invention is the provision of an improved arrangement for defrosting an outdoor coil of a heat pump operating under heating conditions which includes means for temporarily loading the evaporator coil during the period that defrosting occurs. The loading of the evaporator coil occurs in the interest of reducing the defrosting period by providing a relatively high evaporator pressure during the defrosting period.

Another object of the invention is an improved method of defrosting a frost accumulating coil employed as a component in a heat pump.

Other objects and features of the invention will be apparent upon a consideration of the ensuing specification and drawings in which:

FIGURE 1 is a diagrammatic view of a heat punTp equipped with the defrosting control forming the subject of this invention; and

FIGURE 2 is a schematic view of an electric circuit for use with a heat pump employing the invention.

Referring more particularly to FIGURE 1, there is shown for the purpose of illustrating this invention, an air-to-air heat pump employing a refrigeration system operable under the reverse cycle principle. In equipment 3,968,6dl Patented Dec. 18, 1962 "ice of this type a first heat transfer coil is disposed within the area to be served by the heat pump and a second coil is located outside the area usually in the ambient. A compressor 10 discharges relatively hot gaseous refrigerant through discharge line 11 and four-way reversing valve 12 employed for the purpose of reversing refrigerant flow through a portion of the system in order to obtain the desired heating and cooling effects. From the reversing valve 12 which is controlled by the operation of the solenoid in a manner later to be described, the hot gaseous refrigerant flows during cooling cycle operation to an outdoor coil 14 where condensation of the liquid refrigerant occurs as ambient air is passed over the surface thereof by fan 20 driven by motor 21.

Liquid refrigerant formed in coil 14 flows through capillary 15 or other suitable expansion device, to an indoor coil 16 serving as an evaporator. In the indoor coil, liquid refrigerant is converted to vaporous refrigerant as it extracts heat from a stream of air delivered over the coil by fan 18 controlled by motor 19. Vaporous refrigerant so formed flows through the reversing valve 12 to suction line 17 on into the compressor to complete the refrigerant flow cycle.

As is conventional in systems of the type described, the four-way reversing valve 12 may be actuated so that line 11 is placed in communication with the indoor coil 16 when it is desired to operate the unit on a heating cycle. Under these circumstances, heat from the refrigerant flowing in coil 16 is rejected to the air within the enclosure. The rejection of heat from the refrigerant converts the vaporous refrigerant to liquid refrigerant which flows through capillary 15 to the outdoor coil 14 which new functions as an evaporator. The vaporous refrigerant created in outdoor coil 14 as a result of heat transfer between the refrigerant and ambient air flows through the reversing valve into suction line 17.

During the heating cycle operation described, very often the temperature of the outdoor air drops so that a heat sink of a relatively low temperature is presented. The refrigeration system acts to draw a low suction temperature and pressure so that heat may flow from the outdoor air stream to the refrigerant. In so doing, very often a coating of frost accumulates on the outdoor surface of coil 14. An automatic defrosting system depicted in FIGURE 2 is operable to sense the collection of a predetermined amount of frost and operate to temporarily reverse the system to act on cooling cycle operation. In FIGURE 2, there is shown a control circuit adapted to function in this manner. A primary circuit consisting of conductor 25, timer actuated switch 26, thermal responsive switch 28 and coil 31 of solenoid 12 as well as conductor 32 functions to energize under certain circumstances, coil 31. Periodically the timer 27 acts through a cam member to close switch 26 against the action of a spring. As the bulb 29 arranged on the outdoor coil senses a temperature below that indicated as necessity for defrost, bellows 30 forming a part of a. thermal responsive system with bulb 29, contracts and closes switch 28. Under these circumstances, the coil 3 1 of the solenoid controlling reversing valve 12 is energized and moved to the position shown in FIGURE 1 permitting fiow of hot gaseous refrigerant directly to the outdoor coil having a frost accumulation thereon.

In order to maintain coil 31 energized after the timer has moved to the position connecting switch 26 with line 25, a holding circuit including coil 33 is energized. Coil 33 pulls in switch 34 so that the circuit through coil 31 is maintained energized despite the opening of switch 26 until the temperature rises in the outdoor coil indicating the absence of frost from its surface. Under these circumstances bellows 3i expands opening switch 28. Con- .3 nected in parallel with coil 31 in the defrost circuit illustrated in FEGURE 2 are

coils

35 and 36 which

control switches

37 and 38 regulating circuits through the

fan motors

19 and 23. It will thus be appreciated that during the defrosting cycle the motors controlling the operation of fans 18 and it are inactive.

During the defrosting period coil 16 functions as an evaporator and inasmuch as fan 18 is inactive, it functions as an unloaded evaporator. -This causes the temperature and pressure within evaporator 16 to drop to a value which in turn causes a reduction in head pressure. under circumstances Where it is desirable to have a relatively large body of hot gaseous refrigerant the capacity of the compressor is such that it is unable to deliver such a volume. This invention involves connecting line 22 with the compressor discharge and the indoor coil. A valve of the constant pressure type is employed in line 22 for the purpose of regulating fiow therein. Valve 23 functions so that when the pressure within coil 16 drops to a predetermined value, valve 23 opens and permits the flow of a portion of the relatively high pressure discharge gas from the compressor to the evaporator coil. This has the effect of elevating the pressure and temperature of the refrigerant within coil 16 which in turn elevate the temperature and pressure of the gas being directed in line 1 1 to the outdoor coil. 'With the arrangement shown, it is possible to reduce the defrosting period and permit bulb 25* to more quickly sense a temperature high enough to indicate complete defrosting of the outdoor coil. This in turn reduces the time that coil 16 must function as an evaporator when it is desired that it function as a condenser in the interest of maintaining comfortable conditions within the area served by the heat p p- While I have described a preferred embodiment of the invention, it will be understood that the invention is not limited thereto, since it may be otherwise embodied within the scope of the following claims.

I claim: I

1. Air conditioning apparatus including a refrigeration system operable under the reverse cycle principle to supply either heated or cooled air to an enclosure, said system comprising a compressor, a first heat transfer coil located Within the enclosure, a second heat transfer coil Thus located outside the enclosure, refrigerant expansion means interposed between said coils connected to form a closed circuit for the flow of refrigerant, valve means for reversing the direction of refrigerant flow through said coils so that condensation of refrigerant occurs in said first coil, means for supplying a heat exchange medium over said first coil, means for supplying air over said second coil, defrost control means operative to temporarily reverse refrigerant flow within said circuit to supply hot gaseous refrigerant to said second coil, said defrost control means bein effective to terminate operation of said air supply means, a line connecting the compressor outlet with said first coil and means responsive to a predetermined operating characteristic of said first coil regulating passage of a portion of the hot gaseous refrigerant flowing from the compressor to the first coil to raise the pressure therein and increase the loading on said coil.

2. In an air conditioning apparatus including a refrigeration system comprising a compressor, a heat rejection coil, a refrigerant expansion member and a heat absorption coil connected to form a refrigerant flow circuit, means for passing a first medium in heat transfer relation with the heat rejection coil, means for passing a second medium in heat transfer relation with said heat absorption coil, means effective to interchange the heat transfer functions of said coils so that the heat absorption coil becomes a heat rejection coil and the heat rejection coil becomes a heat absorption coil, a line connecting the compressor with one of said coils, and means regulating flow of refrigerant in said line, said means being operative when said coil is acting as a heat absorption coil to meter refrigerant to said heat absorption coil to maintain a predetermined minimum coil temperature.

References {Cited in the file of this patent UNITED STATES PATENTS 2,178,445 Warneke Oct. 31, 1939 2,344,215 Soling Mar. 14, 1944 2,530,440 Nussbaum Nov. 21, 1950 2,716,868 Biehn Sept. 6, 1955 2,774,220 Heym Dec. 18, 1956 2,801,523 Hansen Aug. 6, 1957 2,974,498 Ehrenfreund Mar. 14, 1961