WO2006017959A1 - Refrigerateur composite possedant un systeme de refrigeration a cycles multiples et son procede de controle - Google Patents

Refrigerateur composite possedant un systeme de refrigeration a cycles multiples et son procede de controle Download PDF

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Publication number
WO2006017959A1
WO2006017959A1 PCT/CN2004/001346 CN2004001346W WO2006017959A1 WO 2006017959 A1 WO2006017959 A1 WO 2006017959A1 CN 2004001346 W CN2004001346 W CN 2004001346W WO 2006017959 A1 WO2006017959 A1 WO 2006017959A1
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WO
WIPO (PCT)
Prior art keywords
refrigerating
evaporator
refrigeration
auxiliary
temperature
Prior art date
Application number
PCT/CN2004/001346
Other languages
English (en)
French (fr)
Inventor
Yanquan Li
Original Assignee
Hisense Group Co., Ltd.
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
Priority claimed from CN 200410035589 external-priority patent/CN1598447A/zh
Priority claimed from CN 200410035588 external-priority patent/CN1598446A/zh
Application filed by Hisense Group Co., Ltd. filed Critical Hisense Group Co., Ltd.
Priority to US11/568,432 priority Critical patent/US20080190123A1/en
Priority to EP04797376A priority patent/EP1780484A1/en
Publication of WO2006017959A1 publication Critical patent/WO2006017959A1/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
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • 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
    • F25D11/022—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures with two or more evaporators

Definitions

  • This invention relates to a refrigerator, and more particularly to a refrigerator having a compression device of a plurality of serially arranged refrigeration circuits. Background technique
  • Prior art 1 a general refrigeration refrigeration system refrigerator freezer, the refrigeration cycle is a single system, see Figure 1, the compressor 1 outlet end is connected to the condenser 2, followed by the throttling capillary 3, the capillary 3 is followed by freezing evaporation
  • the refrigerator 4, the refrigerating evaporator 5, or the refrigerating evaporator 5 is connected first, followed by the refrigerating evaporator 4, and finally returned to the compressor 1 via the return air pipe 6.
  • the working principle of the prior art 1 is such that the compressor 1 is stopped and controlled by a temperature sensor placed in the refrigerating compartment.
  • the compressor operates, and the temperature of the two compartments simultaneously decreases; when the temperature is lower than the set shutdown temperature, the compressor stops running.
  • the temperature of both compartments rises at the same time.
  • the temperature of the refrigerating compartment rises to the set starting temperature, it is turned on again, and the cycle is repeated to keep the temperature of the refrigerating compartment within a certain range.
  • the system has a simple structure, and the operation is controlled by the temperature of the refrigerating compartment.
  • the temperature of the freezing compartment cannot be independently controlled.
  • the freezing temperature also changes.
  • the summer ambient temperature rises, the freezer compartment temperature is too low, and consumes more cold.
  • the winter ambient temperature is lower, the refrigeration start-up rate is too low, and the freezer compartment temperature is too high.
  • the general solution is to refrigerate.
  • An auxiliary heating device is added to the chamber to force the cycle to start to lower the temperature in the freezer compartment. Obviously, the auxiliary heating device consumes extra energy.
  • Prior art 2 a conventional dual-system topology, usually on the basis of the aforementioned pre-chilled and connected frozen topology, a solenoid valve 31 is connected to the end of the condenser 2, see FIG. 2, and the solenoid valve 31 has two outlets.
  • the other outlet is connected to the freezing auxiliary throttle capillary 34
  • the end of the capillary 34 is connected to the outlet end of the refrigerating evaporator 5 and the inlet end of the freezing evaporator 4, and the end of the freezing evaporator 4 is passed through the return pipe.
  • 6 Connect the compressor 1 return air end.
  • the working principle of the prior art 2 is as follows: the opening and closing of the compressor 1 is controlled by a temperature sensor placed in the refrigerating compartment. When the temperature of the refrigerating compartment is higher than the set down temperature, the compressor operates, and the temperature of the two compartments simultaneously decreases; when the temperature is lower than the set shutdown temperature, the compressor stops running. The temperature of the two compartments rises at the same time. When the freezing temperature or the lower ambient temperature causes the freezing chamber temperature to rise, the freezing assist cycle can be started to separately lower the freezing chamber temperature. Compared with the general single system circulation loop, the auxiliary heating device is eliminated, and energy can be saved when the ambient temperature is low.
  • the dual-system refrigerated freezer also has the advantage of being able to shut down the refrigerating compartment and use the freezer compartment independently. At the same time, the system also has a large freezing capacity because the freezer compartment has an independent capillary throttling control. This technology has been widely used.
  • Prior Art 3 In order to solve the problem of shutting down the freezer compartment and independently using the refrigerator compartment, the prior invention patent gives a parallel topology, see Fig. 3, which is characterized by two independent throttling and evaporation for refrigeration and freezing. Refrigeration circuit. This topology is simple, and it can independently switch the refrigeration and refrigeration circuits to save energy. However, when it is used normally, that is, when it is refrigerated or frozen, the load changes too much, the evaporation pressure and temperature deviate from the optimum value, the system efficiency decreases, and the power consumption increases. Summary of the invention
  • the novel topology refrigeration system called "re-establishment multi-cycle” proposed by the invention successfully solves the contradiction between the refrigeration efficiency and the freeze-off function, so that the system efficiency is optimal when used under normal use conditions, namely, refrigerating and freezing. , effectively reduce power consumption. At the same time, it can realize the function of closing the freezer compartment, and can convert the cold storage room into different freezer compartments.
  • the so-called “re-establishment,” refers to the “composite” refrigeration system loop and the "independent" control of each compartment temperature.
  • the multi-cycle refrigeration system refrigerator of the present invention is realized by: comprising a main CPU, a temperature sensor and a refrigeration cycle, wherein the refrigeration cycle is composed of a compressor, a condenser, a main capillary, a refrigerating evaporator, a refrigerating evaporator and a return
  • the trachea is connected in series
  • a solenoid valve is connected in series behind the condenser.
  • the solenoid valve has two output ends, one end of which is connected to the main capillary tube, and the other end is connected to the refrigerating auxiliary circulation branch.
  • the program can have the following specific structure: First, the refrigerating evaporator in the refrigeration cycle is preceded, and the refrigerating evaporator is in the rear; the refrigerating auxiliary circulation branch includes a refrigerating auxiliary capillary connected in parallel with the main capillary and the refrigerating evaporator in series, connected to the output of the solenoid valve and Refrigerate the evaporator between the inputs.
  • the refrigeration evaporator is preceded by a refrigerated evaporator, and the refrigerated evaporator is at a rear;
  • the refrigerated auxiliary circulation branch includes an auxiliary capillary and an auxiliary refrigerating evaporator connected in series therewith, the refrigerated auxiliary circulation branch and the main capillary in series and frozen
  • the evaporators are connected in parallel and connected between the solenoid valve output and the refrigerated evaporator input.
  • the refrigeration evaporator is preceded by a refrigerated evaporator, and the refrigerated evaporator is at a rear;
  • the refrigerated auxiliary circulation branch includes an auxiliary capillary and an auxiliary refrigerating evaporator connected in series therewith, the refrigerated auxiliary circulation branch and the main capillary in series, frozen
  • the evaporator is connected in parallel with the refrigerated evaporator and is connected between the solenoid valve output and the refrigerated evaporator output.
  • the refrigerating evaporator in the refrigeration cycle is preceded by a refrigerated evaporator;
  • the refrigerated auxiliary circulation branch includes an auxiliary capillary and an auxiliary refrigerating evaporator connected in series therewith, the refrigerated auxiliary circulation branch and the main capillary in series, refrigerated
  • the evaporator is connected in parallel with the refrigerated evaporator and is connected between the solenoid valve output and the freezer evaporator output.
  • the electromagnetic is a two-way three-way integrated valve, which is respectively connected with a condenser, a main capillary and a cold auxiliary capillary.
  • the solenoid valve can also be two separate electromagnetic shut-off valves, one connected between the condenser and the main capillary, and one connected between the condenser and the refrigerating auxiliary capillary.
  • the control method of the present invention comprises the following steps:
  • the refrigerator is energized, initialized, and the main CPU detects whether "freeze off” is activated. If activated, the solenoid valve closes the refrigeration cycle, simultaneously turns on the refrigeration auxiliary circulation branch, runs to the freezer set temperature, and then starts back. Continue to test; if "freeze off” is not activated, the solenoid valve is connected to the refrigeration cycle, and the refrigeration auxiliary circulation branch is turned off, and then proceeds to step II; II.
  • 1 is a block diagram showing the structure of the prior art 1;
  • Figure 2 is a block diagram showing the structure of the prior art 2
  • Figure 3 is a block diagram showing the structure of the prior art 3
  • FIG. 4 is a block diagram showing the structure of Embodiment 1 of the present invention.
  • Figure 5 is a block diagram showing the structure of a second embodiment of the present invention.
  • FIG. 6 is a block diagram showing the structure of Embodiment 3 of the present invention.
  • FIG. 7 is a block diagram showing the structure of Embodiment 4 of the present invention.
  • Figure 8 is a block diagram showing the configuration of a fifth embodiment of the present invention. BEST MODE FOR CARRYING OUT THE INVENTION
  • Embodiment 1 - shows a typical system topology of the present invention, which includes a main CPU, a temperature sensor and a refrigeration cycle.
  • the refrigeration cycle is composed of a compressor 1, a condenser 2, and a main capillary. 3.
  • the freezing evaporator 41, the refrigerating evaporator 51 and the return air pipe 6 are connected in series, and the solenoid valve 31 is connected in series behind the condenser 2.
  • the electromagnetic valve 31 has two output ends, one end of which is connected to the main capillary 3, and the other One end is connected to the refrigerating auxiliary circulation branch, and the refrigerating auxiliary circulation branch includes a refrigerating auxiliary capillary 32 connected in parallel with the main capillary 3 and the refrigerating evaporator 41 connected in series, and connected to the output end of the electromagnetic valve 31 and the input end of the refrigerating evaporator 51. between.
  • the refrigerant cycle system of the present invention flows in this way:
  • the compressor After the refrigerator is turned on, the compressor starts to operate, the refrigerant is compressed by the compressor 1 into a high-pressure gas, and after being condensed by the condenser 2, it flows through the solenoid valve 31.
  • the temperature sensor detects the temperature of the freezing compartment and the refrigerating compartment.
  • the CPU controls the solenoid valve 31 to throw.
  • the refrigerant At the freezing and refrigerating off position, the refrigerant is compressed by the compressor 1 into a high-pressure gas, and after being condensed by the condenser 2, it flows through the solenoid valve 31.
  • the refrigerant is throttled by the main capillary 3 to become a low-pressure cryogenic liquid.
  • the liquid is partially evaporated into a low temperature gas in the freezing evaporator 41 to absorb the heat of the freezing chamber F.
  • the liquid that has not completely evaporated flows into the refrigerating evaporator 51 to continue to evaporate, absorbs the heat of the refrigerating chamber R, and finally evaporates completely into a low-temperature gas, and is heated by the returning pipe 6 to be sucked into the compressor 1 to form a circulation; at this time, the refrigerating and freezing are simultaneously involved in the circulation.
  • the CPU controls the solenoid valve 31 to be thrown in the freezing opening and refrigerating auxiliary circulation opening position, and the refrigerant is compressed into a high pressure gas by the compressor 1, and after being condensed by the condenser 2, Flows through the solenoid valve 31.
  • the refrigerant is throttled by the main capillary 3 to become a low-pressure cryogenic liquid.
  • the liquid is partially evaporated into a low temperature gas in the freezing evaporator 41 to absorb the heat of the freezing chamber F.
  • the liquid that has not completely evaporated flows into the refrigerating evaporator 51 to continue to evaporate, absorbing the heat of the cooling chamber R.
  • the refrigerant is throttled by the refrigeration auxiliary circulation throttling capillary 32 to become a low pressure cryogenic liquid.
  • the liquid evaporates into a low temperature gas in the refrigerating evaporator 51 to absorb the heat of the refrigerating compartment R.
  • it is completely evaporated into a low-temperature gas, and is heated by the return pipe 6 to be sucked into the compressor 1 to form a cycle; at this time, the temperature of the refrigerator compartment can be lowered, one is to achieve a rapid cooling function, and the other is to convert the refrigerator compartment into a freezer compartment.
  • the CPU controls the solenoid valve 31 to be thrown in the freezing off and the refrigerating auxiliary circulation open position, and the refrigerant is throttled by the refrigerating auxiliary circulation throttling capillary 32.
  • the liquid evaporates into a low temperature gas in the refrigerating evaporator 51, absorbing the heat of the refrigerating compartment R. Finally, it is completely evaporated into a low-temperature gas. After being heated by the return pipe 6, it is sucked into the compressor 1 to form a circulation.
  • the solenoid valve 31 described in this patent is provided as an integral valve of a two-position three-way.
  • the refrigerator, refrigerated evaporator 51 and refrigerated evaporator 41 described in this patent comprise a single evaporator and a combination of multiple evaporators in series for the same or different temperature compartments.
  • the main control of the compressor operation adopts the refrigerating temperature sensor.
  • the system matching principle is the target ambient temperature (for example, 25 degrees Celsius, or other temperature, according to the average temperature of the target market or the climate type of the refrigerator design), and at the same time achieve the refrigerating target. Temperature (eg, 5 degrees Celsius), freezing target temperature (eg, -18 degrees Celsius), to maximize the efficiency of the refrigerant cycle system, to achieve the best energy-saving purposes in the refrigerator at the general target ambient temperature used for refrigeration and freezing.
  • the typical temperature control strategy of the refrigerator described in this patent is as follows: due to the increase of the ambient temperature or the change of the refrigerating load, the refrigerating temperature is raised to a certain amount (refrigerating target temperature + X), and the solenoid valve of the refrigerating auxiliary circulation circuit can be turned on and off. The temperature of the refrigerating compartment is lowered separately to reach the refrigerating target temperature. When the freezing temperature is reduced by more than a certain amount (freezing target temperature -Y), the cold solenoid valve switch can be turned off, the refrigeration cycle is cut off, and energy loss is reduced.
  • X is 1 to 3 degrees Celsius and Y is 2 to 5 degrees Celsius.
  • the program clears START, detects if "freeze off” is activated, and if activated, the solenoid valve closes the refrigeration cycle and turns on the refrigeration auxiliary circuit. It is a “refrigerated” single loop circuit that operates at a set temperature of the "refrigerator” and can be set to a larger temperature range.
  • the solenoid valve opens the refrigeration cycle and shuts off the refrigeration auxiliary circuit.
  • the temperature of the refrigerating compartment and the freezing compartment are detected, and when the refrigerating compartment temperature or the freezing compartment temperature is higher than the set starting temperature, the compressor is started. If the freezing compartment temperature is too low (freezing target temperature -Y) and the refrigerating compartment temperature is higher than the set starting temperature, the solenoid valve closes the refrigerating circuit and turns on the refrigerating auxiliary circulation loop to cool the refrigerating compartment.
  • Example 2 Example 2:
  • the solenoid valve 31 of the present embodiment is two independent electromagnetic cut-off valves, one connected between the condenser 2 and the main capillary 3, and the other connected to the condenser. 2 and the refrigeration auxiliary capillary 32, which respectively control the refrigeration cycle and the refrigeration auxiliary circulation branch, the same as in the first embodiment.
  • Example 3
  • the present embodiment differs from the above embodiment in that a refrigerated auxiliary evaporator 52 is connected in series after the refrigerated auxiliary capillary 32, such that the refrigerated auxiliary circulation branch includes the auxiliary capillary 32 and the auxiliary refrigerating evaporator 52 connected thereto in series.
  • the refrigerated auxiliary circulation branch is connected in parallel with the main capillary 3 and the refrigerating evaporator 41 connected in series, and is connected between the output end of the electromagnetic valve 31 and the output end of the refrigerating evaporator 41.
  • the temperature of the refrigerating compartment can be further lowered to be converted into an ice greenhouse, a one-star, two-star freezer, and the temperature setting range can be large.
  • This embodiment presents a typical system topology of the present invention that is completely different from conventional dual systems.
  • the difference from the embodiment 3 is that the refrigerating auxiliary circulation branch is connected in parallel with the main capillary 3, the refrigerating evaporator 41 and the refrigerating evaporator 51 which are sequentially connected in series, and is connected to the output end of the solenoid valve 31 and the refrigerating evaporator 51. Between the outputs, that is, the end of the refrigerated auxiliary circulation branch is connected to the input end of the return air pipe.
  • the refrigerant cycle system of the present invention flows in this way:
  • the control process of the refrigerator of the present invention is such that after the power is initialized, the temperature sensor starts to detect the temperature of each compartment.
  • the main CPU controls the solenoid valve 31 to be thrown in the main circulation, and the refrigeration assists.
  • the refrigerant cycle is the same as in the normal refrigerator system, and the freezer compartment and the refrigerating compartment are simultaneously cooled.
  • the refrigerant is compressed into high pressure gas by the compressor 1
  • the discharge is condensed by the condenser 2, and then flows through the electromagnetic valve 31.
  • the refrigerant is throttled by the main capillary 3 to become a low-pressure cryogenic liquid.
  • the liquid is partially evaporated into a low temperature gas in the freezing evaporator 41 to absorb the heat of the freezing chamber F.
  • the liquid that has not completely evaporated flows into the refrigerating evaporator 51 to continue to evaporate, absorbing the heat of the refrigerating compartment R.
  • it is completely evaporated into a low-temperature gas, and is sucked into the compressor 1 through the return pipe 6 to form a circulation; at this time, the refrigeration and freezing are simultaneously involved in the cycle, and can be used as a refrigerator in a conventional sense. Since the system load is chilled and frozen series load, it is stable, and the refrigeration system cycle efficiency can be matched to the optimal state at the target ambient temperature, effectively improving energy conversion efficiency.
  • the main CPU can control the solenoid valve 31 to be thrown at the position where the main circulation is opened and the refrigerating auxiliary circulation is opened, and the refrigerant is compressed by the compressor 1 into a high-pressure gas to be discharged, and after being condensed by the condenser 2 , flowing through the solenoid valve 31.
  • the refrigerant is throttled by the main capillary 3 to become a low-pressure cryogenic liquid.
  • the liquid is partially evaporated into a low temperature gas in the freezing evaporator 41 to absorb the heat of the freezing chamber F.
  • the liquid that has not completely evaporated flows into the refrigerating evaporator 51 to continue to evaporate, absorbing the heat of the refrigerating compartment R.
  • the refrigerant is throttled by the refrigeration auxiliary capillary 32 to become a low pressure low temperature liquid.
  • the liquid evaporates into a low temperature gas in the auxiliary refrigerating evaporator 52, absorbing the heat of the refrigerating compartment R.
  • it is completely evaporated into a low-temperature gas, and is heated by the return pipe 6 to be sucked into the compressor 1 to form a cycle; at this time, the temperature of the refrigerator compartment can be lowered, one is to achieve a rapid cooling function, and the other is to convert the refrigerator compartment into a freezer compartment.
  • It is especially suitable for the staged mass storage of frozen foods. Adjusting the time of the solenoid valve 31 refrigerating switch, you can adjust the freezing temperature depth of the refrigerator. This is a very useful feature that is very suitable for Chinese people to use.
  • the CPU can control the solenoid valve to be placed in the refrigeration cycle, and the refrigeration auxiliary circulation branch is opened, and the refrigerant is throttled by the refrigeration auxiliary capillary 32 to become a low pressure low temperature liquid.
  • the liquid evaporates into a low temperature gas in the auxiliary refrigerating evaporator 52, absorbing the heat of the refrigerating compartment R. Finally, it is completely evaporated into a low-temperature gas, and is sucked into the compressor 1 through the return pipe 6 to form a circulation; at this time, the freezing evaporator 41 and the refrigerating evaporator 51 do not participate in the refrigeration cycle, and all the cooling amount comes from the auxiliary refrigerating evaporator 52, which can be used as a refrigerating system.
  • the use of the box greatly reduces power consumption and saves energy. And the purpose of using the refrigerating compartment as a freezing compartment can be achieved. This is also a very useful feature. ⁇
  • the typical matching strategy of the refrigerator described in this patent
  • the main control of the compressor operation adopts the refrigerating temperature sensor.
  • the system matching principle is the target ambient temperature (for example, 25 degrees Celsius, or other temperature, according to the average temperature of the target market or the climate type of the refrigerator design), while achieving refrigeration.
  • Target temperature eg, 5 degrees Celsius
  • freezing target temperature eg, -18 degrees Celsius
  • the typical temperature control strategy of the refrigerator described in this patent is as follows: due to the increase of the ambient temperature or the change of the refrigerating load, the refrigerating temperature is raised to a certain amount (refrigerating target temperature + X), and the solenoid valve of the refrigerating auxiliary circulation circuit can be turned on and off. The temperature of the refrigerating compartment is lowered separately to reach the refrigerating target temperature. When the freezing temperature is reduced by more than a certain amount (freezing target temperature -Y), the cold solenoid valve switch can be turned off, the refrigeration cycle is cut off, and energy loss is reduced.
  • X is 1 to 3 degrees Celsius and Y is 2 to 5 degrees Celsius.
  • the difference between this embodiment and the embodiment 4 is that the end of the refrigerating auxiliary circulation branch is still connected to the input end of the return air pipe, and the positions of the refrigerating evaporator 51 and the refrigerating evaporator in the refrigerating circuit are interchanged.
  • the end of the refrigeration auxiliary circulation circuit is connected between the freezing evaporator 41 and the return air pipe 6, and the rest is the same as in the fourth embodiment.
  • the refrigerator of the present invention includes, but is not limited to, a drawer type and a shelf type domestic refrigerator-freezer, regardless of whether the positions of the refrigerator compartment and the freezing compartment are up, down, or left and right.
  • the multi-cycle refrigeration system refrigerator of the present invention and the control method thereof can be widely applied to the manufacture and use of various refrigerators having a refrigerating and freezing chamber, and the industrial application prospect is very wide.

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Description

复立多循环制冷系统冰箱及其控制方法
技术领域
本发明涉及一种冰箱，具体地说，涉及一种具有若干串、并行配置的 制冷回路的压缩装置的冰箱。 背景技术
现有技术一：一般压缩式制冷系统冷藏冷冻箱，其制冷循环回路为单 系统， 参见附图 1， 压缩机 1出气端接冷凝器 2， 后接节流毛细管 3， 毛 细管 3后接冷冻蒸发器 4、 冷藏蒸发器 5， 或先接冷藏蒸发器 5， 后接冷 冻蒸发器 4， 最后经回气管 6回到压缩机 1。
现有技术一的工作原理是这样的:压缩机 1开停由置于冷藏室的温度 传感器控制。 冷藏室的温度高于设定开机温度时， 压缩机运行， 两个间 室的温度同时下降； 低于设定停机温度时， 压缩机停止运行。 两个间室 的温度同时回升。 当冷藏室温度回升到设定开机温度时， 再次开机， 依 次循环， 使冷藏室温度保持在一定范围内。
这种系统结构简单，运行靠冷藏室温度控制，冷冻室温度不能独立控 制， 环境温度变化时， 冷冻温度也跟随变化。 一般情况下， 夏季环境温 度升高， 冷冻室温度过低， 消耗更多冷量； 而冬季环境温度较低时， 冷 藏要求的开机率太低， 冷冻室温度过高， 一般解决办法是在冷藏室增加 辅助加热装置， 强迫循环启动， 以降低冷冻室温度。 显然， 辅助加热装 置多消耗额外能源。
现有技术二：传统的双系统拓扑，通常在前述先接冷藏后接冷冻拓扑 结构的基础上， 在冷凝器 2末端接一电磁阀 31入端， 参见附图 2， 电磁 阀 31出口有两个， 除一个接冷藏节流毛细管 3外， 另一出口端接冷冻辅 助节流毛细管 34， 毛细管 34末端接冷藏蒸发器 5出口端和冷冻蒸发器 4 入口端， 冷冻蒸发器 4末端经回气管 6接压缩机 1回气端。 N2004/001346 现有技术二的工作原理是这样的:压缩机 1开停由置于冷藏室的温度 传感器控制。 冷藏室的温度高于设定幵机温度时， 压缩机运行， 两个间 室的温度同时下降； 低于设定停机温度时， 压缩机停止运行。 两个间室 的温度同时回升。 当速冻或环境温度较低引起冷冻室温度升高时， 可以 启动冷冻辅助循环， 单独降低冷冻室温度。 与一般单系统循环回路相比， 取消了辅助加热装置， 在环境温度较低时， 可节约能源。
该双系统冷藏冷冻箱的优势还在于可以关闭冷藏室， 独立使用冷冻 室。 同时， 该系统还具备大冷冻能力， 这是因为冷冻室具有独立的毛细 管节流控制装置。 这一技术已普遍应用。
现有技术三： 为解决关闭冷冻室，独立使用冷藏室需求， 已有发明专 利给出了一种并联拓扑结构， 参见附图 3， 其特点是冷藏、冷冻采用了两 个独立节流、 蒸发制冷回路。 这种拓扑结构简单， 可以独立开关冷藏、 冷冻制冷回路， 节约能源。 但其正常使用时， 即冷藏、 冷冻同时使用时， 由于负载变化太大， 蒸发压力、 温度偏离最佳值较大， 系统效率下降， 耗电量增大。 发明内容
本发明提出的称为"复立多循环"的新型拓扑结构制冷系统成功的解 决了制冷效率与冷冻关闭功能之间的矛盾， 使正常使用状态下即冷藏、 冷冻同时使用时， 系统效率最佳， 有效地降低耗电量。 同时又能够实现 关闭冷冻室功能， 并可将冷藏室转化为不同星级的冷冻室使用。 所谓"复 立，，， 是指"复合"制冷系统回路和各间室温度 "独立 "控制。
本发明的复立多循环制冷系统冰箱是这样实现的： 其包括主 CPU、 温度传感器和制冷循环回路， 其中制冷循环回路由压缩机、 冷凝器、 主 毛细管、 冷冻蒸发器、 冷藏蒸发器和回气管串联而成， 在冷凝器后串接 电磁阀， 该电磁阀有两个输出端， 其一端与主毛细管连接， 另一端连接 冷藏辅助循环支路。 该方案可以有如下具体结构： 其一，制冷循环回路中冷冻蒸发器在先，冷藏蒸发器在后；冷藏辅助 循环支路包括冷藏辅助毛细管， 其与串联后的主毛细管和冷冻蒸发器相 并联， 连接在电磁阀输出端和冷藏蒸发器输入端之间。
其二，制冷循环回路中冷冻蒸发器在先，冷藏蒸发器在后；冷藏辅助 循环支路包括辅助毛细管和与其串联的辅助冷藏蒸发器， 该冷藏辅助循 环支路与串联后的主毛细管和冷冻蒸发器相并联， 连接在电磁阀输出端 和冷藏蒸发器输入端之间。
其三，制冷循环回路中冷冻蒸发器在先，冷藏蒸发器在后； 冷藏辅助 循环支路包括辅助毛细管和与其串联的辅助冷藏蒸发器， 该冷藏辅助循 环支路与串联后的主毛细管、 冷冻蒸发器和冷藏蒸发器并联， 连接在电 磁阀输出端和冷藏蒸发器输出端之间。
其四， 制冷循环回路中冷藏蒸发器在先，冷冻蒸发器在后； 冷藏辅助 循环支路包括辅助毛细管和与其串联的辅助冷藏蒸发器， 该冷藏辅助循 环支路与串联后的主毛细管、 冷藏蒸发器和冷冻蒸发器并联， 连接在电 磁阀输出端和冷冻蒸发器输出端之间。
其中， 电磁阔为两位三通的一体阀，其分别与冷凝器、主毛细管和冷 藏辅助毛细管连接。 为实现上述结构， 电磁阀也可以是两个独立的电磁 截止阀， 一个连接在冷凝器和主毛细管之间， 一个连接在冷凝器和冷藏 辅助毛细管之间。
本发明的控制方法， 其包括下列步骤：
I .冰箱通电， 初始化， 主 CPU检测"冷冻关 "是否激活， 如果被激 活， 电磁阀就关断冷冻循环回路， 同时接通冷藏辅助循环支路， 运行至 冷藏室设定温度， 然后回开始继续检测； 如果"冷冻关 "未被激活， 电磁阀 就接通冷冻循环回路， 同时关断冷藏辅助循环支路， 然后进入步骤 II； II .检测冷藏室和冷冻室温度，当冷藏室温度或者冷冻室温度高于设 定开机温度时， 压縮机启动； 若冷冻室温度过低而冷藏室温度高于设定 幵机温度时， 电磁阀关断冷冻循环回路， 接通冷藏辅助循环支路， 为冷 藏室降温， 至设定温度， 然后回步骤 I 。 附图概述
图 1是现有技术一的结构方框图；
图 2是现有技术二的结构方框图；
图 3是现有技术三的结构方框图；
图 4是本发明实施例 1的结构方框图；
图 5是本发明实施例 2的结构方框图；
图 6是本发明实施例 3的结构方框图；
图 7是本发明实施例 4的结构方框图；
图 8是本发明实施例 5的结构方框图。 本发明的最佳实施方式
实施例 1 - 本实施例给出了本发明的一个典型系统拓扑结构， 它包括主 CPU, 温度传感器和制冷循环回路， 参见附图 4, 制冷循环回路由压缩机 1、 冷 凝器 2、 主毛细管 3、 冷冻蒸发器 41、 冷藏蒸发器 51和回气管 6依次串 联而成， 在冷凝器 2后串接电磁阀 31， 该电磁阀 31有两个输出端， 其一 端与主毛细管 3 连接， 另一端连接冷藏辅助循环支路， 冷藏辅助循环支 路包括冷藏辅助毛细管 32，其与串联后的主毛细管 3和冷冻蒸发器 41相 并联， 连接在电磁阀 31输出端和冷藏蒸发器 51输入端之间。
其与附图 2所表示的传统双系统不同之处在于，在回路中冷冻蒸发器 41在先， 冷藏蒸发器 51在后。
本发明的制冷剂循环系统是这样流动的：
冰箱开机后，压缩机开始运转，制冷剂经压缩机 1压缩成高压气体排 出， 经冷凝器 2冷凝后， 流过电磁阀 31。 温度传感器检测冷冻室和冷藏 室的温度， 当冷冻室和冷藏室同时要求开机时， CPU就控制电磁阀 31掷 于冷冻幵、 冷藏关位置， 制冷剂经压縮机 1 压缩成高压气体排出， 经冷 凝器 2冷凝后， 流过电磁阀 31。 制冷剂经主毛细管 3节流， 成为低压低 温液体。 液体在冷冻蒸发器 41中部分蒸发成低温气体， 吸收冷冻室 F热 量。未完全蒸发的液体流入冷藏蒸发器 51继续蒸发，吸收冷藏室 R热量, 最后完全蒸发成低温气体， 经回气管 6升温后吸入压縮机 1， 形成循环； 此时冷藏、 冷冻同时参与循环， 可作为常规意义下的冰箱使用。 由于系 统负载为冷藏冷冻串联负载， 是稳定不变的， 制冷系统循环效率可以在 目标环境温度下匹配至最佳状态， 有效地提高能源转换效率。
当冷藏室内有大量的食品需要的冷量比较多时， CPU就控制电磁阀 31掷于冷冻开、 冷藏辅助循环开位置， 制冷剂经压缩机 1压缩成高压气 体排出， 经冷凝器 2冷凝后， 流过电磁阀 31。制冷剂经主毛细管 3节流， 成为低压低温液体。 液体在冷冻蒸发器 41中部分蒸发成低温气体， 吸收 冷冻室 F热量。 未完全蒸发的液体流入冷藏蒸发器 51继续蒸发， 吸收冷 藏室 R热量。 同时， 制冷剂经冷藏辅助循环节流毛细管 32节流， 成为低 压低温液体。液体在冷藏蒸发器 51中蒸发成低温气体， 吸收冷藏室 R热 量。最后完全蒸发成低温气体， 经回气管 6升温后吸入压缩机 1， 形成循 环； 此时可以将冷藏室温度拉低， 一是实现快速冷却功能， 二是可以实 现将冷藏室转换为冷冻室使用功能。 特别适合于阶段性大量存储冷冻食 品使用。调整电磁阀 31冷藏开关的时间，可以调整冷藏室冷冻温度深度。 这也是一个非常适合中国人使用习惯的、 非常实用的功能。
当冷冻室已经达到设定的温度而冷藏室还没有达到设定温度时， CPU 就控制电磁阀 31掷于冷冻关、 冷藏辅助循环开位置， 制冷剂经冷藏辅助 循环节流毛细管 32节流， 成为低压低温液体。 液体在冷藏蒸发器 51 中 蒸发成低温气体， 吸收冷藏室 R热量。 最后完全蒸发成低温气体， 经回 气管 6升温后吸入压缩机 1，形成循环；此时冷冻蒸发器不参与制冷循环， 所有冷量来自冷藏， 可作为冷藏箱使用， 大幅度降低耗电量， 节约能源。 这是一个非常实用的功能。 本专利所述电磁阀 31设置为两位三通的一体阀。
本专利所述冰箱， 冷藏蒸发器 51和冷冻蒸发器 41包含单一蒸发器 和用于相同或不同温度间室多个蒸发器串联的组合。
本专利所述冰箱典型匹配策略如下：
压缩机运行主控制采用冷藏温度传感器，系统匹配原则为目标环境温 度 （如， 25摄氏度， 也可以是其他温度， 根据目标市场的环境平均温度 或冰箱设计的气候类型定）下， 同时达到冷藏目标温度（如， 5摄氏度）、 冷冻目标温度（如， -18摄氏度） ， 以最大限度的提高制冷剂循环系统效 率， 使冰箱在冷藏、 冷冻同时使用的一般目标环境温度下达到最佳节能 目的。
本专利所述冰箱典型温度控制策略如下：由于环境温度升高或冷藏负 载变化， 使冷藏温度升高到一定量 （冷藏目标温度 +X) ， 可以接通冷藏 辅助循环回路电磁阀开关运行， 使冷藏室温度单独下降， 达到冷藏目标 温度。 而冷冻温度降低超过一定量 （冷冻目标温度 -Y) 时， 可以关断冷 冻电磁阀开关， 切断冷冻循环回路， 减少能量损失。 一般情况下， X为 1〜3摄氏度， Y为 2〜5摄氏度。
本专利所述冰箱典型温度控制程序框架如下：
程序清零 START, 检测是否"冷冻关"激活， 如被激活， 电磁阀关断 冷冻循环回路， 接通冷藏辅助循环回路。它是一个"冷藏"单循环回路， 根 据"冷藏室 "设定温度运行， 温度设定范围可以较大。
如果"冷冻关 "未被激活， 电磁阀接通冷冻循环回路，关断冷藏辅助循 环回路。 检测冷藏室和冷冻室温度， 当冷藏室温度或冷冻室温度高于设 定开机温度时， 压缩机启动。 若冷冻室温度过低 （冷冻目标温度 -Y)而 冷藏室温度高于设定开机温度时， 电磁阀关断冷冻循环回路， 接通冷藏 辅助循环回路， 为冷藏室降温。 实施例 2:
参见附图 5，本实施例与实施例 1的区别在于，本实施例的电磁阀 31 为两个独立电磁截止阀， 一个连接在冷凝器 2和主毛细管 3之间， 另一 个连接在冷凝器 2和冷藏辅助毛细管 32之间， 它们分别对冷冻循环回路 和冷藏辅助循环支路进行控制， 其他同实施例 1。 实施例 3：
参见附图 6， 本实施例与上述实施例的区别在于， 在冷藏辅助毛细管 32后串联了冷藏辅助蒸发器 52, 这样， 冷藏辅助循环支路包括辅助毛细 管 32和与其串联的辅助冷藏蒸发器 52，该冷藏辅助循环支路与串联后的 主毛细管 3、冷冻蒸发器 41并联，连接在电磁阀 31输出端和冷冻蒸发器 41 输出端之间。 相对前两个实施例而言， 可以进一步拉低冷藏室温度， 使其转化为冰温室、 一星级、 二星级冷冻室使用， 温度设定范围可以较 大。 实施例 4
本实施例给出了本发明的一个典型系统拓扑结构，其与传统双系统完 全不同。
参见图 7, 其与实施例 3的区别在于， 冷藏辅助循环支路与依次串联 后的主毛细管 3、 冷冻蒸发器 41和冷藏蒸发器 51并联， 连接在电磁阀 31输出端和冷藏蒸发器 51输出端之间，即冷藏辅助循环支路的末端连接 在回气管的输入端。
本发明制冷剂循环系统是这样流动的：
本发明冰箱的控制过程是这样的，通电初始化后，温度传感器开始检 测各间室的温度， 当冷藏室和冷冻室同时要求开机时， 主 CPU就控制电 磁阀 31掷于主循环开、 冷藏辅助循环关位置， 制冷剂循环与普通冰箱系 统相同， 冷冻室和冷藏室同时制冷。 制冷剂经压縮机 1 压缩成高压气体 排出， 经冷凝器 2冷凝后， 流过电磁阀 31。 制冷剂经主毛细管 3节流， 成为低压低温液体。 液体在冷冻蒸发器 41中部分蒸发成低温气体， 吸收 冷冻室 F热量。 未完全蒸发的液体流入冷藏蒸发器 51继续蒸发， 吸收冷 藏室 R热量。最后完全蒸发成低温气体,经回气管 6升温后吸入压縮机 1， 形成循环； 此时冷藏、 冷冻同时参与循环， 可作为常规意义下的冰箱使 用。 由于系统负载为冷藏冷冻串联负载， 是稳定不变的， 制冷系统循环 效率可以在目标环境温度下匹配至最佳状态， 有效地提高能源转换效率。
当冷藏室需要的冷量比较大时，主 CPU可以控制电磁阀 31掷于主循 环开、 冷藏辅助循环开的位置， 制冷剂经压縮机 1压缩成高压气体排出， 经冷凝器 2冷凝后， 流过电磁阀 31。 制冷剂经主毛细管 3节流， 成为低 压低温液体。 液体在冷冻蒸发器 41中部分蒸发成低温气体， 吸收冷冻室 F热量。 未完全蒸发的液体流入冷藏蒸发器 51继续蒸发， 吸收冷藏室 R 热量。 同时， 制冷剂经冷藏辅助毛细管 32节流， 成为低压低温液体。 液 体在辅助冷藏蒸发器 52中蒸发成低温气体， 吸收冷藏室 R热量。最后完 全蒸发成低温气体， 经回气管 6升温后吸入压缩机 1， 形成循环； 此时可 以将冷藏室温度拉低， 一是实现快速冷却功能， 二是可以实现将冷藏室 转换为冷冻室使用功能。 特别适合于阶段性大量存储冷冻食品使用。 调 整电磁阀 31冷藏开关的时间， 可以调整冷藏室冷冻温度深度。 这是一个 非常适合中国人使用习惯的、 非常实用的功能。
当冷冻室的温度已经达到设定的温度或关闭， 而冷藏室需要冷量时，
CPU可以控制电磁阀置于冷冻循环关， 冷藏辅助循环支路开的位置， 制 冷剂经冷藏辅助毛细管 32节流， 成为低压低温液体。 液体在辅助冷藏蒸 发器 52中蒸发成低温气体， 吸收冷藏室 R热量。最后完全蒸发成低温气 体， 经回气管 6升温后吸入压缩机 1， 形成循环； 此时冷冻蒸发器 41和 冷藏蒸发器 51不参与制冷循环，所有冷量来自辅助冷藏蒸发器 52， 可作 为冷藏箱使用， 大幅度降低耗电量， 节约能源。 并且可以实现冷藏室作 为冷冻室使用的目的。 这也是一个非常实用的功能。 δ 本专利所述冰箱典型匹配策略如下：
压縮机运行主控制采用冷藏温度传感器，系统匹配原则为目标环境温 度 （如， 25摄氏度， 也可以是其他温度， 根据目标市场的环境平均温度 或冰箱设计的气候类型定）下， 同时达到冷藏目标温度（如， 5摄氏度）、 冷冻目标温度（如， -18摄氏度） ， 以最大限度的提高制冷剂循环系统效 率， 使冰箱在冷藏、 冷冻同时使用的一般目标环境温度下达到最佳节能 目的。
本专利所述冰箱典型温度控制策略如下：由于环境温度升高或冷藏负 载变化， 使冷藏温度升高到一定量 （冷藏目标温度 +X) ， 可以接通冷藏 辅助循环回路电磁阀开关运行， 使冷藏室温度单独下降， 达到冷藏目标 温度。 而冷冻温度降低超过一定量（冷冻目标温度 -Y) 时， 可以关断冷 冻电磁阀开关， 切断冷冻循环回路， 减少能量损失。 一般情况下， X为 1〜3摄氏度， Y为 2〜5摄氏度。 实施例 5
参见图 8， 本实施例与实施例 4的区别在于， 冷藏辅助循环支路的末 端仍然连接在回气管的输入端， 而制冷回路中的冷藏蒸发器 51和冷冻蒸 发器的位置互换， 这样， 冷藏辅助循环回路的末端连接在冷冻蒸发器 41 和回气管 6之间， 其余的同实施例 4。 本发明所述冰箱， 包含但不限于抽屉式和层架式家用冷藏冷冻电冰 箱， 无论冷藏室和冷冻室的位置在上、 下或者左、 右。 工业实用性
本发明的复立多循环制冷系统冰箱及其控制方法可广泛应用于各种 具有冷藏冷冻室的冰箱的制造和使用， 工业应用前景十分广泛。

Claims

权 利 要 求 书
1、一种复立多循环制冷系统冰箱， 其包括主 CPU、温度传感器和 制冷循环回路， 其中制冷循环回路由压缩机、 冷凝器、 主毛细管、 冷 冻蒸发器、 冷藏蒸发器和回气管串联而成，
其特征在于： 在冷凝器后串接电磁阀， 该电磁阀有两个输出端， 其一 端与主毛细管连接， 另一端连接冷藏辅助循环支路。
2、 根据权利要求 1所述的复立多循环制冷系统冰箱，
其特征在于： 制冷循环回路中冷冻蒸发器在先， 冷藏蒸发器在后； 冷 藏辅助循环支路包括冷藏辅助毛细管， 其与串联后的主毛细管和冷冻 蒸发器相并联， 连接在电磁阀输出端和冷藏蒸发器输入端之间。
3、 根据权利要求 1所述的复立多循环制冷系统冰箱，
其特征在于： 制冷循环回路中冷冻蒸发器在先， 冷藏蒸发器在后； 冷 藏辅助循环支路包括辅助毛细管和与其串联的辅助冷藏蒸发器， 该冷 藏辅助循环支路与串联后的主毛细管和冷冻蒸发器相并联， 连接在电 磁阀输出端和冷藏蒸发器输入端之间。
4、 根据权利要求 1所述的复立多循环制冷系统冰箱，
其特征在于： 制冷循环回路中冷冻蒸发器在先， 冷藏蒸发器在后； 冷 藏辅助循环支路包括辅助毛细管和与其串联的辅助冷藏蒸发器， 该冷 藏辅助循环支路与串联后的主毛细管、冷冻蒸发器和冷藏蒸发器并联， 连接在电磁阀输出端和冷藏蒸发器输出端之间。
5、 根据权利要求 1所述的复立多循环制冷系统冰箱，
其特征在于： 制冷循环回路中冷藏蒸发器在先， 冷冻蒸发器在后； 冷 藏辅助循环支路包括辅助毛细管和与其串联的辅助冷藏蒸发器， 该冷 藏辅助循环支路与串联后的主毛细管、冷藏蒸发器和冷冻蒸发器并联， 连接在电磁阀输出端和冷冻蒸发器输出端之间。
6、 根据上述任一权利要求所述的复立多循环制冷系统冰箱， 其特征在于： 电磁阀为两位三通的一体阀， 其分别与冷凝器、 主毛细 管和冷藏辅助毛细管连接。
7、 根据上述任一权利要求所述的复立多循环制冷系统冰箱， 其特征在于： 电磁阀为两个独立的电磁截止阀， 一个连接在冷凝器和 主毛细管之间， 一个连接在冷凝器和冷藏辅助毛细管之间。
8、 一种复立多循环制冷系统冰箱的控制方法，
其特征在于， 它包括下列步骤：
I. 冰箱通电， 初始化， 主 CPU检测"冷冻关 "是否激活， 如果 被激活，电磁阀就关断冷冻循环回路，同时接通冷藏辅助循环支路， 运行至冷藏室设定温度， 然后回开始继续检测； 如果"冷冻关 "未被 激活， 电磁阀就接通冷冻循环回路， 同时关断冷藏辅助循环支路， 然后进入步骤 II；
II. 检测冷藏室和冷冻室温度，当冷藏室温度或者冷冻室温度高 于设定开机温度时，压缩机启动；若冷冻室温度过低而冷藏室温度 高于设定开机温度时， 电磁阀关断冷冻循环回路，接通冷藏辅助循 环支路， 为冷藏室降温， 至设定温度， 然后回步骤 I。
PCT/CN2004/001346 2004-08-19 2004-11-24 Refrigerateur composite possedant un systeme de refrigeration a cycles multiples et son procede de controle WO2006017959A1 (fr)

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CN200410035588.0 2004-08-19
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