WO2016029576A1 - 冰箱 - Google Patents

冰箱 Download PDF

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Publication number
WO2016029576A1
WO2016029576A1 PCT/CN2014/092416 CN2014092416W WO2016029576A1 WO 2016029576 A1 WO2016029576 A1 WO 2016029576A1 CN 2014092416 W CN2014092416 W CN 2014092416W WO 2016029576 A1 WO2016029576 A1 WO 2016029576A1
Authority
WO
WIPO (PCT)
Prior art keywords
chamber
dry matter
temperature
capillary
cooling
Prior art date
Application number
PCT/CN2014/092416
Other languages
English (en)
French (fr)
Inventor
俞国新
丁恩伟
张维颖
王爱民
Original Assignee
青岛海尔智能技术研发有限公司
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by 青岛海尔智能技术研发有限公司 filed Critical 青岛海尔智能技术研发有限公司
Priority to RU2017108420A priority Critical patent/RU2655212C1/ru
Priority to EP14900349.3A priority patent/EP3187801B1/en
Priority to JP2017529120A priority patent/JP6423965B2/ja
Priority to US15/505,069 priority patent/US20170276420A1/en
Priority to AU2014404815A priority patent/AU2014404815B2/en
Publication of WO2016029576A1 publication Critical patent/WO2016029576A1/zh

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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
    • 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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/37—Capillary tubes
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same 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
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
    • 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
    • F25D17/045—Air flow control arrangements
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • 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
    • F25B2600/25—Control of valves
    • F25B2600/2507—Flow-diverting valves
    • 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
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D2700/00—Means for sensing or measuring; Sensors therefor
    • F25D2700/02—Sensors detecting door opening

Definitions

  • the invention relates to a refrigerator with a dry matter room, belonging to the field of household appliances.
  • Humidity generally refers to air humidity in meteorology, which is the content of water vapor in the air, and does not contain liquid or solid water. Air without water vapor is called dry air. Since the water vapor in the atmosphere can account for 0% to 4% of the volume of the air, it is generally referred to as the composition of the components in the dry air when the components of the various gases in the air are listed.
  • Absolute humidity refers to the mass of water vapor contained in a volume of air, typically in grams per cubic meter. The maximum absolute humidity is the highest humidity in saturation.
  • Relative Humidity is the ratio between absolute humidity and maximum humidity, and its value indicates how high the saturation of water vapor is.
  • Air with a relative humidity of 100% is saturated air.
  • the relative humidity is 50% of the air containing half of the water vapor reaching the saturation point of the air at the same temperature.
  • Water vapor in the air having a relative humidity of more than 100% generally condenses water or ice.
  • the relative humidity of the air exceeds 100%, the water vapor in the air will condense, which can be used to cool down and dehumidify; then the temperature will rise and the relative humidity will decrease, which can be used for drying purposes.
  • the drying of food is mainly related to relative humidity.
  • the relative humidity is low and the food is less likely to get moisture.
  • a storage room with low relative humidity developed in the refrigerator can be used to store various dry foods or foods that need to be dried (such as tea leaves, dried fruits, etc.). Dry foods are sensitive to the relative humidity of the storage environment, usually require a relatively low relative humidity, and can be kept within a relatively small range of relative humidity changes, otherwise it can easily lead to deterioration of food or affect quality.
  • the traditional way to reduce the relative humidity of the compartment is to use the principle of cooling and dehumidification, that is, using the cooling function of the evaporator, the air in the compartment is cooled down sufficiently by the evaporator, and the water vapor is dehumidified to obtain the air with lower absolute moisture content, and then Replace the air with a high absolute moisture content in the room (ie, the air with a higher absolute moisture content in the room is driven out, and the absolute moisture content in the room is reduced), and then the temperature is raised by the heating of the surrounding environment. In order to achieve a lower relative humidity and achieve the purpose of drying.
  • a refrigerator including a dry matter chamber and a cooling chamber, the refrigerator further including a first refrigeration cycle system and a second refrigeration cycle system for circulating a refrigerant, wherein the first refrigeration cycle The evaporation temperature of the system is lower than the evaporation temperature of the second refrigeration cycle system, and the first refrigeration cycle system includes an evaporator disposed in the cooling chamber, and a cooling passage is disposed between the cooling chamber and the dry chamber.
  • the refrigerator further includes a first capillary and a second capillary connected in parallel to the evaporator, and a control valve disposed on the first capillary and the second capillary, wherein the first capillary The flow rate is less than the flow rate of the second capillary tube, the first refrigeration system includes the evaporator and the first capillary tube, and the second refrigeration cycle system includes the evaporator and the second capillary tube, and the passage is performed according to a humidity condition of the dry matter chamber
  • the control valve performs switching between the opening of the first capillary and the second capillary.
  • the refrigerator further includes a controller electrically connected to the control valve and switching the first capillary and the second capillary according to the humidity condition of the dry matter chamber.
  • the refrigerator further includes a cooling compartment connected to the cooling passage, the cooling passage including a main road connected to the cooling chamber and a fork on the autonomous trunk to form a dry chamber, respectively The first branch road and the second branch road of the compartment.
  • the refrigerating compartment is a combination of any one or more of a refrigerating compartment, a freezing compartment, and a temperature changing compartment.
  • the refrigerator further includes a freezing compartment that is cooled by the first refrigeration cycle system, a refrigerating compartment that is cooled by the second refrigeration cycle system, and the second refrigeration cycle system includes a refrigerating evaporator.
  • the refrigerating compartment and the freezing compartment are formed by a foaming layer partition disposed in a refrigerating compartment, and the cooling passage is disposed to extend from the cooling compartment through the foaming layer partition.
  • the dry matter chamber is disposed or extends from the cooling chamber to the foam layer of the side of the freezer compartment and communicates with the dry matter chamber from the side of the dry matter chamber.
  • the refrigerator further includes a return air duct connecting the dry matter chamber, the return air duct is disposed to penetrate the foam layer partition downward and return the exchange airflow of the dry matter chamber to the freezing compartment Indoor, or arranged to extend from the side or rear of the freezer compartment and directly communicate with the cooling compartment; one side of the return air duct is provided with a return air damper.
  • the opening time of the cooling channel is determined as follows:
  • one side of the cold passage is provided with a damper for opening the cold passage.
  • the dry matter chamber is provided with a humidity sensor for detecting the relative humidity in the dry matter chamber and/or a temperature sensor for detecting the temperature inside the dry matter chamber.
  • the beneficial effects of the present invention are: by using the first refrigeration cycle system and the second refrigeration cycle system, and the dry matter chamber is in communication with the cooling chamber of the first refrigeration cycle system in which the evaporation temperature is relatively low, thereby allowing air entering the dry matter chamber The absolute moisture content is smaller, achieving a lower absolute humidity in the dry matter chamber.
  • FIG. 1 is a partial structural view of a refrigerator in accordance with an embodiment of the present invention.
  • Figure 2 shows a plot of relative humidity versus time in a dry matter chamber using capillary tubes of different thicknesses.
  • FIG. 3 is a partial schematic structural view of a refrigerator according to another embodiment of the present invention.
  • a refrigerator in an embodiment of the present invention has a refrigerating compartment 11, a freezing compartment, a changing greenhouse, a refrigeration cycle system for circulating a refrigerant, and a controller.
  • the refrigerating compartment 11, the freezing compartment and the variable greenhouse are collectively referred to as a refrigerating compartment.
  • the refrigerating compartment 11 is provided with a dry matter chamber 12, wherein the standard temperature in the refrigerating compartment 11 is 0-10°, generally 6-8°; the temperature in the dry compartment 12 is lower than the refrigerating compartment 11
  • the temperature inside is generally 3 ⁇ 5°.
  • a first temperature sensor (not shown) and a first humidity sensor (not shown) for detecting temperature and relative humidity in the dry matter chamber 12 are respectively disposed in the dry matter chamber 12, and the first temperature sensor is provided.
  • the first humidity sensor is electrically connected to the controller.
  • the refrigeration cycle system includes a condenser, a compressor, an evaporator 13, and a capillary.
  • the evaporator 13 is arranged inside a cooling chamber 14, which is arranged on the rear side of the refrigerating compartment.
  • a second temperature sensor (not shown) and a second humidity sensor (not shown) for detecting temperature and relative humidity in the cooling chamber 14 respectively, and the second temperature sensor are disposed in the cooling chamber 14
  • the second humidity sensor is electrically connected to the controller.
  • the dry matter chamber 12 communicates with the cooling chamber 14 and the refrigerating compartment 11 through a cooling passage 15, and the cooling passage 15 includes a main road 151 connected to the cooling chamber 14 and a forked trunk 151 formed on the fork to form a dry chamber.
  • the capillary includes a first capillary 161 and a second capillary 162 connected in parallel on the evaporator 13, wherein the flow rate of the first capillary 161 is smaller than the flow rate of the second capillary 162, and the flow rate of the second capillary 162 is in the existing refrigerator The flow rate of the capillary used is the same.
  • the condenser, the compressor, the evaporator 13, and the first capillary 161 form a first refrigeration cycle system
  • the condenser, the compressor, the evaporator 13, and the first capillary 161 form a second refrigeration cycle system.
  • the second capillary 162 is switched on (ie, the second refrigeration cycle system is switched on), and the refrigerant flows into the evaporator 13 through the second capillary 162.
  • the function of the capillary is to reduce the high-temperature, high-pressure liquid refrigerant to a low-pressure, low-temperature saturated gaseous refrigerant through the throttling action of the capillary.
  • the pressure of the gas and the temperature the lower the pressure, the lower the temperature. Therefore, after the throttling of the capillary, the pressure of the refrigerant is lowered, and the temperature of the refrigerant is lower.
  • the double capillary tube (the first capillary tube 161 and the second capillary tube 162) is used to constitute the double refrigeration cycle system ( The first refrigeration cycle system and the second refrigeration cycle system), therefore, when the second capillary 162 is switched on, the refrigerant flow rate is large, the pressure of the refrigerant after the pressure reduction by the second capillary 162 is small, and the evaporation temperature is relatively high.
  • the first capillary 161 is switched on, the refrigerant flow rate is small, the refrigerant pressure is lowered, and the evaporation temperature is relatively low.
  • the refrigerant flows into the evaporator 13 through the first capillary 161, so that the evaporating temperature is lower, and the absolute humidity of the air of the obtained cooling chamber 14 is also lower.
  • the second capillary 162 is switched on, and the refrigerant flows into the evaporator 13 through the second capillary 162, so that the cooling temperature of the evaporator 13 maintains the normal temperature range of the refrigerating compartment, and the temperature rises, thereby making the relative The humidity value is also reduced.
  • the first capillary tube 161 and the second capillary tube 162 are provided with a control valve 18, and the controller is electrically connected to the electromagnetic valve 8 and switches on and off of the first capillary tube 161 and the second capillary tube 162 according to the humidity condition of the dry matter chamber 12.
  • the controller determines the humidity state in the dry object chamber by the data detected by the first humidity sensor in the dry matter chamber 12, thereby determining whether to perform the switching between the first capillary tube 161 and the second capillary tube 162.
  • a fan 19 is disposed on the lower side of the evaporator 13, and the fan 19 is disposed in the cooling chamber 14.
  • a first damper 171 and a second damper 172 are respectively disposed on one side of the first branch road 152 and the second branch road 153. The opening of the first branch road 152 and the second branch road 153 respectively open the first damper 171
  • the second damper 172 is implemented, and the first damper 171 and the second damper 172 are controlled by the controller to be turned on.
  • the second branch road 153 is always in an open state during the operation of the refrigeration system, or the second branch road 153 is in an open state only when the second capillary 61 is opened, and the opening time of the first branch road 152 is : when the first capillary 161 is turned on or after the first capillary 161 is turned on.
  • the opening time of the first branching road 152 may be a time after the first capillary 161 is opened in the refrigerator, the preset time is the time obtained after multiple tests, or the first The opening time of one lane 152 can be determined as follows:
  • step S1 The specific implementation manner of the step S1 is as follows: the controller in the refrigerator receives and processes the temperature detected by the first temperature sensor and the relative humidity detected by the first humidity sensor to obtain an absolute humidity ⁇ 1, and controls The device receives and processes the temperature detected by the second temperature sensor and the relative humidity detected by the second humidity sensor to obtain an absolute humidity ⁇ 2.
  • the specific implementation of the S1 step may also be as follows: the controller in the refrigerator receives and processes The temperature detected by the first temperature sensor and the relative humidity detected by the first humidity sensor obtain an absolute humidity ⁇ 1, and the controller receives and processes the temperature obtained by the second temperature sensor to obtain an absolute humidity ⁇ 2. At this time, it is not necessary to detect the relative humidity by using the second humidity sensor.
  • the opening time of the second branch road 52 is determined as follows:
  • the opening time of the second branch road 52 can also be determined as follows:
  • the capillary used to form the curve 1 is the first capillary 161
  • the capillary forming the curve 2 is the second capillary 162.
  • the dehumidification effect of the curve 2 is better than the curve 1. Dehumidification effect.
  • the cooling passage 15 is disposed between the cooling chamber 14 and the dry chamber 12, the refrigerating chamber 11, and the fan 19 is disposed at one side of the evaporator 13, although in other embodiments, The cooling passage 15 is disposed between the cooling chamber 14 and the dry chamber 12 and the other refrigerating compartments, and the fan 19 is also disposed in the evaporator 13.
  • the first sub-main road 152 is connected to the main road 151 and the dry chamber 12,
  • the second branch road 153 connects the main road 151 and other refrigerating compartments, which may be freezer compartments.
  • the dual system is realized by connecting the first capillary 161 and the second capillary 162 having different flow rates on the evaporator 13, and since the controller is electrically connected to the electromagnetic valve 8 and is first according to the humidity condition of the dry matter chamber 12
  • the opening of the capillary 161 and the second capillary 162 is switched, so that when the first capillary 161 having a small opening flow rate is switched, the absolute humidity of the air in the cooling chamber 14 is lowered, so that the evaporating temperature is lower, so that the inside of the dry matter chamber 12 is entered.
  • the absolute moisture content of the air is smaller and achieves a better dehumidification effect.
  • a refrigerator in another embodiment of the present invention has a refrigerating compartment 21, a freezing compartment 22, a variable greenhouse, a first refrigeration cycle system for circulating a refrigerant, and a second refrigeration cycle system.
  • the refrigerating compartment 21 and the freezing compartment 22 are separated by a foam layer separator 27.
  • the refrigerating compartment 21 is provided with a dry matter chamber 23, and in the present embodiment, the dry matter chamber 23 is disposed adjacent to the foamed layer partition 27, and the standard temperature in the refrigerating compartment 21 is 0-10. °, generally 6 ⁇ 8°; the temperature in the dry matter chamber 23 is lower than the temperature in the refrigerating compartment 21, generally 3 ⁇ 5°.
  • the evaporation temperature of the first refrigeration cycle system is lower than the evaporation temperature of the second refrigeration cycle system
  • the first refrigeration cycle system includes a refrigeration evaporator 241, a condenser, a capillary tube, and a compressor
  • the second refrigeration cycle system includes Refrigerated evaporator 242, condenser, capillary and compressor.
  • a rear side of the freezing compartment 22 is provided with a first cooling chamber 251
  • a rear side of the refrigerating compartment 21 is provided with a second cooling chamber 252
  • the freezing evaporator 241 is disposed in the first cooling chamber 251, the refrigerating
  • the evaporator 242 is disposed within the second cooling chamber 252.
  • a humidity sensor for detecting the relative humidity in the dry matter chamber 23 and/or a temperature sensor for detecting the temperature in the dry matter chamber 23 are provided in the dry matter chamber 23.
  • the first cooling chamber 251 and the dry matter chamber 23 are communicated by a first cooling passage 26 extending from the first cooling chamber 251 to below the foamed layer partition 27 and extending upward through the foaming
  • the layer separator 27 is connected to the dry matter chamber 23 from the lower side of the dry matter chamber 23.
  • One side of the first cooling amount passage 26 is provided with a damper 28 that controls the first cooling amount passage 26 to open or close.
  • the first cooling channel may also be disposed to extend from the first cooling chamber 251 into the foam layer on the side of the freezing compartment 22 and extend upward to the side of the dry chamber 23 to
  • the dry matter chamber 23 is communicated from the side of the dry matter chamber 23 so as not to pass through the foamed layer separator 27.
  • a return air duct 271 is formed between the dry matter chamber 23 and the freezing compartment 22, and the return air duct 271 penetrates the foam layer partition 27 and the dry chamber 23
  • the exchange airflow is returned to the freezing compartment 22;
  • a return air damper 272 is provided on one side of the return air duct 271.
  • the return air duct 271 may also be disposed not to penetrate the foam layer partition 27, but an independent return air duct independently provided at the side or the rear of the refrigerator and directly communicating with the first cooling chamber 251. .
  • the first cooling chamber 251 and the freezing compartment 22 are not in communication with each other to supply a cold through passage to the freezing compartment 22, of course, in actual design, the first The cold flow passage may be configured to include a main road connected to the first cooling chamber 251 and a branch road formed on the autonomous main road to connect the dry matter chamber 23, the first branch road of the freezing compartment 22, and the second branch road.
  • the structure of the first branch passage may be formed through the foam layer partition 27 or at the side of the freezing compartment 22 as the first cold passage 26 described above.
  • the second cooling chamber 252 and the refrigerating compartment 21 communicate with each other through a second cooling passage 29.
  • the two systems are realized by two evaporators (the freezing evaporator 241 and the refrigerating evaporator 242), and the first cooling passage will be arranged with the freezing.
  • the first cooling chamber 251 of the evaporator 241 is in communication with the dry matter chamber 23, whereby the ventilating air of the dry matter chamber 23 is cooled and dehumidified by the freezing evaporator 241 having a lower temperature, so that the absolute humidity of the air sent into the dry matter chamber 23 is further increased. Low purpose for better dehumidification.
  • the opening time of the cold passage can be determined as follows:
  • the dry matter chambers 12, 23 are connected to the cooling chambers 14, 251 of the first refrigeration cycle system in which the evaporation temperature is relatively low, thereby entering the dry matter
  • the air in the chambers 12, 23 has a smaller absolute moisture content, achieving a lower absolute humidity in the dry chambers 12, 23.

Abstract

一种冰箱，包括干物室（12）和冷却室（14）、供制冷剂循环的第一制冷循环系统和第二制冷循环系统，其中第一制冷循环系统的蒸发温度低于第二制冷循环系统的蒸发温度。第一制冷循环系统包括设置在冷却室（14）内的蒸发器（13），冷却室（14）与干物室（12）之间设置有冷量通道（15），干物室（12）与其中设置蒸发温度相对低的第一制冷循环系统的冷却室（14）连通，从而使进入干物室（12）的空气的绝对含湿度更小，实现干物室（12）内更低的绝对湿度。

Description

冰箱
本申请要求了申请日为2014年08月29日，申请号为 201410432007.0，发明名称为“冰箱”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
【技术领域】
本发明涉及一种具有干物室的冰箱，属于家用电器领域。
【背景技术】
湿度一般在气象学中指的是空气湿度，是空气中水蒸气的含量，而不包含液态或固态的水。不含水蒸气的空气被称为干空气。由于大气中的水蒸气可以占空气体积的0%到4%，一般在列出空气中各种气体的成分的时候是指这些成分在干空气中所占的成分。
“绝对湿度”指一定体积的空气中含有的水蒸气的质量，一般其单位是公克／立方米。绝对湿度的最大限度是饱和状态下的最高湿度。
“相对湿度”（RH）是绝对湿度与最高湿度之间的比，它的值显示水蒸气的饱和度有多高。相对湿度为100%的空气是饱和的空气。相对湿度是50%的空气含有达到同温度的空气的饱和点的一半的水蒸气。相对湿度超过100%的空气中的水蒸气一般凝结出水或者冰。随着温度的升高，空气中能够溶解的水蒸气量增大，空气的绝对湿度值增大。当空气的相对湿度值超过100%时，空气中的水蒸气就会凝结出来，可以用来降温除湿；再将温度升高，相对湿度就会降低，可以用来达到干燥的目的。
食品的干燥，主要和相对湿度有关。相对湿度低，食品得到水分的可能性小。
冰箱中开发低相对湿度的储藏间可以用来储藏各种干物或者需要干燥的食品（如茶叶、干果等）。干燥食品对储藏环境的相对湿度比较敏感，通常需要一个比较低的相对湿度，并且能够恒定在一个比较小的相对湿度变化范围内，否则，极易导致食品的变质或者影响品质。
传统降低间室相对湿度的方式是采用降温除湿的原理，即利用蒸发器的降温功能，将间室内的空气通过蒸发器充分降温冷却，析出水汽除湿，得到绝对含湿量更低的空气，然后与间室内绝对含湿量较高的的空气置换（即将间室内绝对含湿量较高的的空气赶出，间室内的空气绝对含湿量得到降低），然后在周围环境的加热作用下升温，从而实现得到较低的相对湿度，达到干燥的目的。
【发明内容】
本发明的目的在于提供一种冰箱，可给冰箱内的干物室提供绝对含湿量更小的空气，实现更好的除湿效果。
为实现前述目的，本发明采用如下技术方案：一种冰箱，包括干物室和冷却室，所述冰箱还包括供制冷剂循环的第一制冷循环系统和第二制冷循环系统，其中第一制冷循环系统的蒸发温度低于第二制冷循环系统的蒸发温度，所述第一制冷循环系统包括设置在冷却室内的蒸发器，所述冷却室与干物室之间设置有冷量通道。
作为本发明的进一步改进，所述冰箱还包括并联后连接在蒸发器上的第一毛细管和第二毛细管、及设置在第一毛细管、第二毛细管上的控制阀，其中所述第一毛细管的流量小于第二毛细管的流量，所述第一制冷系统包括所述蒸发器和第一毛细管，所述第二制冷循环系统包括所述蒸发器和第二毛细管，根据干物室的湿度状况通过所述控制阀进行第一毛细管、第二毛细管的开启切换。
作为本发明的进一步改进，所述冰箱还包括控制器，所述控制器与控制阀电性连接并根据干物室的湿度状况进行第一毛细管、第二毛细管的开启切换。
作为本发明的进一步改进，所述冰箱还包括与冷量通道连接的制冷间室，所述冷量通道包括与冷却室连接的主干道及自主干道上分叉形成以分别连接干物室、制冷间室的第一分干道、第二分干道。
作为本发明的进一步改进，所述制冷间室为冷藏间室、冷冻间室、变温间室中的任意一种或以上的组合。
作为本发明的进一步改进，所述冰箱还包括由第一制冷循环系统实现制冷的冷冻间室、由第二制冷循环系统实现制冷的冷藏间室，所述第二制冷循环系统包括冷藏蒸发器，所述冷藏间室与冷冻间室通过发泡层隔板分隔形成，所述干物室设置在冷藏间室内，所述冷量通道设置为自冷却室延伸穿过所述发泡层隔板而连通干物室、或者设置为自冷却室延伸至冷冻间室侧部的发泡层内并自干物室的侧部与干物室相连通。作为本发明的进一步改进，所述冰箱还包括连通干物室的回风风道，所述回风风道设置为向下贯穿所述发泡层隔板并将干物室的交换气流回送到冷冻间室内、或者设置为自冷冻间室侧部或后部延伸并直接与冷却室连通；所述回风风道的一侧设置有回风风门。
作为本发明的进一步改进，所述冷量通道的打开时间通过如下方式确定：
S1：获取干物室内的绝对湿度ρ1，获取冷却室内的绝对湿度ρ2；
S2：当绝对湿度ρ1高于绝对湿度ρ2后，所述冷量通道打开；
或者通过如下方式确定：
S1’：获取干物室内的露点温度，获取冷却室内的温度；
S2’：当冷却室内的温度低于干物室内的露点温度后，冷量通道打开；
或者通过如下方式确定：
S1’’：获取干物室的温度W1；
S2’’：将获取到的干物室的温度W1与冰箱内预设的干物室的温度区间D0进行比对，并在干物室的温度W1大于预设的温度区间D0时，冷量通道打开。
作为本发明的进一步改进，所述冷量通道的一侧设置有用以实现打开冷量通道的风门。
作为本发明的进一步改进，所述干物室内设置有用以检测干物室内的相对湿度的湿度传感器和/或用以检测干物室内的温度的温度传感器。
本发明的有益效果是：通过采用第一制冷循环系统和第二制冷循环系统，且干物室与其中设置蒸发温度相对低的第一制冷循环系统的冷却室连通，从而使进入干物室内的空气的绝对含湿量更小，实现干物室内更低的绝对湿度。
【附图说明】
图1为本发明一实施例中冰箱的部分结构示意图。
图2表示在使用不同粗细的毛细管的情况下，干物室内的相对湿度对时间之间的曲线图。
图3为本发明另一实施方式中冰箱的部分结构示意图。
【具体实施方式】
请参见图1，本发明一实施例中的冰箱具有冷藏间室11、冷冻间室、变温室、供制冷剂循环的制冷循环系统及控制器。所述冷藏间室11、冷冻间室和变温室统称为制冷间室。所述冷藏间室11内设置有干物室12，所述冷藏间室11内的标准温度为0~10°，一般在6~8°；所述干物室12内的温度低于冷藏间室11内的温度，一般在3~5°。所述干物室12内设置有分别用以检测干物室12内的温度和相对湿度的第一温度感应器（未图示）和第一湿度感应器（未图示），所述第一温度感应器、第一湿度感应器与控制器电性连接。所述制冷循环系统包括冷凝器、压缩机、蒸发器13及毛细管。所述蒸发器13布置在冷却室14内，该冷却室14布置在制冷间室的后侧。所述冷却室14内设置有分别用以检测冷却室14内的温度和相对湿度的第二温度感应器（未图示）和第二湿度传感器（未图示），所述第二温度感应器、第二湿度感应器与控制器电性连接。所述干物室12与冷却室14、冷藏间室11通过冷量通道15连通，所述冷量通道15包括与冷却室14连接的主干道151及自主干道151上分叉形成以连接干物室12、冷藏间室11的第一分干道152、第二分干道153。所述毛细管包括并联连接在蒸发器13上的第一毛细管161和第二毛细管162，其中，第一毛细管161的流量小于第二毛细管162的流量，该第二毛细管162的流量与现有冰箱中所使用的毛细管的流量相同。所述冷凝器、压缩机、蒸发器13及第一毛细管161形成第一制冷循环系统，所述冷凝器、压缩机、蒸发器13及第一毛细管161形成第二制冷循环系统。在冰箱处于常规制冷时，切换开启第二毛细管162（即切换启动第二制冷循环系统），制冷剂经过该第二毛细管162流入至蒸发器13。
在制冷循环中，毛细管的作用是：通过毛细管的节流作用，将高温、高压态的液体制冷剂降压为低压态、低温态的饱和气态制冷剂。在体积一定的情况下，根据气体的压力和温度的正比关系，压力越低，温度就越低。故，经过毛细管的节流后，制冷剂的压力降低的越大，制冷剂的温度就越低。也就是说，毛细管的流量越小，经过节流后，制冷剂的压力降低的就越大，温度就越低，采用双毛细管（第一毛细管161和第二毛细管162）构成双制冷循环系统（第一制冷循环系统和第二制冷循环系统），所以，当切换开启第二毛细管162时，制冷剂流量大，经过第二毛细管162降压后的制冷剂压力降低的小，蒸发温度相对较高；当切换开启第一毛细管161，制冷剂流量小，制冷剂压力降低的大，蒸发温度相对较低。
当需要进行除湿干燥时，通过切换开启第一毛细管161，制冷剂经过第一毛细管161流入至蒸发器13，使得到的蒸发温度更低，得到的冷却室14的空气的绝对湿度也更低。当除湿功能结束后，切换开启第二毛细管162，制冷剂经过该第二毛细管162流入至蒸发器13，使蒸发器13的制冷温度维持冷藏间室正常的温度范围，温度升高，从而使相对湿度值也减小。
第一毛细管161和第二毛细管162上设置用控制阀18，控制器与电磁阀8电性连接并根据干物室12的湿度状况进行第一毛细管161、第二毛细管162的开启切换。在本实施例中，所述控制器通过干物室12内的第一湿度感应器检测到的数据进行判断干物室内的湿度状态，从而判断是否进行第一毛细管161、第二毛细管162的开启切换。
所述蒸发器13的下侧设置有风机19，该风机19设置在冷却室14内。所述第一分干道152和第二分干道153的一侧分别设置有第一风门171和第二风门172，该第一分干道152、第二分干道153的打开分别通过开启第一风门171、第二风门172实现，所述第一风门171和第二风门172由控制器控制是否开启。所述第二分干道153在制冷系统处于运行过程中，一直处于打开状态，或者该第二分干道153仅在开启第二毛细管61时处于打开状态，所述第一分干道152的打开时间为：在第一毛细管161开启时或者在第一毛细管161开启后。所述第一分干道152的打开时间可以为在冰箱内预设的一个晚于第一毛细管161开启后的时间，该预设时间为多次试验后所得到的时间，又或者，所述第一分干道152的打开时间可以通过如下方式确定：
S1：获取干物室12内的绝对湿度ρ1，获取冷却室14内的绝对湿度ρ2；
S2：当绝对湿度ρ1高于绝对湿度ρ2后，所述第一分干道152打开。
所述S1步骤的具体实现方式如下：所述冰箱内的控制器接收并处理所述第一温度感应器所检测得到的温度和第一湿度传感器所检测得到的相对湿度以获得绝对湿度ρ1，控制器接收并处理第二温度感应器所检测得到的温度和第二湿度感应器所检测得到的相对湿度以获得绝对湿度ρ2。
当所述冷却室14内的相对湿度为100%时，即，蒸发器13上已经有凝露产生时，所述S1步骤的具体实现方式还可以如下：所述冰箱内的控制器接收并处理所述第一温度感应器所检测得到的温度和第一湿度传感器所检测得到的相对湿度以获得绝对湿度ρ1，控制器接收并处理第二温度感应器所得到的温度以获得绝对湿度ρ2。此时，无需采用第二湿度感应器检测获得相对湿度。
而因绝对湿度值在冰箱中不易被测量，所以，在具体控制时，可采用温度作为标准，此时，第二分干道52打开时间通过如下方式确定：
S1’：获取干物室12内的露点温度，获取冷却室14内的温度，干物室12内的露点温度与冷却室14内的温度通过如下方式获得：冰箱内的控制器接收并处理干物室12内的第一温度感应器所检测到的温度和第一湿度传感器所检测到的相对湿度以获得露点温度，冷却室14的温度通过冷却室14内的第二温度感应器检测得到，所述露点温度通过在控制器内预置的湿空气焓湿图查询得知，具体由控制器根据所接收到的第一温度感应器所检测到的温度及湿度感应器所检测到的相对湿度后计算并查询得知；
S2’：当冷却室14内的温度低于干物室12内的露点温度后，第一分干道152打开。
除上述两种方式判断第二分干道52打开时间外，所述第二分干道52打开时间还可以通过如下方式确定：
S1’’：获取干物室12的温度W1；
S2’’：将获取到的干物室12的温度W1与冰箱内预设的干物室12的温度区间D0进行比对，并在干物室12的温度W1大于预设的温度区间D0时，冷量通道打开。
请参见图2，图中，形成曲线1所使用的毛细管为第一毛细管161，形成曲线2的毛细管为第二毛细管162，通过图2可看出，曲线2所反应的除湿效果优于曲线1的除湿效果。
在上述实施例中，所述冷量通道15为设置在冷却室14与干物室12、冷藏间室11之间，而风机19设置在蒸发器13的一侧，诚然，在其他实施方式中，所述冷量通道15为设置在冷却室14与干物室12和其他制冷间室之间，风机19同样设置在蒸发器13，此时第一分干道152为连接主干道151和干物室12，第二分干道153连接主干道151和其他制冷间室，该其他间室可以为冷冻间室。
在本实施例中，双系统由蒸发器13上连接流量不同的第一毛细管161和第二毛细管162实现，且由于控制器与电磁阀8电性连接并根据干物室12的湿度状况进行第一毛细管161、第二毛细管162的开启切换，从而当切换开启流量较小的第一毛细管161时，冷却室14内空气的绝对湿度降低，使得到的蒸发温度更低，使进入干物室12内的空气的绝对含湿量更小，实现更好的除湿效果。
请参见图3，本发明另一实施例中的冰箱具有冷藏间室21、冷冻间室22、变温室、供制冷剂循环的第一制冷循环系统和第二制冷循环系统。所述冷藏间室21与冷冻间室22通过发泡层隔板27分隔形成。所述冷藏间室21内设置有干物室23，在本实施方式中，所述干物室23贴靠所述发泡层隔板27设置，所述冷藏间室21内的标准温度为0~10°，一般在6~8°；所述干物室23内的温度低于冷藏间室21内的温度，一般在3~5°。所述第一制冷循环系统的蒸发温度低于第二制冷循环系统的蒸发温度，所述第一制冷循环系统包括冷冻蒸发器241、冷凝器、毛细管和压缩机，所述第二制冷循环系统包括冷藏蒸发器242、冷凝器、毛细管和压缩机。冷冻间室22的后侧设置有第一冷却室251，所述冷藏间室21的后侧设置有第二冷却室252，所述冷冻蒸发器241布置在第一冷却室251内，所述冷藏蒸发器242布置在第二冷却室252内。所述干物室23内设置有用以检测干物室23内的相对湿度的湿度传感器和/或用以检测干物室23内的温度的温度传感器。
所述第一冷却室251与干物室23通过第一冷量通道26连通，所述第一冷量通道26自第一冷却室251延伸至发泡层隔板27下方并向上贯穿所述发泡层隔板27，从而自干物室23下侧连通干物室23。所述第一冷量通道26的一侧设置有控制第一冷量通道26打开或者关闭的风门28。当然，在其他实施方式中，所述第一冷量通道也可以设置为自第一冷却室251延伸至冷冻间室22侧部的发泡层内并向上延伸至干物室23的侧部，以从干物室23的侧部连通干物室23，从而无需经过发泡层隔板27。
另外，在本实施例中，所述干物室23与冷冻间室22之间还形成有回风风道271，该回风风道271贯穿所述发泡层隔板27，并将干物室23的交换气流回送到冷冻间室22内；所述回风风道271的一侧设置有回风风门272。当然，所述回风风道271也可设置为不贯穿所述发泡层隔板27，而是独立设置在冰箱侧部或后部并直接与第一冷却室251连通的独立回风风道。
此外，在本实施例中，所述第一冷却室251与冷冻间室22未视出连通两者以向冷冻间室22供应冷量的直通通道，当然，在实际设计时，所述第一冷量通道可以设置为包括与第一冷却室251连接的主干道及自主干道上分叉形成以连接干物室23、冷冻间室22的第一分干道、第二分干道。所述第一分干道的结构可以如上述第一冷量通道26形成为穿过发泡层隔板27或者设置在冷冻间室22的侧部。所述第二冷却室252与冷藏间室21之间通过第二冷量通道29连通。
在本实施例中，通过双系统（第一制冷循环系统和第二制冷循环系统）由两个蒸发器（冷冻蒸发器241和冷藏蒸发器242）实现，且第一冷量通道将布置有冷冻蒸发器241的第一冷却室251与干物室23连通，从而，利用温度更低的冷冻蒸发器241，对干物室23换气空气进行降温除湿，实现送入干物室23内空气的绝对湿度更低的目的，达到更好的除湿效果。
本实施例中，为了使进入干物室内23的空气的绝对含湿量更小，冷量通道的打开时间可通过如下方式确定：
S1：获取干物室内的绝对湿度ρ1，获取冷却室内的绝对湿度ρ2；
S2：当绝对湿度ρ1高于绝对湿度ρ2后，所述冷量通道打开；
或者通过如下方式确定：
S1’：获取干物室内的露点温度，获取冷却室内的温度；
S2’：当冷却室内的温度低于干物室内的露点温度后，冷量通道打开；
或者通过如下方式确定：
S1’’：获取干物室的温度W1；
S2’’：将获取到的干物室的温度W1与冰箱内预设的干物室的温度区间D0进行比对，并在干物室的温度W1大于预设的温度区间D0时，冷量通道打开。
综上所述，通过采用第一制冷循环系统和第二制冷循环系统，且干物室12、23与其中设置蒸发温度相对低的第一制冷循环系统的冷却室14、251连通，从而使进入干物室内12、23的空气的绝对含湿量更小，实现干物室12、23内更低的绝对湿度。
尽管为示例目的，已经公开了本发明的优选实施方式，但是本领域的普通技术人员将意识到，在不脱离由所附的权利要求书公开的本发明的范围和精神的情况下，各种改进、增加以及取代是可能的。

Claims (10)

  1. 一种冰箱，包括干物室和冷却室，其特征在于：所述冰箱还包括供制冷剂循环的第一制冷循环系统和第二制冷循环系统，其中第一制冷循环系统的蒸发温度低于第二制冷循环系统的蒸发温度，所述第一制冷循环系统包括设置在冷却室内的蒸发器，所述冷却室与干物室之间设置有冷量通道。
  2. 根据权利要求1所述的冰箱，其特征在于：所述冰箱还包括并联后连接在蒸发器上的第一毛细管和第二毛细管、及设置在第一毛细管、第二毛细管上的控制阀，其中所述第一毛细管的流量小于第二毛细管的流量，所述第一制冷系统包括所述蒸发器和第一毛细管，所述第二制冷循环系统包括所述蒸发器和第二毛细管，根据干物室的湿度状况通过所述控制阀进行第一毛细管、第二毛细管的开启切换。
  3. 根据权利要求2所述的冰箱，其特征在于：所述冰箱还包括控制器，所述控制器与控制阀电性连接并根据干物室的湿度状况进行第一毛细管、第二毛细管的开启切换。
  4. 根据权利要求2所述的冰箱，其特征在于：所述冰箱还包括与冷量通道连接的制冷间室，所述冷量通道包括与冷却室连接的主干道及自主干道上分叉形成以分别连接干物室、制冷间室的第一分干道、第二分干道。
  5. 根据权利要求4所述的冰箱，其特征在于：所述制冷间室为冷藏间室、冷冻间室、变温间室中的任意一种或以上的组合。
  6. 根据权利要求1所述的冰箱，其特征在于：所述冰箱还包括由第一制冷循环系统实现制冷的冷冻间室、由第二制冷循环系统实现制冷的冷藏间室，所述第二制冷循环系统包括冷藏蒸发器，所述冷藏间室与冷冻间室通过发泡层隔板分隔形成，所述干物室设置在冷藏间室内，所述冷量通道设置为自冷却室延伸穿过所述发泡层隔板而连通干物室、或者设置为自冷却室延伸至冷冻间室侧部的发泡层内并自干物室的侧部与干物室相连通。
  7. 根据权利要求6所述的冰箱，其特征在于：所述冰箱还包括连通干物室的回风风道，所述回风风道设置为向下贯穿所述发泡层隔板并将干物室的交换气流回送到冷冻间室内、或者设置为自冷冻间室侧部或后部延伸并直接与冷却室连通；所述回风风道的一侧设置有回风风门。
  8. 根据权利要求1所述的冰箱，其特征在于：所述冷量通道的打开时间通过如下方式确定：
    S1：获取干物室内的绝对湿度ρ1，获取冷却室内的绝对湿度ρ2；
    S2：当绝对湿度ρ1高于绝对湿度ρ2后，所述冷量通道打开；
    或者通过如下方式确定：
    S1’：获取干物室内的露点温度，获取冷却室内的温度；
    S2’：当冷却室内的温度低于干物室内的露点温度后，冷量通道打开；
    或者通过如下方式确定：
    S1’’：获取干物室的温度W1；
    S2’’：将获取到的干物室的温度W1与冰箱内预设的干物室的温度区间D0进行比对，并在干物室的温度W1大于预设的温度区间D0时，冷量通道打开。
  9. 根据权利要求1所述的冰箱，其特征在于：所述冷量通道的一侧设置有用以实现打开冷量通道的风门。
  10. 根据权利要求1所述的冰箱，其特征在于：所述干物室内设置有用以检测干物室内的相对湿度的湿度传感器和/或用以检测干物室内的温度的温度传感器。
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Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9994385B2 (en) 2016-06-06 2018-06-12 Google Llc Shipping container with multiple temperature zones
CN107883664A (zh) * 2016-09-30 2018-04-06 松下电器研究开发(苏州)有限公司 干物制备装置、干物制备方法以及冰箱
DE102016220163A1 (de) * 2016-10-14 2018-04-19 BSH Hausgeräte GmbH Kältegerät mit Dörrfunktion und Betriebsverfahren dafür
CN108548362B (zh) * 2018-03-26 2021-05-25 重庆海尔制冷电器有限公司 具有干燥区的冰箱及干燥区的除湿方法
CN110440519B (zh) * 2018-05-04 2022-11-04 青岛海尔智能技术研发有限公司 一种冰箱的控制方法、装置、存储介质和冰箱
CN110440517B (zh) * 2018-05-04 2022-10-28 青岛海尔智能技术研发有限公司 一种冰箱的湿度控制方法、装置、存储介质和冰箱
CN110440497A (zh) * 2018-05-04 2019-11-12 青岛海尔智能技术研发有限公司 一种冰箱及其控制方法
CN111121368B (zh) * 2018-11-01 2022-10-28 博西华电器（江苏）有限公司 制冷器具及其控制方法
CN111854265B (zh) * 2019-04-30 2022-06-14 松下电器研究开发(苏州)有限公司 冰箱及其控制方法
CN115507599B (zh) * 2021-06-07 2024-03-19 青岛海尔电冰箱有限公司 冷藏冷冻装置及其控制方法

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1530618A (zh) * 2003-03-12 2004-09-22 乐金电子(天津)电器有限公司 电冰箱应对负荷的运行方法
CN1553128A (zh) * 2003-06-06 2004-12-08 博西华家用电器有限公司 家用控温控湿电冰箱及其控制方法
CN101266094A (zh) * 2003-12-09 2008-09-17 松下电器产业株式会社 冰箱
JP2009287817A (ja) * 2008-05-28 2009-12-10 Hitachi Appliances Inc 冷蔵庫
CN203190740U (zh) * 2013-01-31 2013-09-11 松下电器产业株式会社 干燥装置以及具备该干燥装置的冰箱
CN103557657A (zh) * 2013-11-15 2014-02-05 合肥美的电冰箱有限公司 风冷冰箱

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS495980Y1 (zh) * 1969-07-01 1974-02-12
US5375428A (en) * 1992-08-14 1994-12-27 Whirlpool Corporation Control algorithm for dual temperature evaporator system
US5231847A (en) * 1992-08-14 1993-08-03 Whirlpool Corporation Multi-temperature evaporator refrigerator system with variable speed compressor
JPH07180951A (ja) * 1993-12-24 1995-07-18 Toshiba Corp 乾燥機能付き冷蔵庫
DE69524370T2 (de) * 1994-08-03 2002-08-22 Matsushita Refrigeration Kühlschrank
JP4206792B2 (ja) * 2003-03-25 2009-01-14 三菱電機株式会社 冷蔵庫
JP2006266585A (ja) * 2005-03-23 2006-10-05 Toshiba Corp 冷蔵庫
JP5251228B2 (ja) * 2007-04-26 2013-07-31 パナソニック株式会社 冷蔵庫
JP4192200B1 (ja) * 2007-11-28 2008-12-03 株式会社東芝 冷凍冷蔵庫
CN201344692Y (zh) * 2008-11-24 2009-11-11 海信（北京）电器有限公司 可自动调节制冷剂流量的电冰箱
CN101865585A (zh) * 2009-04-15 2010-10-20 凌建军 一种双毛细管多制冷回路的冰箱
KR101641225B1 (ko) * 2009-06-30 2016-07-20 엘지전자 주식회사 냉장고의 온도 제어방법 및 그를 이용한 냉장고
CN202420079U (zh) * 2011-11-10 2012-09-05 苏州三星电子有限公司 一种具有干燥间的冰箱
US20130186129A1 (en) * 2012-01-25 2013-07-25 Lg Electronics Inc. Refrigerator
DE102013005476A1 (de) * 2012-04-01 2013-10-02 Liebherr-Hausgeräte Ochsenhausen GmbH Kühl- und/oder Gefriergerät

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1530618A (zh) * 2003-03-12 2004-09-22 乐金电子(天津)电器有限公司 电冰箱应对负荷的运行方法
CN1553128A (zh) * 2003-06-06 2004-12-08 博西华家用电器有限公司 家用控温控湿电冰箱及其控制方法
CN101266094A (zh) * 2003-12-09 2008-09-17 松下电器产业株式会社 冰箱
JP2009287817A (ja) * 2008-05-28 2009-12-10 Hitachi Appliances Inc 冷蔵庫
CN203190740U (zh) * 2013-01-31 2013-09-11 松下电器产业株式会社 干燥装置以及具备该干燥装置的冰箱
CN103557657A (zh) * 2013-11-15 2014-02-05 合肥美的电冰箱有限公司 风冷冰箱

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3187801A4 *

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