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US20070137227A1 - Refrigeration device comprising controlled de-humidification - Google Patents

Refrigeration device comprising controlled de-humidification Download PDF

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Publication number
US20070137227A1
US20070137227A1 US10/560,156 US56015604A US2007137227A1 US 20070137227 A1 US20070137227 A1 US 20070137227A1 US 56015604 A US56015604 A US 56015604A US 2007137227 A1 US2007137227 A1 US 2007137227A1
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United States
Prior art keywords
fan
evaporator
refrigeration device
storage compartment
control circuit
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
Application number
US10/560,156
Inventor
Kelmut Konopa
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BSH Hausgeraete GmbH
Original Assignee
BSH Bosch und Siemens Hausgeraete GmbH
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Filing date
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Assigned to BSH BOSCH UND SIEMENS HAUSGERATE GMBH reassignment BSH BOSCH UND SIEMENS HAUSGERATE GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KONOPA, HELMUT
Publication of US20070137227A1 publication Critical patent/US20070137227A1/en
Abandoned legal-status Critical Current

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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
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
    • F25D17/042—Air treating means within refrigerated spaces
    • 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
    • F25D29/00—Arrangement or mounting of control or safety devices
    • 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation
    • 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
    • F25B2600/00—Control issues
    • F25B2600/11—Fan speed control
    • F25B2600/112—Fan speed control of evaporator fans
    • 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
    • F25B2700/02—Humidity
    • 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
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
    • F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
    • F25D17/062—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation in household refrigerators
    • 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
    • F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
    • F25D2317/04—Treating air flowing to refrigeration compartments
    • F25D2317/041—Treating air flowing to refrigeration compartments by purification
    • F25D2317/0411—Treating air flowing to refrigeration compartments by purification by dehumidification
    • 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
    • F25D2400/00—General features of, or devices for refrigerators, cold rooms, ice-boxes, or for cooling or freezing apparatus not covered by any other subclass
    • F25D2400/04—Refrigerators with a horizontal mullion
    • 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
    • F25D2700/00—Means for sensing or measuring; Sensors therefor
    • F25D2700/12—Sensors measuring the inside temperature
    • 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
    • F25D2700/00—Means for sensing or measuring; Sensors therefor
    • F25D2700/14—Sensors measuring the temperature outside the refrigerator or freezer

Definitions

  • the present invention relates to a no-frost refrigeration device and an operating method for such a device.
  • an evaporator is disposed in a chamber separated from a storage compartment for chilled goods and heat exchange takes place between the chamber and the storage compartment by which means the storage compartment is cooled by blowing cooled and dried air into the storage compartment with the aid of a fan at the evaporator and extracting relatively warm moist air from the storage compartment into the chamber.
  • the storage compartment is not only cooled but also de-humidified.
  • the moisture is deposited on the evaporator.
  • This de-humidification prevents condensation from being deposited on storage surfaces and chilled goods in the storage compartment under critical climatic conditions, especially when the refrigerator is used in a warm environment at high air humidity.
  • this advantage can be converted into a disadvantage if stored foodstuffs are dried out by the intensive de-humidification.
  • the object was solved by a refrigeration device having the features of claim 1 or a method having the features of claim 10 .
  • the circulation power of the fan in such a refrigeration device By varying the circulation power of the fan in such a refrigeration device, at a given temperature difference between the storage compartment of the refrigeration device and the evaporator the heat flow between the two is also varied. That is to say, a reduction in the circulation power results in a reduced heat exchange and thus in stronger cooling of the evaporator. This intensified cooling causes more intensive drying of the air flowing past the evaporator.
  • the reduced circulation power has the effect that if the evaporator and fan are both activated, the cooling of the storage compartment takes place more slowly than at a higher circulation power so that the activation time of the evaporator is lengthened. This lengthening compensates for the reduced circulation power and has the result that in the course of an activation phase of the evaporator, more moisture is collected at low circulation power that at high circulation power.
  • a variable circulation power of the evaporator can be simply achieved by making the fan capable of being deactivated temporarily in the activated phase of the evaporator.
  • a control circuit is provided for controlling the operation of the evaporator and the fan which is set up to intermittently operate the fan when the evaporator is activated and thereby throttle its average circulation power compared to continuous operation.
  • a selector switch can be provided on the refrigeration device which allows the user to set a duty cycle for the intermittent operation of the fan and thus adapt the drying effect of the refrigeration device to the requirement.
  • the control circuit is coupled to at least one air conditioning sensor to record an air conditioning parameter such as the ambient temperature of the refrigeration device, the humidity of the ambient air or the humidity of the air in the interior and is set up to control the duty cycle as a function of at least one air conditioning parameter recorded by the sensor.
  • the fan can be set to different non-zero speeds to adapt the average circulation power to the requirements.
  • a selector switch can be provided which allows the user to preset a desired speed for the control circuit of the fan or the control circuit can be coupled to at least one air conditioning sensor in order to automatically control the circulation power of the fan using an air-conditioning parameter recorded by the sensor and a predefined target value of the air humidity.
  • the subject matter of the invention is also a method for operating a refrigeration device of the type described above, comprising the steps:
  • the estimate preferably comprises an air humidity measurement made directly in the affected storage compartment. It is then especially possible to take into account influences of the operation of the evaporator and the fan on the air humidity in the storage compartment when selecting the circulation power. In principle, however, it is also possible to estimate the air humidity in the storage compartment by using quantities correlated therewith such as temperature and air humidity of the environment and to select the circulation power as a function of the result of the estimate.
  • FIG. 1 is a schematic diagram of a no-frost refrigeration device according to the invention
  • FIG. 2 is a time diagram of the operation of an evaporator and fan according to a first embodiment of the invention.
  • FIG. 3 is a time diagram similar to FIG. 2 for a second embodiment of the invention.
  • FIG. 1 is a schematic diagram of a combination refrigeration device on which the present invention is implemented.
  • a cooling compartment 1 and a freezing compartment 2 form two temperature zones of the refrigeration device.
  • a coolant circuit comprises a compressor 3 which pumps a compressed coolant successively through two evaporators 4 , 5 of the freezing compartment 2 or the cooling compartment 1 and a heat exchanger 6 through which the coolant passes after it has expanded in the evaporators 4 , 5 before it re-enters the compressor 3 .
  • the evaporator 5 associated with the cooling compartment 1 is accommodated in a chamber 8 separated from the cooling compartment 1 by a thermally insulating wall 7 .
  • the chamber 8 communicates with the cooling compartment 1 via air inlet and outlet openings and a fan 9 for forced circulation of air between the chamber 8 and the cooling compartment 1 is disposed in one of said openings.
  • a control circuit 10 is connected to a temperature sensor 12 arranged in the cooling compartment and via control leads to the compressor 3 and the fan 9 and is capable of activating or de-activating the compressor 3 and the fan 9 , and indirectly via the compressor 3 the evaporators 4 , 5 , depending on a temperature recorded by the temperature sensor 12 .
  • the control circuit 10 is further connected to an air humidity sensor 13 which is disposed in the cooling compartment 1 .
  • a user-actuated selector switch 11 can be provided at the control circuit 10 which can be used to select a target value for the air humidity in the cooling compartment 1 .
  • the air humidity sensor 13 in the cooling compartment 1 can also be replaced by an air humidity sensor outside the cooling compartment and/or a sensor for the ambient temperature of the refrigeration device since its measured values allow the air humidity in the cooling compartment 1 to be deduced.
  • FIG. 2 illustrates the operating mode of the control circuit 10 with reference to the time profiles of a plurality of operating parameters of the refrigeration device.
  • Curve 3 ′ gives the operating state of the compressor 3 .
  • the temperature sensor 12 records that an upper limiting temperature has been exceeded, at time t it is activated until at time t 2 the temperature in the cooling compartment 1 falls below a lower limit. From this time the cooling compartment 1 heats up again until at time t 3 a new activation phase of the compressor 3 begins.
  • the air humidity recorded by the sensor 13 in the cooling compartment 1 is at a constant low level.
  • the fan 9 also starts operating, as shown by a curve 9 ′.
  • the temperature of the evaporator 5 shown by curve 5 ′, returns from a rest value To to a value T 1 .
  • Moisture from the air circulated by the fan 9 is deposited on the evaporator 5 so that the air humidity 13 ′ decreases slowly as far as the time t 2 when the fan 9 is de-activated. From the time t 3 the humidity 13 ′ increases substantially, for example, because the door of the refrigeration device is opened and warm moist air penetrates from outside.
  • the control circuit 10 recognises that more intensive drying is required and operates the fan 9 when at time t 4 the compressor 3 is activated again, intermittently with a duty cycle which is selected as a function of the air humidity recorded at time t 4 .
  • the activation time interval t 4 to t 5 is thus longer than the time interval t 1 to t 2 and the temperature T 2 of the evaporator 5 achieved during this time interval is lower than T 1 .
  • This lower temperature T 2 has the result that the air flowing past the evaporator 5 is dried more effectively and as a result of the lengthened activation time of the compressor 3 , a low air humidity value is finally achieved again.
  • the duty cycle with which the control circuit 10 operates the fan during the activation phase of the evaporator is, in the simplest case, a step function which has the value 1 for low air humidities and a non-zero value less than 1 for high air humidities; a step function having a plurality of values of the duty cycle which decrease with increasing air humidity or a continuous function can also be used for the control.
  • the control circuit 10 is designed to set different speeds of the fan 9 as a function of the measured air humidity.
  • the operating mode of this embodiment is shown in FIG. 3 . If the air humidity is low, the fan 9 runs at maximum speed in an activation phase of the evaporator 4 and the time profiles of activation and de-activation phases, evaporator temperature and air humidity are the same as in the case in FIG. 2 . Consequently, the diagram in FIG. 3 does not differ from that in FIG. 2 as far as the time t 4 . At time t 4 , with reference to the high air humidity measured at this time the control circuit 10 selects a speed of the fan 9 which is lower than its maximum speed.
  • the air humidity decreases continuously and accordingly, the speed of the fan 9 selected by the control circuit 10 with reference to the measured air humidity increases and as circulation power of the fan 9 increases, the temperature of the evaporator 5 also increases continuously over a large part of the time interval t 4 to t 5 .
  • FIGS. 2 and 3 show the case of rapid drying when a single activation phase t 4 to t 5 is sufficient to return the air humidity in the cooling compartment to a target value.
  • the drying process can also be distributed over a plurality of successive activation phases.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Air Conditioning Control Device (AREA)
  • Drying Of Solid Materials (AREA)

Abstract

A no-frost refrigeration device including at least one storage compartment with an evaporator located in a chamber separated from the storage compartment with a fan for circulating air between the storage compartment and the chamber. The evaporator is alternately activated and deactivated and the average circulation power of the fan during activation of the evaporator can be varied in order to raise the temperature of the evaporator by increasing the circulation power of the fan, thus shortening the duration of the activation phases of the evaporator and reducing the humidity in the storage compartment. In order to lower the temperature of the evaporator the circulation power of the fan is reduced, thus lengthening the duration of the activation phases of the evaporator and increasing the humidity in the storage compartment.

Description

  • The present invention relates to a no-frost refrigeration device and an operating method for such a device.
  • In refrigeration devices of this type, an evaporator is disposed in a chamber separated from a storage compartment for chilled goods and heat exchange takes place between the chamber and the storage compartment by which means the storage compartment is cooled by blowing cooled and dried air into the storage compartment with the aid of a fan at the evaporator and extracting relatively warm moist air from the storage compartment into the chamber. In this case, the storage compartment is not only cooled but also de-humidified. The moisture is deposited on the evaporator. This de-humidification prevents condensation from being deposited on storage surfaces and chilled goods in the storage compartment under critical climatic conditions, especially when the refrigerator is used in a warm environment at high air humidity. However, under less critical ambient conditions, this advantage can be converted into a disadvantage if stored foodstuffs are dried out by the intensive de-humidification.
  • There is thus a need for a no-frost refrigeration device and an operating method for such a device which allows flexible adaptation to the climatic conditions in the environment of the refrigerator.
  • The object was solved by a refrigeration device having the features of claim 1 or a method having the features of claim 10.
  • By varying the circulation power of the fan in such a refrigeration device, at a given temperature difference between the storage compartment of the refrigeration device and the evaporator the heat flow between the two is also varied. That is to say, a reduction in the circulation power results in a reduced heat exchange and thus in stronger cooling of the evaporator. This intensified cooling causes more intensive drying of the air flowing past the evaporator. At the same time, the reduced circulation power has the effect that if the evaporator and fan are both activated, the cooling of the storage compartment takes place more slowly than at a higher circulation power so that the activation time of the evaporator is lengthened. This lengthening compensates for the reduced circulation power and has the result that in the course of an activation phase of the evaporator, more moisture is collected at low circulation power that at high circulation power.
  • A variable circulation power of the evaporator can be simply achieved by making the fan capable of being deactivated temporarily in the activated phase of the evaporator. Advantageously, a control circuit is provided for controlling the operation of the evaporator and the fan which is set up to intermittently operate the fan when the evaporator is activated and thereby throttle its average circulation power compared to continuous operation.
  • A selector switch can be provided on the refrigeration device which allows the user to set a duty cycle for the intermittent operation of the fan and thus adapt the drying effect of the refrigeration device to the requirement. In a more convenient embodiment the control circuit is coupled to at least one air conditioning sensor to record an air conditioning parameter such as the ambient temperature of the refrigeration device, the humidity of the ambient air or the humidity of the air in the interior and is set up to control the duty cycle as a function of at least one air conditioning parameter recorded by the sensor.
  • As a result of another embodiment in the activation phase of the evaporator, the fan can be set to different non-zero speeds to adapt the average circulation power to the requirements. Here also a selector switch can be provided which allows the user to preset a desired speed for the control circuit of the fan or the control circuit can be coupled to at least one air conditioning sensor in order to automatically control the circulation power of the fan using an air-conditioning parameter recorded by the sensor and a predefined target value of the air humidity.
  • The subject matter of the invention is also a method for operating a refrigeration device of the type described above, comprising the steps:
    • a) estimating a moisture value in the storage compartment of the refrigeration device;
    • b) selecting a circulating power for the fan as a function of the estimated moisture value;
    • c) operating the fan at the selected circulating power.
  • The estimate preferably comprises an air humidity measurement made directly in the affected storage compartment. It is then especially possible to take into account influences of the operation of the evaporator and the fan on the air humidity in the storage compartment when selecting the circulation power. In principle, however, it is also possible to estimate the air humidity in the storage compartment by using quantities correlated therewith such as temperature and air humidity of the environment and to select the circulation power as a function of the result of the estimate.
  • Further features and advantages of the invention are obtained from the following description of the exemplary embodiments with reference to the appended figures. In the figures:
  • FIG. 1 is a schematic diagram of a no-frost refrigeration device according to the invention,
  • FIG. 2 is a time diagram of the operation of an evaporator and fan according to a first embodiment of the invention; and
  • FIG. 3 is a time diagram similar to FIG. 2 for a second embodiment of the invention.
  • FIG. 1 is a schematic diagram of a combination refrigeration device on which the present invention is implemented. A cooling compartment 1 and a freezing compartment 2 form two temperature zones of the refrigeration device. A coolant circuit comprises a compressor 3 which pumps a compressed coolant successively through two evaporators 4, 5 of the freezing compartment 2 or the cooling compartment 1 and a heat exchanger 6 through which the coolant passes after it has expanded in the evaporators 4, 5 before it re-enters the compressor 3. The evaporator 5 associated with the cooling compartment 1 is accommodated in a chamber 8 separated from the cooling compartment 1 by a thermally insulating wall 7. The chamber 8 communicates with the cooling compartment 1 via air inlet and outlet openings and a fan 9 for forced circulation of air between the chamber 8 and the cooling compartment 1 is disposed in one of said openings.
  • A control circuit 10 is connected to a temperature sensor 12 arranged in the cooling compartment and via control leads to the compressor 3 and the fan 9 and is capable of activating or de-activating the compressor 3 and the fan 9, and indirectly via the compressor 3 the evaporators 4, 5, depending on a temperature recorded by the temperature sensor 12. The control circuit 10 is further connected to an air humidity sensor 13 which is disposed in the cooling compartment 1. A user-actuated selector switch 11 can be provided at the control circuit 10 which can be used to select a target value for the air humidity in the cooling compartment 1.
  • As a variant, the air humidity sensor 13 in the cooling compartment 1 can also be replaced by an air humidity sensor outside the cooling compartment and/or a sensor for the ambient temperature of the refrigeration device since its measured values allow the air humidity in the cooling compartment 1 to be deduced.
  • FIG. 2 illustrates the operating mode of the control circuit 10 with reference to the time profiles of a plurality of operating parameters of the refrigeration device. Curve 3′ gives the operating state of the compressor 3. At time t0 it is de-activated; as soon as the temperature sensor 12 records that an upper limiting temperature has been exceeded, at time t it is activated until at time t2 the temperature in the cooling compartment 1 falls below a lower limit. From this time the cooling compartment 1 heats up again until at time t3 a new activation phase of the compressor 3 begins.
  • From t0 to t1 the air humidity recorded by the sensor 13 in the cooling compartment 1 is at a constant low level. When the compressor 3 is activated, at time t1 the fan 9 also starts operating, as shown by a curve 9′. The temperature of the evaporator 5, shown by curve 5′, returns from a rest value To to a value T1. Moisture from the air circulated by the fan 9 is deposited on the evaporator 5 so that the air humidity 13′ decreases slowly as far as the time t2 when the fan 9 is de-activated. From the time t3 the humidity 13′ increases substantially, for example, because the door of the refrigeration device is opened and warm moist air penetrates from outside. The control circuit 10 recognises that more intensive drying is required and operates the fan 9 when at time t4 the compressor 3 is activated again, intermittently with a duty cycle which is selected as a function of the air humidity recorded at time t4. This results in an average lower circulation power of the fan 9 than that during the time interval t1 to t2 so that heat exchange between the evaporator 5 and the cooling compartment 1 is slowed. The activation time interval t4 to t5 is thus longer than the time interval t1 to t2 and the temperature T2 of the evaporator 5 achieved during this time interval is lower than T1. This lower temperature T2 has the result that the air flowing past the evaporator 5 is dried more effectively and as a result of the lengthened activation time of the compressor 3, a low air humidity value is finally achieved again.
  • The duty cycle with which the control circuit 10 operates the fan during the activation phase of the evaporator is, in the simplest case, a step function which has the value 1 for low air humidities and a non-zero value less than 1 for high air humidities; a step function having a plurality of values of the duty cycle which decrease with increasing air humidity or a continuous function can also be used for the control.
  • In a second embodiment of the invention the control circuit 10 is designed to set different speeds of the fan 9 as a function of the measured air humidity. The operating mode of this embodiment is shown in FIG. 3. If the air humidity is low, the fan 9 runs at maximum speed in an activation phase of the evaporator 4 and the time profiles of activation and de-activation phases, evaporator temperature and air humidity are the same as in the case in FIG. 2. Consequently, the diagram in FIG. 3 does not differ from that in FIG. 2 as far as the time t4. At time t4, with reference to the high air humidity measured at this time the control circuit 10 selects a speed of the fan 9 which is lower than its maximum speed. During operation of the compressor and the fan, the air humidity decreases continuously and accordingly, the speed of the fan 9 selected by the control circuit 10 with reference to the measured air humidity increases and as circulation power of the fan 9 increases, the temperature of the evaporator 5 also increases continuously over a large part of the time interval t4 to t5.
  • FIGS. 2 and 3 show the case of rapid drying when a single activation phase t4 to t5 is sufficient to return the air humidity in the cooling compartment to a target value. Naturally, the drying process can also be distributed over a plurality of successive activation phases.
  • In FIGS. 2 and 3 it was assumed that respectively the maximum circulation power of the fan 9 corresponds to a desired low air humidity value in the cooling compartment so that intensified drying can be achieved by throttling the circulation power. However, it is quite expedient to dimension the fan 9 so that a desired air humidity can already be achieved at an average circulation power. This allows the heat exchange between cooling compartment 1 and evaporator 5 to be intensified by increasing the circulation power above this average power so that the duration of an activation phase of the compressor 3 is shortened and in this activation phase, as a result of a relatively high temperature of the evaporator 5 its drying effect is weakened. It is thereby also possible to specifically increase the air humidity in the cooling compartment 1 when this falls below a desired value.

Claims (17)

1-11. (canceled)
12. A no-frost refrigeration device, comprising:
at least one storage compartment;
an evaporator which is alternately activated and deactivated located in a chamber separated from said storage compartment;
a fan for circulating air between said storage compartment and said evaporator chamber; and
a control circuit which makes an average circulation power of said fan variable during an activation phase of said evaporator.
13. The no-frost refrigeration device according to claim 12, including said fan can be switched off temporarily during said activated phase of said evaporator.
14. The no-frost refrigeration device according to claim 13, including said control circuit controlling the operation of said evaporator and said fan set up to intermittently operate said fan during said activated phase of said evaporator.
15. The no-frost refrigeration device according to claim 14, including a selector switch on which a duty cycle can be set for said intermittent operation of said fan.
16. The no-frost refrigeration device according to claim 14, including said control circuit coupled to at least one air conditioning sensor and said control circuit regulates the duty cycle as a function of at least one air conditioning parameter recorded by said sensor.
17. The no-frost refrigeration device according to claim 12, including said activation phase of said evaporator and said fan can be set to different non-zero speeds.
18. The no-frost refrigeration device according to claim 17, including said control circuit for controlling the operation of said evaporator and said fan is set to operate said fan at one of a plurality of selectable non-zero speeds when said evaporator is activated.
19. The no-frost refrigeration device according to claim 18, including a selector switch on which a speed for operation of said fan can be set.
20. The no-frost refrigeration device according to claim 18, including said control circuit coupled to at least one air conditioning sensor and said control circuit regulates the speed of said fan using at least one air conditioning parameter recorded by said sensor.
21. A method for operating a refrigeration device, including
at least one storage compartment;
an evaporator which is alternately activated and deactivated located in a chamber separated from said storage compartment;
a fan for circulating air between said storage compartment and said evaporator chamber;
a control circuit which makes an average circulation power of said fan variable during an activation phase of said evaporator, comprising the steps of:
a) estimating a moisture value in said storage compartment;
b) selecting a circulating power for said fan as a function of said estimated moisture value; and
c) operating said fan at said selected circulating power.
22. The method according to claim 21, including selecting said circulating power to be lower, the higher said estimated moisture value.
23. The method according to claim 21, including switching said fan off temporarily during said activated phase of said evaporator.
24. The method according to claim 21, including controlling the operation of said evaporator and intermittently operating said fan during said activated phase of said evaporator.
25. The method according to claim 21, including sensing at least one air conditioning parameter and regulating the duty cycle as a function of at least one sensed air conditioning parameter.
26. The method according to claim 21, including setting said activation phase of said evaporator and said fan to different non-zero speeds.
27. The method according to claim 21, including controlling the operation of said evaporator and said fan and operating said fan at one of a plurality of selectable non-zero speeds when said evaporator is activated.
US10/560,156 2003-06-11 2004-06-09 Refrigeration device comprising controlled de-humidification Abandoned US20070137227A1 (en)

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DE20321771U1 (en) 2009-10-29
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