CN116972583A

CN116972583A - Control method for refrigeration equipment and refrigeration equipment

Info

Publication number: CN116972583A
Application number: CN202210431829.1A
Authority: CN
Inventors: 达朝彬; 孙永升; 侯鸿彬
Original assignee: Qingdao Haier Smart Technology R&D Co Ltd; Haier Smart Home Co Ltd
Current assignee: Qingdao Haier Smart Technology R&D Co Ltd; Haier Smart Home Co Ltd
Priority date: 2022-04-22
Filing date: 2022-04-22
Publication date: 2023-10-31

Abstract

The invention provides a control method for refrigeration equipment and the refrigeration equipment, wherein the refrigeration equipment comprises a box body with a storage room, a door body, a refrigeration system filled with refrigerant and an anti-condensation system filled with refrigerating medium, the anti-condensation system comprises a circulating pump, a heat exchange component and an anti-condensation pipe which are connected in series, and the heat exchange component is thermally connected with the refrigeration system so that the refrigerating medium in the heat exchange component absorbs heat of the refrigeration system. The control method of the invention comprises the following steps: determining the current environment temperature and the current environment humidity of the environment where the refrigeration equipment is located; determining a current dew point temperature according to the current ambient temperature and the current ambient humidity; determining the temperature of the anti-dew tube; controlling the circulating pump to rotate in response to the temperature of the dew point preventing pipe being lower than or equal to the current dew point temperature; and controlling the circulating pump to stop rotating in response to the fact that the dew-proof pipe is filled with the high-temperature secondary refrigerant in the heat exchange component.

Description

Control method for refrigeration equipment and refrigeration equipment

Technical Field

The invention belongs to the technical field of refrigeration equipment, and particularly provides a control method for refrigeration equipment and the refrigeration equipment.

Background

Existing refrigerators generally have a refrigerating compartment and a freezing compartment. The temperature of the refrigerating chamber and the freezing chamber is lower than the environment temperature of the refrigerator, and the working temperature of the refrigerating chamber is lower than 4 ℃ and the working temperature of the freezing chamber is lower than-16 ℃ in normal condition.

During the use of the refrigerator, the door seals of the refrigerator are cooled by the low-temperature refrigerating compartment and the freezing compartment, so that the temperature of the refrigerator door seals is lower than the ambient temperature. When the temperature at the door seal of the refrigerator is lower than the dew point temperature of the current environment, condensation can appear at the door seal of the refrigerator. In order to avoid condensation, the existing refrigerators are generally provided with a dew-proof pipe so as to heat the door seal of the refrigerator to be above the dew point temperature through the dew-proof pipe.

Because the dew-proof pipe on the existing refrigerator is usually connected in series between the outlet of the compressor and the inlet of the condenser, the refrigerant can flow through the dew-proof pipe only in the working process of the compressor, and the door seal of the refrigerator can be heated. Therefore, the existing refrigerator is still easy to be condensed when the compressor stops rotating. In addition, the temperature of the dew-proof pipe is higher due to higher temperature of the refrigerant flowing out of the compressor, so that the temperature of the door seal of the refrigerator is always far higher than the dew-point temperature, the temperature difference between the refrigerating chamber and the freezing chamber is larger, and the cold leakage of the refrigerator at the door seal is larger.

Disclosure of Invention

The invention aims to solve the problem that the existing refrigerator cannot heat the dew-proof pipe when the compressor is stopped.

Another object of the present invention is to provide a refrigeration apparatus and a control method for the refrigeration apparatus, by which the refrigeration apparatus is controlled to heat its dew-preventing pipe, preventing the refrigeration apparatus from dew at the door seal.

It is a further object of the present invention to increase the heating efficiency of the coolant on the dew point preventing tube.

In order to achieve the above object, the present invention provides in a first aspect a control method for a refrigeration apparatus including a cabinet having a storage compartment, a door, a refrigeration system filled with a refrigerant, and an anti-condensation system filled with a coolant, the anti-condensation system including a circulation pump, a heat exchange member, and an anti-condensation pipe connected in series, the heat exchange member being thermally connected to the refrigeration system so that the coolant in the heat exchange member absorbs heat of the refrigeration system, a volume of the heat exchange member being not less than a volume of the anti-condensation pipe;

the control method comprises the following steps:

determining the current environment temperature and the current environment humidity of the environment where the refrigeration equipment is located;

determining a current dew point temperature according to the current ambient temperature and the current ambient humidity;

determining the temperature of the anti-dew tube;

controlling the circulating pump to rotate in response to the temperature of the dew point preventing pipe being lower than or equal to the current dew point temperature;

and controlling the circulating pump to stop rotating in response to the fact that the dew-proof pipe is filled with the high-temperature secondary refrigerant in the heat exchange component.

Optionally, the controlling the circulation pump to stop rotating in response to the coolant at a high temperature in the heat exchange member filling the dew-preventing pipe includes:

and controlling the circulating pump to stop rotating in response to the rotation of the circulating pump for a preset period of time.

and controlling the circulation pump to stop rotating in response to the circulation pump rotating by a preset number of revolutions.

and controlling the circulating pump to stop rotating in response to the temperature rise at the outlet of the dew-proof pipe.

Optionally, after the circulation pump is controlled to stop rotating in response to the coolant at a high temperature in the heat exchange member filling the dew-preventing pipe, the control method further includes:

and controlling the circulating pump to rotate again in response to the temperature of the refrigerating medium in the dew-proof pipe not being greater than a first preset temperature.

and controlling the circulating pump to rotate again in response to the cooling rate of the refrigerating medium in the dew-proof pipe is smaller than or equal to a preset rate.

Optionally, the control method further includes:

controlling the circulating pump to stop in response to the temperature of the dew prevention pipe reaching a second preset temperature;

wherein the second preset temperature is greater than the current dew point temperature and not greater than the current ambient temperature.

The present invention provides in a second aspect a refrigeration appliance comprising:

a case defining a storage chamber therein;

a door body for shielding the storage chamber;

the refrigerating system is filled with refrigerant and comprises a compressor, a condenser, a throttling and depressurization component and an evaporator which are connected end to end in sequence, wherein the evaporator is used for providing cold energy for the storage chamber;

the condensation prevention system filled with the secondary refrigerant comprises a circulating pump, a heat exchange component and a condensation prevention pipe which are connected in series, wherein the heat exchange component is in thermal connection with the refrigerating system, and the volume of the heat exchange component is not smaller than that of the condensation prevention pipe;

a controller;

a memory having stored thereon execution instructions that, when executed, enable the refrigeration appliance to perform the control method of any of the first aspects.

Optionally, the anti-condensation system further comprises a one-way valve connected in series between the outlet of the circulation pump and the inlet of the anti-condensation pipe.

Optionally, the circulating pump, the heat exchange component, the one-way valve and the dew prevention pipe are connected end to end in sequence.

Based on the foregoing description, it can be understood by those skilled in the art that in the foregoing technical solutions of the present invention, by configuring a separate anti-condensation system for a refrigeration apparatus and thermally connecting a heat exchange member of the anti-condensation system with the refrigeration system, the anti-condensation system can absorb heat in the refrigeration system through the heat exchange member, so that a high-temperature coolant in the heat exchange member flows to the anti-condensation pipe under the action of the circulating pump to heat the anti-condensation pipe. Further, determining the current environment temperature and the current environment humidity of the environment where the refrigeration equipment is located, determining the current dew point temperature according to the current environment temperature and the current environment humidity, and determining the temperature of the dew-proof pipe; when the temperature of the dew-proof pipe is lower than or equal to the current dew point temperature, the circulating pump is controlled to rotate; when the dew-proof pipe is filled with the high-temperature secondary refrigerant in the heat exchange component, the circulating pump is controlled to stop rotating, and the heating efficiency of the secondary refrigerant on the dew-proof pipe is improved. The reasons are as follows:

when the circulating pump does not work, only the heat exchange component in the anti-condensation system absorbs heat, so that the temperature of the secondary refrigerant in only the heat exchange component in the anti-condensation system is higher, and the temperature of the secondary refrigerant in other parts of the anti-condensation system is lower. When the circulating pump is just started, one section in the anti-condensation system is a high-temperature secondary refrigerant, and the other section in the anti-condensation system is a low-temperature secondary refrigerant. The coolant with high temperature heats the dew-proof pipe when flowing to the dew-proof pipe, and the coolant with low temperature absorbs the heat of the dew-proof pipe when flowing to the dew-proof pipe, so that the temperature of the dew-proof pipe is slow. Therefore, the invention fills the dew-proof pipe with the high-temperature secondary refrigerant in the heat exchange component and resides in the dew-proof pipe, so that the high-temperature secondary refrigerant can fully release heat in the dew-proof pipe to heat the dew-proof pipe. At the same time, the newly introduced coolant in the heating element also has sufficient time to be heated by the refrigeration system.

Further, when the temperature of the coolant in the exposure prevention pipe is not greater than a first preset temperature, or when the cooling rate of the coolant in the exposure prevention pipe is smaller than or equal to a preset rate, the circulating pump is controlled to rotate again, so that the exposure prevention pipe can continuously flow in the high-temperature coolant. Meanwhile, as the starting time of the circulating pump is increased, the heat of the refrigerating medium in the whole anti-condensation system is improved, and the working frequency of the circulating pump is higher and higher.

The above, as well as additional objectives, advantages, and features of the present invention will become apparent to those skilled in the art from the following detailed description of a specific embodiment of the present invention when read in conjunction with the accompanying drawings.

Drawings

In order to more clearly illustrate the technical solution of the present invention, some embodiments of the present invention will be described hereinafter with reference to the accompanying drawings. It will be understood by those skilled in the art that components or portions thereof identified in different drawings by the same reference numerals are identical or similar; the drawings of the invention are not necessarily to scale relative to each other.

In the accompanying drawings:

fig. 1 is an effect schematic view of a refrigerating apparatus provided according to the technical concept of the present invention;

fig. 2 is a schematic view showing the constitution of a refrigeration system and an anti-condensation system according to a first embodiment of the present invention;

FIG. 3 is an isometric view of an priming device in a first embodiment of the present invention;

FIG. 4 is a cross-sectional view of the priming device of FIG. 3 taken along the direction A-A;

FIG. 5 is a cross-sectional view of a liquid injection apparatus according to a second embodiment of the present invention;

FIG. 6 is a cross-sectional view of the fill valve of FIG. 5;

FIG. 7 is a schematic view of the filling exhaust valve of FIG. 6 in a filling state;

FIG. 8 is a schematic diagram showing the state of the liquid injection exhaust valve in FIG. 6 during exhaust;

FIG. 9 is a schematic diagram of the thermal connection of a refrigeration system and an anti-condensation system in a third embodiment of the invention;

FIG. 10 is a schematic diagram of the thermal connection of a refrigeration system and an anti-condensation system according to a fourth embodiment of the present invention;

FIG. 11 is a schematic view of the thermal connection of a refrigeration system and an anti-condensation system according to a fifth embodiment of the present invention;

FIG. 12 is a schematic view of a thermal connection between a refrigeration system and an anti-condensation system according to a sixth embodiment of the present invention;

fig. 13 is a flowchart showing the main steps of a control method for a refrigeration appliance according to a seventh embodiment of the present invention;

FIG. 14 is a temperature-dew point temperature comparison table;

fig. 15 is a schematic view showing a part of functional blocks of a refrigeration apparatus according to an eighth embodiment of the present invention.

Detailed Description

It should be understood by those skilled in the art that the embodiments described below are only some embodiments of the present invention, but not all embodiments of the present invention, and the some embodiments are intended to explain the technical principles of the present invention and are not intended to limit the scope of the present invention. All other embodiments, which can be obtained by a person skilled in the art without any inventive effort, based on the embodiments provided by the present invention, shall still fall within the scope of protection of the present invention.

It should be noted that, in the description of the present invention, terms such as "center", "upper", "lower", "top", "bottom", "left", "right", "vertical", "horizontal", "inner", "outer", and the like indicate directions or positional relationships, which are based on the directions or positional relationships shown in the drawings, are merely for convenience of description, and do not indicate or imply that the apparatus or elements must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.

Further, it should also be noted that, in the description of the present invention, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; can be directly connected, can be indirectly connected through an intermediate medium, and can also be communicated with the inside of two elements. The specific meaning of the above terms in the present invention can be understood by those skilled in the art according to the specific circumstances.

In addition, it should be noted that, in the description of the present invention, the terms "cooling capacity" and "heating capacity" are two descriptions of the same physical state. That is, the higher the "cooling capacity" of a certain object (for example, evaporator, air, condenser, etc.), the lower the "heat" of the object, and the lower the "cooling capacity" of the object, the higher the "heat" of the object. Some object absorbs the cold and releases the heat, and the object releases the cold and absorbs the heat. A target maintains "cold" or "heat" to maintain the target at a current temperature. "refrigeration" and "heat absorption" are two descriptions of the same physical phenomenon, i.e., a target (e.g., an evaporator) absorbs heat while it is refrigerating.

As shown in fig. 1, in the present invention, a refrigerating apparatus includes a cabinet 100 and a door 200 mounted on the cabinet 100, and a storage compartment 110 is defined on the cabinet 100.

Alternatively, the refrigeration device is a refrigerator, freezer or freezer.

When the refrigeration appliance is a refrigerator, the storage compartment 110 includes at least one of a refrigerating compartment, a freezing compartment, and a temperature changing compartment. Preferably, the storage compartment 110 includes a refrigerating compartment and a freezing compartment.

When the refrigeration appliance is a freezer, the storage compartment 110 includes a freezer compartment.

When the refrigeration appliance is a refrigerated cabinet, the storage compartment 110 includes a refrigerated compartment.

The refrigerating apparatus of the present invention will be further described with reference to fig. 2 to 4. Wherein fig. 2 is a schematic view showing the constitution of a refrigeration system and an anti-condensation system according to a first embodiment of the present invention, fig. 3 is an isometric view of an injection device according to the first embodiment of the present invention, and fig. 4 is a sectional view of the injection device according to the first embodiment of the present invention taken along the direction A-A.

As shown in fig. 2, in the first embodiment of the present invention, the refrigeration apparatus further includes a refrigeration system 300 filled with a refrigerant and an anti-condensation system 400 filled with a coolant, and the anti-condensation system 400 is thermally connected with the refrigeration system 300 such that the anti-condensation system 400 absorbs heat of the refrigeration system 300.

The refrigerant is a conventional refrigerant in the refrigeration system 300 of the refrigerator or the air conditioner, and will not be described herein. The coolant is a liquid, preferably the coolant has a freezing point below-5 ℃. In the first embodiment of the invention, the coolant can be any feasible liquid such as sodium chloride solution, aqueous glycol, and the like.

With continued reference to fig. 2, in a first embodiment of the invention, a refrigeration system 300 includes a compressor 310, a condenser 320, a throttle and pressure reducing member 330, and an evaporator 340 for providing refrigeration to the storage 110, in that order, end-to-end. That is, the outlet of the compressor 310 is fluidly connected to the inlet of the condenser 320, the outlet of the condenser 320 is fluidly connected to the inlet of the throttle reducing member 330, the outlet of the throttle reducing member 330 is fluidly connected to the inlet of the evaporator 340, and the outlet of the evaporator 340 is fluidly connected to the inlet of the compressor 310.

The throttle reducing member 330 may be a capillary tube or an expansion valve.

With continued reference to fig. 2, the refrigeration system 300 further includes a filter 350 and an evaporator tube 360. The filter 350 is connected in series between the outlet of the condenser 320 and the inlet of the throttle reducing member 330. An evaporation tube 360 is connected in series between the outlet of the compressor 310 and the inlet of the condenser 320, and the refrigeration system 300 is thermally connected to the anti-condensation system 400 through the evaporation tube 360.

As shown in fig. 2, in a first embodiment of the present invention, the anti-condensation system 400 includes a circulation pump 410, a heat exchange member 420, an anti-condensation tube 430, a priming device 440, and an optional one-way valve 450, in end-to-end relationship. That is, the outlet of the circulation pump 410 is fluidly connected to the inlet of the heat exchange member 420, the outlet of the heat exchange member 420 is fluidly connected to the inlet of the check valve 450, the outlet of the check valve 450 is fluidly connected to the inlet of the anti-dew tube 430, the outlet of the anti-dew tube 430 is fluidly connected to the inlet of the priming device 440, and the outlet of the priming device 440 is fluidly connected to the inlet of the circulation pump 410.

Preferably, the check valve 450 is disposed proximate to the inlet of the anti-drip tube 430 and the priming device 440 is disposed proximate to the outlet of the anti-drip tube 430. And, the volume of the heat exchanging member 420 is not less than the volume of the dew-preventing tube 430, so that the high-temperature coolant in the heat exchanging member 420 can fill the dew-preventing tube 430.

The circulation pump 410 may be any feasible pump such as a submersible pump, peristaltic pump, vane pump, etc.

In the anti-condensation system 400, the serial connection sequence of the circulation pump 410, the heat exchange member 420, the anti-condensation tube 430 and the liquid injection device 440 is not limited to the one shown in fig. 2, and one skilled in the art may connect the circulation pump 410, the heat exchange member 420, the anti-condensation tube 430 and the liquid injection device 440 in any other feasible sequence as required. For example, the priming device 440 is connected in series between the circulation pump 410 and the heat exchange member 420.

As shown in fig. 2, the anti-condensation system 400 is thermally connected with the evaporation tube 360 through the heat exchange member 420.

In the first embodiment of the present invention, the heat exchanging member 420 may be any type of member and may be thermally coupled with the evaporation tube 360 in any manner. For example, the heat exchange member 420 is a pipe member, and the heat exchange member 420 is wound on the outside of the evaporation tube 360; alternatively, the heat exchange member 420 and the evaporation tube 360 are wound around each other in a twist shape; alternatively, the heat exchange member 420 abuts the evaporation tube 360 and is surrounded by a heat insulating layer.

As shown in fig. 3 and 4, in the first embodiment of the present invention, the priming device 440 includes a housing 441, a vent valve 442, a closure 443, and a priming check valve 444. The top of the housing 441 is provided with a liquid injection port 4411 and an air exhaust port 4412, the bottom of the housing 441 is provided with a liquid inlet 4413 and a liquid outlet 4414, the liquid inlet 4413 is in fluid connection with the anti-exposure pipe 430, and the liquid outlet 4414 is in fluid connection with the circulating pump 410. The exhaust valve 442 is installed at the exhaust port 4412, and the exhaust valve 442 is disposed to allow only the gas to flow from the inside of the housing 441 to the outside of the housing 441. A stopper 443 is detachably mounted to the housing 441 and serves to block the liquid inlet 4411. The charge check valve 444 is disposed at the inlet 4413, the charge check valve 444 being configured to permit only coolant to flow from the exterior of the housing 441 to the interior of the housing 441.

As shown in fig. 4, a baffle 4415 is provided in the housing 441, and the baffle 4415 divides the housing 441 into a liquid inlet chamber 4416 communicating with the liquid inlet 4413 and a liquid outlet chamber 4417 communicating with the liquid outlet 4414, and the liquid in the liquid inlet chamber 4416 flows into the liquid outlet chamber 4417 through the upper side of the baffle 4415. Preferably, the top end of the barrier 4415 is provided as an upwardly convex arcuate surface.

With continued reference to fig. 4, a spoiler 445 is also disposed within the housing 441 and aligned with the fluid inlet 4413.

The method of using and operating the priming device 440 in the first embodiment of the present invention will be described in detail with reference to fig. 3 and 4.

As shown in fig. 3 and 4, when it is desired to charge the anti-condensation system 400 with coolant, the closure 443 is opened and the coolant is charged from the fill port 4411 into the filler device 440. Meanwhile, when the coolant is filled, the circulation pump 410 is activated so that the circulation pump 410 drives the coolant to fill the entire anti-condensation system 400. After filling, the stopper 443 is attached to the filling port 4411.

As shown in FIG. 4, during operation of the anti-condensation system 400, after the coolant enters the housing 441 from the liquid inlet 4413, the spoiler 445 is first struck to extract the air from the coolant. The coolant then flows from the inlet chamber 4416 to the outlet chamber 4417 along an arcuate surface at the top of the baffle 4415. When the secondary refrigerant flows through the arc-shaped surface, the thickness of the secondary refrigerant is smaller, the contact area between the secondary refrigerant and the air is larger, and bubbles in the secondary refrigerant are easy to release into the air.

Further, as the air bubbles in the coolant are continuously released into the air within the housing 441, the air pressure within the housing 441 is continuously increased, and when the air pressure is increased to a certain degree, the exhaust valve 442 is opened, thereby allowing the air within the housing 441 to escape to the outside. As the air in the housing 441 flows out, the air pressure in the housing 441 is continuously reduced, and when the air in the housing 441 is reduced to a certain value, the exhaust valve 442 is closed again.

Based on the foregoing description, it will be appreciated by those skilled in the art that in the first embodiment of the present invention, the refrigeration apparatus is capable of heating the dew-preventing tubes 430 by absorbing heat in the refrigeration system 300 of the dew-preventing system 400 and causing the coolant at a high temperature in the heat exchanging member 420 to flow to the dew-preventing tubes 430 by the circulating pump 410. Therefore, the refrigerating apparatus can heat the dew-preventing pipe 430 through the circulating pump 410 of the dew-preventing system 400 itself even when the compressor 310 is not in operation, and the problem that the refrigerating apparatus cannot heat the dew-preventing pipe 430 when the compressor 310 is stopped is overcome.

Further, by configuring the anti-condensation system 400 with the priming device 440, an operator is enabled to charge the anti-condensation system 400 with coolant through the priming device 440. By providing the priming vent valve 446 with the priming device 440, the priming device 440 can also achieve the effect of automatically venting air within the anti-condensation system 400 while achieving the purpose of filling coolant.

In addition, one skilled in the art can also make the priming device 440 independent of the anti-sweat system 400, i.e., detach the priming device 440 from the anti-sweat system 400 after the anti-sweat system 400 is filled. One skilled in the art may also omit the priming device 440 as needed and directly prime the anti-condensation system 400 without the priming device 440.

As shown in fig. 5 to 8, the present invention also provides another priming device 440 in the second embodiment. The priming device 440 shown in the second embodiment of the present invention will be described in detail below with reference to fig. 5 to 8. Fig. 5 is a cross-sectional view of a liquid injection device 440 according to a second embodiment of the present invention, fig. 6 is a cross-sectional view of a liquid injection exhaust valve according to fig. 5, fig. 7 is a schematic diagram of a state of the liquid injection exhaust valve according to fig. 6 when liquid is injected, and fig. 8 is a schematic diagram of a state of the liquid injection exhaust valve according to fig. 6 when liquid is exhausted.

It should be noted that, for convenience of description and for enabling those skilled in the art to quickly understand the technical solution of the present invention, only the differences between the second embodiment and the first embodiment will be described in detail. For the second embodiment in common with the first embodiment, a person skilled in the art can refer to the description of the first embodiment hereinbefore.

As shown in fig. 5, in comparison with the first embodiment, in the second embodiment of the present invention, the top of the housing 441 of the priming device 440 is provided with a priming vent 4418. Also, the injection device 440 further includes an injection vent valve 446, the injection vent valve 446 being mounted at the injection vent 4418, the injection vent valve 446 being configured to allow coolant to flow from the exterior of the housing 441 to the interior of the housing 441 and to allow gas to flow from the interior of the housing 441 to the exterior of the housing 441.

As can be seen from fig. 4 and 5, the liquid injection vent 4418 in the second embodiment replaces the liquid injection vent 4411 and vent 4412 in the first embodiment, and the liquid injection vent 446 in the second embodiment replaces the vent 442 and the closure 443 in the first embodiment. The liquid injection exhaust valve 446 in the second embodiment is described in detail below with reference to fig. 6.

As shown in fig. 6, in the second embodiment of the present invention, the liquid injection/discharge valve 446 includes a valve body 4461, a first spool 4462, a first spring 4463, a second spool 4464, and a second spring 4465. Wherein the valve body 4461 is installed at the liquid injection exhaust port 4418, and a valve body hole 44611 is provided on the valve body 4461. The first valve element 4462 is slidably mounted in the valve body hole 44611, and the first valve element 4462 is provided with a valve element hole 44621 and a pilot passage 44622. The first spring 4463 is disposed between the first valve body 4462 and the valve body 4461, and the first spring 4463 is configured to provide a force to the first valve body 4462 directed to the outside of the housing 441 such that the first valve body 4462 blocks the valve body orifice 44611 and blocks the fluid guide passage 44622. The second valve spool 4464 is slidably mounted within the valve spool bore 44621, and an air guide passage 44641 is provided on the second valve spool 4464. The second spring 4465 is disposed between the second valve cartridge 4464 and the first valve cartridge 4462, the second spring 4465 being for providing a force directed toward the inside of the housing 441 to the second valve cartridge 4464 such that the second valve cartridge 4464 blocks the valve cartridge hole 44621 and the air guide passage 44641, the elastic force of the second spring 4465 being smaller than that of the first spring 4463.

The method of using and operating the priming device 440 in the second embodiment of the present invention will be described in detail with reference to fig. 7 and 8.

As shown in fig. 7, when it is desired to charge the anti-condensation system 400 with coolant, the first valve spool 4462 is pressed downward against the spring force of the first spring 4463, thereby moving the first valve spool 4462 downward from the position shown in fig. 6 to the position shown in fig. 7. At this time, the inner and outer sides of the liquid-injection exhaust valve 446 are communicated through the valve body hole 44611, the valve body hole 44621 and the liquid-guide passage 44622, and the external coolant enters the casing 441 through the valve body hole 44621, the liquid-guide passage 44622 and the valve body hole 44611 as shown by arrows in fig. 7.

As shown in fig. 8, when the air pressure in the housing 441 is high, the air in the housing 441 overcomes the elastic force of the second spring 4465, driving the second valve core 4464 to move upward from the position shown in fig. 6 to the position shown in fig. 8. At this time, the valve body hole 44611, the valve body hole 44621, and the air guide passage 44641 communicate, and air in the housing 441 flows out through the valve body hole 44611, the valve body hole 44621, and the air guide passage 44641 as indicated by arrows in fig. 8.

The priming device 440 in the second embodiment of the present invention has the same advantageous effects as the priming device 440 in the first embodiment, and also makes the construction of the priming device 440 more compact.

In addition, the present invention also provides four ways of exchanging heat between the refrigeration system 300 and the anti-condensation system 400, as shown in fig. 9-12. Fig. 9 is a schematic diagram of thermal connection between a refrigeration system 300 and an anti-condensation system 400 according to a third embodiment of the present invention, fig. 10 is a schematic diagram of thermal connection between a refrigeration system 300 and an anti-condensation system 400 according to a fourth embodiment of the present invention, fig. 11 is a schematic diagram of thermal connection between a refrigeration system 300 and an anti-condensation system 400 according to a fifth embodiment of the present invention, and fig. 12 is a schematic diagram of thermal connection between a refrigeration system 300 and an anti-condensation system 400 according to a sixth embodiment of the present invention.

As shown in fig. 9, in comparison with the first embodiment, in the third embodiment of the present invention, the refrigeration apparatus further includes a water tray 500, and the evaporation tube 360 is further used to heat the liquid (defrosting water, condensed water, etc.) in the water tray 500. Specifically, the evaporation tube 360 includes an upstream portion 361 (a portion of the evaporation tube 360 below the dotted line in fig. 9) and a downstream portion 362 (a portion of the evaporation tube 360 above the dotted line in fig. 9) located above the upstream portion 361. The upstream portion 361 is used for heating the liquid in the water tray 500, and the downstream portion 362 is thermally connected to the heat exchanging member 420. Preferably, the downstream portion 362 and the heat exchange member 420 are both located above the highest level of liquid within the drip tray 500, and more preferably, the downstream portion 362 and the heat exchange member 420 are both located above the drip tray 500.

As shown in fig. 10, in the fourth embodiment of the present invention, compared to the first embodiment, the heat exchange member 420 is a heat exchange tube, and the heat exchange tube is fixedly connected with the shell of the compressor 310. Preferably, the heat exchange tube is coiled on top of the shell of the compressor 310; and/or the heat exchange tube is fixed with the casing of the compressor 310 by a heat conductive adhesive.

As shown in fig. 11, in the fifth embodiment of the present invention, compared to the first embodiment, the heat exchange member 420 is a heat exchange tube, and the heat exchange tube is wound on the outside of the discharge pipe 311 of the compressor 310.

As shown in fig. 12, in comparison with the first embodiment, in the sixth embodiment of the present invention, the heat exchange member 420 is a heat exchange tube, and the heat exchange tube is fixedly connected with fins (not labeled in the drawing) of the condenser 320. Illustratively, each fin of the condenser 320 is provided with a plurality of through holes allowing the heat exchange tubes to pass therethrough, through which the heat exchange tubes pass and are thus secured to the condenser 320, effecting thermal connection of the heat exchange tubes to the condenser 320.

The control method for the refrigerating apparatus in the present invention will be described in detail. It should be noted that the control method described later is applicable to the refrigeration apparatus described in any of the foregoing embodiments.

As shown in fig. 13, in a seventh embodiment of the present invention, a control method for a refrigeration apparatus includes:

step S100, determining the current environment temperature and the current environment humidity of the environment where the refrigeration equipment is located.

Specifically, the refrigeration apparatus includes an ambient temperature detecting device (not shown in the drawing) and an ambient humidity detecting device (not shown in the drawing) provided on the case 100 or the door 200, so that the refrigeration apparatus detects a current ambient temperature of an environment in which the refrigeration apparatus is located through the ambient temperature detecting device, and detects a current ambient humidity of the environment in which the refrigeration apparatus is located through the ambient humidity detecting device.

In addition, the person skilled in the art can set the ambient temperature detecting device and the ambient humidity detecting device as a whole as required, in other words, the refrigerating device detects the current ambient temperature of the environment where the refrigerating device is located and the current ambient humidity of the environment where the refrigerating device is located through the same detecting device.

Step S200, determining the current dew point temperature according to the current ambient temperature and the current ambient humidity.

Specifically, the determined current ambient temperature and current ambient humidity are substituted into the temperature and humidity-dew point temperature map shown in fig. 14, and thus the current dew point temperature is determined.

In the temperature-humidity-dew point temperature comparison table shown in fig. 14, the abscissa represents ambient humidity, the ordinate represents temperature, and the data between the abscissas and the ordinates represents dew point temperature.

It should be noted that, since the temperature-humidity-dew point temperature comparison table is common knowledge in the art, and for the convenience of understanding of those skilled in the art, the temperature-humidity-dew point temperature comparison table shown in fig. 14 only lists a partial comparison relationship of temperature-humidity-dew point temperature.

Illustratively, if the current ambient temperature is 25 ℃, the current ambient humidity is 50%, the current dew point temperature is 13.9 ℃.

In step S300, the temperature of the dew-preventing tube 430 is determined.

Specifically, the refrigeration apparatus further includes a temperature sensor for detecting the temperature of the dew-preventing pipe 430, such that the refrigeration apparatus detects the temperature of the dew-preventing pipe 430 through the temperature sensor.

As an example one, a temperature sensor is provided at the outlet of the dew-preventing pipe 430 so that the refrigerating apparatus detects the temperature at the outlet of the dew-preventing pipe 430 through the temperature sensor and serves as the temperature of the dew-preventing pipe 430.

As an example two, the inlet and outlet of the dew-preventing tube 430 are respectively configured with temperature sensors such that the refrigerating apparatus takes an average value of the temperature sensors at the two places as the temperature of the dew-preventing tube 430.

As an example three, a temperature sensor is provided at the middle of the dew-preventing tube 430 such that the refrigerating apparatus detects the temperature of the dew-preventing tube 430 through the temperature sensor.

In step S400, the circulation pump 410 is controlled to rotate in response to the temperature of the dew point preventing pipe 430 being lower than or equal to the current dew point temperature.

In step S500, the circulation pump 410 is controlled to stop rotating in response to the coolant at a high temperature in the heat exchange member 420 filling the dew-preventing pipe 430.

As an example one, step S500 includes: in response to the circulation pump 410 being rotated for a preset period of time, the circulation pump 410 is controlled to stop rotating.

Specifically, when the circulation pump 410 is rotated for a preset period of time, it is determined that the coolant at a high temperature in the heat exchange member 420 has filled the dew-preventing tube 430, and the circulation pump 410 is controlled to stop rotating.

It will be appreciated by those skilled in the art that the predetermined duration may be any feasible duration provided that the coolant at a high temperature within the heat exchange member 420 is guaranteed to have filled the dew point preventing tubes 430. For example, 10S, 25S, 43S, 1min, 1.5min, etc. The specific value of the preset time period can be determined through multiple experiments.

Preferably, the volume of the heat exchange member 420 is greater than the volume of the dew-preventing tube 430, and when the circulation pump 410 is rotated for a predetermined period of time, the high-temperature coolant flowing out of the heat exchange member 420 is mostly located within the dew-preventing tube 430, and a small portion is located upstream and downstream of the dew-preventing tube 430, to ensure that the dew-preventing tube 430 can be filled with the high-temperature coolant each time.

As an example two, step S500 includes: in response to the circulation pump 410 being rotated by a preset number of rotations, the circulation pump 410 is controlled to stop rotating.

Specifically, when the circulation pump 410 rotates a preset number of revolutions, it is determined that the coolant of high temperature in the heat exchange member 420 has filled the dew-preventing tube 430, and the circulation pump 410 is controlled to stop rotating.

It will be appreciated by those skilled in the art that the predetermined number of revolutions can be any number of revolutions that is feasible provided that the coolant at a high temperature within the heat exchange member 420 is guaranteed to have been filled with the dew point preventing tubes 430. Such as 50 revolutions, 80 revolutions, 120 revolutions, 155 revolutions, 300 revolutions, etc. The specific number of preset revolutions may be determined by a number of experiments.

Preferably, the volume of the heat exchange member 420 is greater than the volume of the dew-preventing tube 430, and when the circulation pump 410 is rotated a predetermined number of revolutions, the high-temperature coolant flowing out of the heat exchange member 420 is mostly located inside the dew-preventing tube 430, and a small portion is located upstream and downstream of the dew-preventing tube 430, to ensure that the dew-preventing tube 430 can be filled with the high-temperature coolant each time.

As an example three, step S500 includes: the circulation pump 410 is controlled to stop rotating in response to the temperature increase at the outlet of the dew-preventing pipe 430.

Specifically, a temperature sensor is provided at the outlet of the dew-preventing tube 430, and when the temperature sensor detects that the temperature at the outlet of the dew-preventing tube 430 is raised by a certain temperature (e.g., 0.3 ℃, 0.5 ℃, 0.8 ℃, 1 ℃, 1.2 ℃, 2 ℃, etc.), it is determined that the dew-preventing tube 430 has been filled with the coolant of high temperature in the heat exchanging member 420, and the circulation pump 410 is controlled to stop rotating. Preferably, the temperature sensor is configured to directly detect the temperature of the coolant at the outlet of the dew-preventing tube 430 to ensure the immediacy of the detection by the temperature sensor.

In an optional step S600, the circulation pump 410 is controlled to rotate again in response to the temperature of the coolant in the dew-preventing pipe 430 being not greater than a first preset temperature.

Specifically, the refrigeration apparatus also includes a coolant temperature sensor for detecting the temperature of the coolant within the dew-preventing tube 430, which can be located at any location of the dew-preventing tube 430, such as at the middle of the dew-preventing tube 430, near the outlet of the dew-preventing tube 430, or near the inlet of the dew-preventing tube 430. Preferably, the coolant temperature sensor can be disposed in the middle of the dew point preventing tube 430. Further, a mounting hole is provided in the middle of the dew-preventing tube 430, the coolant temperature sensor is mounted in the mounting hole, and a portion of the coolant temperature sensor extends into the dew-preventing tube 430.

Wherein the first preset temperature is a value not greater than the current dew point temperature. For example, the first preset temperature is the current dew point temperature, or the first preset temperature is 0.5 ℃, 1 ℃, 2 ℃ less than the current dew point temperature, etc. Alternatively, the first preset temperature may be set to a specific value, such as 20 ℃, 22 ℃, 25 ℃, etc., as needed by those skilled in the art.

Those skilled in the art will appreciate that when the temperature of the coolant within the dew-preventing tubes 430 is not greater than the first predetermined temperature, it is indicative that the coolant within the dew-preventing tubes 430 has released a sufficient amount of heat to provide a lower heat exchange efficiency with the dew-preventing tubes 430.

In an optional step S700, the circulation pump 410 is controlled to stop in response to the temperature of the dew-preventing pipe 430 reaching a second preset temperature.

Wherein the second preset temperature is greater than the current dew point temperature and not greater than the current ambient temperature. Preferably, the second preset temperature is an average value of the current dew point temperature and the current ambient temperature, so as to reduce the energy consumption of the refrigeration equipment on the premise of ensuring that condensation does not occur after the circulating pump 410 is stopped at the door seal of the refrigeration equipment.

Based on the foregoing description, it will be understood by those skilled in the art that in the seventh embodiment of the present invention, the circulation pump 410 is controlled to rotate when the temperature of the dew point preventing pipe 430 is lower than or equal to the current dew point temperature; when the dew-preventing pipe 430 is filled with the high-temperature coolant in the heat exchanging member 420, the circulation pump 410 is controlled to stop rotating, so that the high-temperature coolant sufficiently heats the dew-preventing pipe 430, and the waste of coolant heat is avoided. Further, when the temperature of the coolant in the dew-preventing pipe 430 is not greater than the first preset temperature, or when the cooling rate of the coolant in the dew-preventing pipe 430 is less than or equal to the preset rate, the circulating pump 410 is controlled to rotate again, so that the dew-preventing pipe 430 can continuously flow in the high-temperature coolant. Meanwhile, as the starting time of the circulation pump 410 increases, the heat of the coolant in the entire anti-condensation system 400 is increased, so that the working frequency of the circulation pump 410 is higher and higher.

In addition, in other embodiments of the present invention, the person skilled in the art may replace the step S600 with: in response to the cooling rate of the coolant within the dew-preventing tubes 430 being less than or equal to the predetermined rate, the circulation pump 410 is controlled to rotate again.

The preset rate may be any feasible value, such as 0.1C/min, 0.15C/min, 0.3C/min, 0.5C/min, etc.

Those skilled in the art will appreciate that when the cooling rate of the coolant within the dew-preventing tubes 430 is less than or equal to the predetermined rate, it is indicative that the coolant within the dew-preventing tubes 430 has released a sufficient amount of heat to provide a lower heat exchange efficiency with the dew-preventing tubes 430.

Specifically, after the circulation pump 410 stops rotating, the temperature of the coolant in the dew-preventing pipe 430 is detected every 1 minute, and a difference between the detected temperatures is calculated, and the absolute value of the difference is the cooling rate of the coolant.

As shown in fig. 15, in the eighth embodiment of the present invention, the refrigeration apparatus further includes a controller 600 and a memory 700.

In the present embodiment, the memory 700 is used to store execution instructions, in particular computer programs that can be executed. Further, the execution instructions stored by the memory 700 are configured to, when executed by the controller 600, enable the refrigeration appliance to perform the control method described in any of the embodiments above.

In this embodiment, the memory 700 may include a memory and a non-volatile memory (non-volatile memory), and provide the controller 600 with execution instructions and data. By way of example, the Memory may be a Random-Access Memory (RAM), and the non-volatile Memory may be at least 1 disk Memory.

In this embodiment, the controller 600 is an integrated circuit chip with the capability of processing signals. The controller 600 may be a general-purpose processor such as a central processing unit (Central Processing Unit, CPU), network processor (Network Processor, NP), digital signal processor (Digital Signal Processor, DSP), application specific integrated circuit (Application Specific Integrated Circuit, ASIC), field-programmable gate array (Field-Programmable Gate Array, FPGA) or other programmable logic device, discrete gate or transistor logic device, discrete hardware components, microprocessor, or any other conventional processor.

Thus far, the technical solution of the present invention has been described in connection with the foregoing embodiments, but it will be readily understood by those skilled in the art that the scope of the present invention is not limited to only these specific embodiments. The technical solutions in the above embodiments can be split and combined by those skilled in the art without departing from the technical principles of the present invention, and equivalent changes or substitutions can be made to related technical features, so any changes, equivalent substitutions, improvements, etc. made within the technical principles and/or technical concepts of the present invention will fall within the protection scope of the present invention.

Claims

1. A control method for a refrigeration apparatus including a cabinet having a storage compartment, a door, a refrigeration system filled with a refrigerant, and an anti-condensation system filled with a coolant, the anti-condensation system including a circulation pump, a heat exchange member, and an anti-condensation pipe in series, the heat exchange member being thermally connected to the refrigeration system so that the coolant in the heat exchange member absorbs heat of the refrigeration system, the volume of the heat exchange member being not less than the volume of the anti-condensation pipe;

the control method comprises the following steps:

determining the temperature of the anti-dew tube;

2. The control method for a refrigeration appliance according to claim 1, wherein,

the control of the circulation pump to stop rotation in response to the coolant at a high temperature in the heat exchange member filling the dew-preventing pipe comprises:

3. The control method for a refrigeration appliance according to claim 1, wherein,

4. The control method for a refrigeration appliance according to claim 1, wherein,

5. A control method for a refrigeration appliance according to any one of claims 1 to 4, wherein,

after the dew-preventing pipe is filled with the coolant in response to the high temperature in the heat exchange member, the control method further includes:

6. A control method for a refrigeration appliance according to any one of claims 1 to 4, wherein,

7. A control method for a refrigeration appliance according to any one of claims 1 to 4, wherein,

the control method further includes:

8. A refrigeration appliance comprising:

a case defining a storage chamber therein;

a door body for shielding the storage chamber;

a controller;

a memory having stored thereon execution instructions that, when executed, enable the refrigeration appliance to perform the control method of any one of claims 1 to 7.

9. The refrigeration appliance of claim 8 wherein,

the anti-condensation system further comprises a one-way valve which is connected in series between the outlet of the circulating pump and the inlet of the anti-condensation pipe.

10. The refrigeration appliance of claim 9 wherein,

the circulating pump, the heat exchange component, the one-way valve and the dew prevention pipe are connected end to end in sequence.