US20070033955A1 - Electrically controlled defrost and expansion valve apparatus - Google Patents
Electrically controlled defrost and expansion valve apparatus Download PDFInfo
- Publication number
- US20070033955A1 US20070033955A1 US11/483,258 US48325806A US2007033955A1 US 20070033955 A1 US20070033955 A1 US 20070033955A1 US 48325806 A US48325806 A US 48325806A US 2007033955 A1 US2007033955 A1 US 2007033955A1
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- US
- United States
- Prior art keywords
- controller
- defrost
- evaporator
- refrigeration system
- expansion valve
- 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.)
- Abandoned
Links
- 238000001816 cooling Methods 0.000 claims abstract description 11
- 238000005057 refrigeration Methods 0.000 claims description 30
- 239000003507 refrigerant Substances 0.000 claims description 26
- 238000001704 evaporation Methods 0.000 claims description 5
- 239000007788 liquid Substances 0.000 claims description 5
- 238000000034 method Methods 0.000 abstract description 6
- 238000010257 thawing Methods 0.000 abstract description 4
- 230000008859 change Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000008901 benefit Effects 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000010025 steaming Methods 0.000 description 1
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
- 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
- F25B47/02—Defrosting cycles
- F25B47/022—Defrosting cycles hot gas defrosting
- F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
-
- 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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2104—Temperatures of an indoor room or compartment
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator
-
- 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
- F25D21/002—Defroster control
- F25D21/006—Defroster control with electronic control circuits
Definitions
- This invention relates generally to space cooling systems, in particular to apparatus for controlling a space cooling system with respect to the defrost cycle.
- a typical space cooling system includes at least one evaporator system contained within the space that is to be cooled, a condenser system that is located outside of the cooled space, and a compressor positioned between the condenser system outlet and the evaporator system inlet and, finally, an expansion valve which completes the loop joining together the condenser system outlet and the evaporator system inlet.
- a refrigerant is circulated within the loop which cools the space as follows. The refrigerant is compressed by the compressor which raises the temperature and pressure of the refrigerant. The hot pressurized refrigerant gas then flows through the condenser system which serves as heat exchanger to allow the refrigerant to dissipate the heat of pressurization.
- the refrigerant condenses into a liquid and then flows through the expansion valve, where the liquid refrigerant moves from a high pressure zone into a low pressure zone, thus expanding and evaporating.
- the refrigerant becomes cold where it then passes into coils of the evaporator, thus absorbing heat from inside the space that is to be cooled and the cycle then repeats until the space reaches the desired temperature.
- a fan assist the heat transfer from the cooled space to the coils of the evaporator system and another fan is used to assist the heat transfer from the coils of the condenser to outside environment.
- a negative pressure differential is present on the evaporator outlet when the device is operating in a refrigeration mode thereby suctioning the gas refrigerant to the compressor.
- thermistor sensors are placed at the inlet and outlet of the evaporator system for measuring the level of superheat across the evaporator.
- a sensor located on the outlet side of the compressor measures the discharge temperature of compressor.
- the ambient temperature of the spaced to be cooled is measured by still another sensor.
- the need to defrost the evaporator from any ice build-up due to the cooling process is determined by another sensor that is associated with evaporator so that defrosting procedures can be monitored.
- An refrigeration apparatus that has both an electrical controller that responds to evaporator superheat and return air temperature to the expansion valve as well as controls a reversing valve which provides for a defrosting cycle, eliminates the need for electric heaters, check valves, head pressure control valve as well as the associated piping and connections is not found in the prior art.
- Another aspect of the invention is to provide a refrigeration system that leaves the evaporator coil virtually clean after each defrost cycle.
- Another aspect of the invention is to provide a refrigeration system that eliminates the need for check valves and an expansion valve at the condenser.
- Still another aspect of the invention is to provide a refrigeration system that has less wiring and is less expensive to produce and operate than present devices.
- FIG. 1 is a schematic of the most basic embodiment of the invention operating during a refrigeration cycle.
- FIG. 2 is a schematic of the embodiment shown in FIG. 1 operating during a defrost cycle.
- FIG. 1 which depicts the basic elements of the invention 10
- the refrigeration cycle is similar to that discussed above for the typical space cooling device discussed in the background.
- invention 10 includes both a controller 12 and a reversing valve 24 which are discussed below.
- Refrigerant (not shown) is compressed by the compressor 26 .
- the temperature and pressure of the refrigerant is raised.
- the hot pressurized refrigerant gas then flows through the reversing valve 24 to the condenser system 22 .
- condenser system 22 functions as a heat exchanger to allow the refrigerant to dissipate the heat of pressurization.
- the refrigerant condenses into a liquid and then flows through the expansion valve 20 , where the liquid refrigerant moves from a high pressure zone into a low pressure zone, thus expanding and evaporating.
- Electric expansion valve 20 is preferably a step motor such as manufactured by companies such as Sporlan, Alco, Parker or Danfoss.
- the refrigerant flow of the electric expansion valve 20 is controlled by controller 12 and is modulated to control the superheat of the evaporator 28 .
- the superheat of evaporator 28 is determined by measuring sensor 16 and 18 using techniques well known in the art. In evaporating, the refrigerant then passes into coils of the evaporator 28 , thus absorbing heat from inside the space 30 that is to be cooled and the cycle then repeats until the space reaches the desired temperature as provided by sensor 14 .
- the controller 12 can be set to defrost mode that is either electric (using standard heater technology) or reverse cycle (utilizing the instant invention).
- defrost mode that is either electric (using standard heater technology) or reverse cycle (utilizing the instant invention).
- Reverse valve assembly 24 is readily available from companies such as Ranco, Alco, Danfoss and Sanhua. This type of valve is typically used on heat pumps. As shown in FIG. 2 , the refrigerant flows change from refrigerating cycle to defrost cycle.
- the electrical expansion valve 20 is forced open ranging from 40% to 60% of maximum. Controller 12 then checks sensors 16 and 18 . If the temperature at sensor 18 indicates that it is greater than or equal to the defrost termination temperature (DTT), the defrost ends and then goes to a drip mode.
- DTT defrost termination temperature
- the sensor 18 is monitored continuously by controller 12 to determine the coil temperature rise of evaporator 28 relative to the DTT temperature. When the temperature reading on sensor 18 is greater than or equal to the pre-set DTT, defrost is considered to be complete and controller 12 will enter the drip mode and close the expansion valve 20 completely.
- Compressor 26 may pumpdown the refrigerant and may be cut off by the low-pressure control of compressor 26 . While the compressor 26 is engaged in the pumpdown mode, the evaporator fans (not shown) remain off. Compressor 26 may also be shut off by controller 12 if so wired.
- Reversing valve assembly 24 is not de-energized until the end of the drip mode.
- the refrigerant flows change from defrost cycle to refrigerating cycle when controller 12 enters the fan delay mode (cool mode if the fan delay mode is skipped) after drip mode. If the pumpdown after a defrost cycle takes longer than drip mode, the controller 12 will enter fan delay mode even though the pumpdown may not be completed. For example, if a pumpdown takes 4 minutes to complete and the drip time is pre-set to 3 minutes, when the 3 minute drip time expires, controller 12 will enter fan delay mode and expansion valve 20 will be modulating. Note the compressor 26 may be running through pumpdown mode, drip mode and fan delay mode. A reverse cycle defrost is considered complete when the controller 12 enters the fan delay mode. As noted above, when there is no defrost, all operations are the same as current version of the applicant's electric expansion valve refrigeration control system which is well known in the art.
Abstract
A cooling system that has an electrical controller that controls an electric expansion valve and the defrost cycle using a reversing valve. The need for heater circuit to achieve defrost is eliminated. The system permits the defrosting the evaporator system in less time required for conventional defrost methods. The cooling system also eliminates the need for a head pressure control valve and check valves. Due to the less wiring and lower operating costs, the invention provides significant cost savings.
Description
- This application is a continuation application of U.S. patent application Ser. No. 10/888,561 filed on Jul. 9, 2004, to be issued on Jul. 11, 2006 as U.S. Pat. No. 7,073,344 which claims the benefit of U.S. Provisional Application No. 60/485,836 filed Jul. 10, 2003.
- This invention relates generally to space cooling systems, in particular to apparatus for controlling a space cooling system with respect to the defrost cycle.
- A typical space cooling system includes at least one evaporator system contained within the space that is to be cooled, a condenser system that is located outside of the cooled space, and a compressor positioned between the condenser system outlet and the evaporator system inlet and, finally, an expansion valve which completes the loop joining together the condenser system outlet and the evaporator system inlet. A refrigerant is circulated within the loop which cools the space as follows. The refrigerant is compressed by the compressor which raises the temperature and pressure of the refrigerant. The hot pressurized refrigerant gas then flows through the condenser system which serves as heat exchanger to allow the refrigerant to dissipate the heat of pressurization. The refrigerant condenses into a liquid and then flows through the expansion valve, where the liquid refrigerant moves from a high pressure zone into a low pressure zone, thus expanding and evaporating. In evaporating, the refrigerant becomes cold where it then passes into coils of the evaporator, thus absorbing heat from inside the space that is to be cooled and the cycle then repeats until the space reaches the desired temperature.
- In addition to these major components, additional components are also included. A fan assist the heat transfer from the cooled space to the coils of the evaporator system and another fan is used to assist the heat transfer from the coils of the condenser to outside environment. A negative pressure differential is present on the evaporator outlet when the device is operating in a refrigeration mode thereby suctioning the gas refrigerant to the compressor. Further, thermistor sensors are placed at the inlet and outlet of the evaporator system for measuring the level of superheat across the evaporator. A sensor located on the outlet side of the compressor measures the discharge temperature of compressor. The ambient temperature of the spaced to be cooled is measured by still another sensor. Finally, the need to defrost the evaporator from any ice build-up due to the cooling process is determined by another sensor that is associated with evaporator so that defrosting procedures can be monitored.
- There are two basic options for providing a defrost cycle. U.S. Pat. No. 5,551,248, issued to Derosier on Sep. 3, 1996, discloses the use of a controller to control the operation of a space cooling system. While this device permits the use of an electrically controlled expansion valve, either utilizing an electrically operated solenoid or an electrically operated step motor, Derosier also teaches the use of heater which is activated on a programmed time schedule, either a time between successive defrost cycles or a compressor run time. The use of heater for providing defrost function requires the additional expense of the heater as well as associated valving, piping and supply wiring connections. Additionally, there must a pumpdown condition present before defrost procedures can begin and the fans must remain on during pumpdown.
- Another option is disclosed by Russell of Brea, Calif. in its HIGH SIERRA model refrigeration device. This device teaches the use of reversing valve which permits the elimination of the heater. However, the HIGH SIERRA model requires the use of check valve at the outlet of the compressor and another check valve in the drain pan circuit as well as additional piping and connection fittings. Most importantly, the HIGH SIERRA model does not disclose or suggest the use of an electrical controller which permits, among other things, the use of electrically controlled expansion valve such as taught by Derosier.
- An refrigeration apparatus that has both an electrical controller that responds to evaporator superheat and return air temperature to the expansion valve as well as controls a reversing valve which provides for a defrosting cycle, eliminates the need for electric heaters, check valves, head pressure control valve as well as the associated piping and connections is not found in the prior art.
- It is an aspect of the invention to provide a refrigeration system that provides an electrical controller that controls the electric expansion valve and the defrost cycle using a reversing valve.
- It is another aspect of the invention to provide a refrigeration system that eliminates the need for a heater circuit to achieve a defrost of the evaporator system.
- It is still another aspect of the invention to provide a refrigeration system that permits defrosting the evaporator system in less than the time required for a conventional electronic defrost system.
- Further, another aspect of the invention is to provide a refrigeration system that leaves the evaporator coil virtually clean after each defrost cycle.
- It is another aspect of the invention to provide a refrigeration system that eliminates the need for a head pressure control valve.
- Another aspect of the invention is to provide a refrigeration system that eliminates the need for check valves and an expansion valve at the condenser.
- Still another aspect of the invention is to provide a refrigeration system that has less wiring and is less expensive to produce and operate than present devices.
- It is another aspect of the invention to provide a refrigeration system that requires no pumpdown before the defrost cycle has been initiated.
- It is another aspect of the invention to provide a refrigeration system that enables the compressor to run during defrost.
- It is still another aspect of the invention to provide a refrigeration system wherein the need to defrost is determined by the controller and defrost will only occur when it is necessary thus saving energy costs associated with unnecessary defrost.
- Finally, it is another aspect of the invention to provide a refrigeration system that prevents steaming and heat from being introduced into the cooled space during the defrost cycle.
- These and other aspects of the invention will become apparent in light of the detailed description of the invention which follows.
-
FIG. 1 is a schematic of the most basic embodiment of the invention operating during a refrigeration cycle. -
FIG. 2 is a schematic of the embodiment shown inFIG. 1 operating during a defrost cycle. - While certain representative embodiments of the invention have been described herein for the purposes of illustration, it will be apparent to those skilled in the art that modification therein may be made without departure from the spirit and scope of the invention. Like parts are referenced in the specification and accompanying figures with the same reference call out numbers. Note that the drawings are not necessarily to scale and that some elements may be larger or smaller or otherwise oriented to more clearly depict the important features of the invention.
- As shown in
FIG. 1 . which depicts the basic elements of theinvention 10, the refrigeration cycle is similar to that discussed above for the typical space cooling device discussed in the background. However, note that unlike prior art devices,invention 10 includes both acontroller 12 and a reversingvalve 24 which are discussed below. Refrigerant (not shown) is compressed by thecompressor 26. The temperature and pressure of the refrigerant is raised. The hot pressurized refrigerant gas then flows through the reversingvalve 24 to thecondenser system 22. As above,condenser system 22 functions as a heat exchanger to allow the refrigerant to dissipate the heat of pressurization. The refrigerant condenses into a liquid and then flows through theexpansion valve 20, where the liquid refrigerant moves from a high pressure zone into a low pressure zone, thus expanding and evaporating.Electric expansion valve 20 is preferably a step motor such as manufactured by companies such as Sporlan, Alco, Parker or Danfoss. The refrigerant flow of theelectric expansion valve 20 is controlled bycontroller 12 and is modulated to control the superheat of theevaporator 28. The superheat ofevaporator 28 is determined by measuringsensor evaporator 28, thus absorbing heat from inside thespace 30 that is to be cooled and the cycle then repeats until the space reaches the desired temperature as provided bysensor 14. - The
controller 12 can be set to defrost mode that is either electric (using standard heater technology) or reverse cycle (utilizing the instant invention). When the reverse cycle defrost option is selected, the following sequence will be used as shown inFIG. 2 . - When there is a demand for defrost whether by set time schedule or manual defrost or demand defrost as determined by the
controller 12, thecontroller 12 sends a signal to reversevalve assembly 24.Reverse valve assembly 24 is readily available from companies such as Ranco, Alco, Danfoss and Sanhua. This type of valve is typically used on heat pumps. As shown inFIG. 2 , the refrigerant flows change from refrigerating cycle to defrost cycle. - Simultaneously, the
electrical expansion valve 20 is forced open ranging from 40% to 60% of maximum.Controller 12 then checkssensors sensor 18 indicates that it is greater than or equal to the defrost termination temperature (DTT), the defrost ends and then goes to a drip mode. The default setting oncontroller 12 is preferably ranges from 40° F. to approximately 50° F. If 40° F.>Sensor 16−DTT>20° F.,expansion valve 20 is changed ranging from 20% to 30% of the fully open position. The temperature monitored atsensor 16 will keep rising. If 99° F.>sensor 16>=40° F.+DTT, thecontroller 12 will again close theexpansion valve 20 ranging from 5% to 15% of the fully open position.Sensor 18 will continue to be monitored to determine whether the DTT temperature has been reached. As noted, once it has, the defrost ends. This process will repeat untilsensor 18 indicates that the DTT temperature has been reached and then defrost ends. - The
sensor 18 is monitored continuously bycontroller 12 to determine the coil temperature rise ofevaporator 28 relative to the DTT temperature. When the temperature reading onsensor 18 is greater than or equal to the pre-set DTT, defrost is considered to be complete andcontroller 12 will enter the drip mode and close theexpansion valve 20 completely.Compressor 26 may pumpdown the refrigerant and may be cut off by the low-pressure control ofcompressor 26. While thecompressor 26 is engaged in the pumpdown mode, the evaporator fans (not shown) remain off.Compressor 26 may also be shut off bycontroller 12 if so wired. - Reversing
valve assembly 24 is not de-energized until the end of the drip mode. The refrigerant flows change from defrost cycle to refrigerating cycle whencontroller 12 enters the fan delay mode (cool mode if the fan delay mode is skipped) after drip mode. If the pumpdown after a defrost cycle takes longer than drip mode, thecontroller 12 will enter fan delay mode even though the pumpdown may not be completed. For example, if a pumpdown takes 4 minutes to complete and the drip time is pre-set to 3 minutes, when the 3 minute drip time expires,controller 12 will enter fan delay mode andexpansion valve 20 will be modulating. Note thecompressor 26 may be running through pumpdown mode, drip mode and fan delay mode. A reverse cycle defrost is considered complete when thecontroller 12 enters the fan delay mode. As noted above, when there is no defrost, all operations are the same as current version of the applicant's electric expansion valve refrigeration control system which is well known in the art. - Although the present invention has been described in considerable detail with reference to certain preferred versions thereof, other versions would be readily apparent to those of ordinary skill in the art. Therefore, the spirit and scope of the appended claims should not be limited to the description of the preferred versions contained herein.
Claims (10)
1. A refrigeration system for a cooling a space comprising:
a compressor to compress a refrigerant gas;
a reversing valve connected to said compressor;
a condenser connected to said reversing valve which receives the hot pressurized refrigerant gas provided by said compressor; wherein said condenser finctions as a heat exchanger to allow the refrigerant gas to dissipate the heat of pressurization such that the refrigerant condenses into a liquid;
an electric expansion valve connected to said condenser wherein the refrigerant passing through said expansion valve expands and evaporates;
a controller electrically connected to said electric expansion valve and to said reversing valve;
an evaporator connected to said electric expansion valve wherein the evaporating refrigerant absorbs heat from a space to be cooled; and
wherein said controller modulates a superheat temperature provided by said evaporator until a predetermined temperature is reached; and
wherein once said controller is set to defrost cycle, said controller causes said reversing valve to reverse, said electrical expansion valve is further opened, and said refrigeration system enters a defrost mode.
2. The refrigeration system of claim 1 wherein said controller can be set to defrost in accordance with a predetermined time that elapses between defrost cycles.
3. The refrigeration system of claim 1 wherein said controller can be set to defrost by actuating a manual setting.
4. The refrigeration system of claim 1 wherein said controller can be set to defrost by demand defrost as determined by said controller.
5. The refrigeration system of claim 1 wherein said controller further comprises:
a cooling space temperature sensor that indicates the temperature in the cooled space so that said controller can control the cooling cycle of said refrigeration system.
6. The refrigeration system of claim 5 wherein said controller further comprises:
a first evaporator temperature sensor positioned adjacent to the evaporator on the connection between said evaporator and said electric expansion valve.
7. The refrigeration system of claim 6 wherein said controller further comprises;
a second evaporator temperature sensor positioned on the connection between said evaporator and said compressor wherein said second evaporator temperature sensor is adjacent to said evaporator but outside the cooled space.
8. The refrigeration system of claim 7 wherein the superheat of said evaporator is determined by said controller by measuring said first evaporator temperature sensor and said second evaporator temperature sensor.
9. The refrigeration system of claim 8 wherein during a defrost cycle, said controller causes said electrical expansion valve to open ranging 40 to 60% of the maximum open position.
10. The refrigeration system of claim 8 wherein if said second evaporator temperature sensor indicates to said controller that the temperature is greater than or equal to a defrost termination temperature set in said controller, said controller ends the defrost cycle and causes said refrigeration system to enter a drip mode.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/483,258 US20070033955A1 (en) | 2003-07-10 | 2006-07-07 | Electrically controlled defrost and expansion valve apparatus |
PCT/US2007/015656 WO2008018968A2 (en) | 2006-07-07 | 2007-07-09 | Electrically controlled defrost and expansion valve apparatus |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US48583603P | 2003-07-10 | 2003-07-10 | |
US10/888,561 US7073344B2 (en) | 2003-07-10 | 2004-07-09 | Electrically controlled defrost and expansion valve apparatus |
US11/483,258 US20070033955A1 (en) | 2003-07-10 | 2006-07-07 | Electrically controlled defrost and expansion valve apparatus |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/888,561 Continuation US7073344B2 (en) | 2003-07-10 | 2004-07-09 | Electrically controlled defrost and expansion valve apparatus |
Publications (1)
Publication Number | Publication Date |
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US20070033955A1 true US20070033955A1 (en) | 2007-02-15 |
Family
ID=39033457
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US11/483,258 Abandoned US20070033955A1 (en) | 2003-07-10 | 2006-07-07 | Electrically controlled defrost and expansion valve apparatus |
Country Status (2)
Country | Link |
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US (1) | US20070033955A1 (en) |
WO (1) | WO2008018968A2 (en) |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20120055179A1 (en) * | 2010-09-02 | 2012-03-08 | Brent Alden Junge | Dsm defrost during high demand |
CN105571222A (en) * | 2015-12-22 | 2016-05-11 | 佛山欧思丹热能科技有限公司 | Heat pump defrosting control method |
EP3196569A1 (en) * | 2016-01-21 | 2017-07-26 | Vaillant GmbH | Sensor arramgement in a heat pump system |
US20170321939A1 (en) * | 2014-12-26 | 2017-11-09 | Daikin Industries, Ltd. | Air conditioner |
US11015851B2 (en) * | 2017-07-07 | 2021-05-25 | Mitsubishi Electric Corporation | Refrigeration cycle device |
US20210207874A1 (en) * | 2017-04-28 | 2021-07-08 | Lg Electronics Inc. | Refrigerator and method for controlling the same |
US11377578B2 (en) * | 2016-12-13 | 2022-07-05 | Daikin Industries, Ltd. | Heat transfer device and heat transfer method using same |
US11396218B2 (en) * | 2018-12-28 | 2022-07-26 | Thermo King Corporation | Methods and systems for supplemental flow control of working fluid through a climate control circuit |
Citations (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4017286A (en) * | 1975-12-22 | 1977-04-12 | Westinghouse Electric Corporation | Heat pump suction line vent |
US4333316A (en) * | 1980-10-14 | 1982-06-08 | General Electric Company | Automatic control apparatus for a heat pump system |
US4766734A (en) * | 1987-09-08 | 1988-08-30 | Electric Power Research Institute, Inc. | Heat pump system with hot water defrost |
US5187944A (en) * | 1992-04-10 | 1993-02-23 | Eaton Corporation | Variable superheat target strategy for controlling an electrically operated refrigerant expansion valve |
US5460009A (en) * | 1994-01-11 | 1995-10-24 | York International Corporation | Refrigeration system and method |
US5475986A (en) * | 1992-08-12 | 1995-12-19 | Copeland Corporation | Microprocessor-based control system for heat pump having distributed architecture |
US5546756A (en) * | 1995-02-08 | 1996-08-20 | Eaton Corporation | Controlling an electrically actuated refrigerant expansion valve |
US5628199A (en) * | 1992-07-01 | 1997-05-13 | Gas Research Institute | Microprocessor-based controller |
US5927083A (en) * | 1998-03-09 | 1999-07-27 | Carrier Corporation | Compressor cycle dependent defrost control |
US6334321B1 (en) * | 2000-03-15 | 2002-01-01 | Carrier Corporation | Method and system for defrost control on reversible heat pumps |
US6467282B1 (en) * | 2000-09-27 | 2002-10-22 | Patrick D. French | Frost sensor for use in defrost controls for refrigeration |
US6601396B2 (en) * | 2001-12-03 | 2003-08-05 | Kendro Laboratory Products, Lp | Freezer defrost method and apparatus |
US6874693B2 (en) * | 2002-12-20 | 2005-04-05 | Honeywell International Inc. | Method and apparatus for controlling a multi-source heating system |
-
2006
- 2006-07-07 US US11/483,258 patent/US20070033955A1/en not_active Abandoned
-
2007
- 2007-07-09 WO PCT/US2007/015656 patent/WO2008018968A2/en active Application Filing
Patent Citations (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4017286A (en) * | 1975-12-22 | 1977-04-12 | Westinghouse Electric Corporation | Heat pump suction line vent |
US4333316A (en) * | 1980-10-14 | 1982-06-08 | General Electric Company | Automatic control apparatus for a heat pump system |
US4766734A (en) * | 1987-09-08 | 1988-08-30 | Electric Power Research Institute, Inc. | Heat pump system with hot water defrost |
US5187944A (en) * | 1992-04-10 | 1993-02-23 | Eaton Corporation | Variable superheat target strategy for controlling an electrically operated refrigerant expansion valve |
US5628199A (en) * | 1992-07-01 | 1997-05-13 | Gas Research Institute | Microprocessor-based controller |
US5475986A (en) * | 1992-08-12 | 1995-12-19 | Copeland Corporation | Microprocessor-based control system for heat pump having distributed architecture |
US5460009A (en) * | 1994-01-11 | 1995-10-24 | York International Corporation | Refrigeration system and method |
US5546756A (en) * | 1995-02-08 | 1996-08-20 | Eaton Corporation | Controlling an electrically actuated refrigerant expansion valve |
US5927083A (en) * | 1998-03-09 | 1999-07-27 | Carrier Corporation | Compressor cycle dependent defrost control |
US6334321B1 (en) * | 2000-03-15 | 2002-01-01 | Carrier Corporation | Method and system for defrost control on reversible heat pumps |
US6467282B1 (en) * | 2000-09-27 | 2002-10-22 | Patrick D. French | Frost sensor for use in defrost controls for refrigeration |
US6601396B2 (en) * | 2001-12-03 | 2003-08-05 | Kendro Laboratory Products, Lp | Freezer defrost method and apparatus |
US6874693B2 (en) * | 2002-12-20 | 2005-04-05 | Honeywell International Inc. | Method and apparatus for controlling a multi-source heating system |
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US20120055179A1 (en) * | 2010-09-02 | 2012-03-08 | Brent Alden Junge | Dsm defrost during high demand |
US8291718B2 (en) * | 2010-09-02 | 2012-10-23 | General Electric Company | DSM defrost during high demand |
US20170321939A1 (en) * | 2014-12-26 | 2017-11-09 | Daikin Industries, Ltd. | Air conditioner |
US10544958B2 (en) * | 2014-12-26 | 2020-01-28 | Daikin Industries, Ltd. | Air conditioner with defrost control |
CN105571222A (en) * | 2015-12-22 | 2016-05-11 | 佛山欧思丹热能科技有限公司 | Heat pump defrosting control method |
EP3196569A1 (en) * | 2016-01-21 | 2017-07-26 | Vaillant GmbH | Sensor arramgement in a heat pump system |
US11377578B2 (en) * | 2016-12-13 | 2022-07-05 | Daikin Industries, Ltd. | Heat transfer device and heat transfer method using same |
US20210207874A1 (en) * | 2017-04-28 | 2021-07-08 | Lg Electronics Inc. | Refrigerator and method for controlling the same |
US11668512B2 (en) * | 2017-04-28 | 2023-06-06 | Lg Electronics Inc. | Refrigerator and method for controlling the same |
US11015851B2 (en) * | 2017-07-07 | 2021-05-25 | Mitsubishi Electric Corporation | Refrigeration cycle device |
US11396218B2 (en) * | 2018-12-28 | 2022-07-26 | Thermo King Corporation | Methods and systems for supplemental flow control of working fluid through a climate control circuit |
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WO2008018968A2 (en) | 2008-02-14 |
WO2008018968A3 (en) | 2008-11-13 |
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