Patent Application
20100229575
This invention relates to the field of heat pumps. More particularly, this invention relates to the field of defrost technology for air source heat pumps.
Air source heat pumps operate by extracting heat energy from outdoor air and delivering that heat energy to heat an interior space. In periods of high outdoor relative humidity combined with an outdoor temperature close to the freezing point of water, frost and/or ice will develop on the outdoor coil of the heat pump, thus impeding heat transfer to the coil surface areas. Defrost operation is required to remove the accumulated frost and/or ice. Defrosting may be accomplished on a timed schedule (time defrost), and/or by sensing the need to accomplish defrosting (demand defrost).
Whether defrosting is accomplished on a time basis or a demand basis, defrosting is typically accomplished by reverse cycle defrosting. In reverse cycle defrosting, a four-way valve is operated so that the heat pump is, in effect, operated in a cooling mode of operation wherein heat energy is extracted from the previously heated interior space to heat the refrigerant fluid circulating in the system, and the heat energy is transported to the outdoor coil to melt and remove the frost/ice that has accumulated on the outdoor coil. The interior of the previously heated space is thus impacted in two ways. One is by removal of significant amounts of heat energy that has just been delivered to the interior space. The other is by creating an uncomfortable flow of cool air felt by occupants of the previously heated space.
Another problem with reverse cycle defrosting is that the warm refrigerant is delivered to the top of the outdoor coil (the vapor outlet side in heating operation) and melts the frost/ice accumulation from the top of the coil downward. This can result in refreezing on the lower parts of the coil.
Reverse cycle defrosting impairs the efficiency of operation of heat pump systems, especially as the frequency of defrost operation increases, and it also results in discomfort of the occupants of the interior space to be heated.
The above-discussed problems of prior art heat pumps are overcome or alleviated by the present invention. In accordance with the present invention, an electrically operated flow control defrost valve is positioned downstream of the discharge of the compressor(s) of the heat exchange system, with the defrost valve being in a defrost refrigerant flow line connected between the compressor discharge and the bottom of the outdoor coil. The defrost valve is normally closed, so that refrigerant does not flow through the defrost line during normal (i.e. non-defrost operation) of the system. However, when defrost operation is desired, the defrost valve is opened, and warm refrigerant vapor is delivered from the discharge of the compressor(s) to the bottom of the outdoor coil to heat the outdoor coil and melt accumulated frost/ice. The defrost valve is closed when defrost operation is completed, and normal operation of the heat pump system is resumed.
An important feature of this invention is that it eliminates the need for the conventional reverse cycle defrosting heretofore used in heat pump systems. Accordingly, this invention eliminates the need to extract energy from the previously heated interior space, since warm indoor air is no longer used as the source of energy for defrosting the outside coil, and cold drafts, which discomfort occupants of the interior space, are also eliminated.
In the present invention, the frost/ice accumulation on the outdoor coil is melted from the bottom of the coil up to the top, thus eliminating or reducing the problem of possible refreezing of the coil when melted from the top down as in the prior art reverse cycle defrosting.
Instead of extracting energy from the heated interior space for defrost operation, the energy source for defrost operation in the present invention is a combination of the electrical input to the compressor(s) and an accumulator heating element in the heat pump system.
The present invention also incorporates a sensor to detect the build-up of frost/ice on the outdoor coil and initiate defrost operation when required. The sensor includes a light emitting diode (LED) and a photo-transistor secured between adjacent fins in the outdoor coil. A build-up of frost/ice between the LED and the photo-transistor partially blocks light transmission, and this blockage of light is used as a defrost initiating signal by the heat pump system microprocessor to initiate defrost operation for a predetermined time period, the time of defrost operation being a function of outdoor air temperature as sensed by the microprocessor at the initiation of defrost operation.
Referring to the drawings, where like elements are numbered alike in the several figures:
Referring to
The system also has a refrigerant circulation conduit system including: a conduit segment 20 which receives compressed refrigerant from the discharge from primary compressor 10 and delivers the refrigerant through 4 way valve 18 as shown; a conduit segment 22 which delivers the compressed refrigerant to indoor coil 16 to heat the indoor space by heat transfer exchange with air (indicated by arrows flowing over the coil) supplied by a fan 16A; a conduit segment 24A that delivers the refrigerant through a check valve 24B and around a closed thermal expansion valve (TXV) 25 to a conduit segment 26; a conduit segment 26 including a thermal expansion valve 27 through which the refrigerant flows to a refrigerant distributor 14B and then to the bottom of outdoor coil 14 and through outdoor coil 14 to extract heat from the outdoor air flowing over coil 14 (indicated by arrows flowing over the coil) supplied by fan 14A; a conduit segment 28 that delivers the refrigerant through 4 way valve 18 as shown to conduit segment 29 and then to accumulator 30 where oil entrained in the refrigerant is separated for return to the compressor sumps (separation and return of the oil not shown); and the refrigerant is then delivered to conduit segments 31 and 32 and through check valve 34; and the refrigerant then flows to conduit segments 36 and 38 which receive the refrigerant from check valve 34 and deliver the refrigerant to the inlet to primary compressor 10. The flow of refrigerant through the conduit system for the heating mode of operation is indicated by the arrows in the various conduit segments.
If booster compressor 12 is also operating, check valve 34 is closed by the discharge pressure from booster compressor 12, and the refrigerant flows from branch conduit 31 to branch conduit 40, and then to the inlet to booster compressor 12; and the refrigerant discharged from booster compressor 12 is delivered via branch conduit 42 and branch conduit 38 to the inlet to primary compressor 10.
For operation of the system in the cooling mode, 4 way valve 18 is moved to the position shown in by the dashed lines, whereby the direction of flow of refrigerant in the system is reversed. In that case, the system operates as in a cooling mode. Heat is extracted from the indoor space at indoor coil 16, and the heated refrigerant is delivered through 4 way valve 18 and conduit segment 29 to accumulator 30 and to conduit segments 31, 32, 34, 36 and 38 to the inlet to primary compressor 10 if primary compressor 10 is on and booster compressor 12 is off (or if both compressors are on, the refrigerant from indoor coil 16 is delivered via conduit segment 22 and through 4 way valve 18 to conduit segment 29 and accumulator 30 and conduit segment 40 to the inlet to booster compressor 12, and then from the discharge from booster compressor 12 to the inlet to primary compressor 10). The compressed refrigerant discharged from primary compressor 10 then flows via conduit segment 20 and through 4 way valve 18 and via conduit segment 28 to the top of outdoor coil 14 and through coil 14 to discharge heat at the outdoor coil. The refrigerant then flows around closed TXV 27 via bypass line 26A and check valve 41 to conduit segments 26 and 24 to TXV 25 and to indoor coil 16 where heat is removed from the space to be cooled. The refrigerant is then delivered by conduit segment 22, 4 way valve 18, conduit segment 29, accumulator 30 and conduit segments 31, 32, 36 and 38 and check valve 34 to the inlet to primary compressor 10.
In prior art heat pump systems when operating in the heating mode, frost and/or ice can accumulate on the outdoor coil 14, necessitating the need to effect a defrost operation. That defrost operation typically involves reversing the operation of the system to the cooling mode, whereby warm refrigerant is delivered to flow from the top of outdoor coil 14 to the bottom of outdoor coil 14 to melt to frost and/or ice accumulated on the coil.
This is sometimes referred to as “reverse cycle defrost” operation. However, this reverse cycle defrost operation has several problems well known in the art. Perhaps foremost among these problems is that heat energy is extracted from the previously heated space by indoor coil 16 to heat the refrigerant flowing through the system, and that heat energy is transported to outdoor coil 14 to defrost the accumulated frost/ice on outdoor coil 14. The interior of the previously heated indoor space is thus negatively impacted in two ways. One is by removal of significant amounts of heat energy that has just been delivered to the interior space; the other is by creating an uncomfortable flow of cool air felt by occupants of the previously heated space. Another problem with the prior art reverse cycle defrosting is that the warm refrigerant is delivered to the top of the outdoor coil (the vapor outlet side in heating operation) and melts the frost/ice accumulation from the top of the coil downward. This can result in refreezing on the lower parts of the coil. Especially in situations of high humidity and a temperature at or near freezing for the outside air, frequent defrosting can be required, and system efficiency is impaired. These problems of the prior art are eliminated or substantially reduced in the present invention.
In accordance with the present invention, a defrost branch conduit 50 is connected from the discharge from primary compressor 10 to refrigerant distributor 14B at the bottom of outdoor coil 14. An electrically operated flow control defrost valve 52 in conduit 50 controls the flow of refrigerant in conduit 50 to outdoor coil 14. Valve 52 is a combination back pressure regulator/on-off control valve. When called upon to open, it will prevent the compressor discharge pressure from dropping below the equivalent of about 70 degrees F., thus ensuring that indoor coil 16 remains sufficiently pressurized to quickly resume heating upon completion of defrost. Defrost valve 52 is closed during normal heating operation of the heat pump system, so no refrigerant flows through conduit 50 to outdoor coil 14 during normal heating operation of the system. However, when frost and/or ice accumulates on outdoor coil 14 requiring defrost, a signal is delivered from the system microprocessor controller 54 to open defrost valve 52, whereby warm refrigerant vapor discharged from primary compressor 10 is delivered to distributor 14B and then to the bottom of outdoor coil 14 and flows through outdoor coil 14 to melt the accumulated ice and/or frost. The outlet from distributor 14B connects to each one of the circuits in outdoor coil 14 to evenly distribute the flowing refrigerant to the outdoor coil circuits. Distributor 14B has an internal orifice at its entry which further expands the refrigerant exiting TXV 27 during heating operation. Defrost conduit 50 is connected to distributor 14B downstream (in the direction of refrigerant flow during heating operation) of the internal orifice in distributor 14B so that the internal orifice does not restrict the flow of defrost refrigerant to outdoor coil 14. After passing through outdoor coil 14, the defrost refrigerant passes through conduit segment 28 and through 4 way valve 18 to conduit segment 29 and through accumulator 30 and is delivered to the inlet of primary compressor 10 (or to the inlet to booster compressor 12 if both compressors are on) for compression and delivery of warm refrigerant vapor through defrost conduit 50 to outdoor coil 14 to continue the defrost cycle.
Most importantly, defrost of outdoor coil 14 is accomplished without moving 4 way valve 18 to the cooling position, and without extracting heat energy from the interior space being heated (as happens in the prior art reverse cycle defrost operation), so the major problems of the prior art reverse cycle defrost operation are eliminated. Also, the warm refrigerant vapor delivered to outdoor coil 14 for defrost is delivered to the bottom of the coil (which previously received liquid refrigerant in the heating cycle), so the frost/ice on outdoor coil 14 is melted from the bottom to the top of the coil, thus reducing or eliminating the prior art problem of refreezing of the coil during defrost operation.
Accumulator 30 has a heating element 56 which is activated by controller 54 to provide additional heat input to the defrost refrigerant if the warm refrigerant vapor discharged from the compressor(s) is not sufficient to accomplish defrost operation. In effect, the electrical input to drive the primary compressor (or the electrical input to drive both compressors if both are operating) plus the electrical input to the heating element 56 in accumulator 30 is the energy source for defrost operation. It should be noted that signals from controller 54 to fans 14A and 16A stop the operation of those fans during defrost operation. Some prior art accumulators have included a heating element used to boil off liquid refrigerant in the accumulator to return the refrigerant to circulation in the system. In the present invention, the heating element in the accumulator performs the function of adding heat energy to the refrigerant to increase the heat energy content of the refrigerant vapor for defrost operation.
Referring now to
With the use of the detector system of
Operation of the defrost system of the present invention can, if desired, be modulated by sensing the humidity and temperature of the outdoor air to adjust the operation of the defrost system for conditions of high humidity and low temperature
Referring now to
While preferred embodiments of the present invention have been shown and described, various modifications and substitutions may be made thereto without departing from the spirit and scope of the invention. Accordingly, it is to be understood that the present invention has been described and shown by way of illustration and not limitation.
