CN221944591U - Countercurrent defrosting refrigerator - Google Patents

Abstract

The utility model discloses a countercurrent defrosting refrigerator, relates to the technical field of refrigerators, and aims to solve the problem that condensation is generated near a door frame and a door body of the countercurrent defrosting refrigerator under a defrosting working condition. The reverse flow defrost refrigerator includes a condenser, a dew removing tube, a first pressure reducer, a first switching valve, and a second pressure reducer, the condenser configured to release heat during a cooling operation and absorb heat during a defrost operation. One end of the condenser is connected with one end of the first pressure reducer through the dew removing pipe, at least part of the first switching valve is connected with the first pressure reducer in parallel, and the second pressure reducer is connected between the condenser and the first pressure reducer in parallel along the flowing direction of the refrigerant. The reverse flow defrost refrigerator is configured to: under the refrigeration working condition, the refrigerant flows through the condenser, the dew removing pipe and the first pressure reducer in sequence. Under defrosting operation, the refrigerant flows from the first switching valve to the condenser through at least the second pressure reducer. The countercurrent defrosting refrigerator provided by the utility model is used for solving the problem of condensation near the door body and the door frame.

Description

Countercurrent defrosting refrigerator

Technical Field

The utility model relates to the technical field of refrigerators, in particular to a countercurrent defrosting refrigerator.

Background

The refrigerator is a common electrical appliance in daily life, and the refrigerator has the problem of frosting on the surfaces of evaporators used for cooling the freezing chamber and the temperature-changing chamber under the refrigerating working condition because the storage chambers such as the freezing chamber and the temperature-changing chamber have lower temperature. Therefore, the flow direction of the refrigerant in the evaporator and the condenser can be changed to enable the refrigerator to be in a defrosting working condition, and the refrigerant is liquefied and releases heat in the evaporator at the moment and is used for melting frosting on the surface of the evaporator.

In the refrigeration working condition of the refrigerator, the temperature of the door frame and the door body of the storage cavity is lower than the dew point temperature due to the fact that the temperature of the storage cavity is lower. When the ambient humidity is higher, the lower temperature of door frame and door body department can lead to this position department to produce the condensation, influences user's use experience. In the related art, the dew removing pipe is connected in series between the condenser and the capillary tube and is arranged close to the door frame of the storage cavity, so that the dew removing pipe in a refrigeration working condition can heat the door frame and the door body through heat released by liquefying the refrigerant, and the phenomenon of condensation at the door frame and the door body is avoided.

However, in the reverse defrosting mode, the refrigerant flowing through the dew removing pipe is vaporized and absorbs heat nearby, so that the temperature nearby the door frame and the door body is lower, namely condensation is still generated nearby the door frame and the door body in the defrosting mode.

Disclosure of utility model

The utility model provides a countercurrent defrosting refrigerator, which aims to solve the problem that condensation is generated near a door frame and a door body of the countercurrent defrosting refrigerator in defrosting working conditions.

In order to achieve the above purpose, the utility model adopts the following technical scheme:

In a first aspect, the present utility model provides a reverse flow defrost refrigerator comprising a condenser, a dew removal tube, a first pressure reducer, a first switch valve, and a second pressure reducer, the condenser configured to release heat during a cooling mode and to absorb heat during a defrost mode. One end of the condenser is connected with one end of the first pressure reducer through the dew removing pipe, at least part of the first switching valve is connected with the first pressure reducer in parallel, and the second pressure reducer is connected between the condenser and the first pressure reducer in parallel along the flowing direction of the refrigerant. The reverse flow defrost refrigerator is configured to: under the refrigeration working condition, the refrigerant flows through the condenser, the dew removing pipe and the first pressure reducer in sequence. Under defrosting operation, the refrigerant flows from the first switching valve to the condenser through at least the second pressure reducer.

Therefore, in the refrigeration working condition of the countercurrent defrosting refrigerator, the refrigerant sequentially flows through the condenser, the dew removing pipe and the first pressure reducer, and under the action of the first pressure reducer, the high-temperature and high-pressure gaseous refrigerant can liquefy and release heat in the condenser and the dew removing pipe, so that the dew removing pipe arranged near the door body or the door frame can heat the door body or the door frame through the heat released by the liquefaction of the refrigerant, and the door frame and the door body are prevented from being at lower temperature and generating a condensation phenomenon.

In addition, when the countercurrent defrosting refrigerator is in a defrosting working condition, the refrigerant flows to the condenser through at least the second pressure reducer by the first switching valve, and by switching the pressure reducing equipment from the first pressure reducer in the refrigerating working condition to the second pressure reducer in the defrosting working condition, the dew removing pipe arranged at the upstream of the second pressure reducer or in parallel with the second pressure reducer can be in a heating state (namely, the refrigerant flows through the dew removing pipe and liquefies and releases heat) or does not circulate the refrigerant, so that the condition that the temperature near the door frame and the door body is lower than the dew point temperature and condensation is generated due to the continuous cooling of the dew removing pipe in the defrosting working condition is avoided.

In some embodiments, the reverse flow defrost refrigerator further includes a second switching valve located between the condenser and the dew removing tube in a flow direction of the refrigerant. The second switching valve is connected with the dew removing pipe in series, and the second switching valve and the dew removing pipe are connected with the second pressure reducer in parallel.

In a second aspect, the present utility model provides a reverse flow defrost refrigerator comprising a condenser, a dew removal tube, a first pressure reducer, a first switching valve, a second pressure reducer, and a second switching valve, the condenser being configured to release heat during a cooling mode and to absorb heat during a defrost mode. One end of the condenser is connected with one end of the first pressure reducer through the dew removing pipe, and the first switching valve is at least partially connected with the first pressure reducer in parallel. Along the flowing direction of the refrigerant, a second switching valve is arranged in series between the condenser and the dew removing pipe, and a second pressure reducer is arranged between the condenser and the dew removing pipe and is connected with at least part of the second switching valve in parallel. The first switching valve and the second switching valve are adjusted, so that the refrigerant in the defrosting working condition can be heated when flowing through the dew removing pipe, and the condition that the temperature near the door frame and the door body is lower than the dew point temperature and condensation is generated due to continuous cooling of the dew removing pipe in the defrosting working condition is avoided.

Because the two countercurrent defrosting refrigerators provided by the embodiment of the application can be provided with the dew removing pipe which is not in a refrigerating state in defrosting, the problem of condensation nearby caused by cooling of the dew removing pipe in defrosting working conditions is avoided.

In addition, the countercurrent defrosting refrigerator in the second aspect can further enable the dew removing pipe to be adjusted to be in a heating state in a defrosting working condition, so that the temperature near the door frame and the door body is further improved, and the problem that dew is generated near the defrosting working condition due to cooling of the dew removing pipe is avoided.

In some embodiments, the second switching valve is a two-position, two-way electrically controlled valve, and the second pressure reducer is disposed in parallel with the second switching valve.

In some embodiments, the second switching valve is a two-position three-way electric control valve, and the condenser is connected in series with the dew removing pipe through a first end and a second end of the second switching valve along the flowing direction of the refrigerant, and a third end of the second switching valve is connected with the first end or the second end of the second switching valve through a second pressure reducer.

In some embodiments, the first switching valve is a two-position, two-way electrically controlled valve, and the first switching valve is disposed in parallel with the first pressure reducer.

In some embodiments, the first switching valve is a two-position three-way electrically controlled valve, and the first switching valve is located at an end of the dew removing pipe away from the condenser along the flow direction of the refrigerant. The first end of the first switching valve is connected with the dew removing pipe, the second end of the first switching valve is used for being connected with the evaporator, and the third end of the first switching valve is connected with the dew removing pipe or the evaporator through the first pressure reducer.

In some embodiments, a reverse flow defrost refrigerator includes a four-way valve, a first relay, and a second relay. The first relay is electrically connected with the four-way valve and used for controlling the four-way valve to switch and adjust the refrigerating working condition and the defrosting working condition. The second relay is electrically connected with the first switching valve and the second switching valve, and the second relay is arranged in parallel with the first relay. The first relay and the second relay are configured to: the first relay controls the four-way valve to be in a refrigerating working condition, the second relay controls the first switching valve and the second switching valve to be in a first state, so that the first switching valve closes a loop of the first pressure reducer connected in parallel, and the second switching valve opens a loop of the second pressure reducer connected in parallel.

In some embodiments, the first relay and the second relay are further configured to: the first relay controls the four-way valve to switch to a defrosting working condition, the second relay controls the first switching valve and the second switching valve to switch to a second state, so that the first switching valve opens a loop connected with the first pressure reducer in parallel, and the second switching valve closes the loop connected with the second pressure reducer in parallel.

In some embodiments, the reverse flow defrost refrigerator further includes a temperature and humidity control module, a temperature sensor, a humidity sensor, and a third relay. The temperature sensor is used for detecting the ambient temperature and is electrically connected with the temperature and humidity control module, and the humidity sensor is used for detecting the ambient humidity and is electrically connected with the temperature and humidity control module. The second relay is electrically connected with the first switching valve and the second switching valve sequentially through the temperature and humidity control module and the third relay. In the cooling condition, the first switching valve and the second switching valve are in a first state. The first relay controls the four-way valve to switch to a defrosting working condition, the second relay starts the temperature and humidity control module, and the temperature and humidity control module is configured to: when the ambient temperature is higher than the preset temperature and the ambient humidity is lower than the preset humidity, the temperature and humidity control module controls the first switching valve and the second switching valve to be in a first state through the third relay. Otherwise, the temperature and humidity control module controls the first switching valve and the second switching valve to be in the second state through the third relay.

In some embodiments, the first pressure reducer is a capillary tube or an electronic expansion valve.

In some embodiments, the second pressure reducer is a capillary tube or an electronic expansion valve.

In some embodiments, the reverse flow defrost refrigerator further includes a compressor having a return air end and a discharge air end, a four-way valve, and an evaporator. The four-way valve is provided with a first port, a second port, a third port and a fourth port, wherein the first port is connected with the air return end, the second port is connected with the exhaust end, and the third port is connected with one end of the condenser, which is far away from the dew removing pipe, along the flowing direction of the refrigerant. Along the flow direction of the refrigerant, one end of the evaporator is connected with the fourth port, and a first switching valve and a first pressure reducer are arranged between the other end of the evaporator and the dew removing pipe. The first port is communicated with the fourth port, and the second port is communicated with the third port, so that the countercurrent defrosting refrigerator enters a refrigeration working condition. The first port is communicated with the third port, and the second port is communicated with the fourth port, so that the countercurrent defrosting refrigerator enters a defrosting working condition.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings required for the description of the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present application, and other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.

Fig. 1 is a schematic perspective view of a refrigerator according to an embodiment of the present application;

FIG. 2 is a cross-sectional view of the case shown in FIG. 1;

fig. 3 is a schematic diagram of a first refrigerator according to an embodiment of the present application in a refrigeration condition;

FIG. 4 is a schematic view of the first refrigerator shown in FIG. 3 in a defrost mode;

Fig. 5 is a schematic view of a refrigerator according to the related art, in which a dew removing pipe is installed;

fig. 6 is a schematic diagram of a second refrigerator according to an embodiment of the present application in a refrigeration condition;

FIG. 7 is a schematic view of the second refrigerator shown in FIG. 6 in a defrost mode;

FIG. 8 is another schematic view of the second refrigerator shown in FIG. 6 in a defrost mode;

FIG. 9 is a schematic diagram of one control connection of the four-way valve, the first switching valve, and the second switching valve shown in FIG. 6;

FIG. 10 is a schematic diagram of another control connection of the four-way valve, the first switching valve, and the second switching valve shown in FIG. 6;

FIG. 11 is a schematic diagram of a third refrigerator according to an embodiment of the present application in a defrosting mode;

Fig. 12 is a schematic diagram of a fourth refrigerator according to an embodiment of the present application in a refrigeration condition;

fig. 13 is a schematic view of a fourth refrigerator according to an embodiment of the present application in a defrosting mode.

Reference numerals:

100-refrigerator;

1-a box body; 11-an object placing cavity; 12-a housing; 13-an inner container; 14-an insulating layer;

2-door body;

31-a compressor; 32-four-way valve; 33-a condenser; 34-a pressure reducer; 341-a first pressure reducer; 342-a second pressure reducer; 35-an evaporator; 36-a dew removing pipe;

41-a first switching valve; 42-a second switching valve;

51-a first relay; 52-a second relay; 53-a third relay;

61-a temperature and humidity control module; 62-a temperature sensor; 63-a humidity sensor;

7-a controller.

Detailed Description

The following description of the embodiments of the present utility model will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present utility model, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the utility model without making any inventive effort, are intended to be within the scope of the utility model.

In the description of the present utility model, it should be understood that the terms "upper", "lower", "left", "right", "front", "rear", "inner", "outer", and the like indicate orientations or positional relationships based on the orientations or relative positional relationships shown in the drawings, are merely for convenience in describing the present utility model and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present utility model. Unless otherwise specified, the above description of the azimuth may be flexibly set in the course of practical application in the case where the relative positional relationship shown in the drawings is satisfied.

The terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated, whereby features defining "first," "second," or the like, may explicitly or implicitly include one or more such features. In the description of the present utility model, unless otherwise indicated, the meaning of "a plurality" is two or more.

In the description of the present utility model, it should be noted that the terms "mounted," "connected," and "communicating" are to be construed broadly as being fixedly connected, detachably connected, and integrally connected, unless otherwise specifically defined and limited. Either directly or indirectly through intermediaries, or in communication between two elements, or electrically, the specific meaning of the terms in the present disclosure will be understood by those skilled in the art in view of the specific circumstances.

In embodiments of the present utility model, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, article, or apparatus. Without further limitation, an element defined by the phrase "comprising one … …" does not exclude the presence of other like elements in a process, article or apparatus that comprises the element.

In embodiments of the utility model, words such as "exemplary" or "such as" are used to mean serving as an example, instance, or illustration. Any embodiment or design described as "exemplary" or "e.g." in an embodiment of the present utility model should not be construed as preferred or advantageous over other embodiments or designs, rather, the use of the word "exemplary" or "e.g." is intended to present the relevant concepts in a concrete fashion.

As shown in fig. 1, fig. 1 is a schematic perspective view of a reverse flow defrosting refrigerator (hereinafter referred to as a refrigerator 100) according to an embodiment of the present application, the refrigerator 100 may include a box 1 and a door 2, the box 1 may be a box-like structure similar to a cuboid, and the box 1 may be a box-like structure with other shapes. The inside of the box body 1 is provided with a storage cavity 11 for freezing or refrigerating preset articles, and the door body 2 is connected with the box body 1, so that the door body 2 can open or close the storage cavity 11.

Illustratively, the door 2 may be rotatably coupled to one side of the case 1 such that the door 2 may rotatably open or close the storage chamber 11. Or the door body 2 can be connected with the box body 1 through a hinge or a guide rail, and the object placing cavity 11 can be opened or closed through the door body 2.

In some embodiments, as shown in fig. 2, the case 1 may include a housing 12, a liner 13, and an insulation layer 14, wherein a storage cavity 11 is formed inside the liner 13, and the storage cavity 11 is used for refrigerating or freezing preset articles. The inner container 13 is located in the shell 12, so that the structural strength of the box body 1 is improved through the shell 12, the heat insulation layer is filled between the inner container 13 and the shell 12, so that heat exchange between the storage cavity 11 and the external environment is reduced, the low-temperature storage life of preset articles in the storage cavity 11 is prolonged, and refrigeration power consumption is reduced.

In order to maintain a stable freezing and/or refrigerating temperature in the storage chamber 11, as shown in fig. 3, the refrigerator 100 includes a compressor 31, a four-way valve 32, a condenser 33, a pressure reducer 34, and an evaporator 35, the compressor 31 has a return air end and an exhaust air end, and the four-way valve 32 has a first port a, a second port B, a third port C, and a fourth port D. The first port a is connected with the return air end, the second port B is connected with the exhaust air end, one end of the condenser 33 may be connected with the third port C, one end of the evaporator 35 may be connected with the other end of the condenser 33 through the pressure reducer 34, and the other end of the evaporator 35 may be connected with the fourth port D.

When the first port a is connected to the fourth port D and the second port B is connected to the third port C as shown in fig. 3, so that the refrigerator 100 is in a cooling condition, the refrigerant flowing out from the air discharge end of the compressor 31 may circulate along the second port B, the third port C, the condenser 33, the pressure reducer 34, the evaporator 35, the fourth port D, the first port a and the air return end of the compressor 31 in sequence.

In this way, the gaseous refrigerant flowing out of the compressor 31 can liquefy and release heat at the condenser 33, the liquefied refrigerant is vaporized in the evaporator 35 after flowing through the capillary tube or the pressure reducer 34 of the electronic throttle valve structure and absorbs heat through the evaporator 35, thereby cooling the periphery of the evaporator 35, and the vaporized refrigerant is sucked into the compressor 31 and compressed. The air in the storage cavity 11 can be circulated through the evaporator 35 by the air duct structure and the fan to maintain the refrigeration temperature and the freezing temperature in the storage cavity 11 (such as the freezing cavity, the refrigerating cavity and the temperature changing cavity), and the energy-saving effect of the refrigerator 100 in refrigeration working conditions can be improved due to the fact that the compressor 31 is used for refrigerating, namely the refrigerator 100 is low in power consumption and environment-friendly.

In addition, when the first port a is connected to the third port C as shown in fig. 4 and the second port B is connected to the fourth port D to make the refrigerator 100 in the defrosting mode, the refrigerant flowing out of the discharge end of the compressor 31 may circulate along the second port B, the fourth port D, the evaporator 35, the pressure reducer 34, the condenser 33, the third port C, the first port a and the return air end of the compressor 31 in this order, i.e., the refrigerant reversely flows between the condenser 33, the pressure reducer 34 and the evaporator 35 compared to the refrigerating mode.

In this way, the gaseous refrigerant flowing out of the compressor 31 can liquefy and release heat at the evaporator 35, the liquefied refrigerant is vaporized in the condenser 33 after flowing through the pressure reducer 34 and absorbs heat through the condenser 33, thereby cooling the surroundings of the evaporator 35, and the vaporized refrigerant is sucked into the compressor 31 and compressed. If the surface of the evaporator 35 is frosted during the refrigeration condition, the refrigerator 100 can be adjusted to be in the defrosting condition to melt the frosting of the surface of the evaporator 35 through the liquefaction heat release of the refrigerant, so that the heat exchange efficiency of the evaporator 35 and the air flowing through can be improved.

Between the compressor 31 and the condenser 33 and the evaporator 35, the four-way valve 32 in the above-described embodiment can be used to switch the cooling and heating conditions of the refrigerator 100. In addition, a switching loop of a refrigerating working condition and a heating working condition can be formed by connecting the electromagnetic valve and the flow pipeline.

For example, the discharge end of the compressor 31, the condenser 33, the pressure reducer 34, the evaporator 35, and the return end of the compressor 31 are connected in this order, the evaporator 35 and the return end of the compressor 31 are connected by a two-position three-way valve, and the condenser 33 and the discharge end of the compressor 31 are connected by another two-position three-way valve. The last port of the former two-position three-way valve is connected with the exhaust end of the compressor 31 through a pipeline, and the last port of the latter two-position three-way valve is connected with the return air end of the compressor 31 through a pipeline, namely, the refrigerator 100 can be switched and adjusted between the refrigeration working condition and the defrosting working condition by controlling the conduction states of the two-position three-way valves.

The evaporator 35 is heated and defrosted by the countercurrent of the refrigerant, so that the defrosting speed and the melting efficiency of the surface of the evaporator 35 can be improved, and the energy consumption ratio is high.

However, in the refrigerating condition of the refrigerator 100, since the interior of the storage chamber 11 has a relatively low temperature, particularly, the interior temperature of the storage chamber 11 for freezing is below-15 ℃, the temperature of the door frame of the storage chamber 11 (i.e., the edge of the case 1 near the opening of the storage chamber 11) and the nearby door body is lower than the dew point temperature. When the ambient humidity is higher, the lower temperature of door frame and door body department can lead to this position department to produce the condensation, influences user's use experience.

In the related art, as shown in fig. 5, the refrigerator 100 further includes a dew removing tube 36, and the dew removing tube 36 is installed between the condenser 33 and the reducer 34 in a flow direction of the refrigerant. As shown in fig. 2, the dew removing tube 36 is located between the liner 13 and the outer shell 12 of the box 1 and is close to the front opening of the storage cavity 11, that is, the dew removing tube 36 may be installed close to the door frame of the box 1, or the dew removing tube 36 may be installed in the door body 2 (as shown in fig. 1) and is close to the door frame.

In view of this, in the cooling condition shown in fig. 5, a part of the refrigerant flowing out from the condenser 33 may liquefy and release heat at the dew removing pipe 36 before flowing into the evaporator 35 through the pressure reducer 34, thereby heating the door frame and the door body 2 in the vicinity shown in fig. 1. Therefore, the door frame and the nearby door body 2 are heated through the dew removing pipe under the refrigeration working condition, and the temperature of the door frame and the door body 2 is prevented from being lower than the dew point temperature, so that the condensation phenomenon on the door frame and the door body 2 is prevented.

However, when the refrigerator 100 is in the reverse defrosting mode, the refrigerant flows from the evaporator 35 shown in fig. 5 to the condenser 33 through the pressure reducer 34 and the dew removing pipe 36, at this time, the refrigerant liquefies and releases heat at the evaporator 35, and the refrigerant vaporizes and absorbs heat of the door frame and the door body at the dew removing pipe 36. Therefore, the temperature of the door frame and the door body in the defrosting working condition is lower, and the refrigerant in the defrosting working condition firstly flows through the dew removing pipe 36, so that the temperature of the door frame and the door body is quickly reduced below the dew point temperature, condensation can be generated near the door frame and the door body under the defrosting working condition according to the scheme shown in fig. 5, and the setting is more serious.

In order to solve the above problems, as shown in fig. 6 and 7, the refrigerator 100 includes a condenser 33, a dew removing pipe 36, a first pressure reducer 341, a second pressure reducer 342, and a first switching valve 41, one end of the condenser 33 is connected to the first pressure reducer 341 through the dew removing pipe 36, and the other end of the condenser 33 is used to connect the four-way valve 32. The first switching valve 41 is at least partially disposed in parallel with the first pressure reducer 341, and the second pressure reducer 342 is disposed in parallel between the condenser 33 and the first pressure reducer 341 along the flow direction of the refrigerant, for example, an end of the first pressure reducer 341 away from the dew removing pipe 36 may be connected to the four-way valve 32 through the evaporator 35.

As such, the refrigerator 100 is configured to: in the refrigerating condition shown in fig. 6, the refrigerant flowing out from the compressor 31 through the four-way valve 32 in the refrigerating condition may flow through the condenser 33, the dew removing pipe 36 and the first pressure reducer 341 in order, and the refrigerant flowing out from the first pressure reducer 341 may flow back to the air return end of the compressor 31 through the evaporator 35 and the four-way valve 32. Under the action of the first pressure reducer 341, the high-temperature and high-pressure gaseous refrigerant can liquefy and release heat in the condenser 33 and the dew removing pipe 36, so that the dew removing pipe 36 installed at or near the door body can heat the door body or the door frame by the heat released by the refrigerant liquefaction, thereby avoiding the door body and the door body from being at a lower temperature and generating a condensation phenomenon.

In addition, when the refrigerator 100 is in the defrosting mode shown in fig. 7, the refrigerant flowing out of the compressor 31 through the four-way valve 32 of the defrosting mode may be configured to flow from the first switching valve 41 to the condenser 33 through at least the second reducer 342 after flowing through the evaporator 35 and liquefying and releasing heat to melt frost at the evaporator 35. In this way, by switching the decompression device from the first decompression device 341 in the refrigeration condition to the second decompression device 342 in the defrosting condition, the dew removing pipe 36 located upstream of the second decompression device 342 or arranged in parallel with the second decompression device 342 may be in a heating state (i.e. the refrigerant flows through the dew removing pipe 36 and liquefies and releases heat) or does not circulate the refrigerant, so as to avoid the occurrence of the condition that the temperature near the door frame and the door body is lower than the dew point temperature and condensation is generated due to the continuous cooling of the dew removing pipe 36 in the defrosting condition.

It should be noted that, along the flow direction of the refrigerant, one end of the first pressure reducer 341 away from the condenser 33 may be connected to the evaporator 35, and then different air channels may be configured, so that the air in the storage chamber 11 for refrigeration, freezing and temperature changing may flow through the evaporator 35 under the driving of the fan. Alternatively, between the first pressure reducer 341 and the fourth port D of the four-way valve 32, the evaporators may be configured as parallel and/or serial freezing evaporators, refrigerating evaporators and/or temperature-changing evaporators along the flow direction of the refrigerant, so as to maintain the temperatures of the corresponding storage chambers, respectively.

In addition, the compressor 31 may be connected to the evaporator 35 and the condenser 33 through other switching circuits for switching the cooling and defrosting conditions of the refrigerator 100.

In some embodiments, as shown in fig. 6 and 7, the refrigerator 100 further includes a second switching valve 42, the second switching valve 42 is installed in series between the condenser 33 and the dew removing pipe 36 in the flow direction of the refrigerant, and a second pressure reducer 342 is located between the condenser 33 and the dew removing pipe 36 and is disposed in parallel with at least a portion of the second switching valve 42. In this way, the operating states of the first pressure reducer 341 and the second pressure reducer 342 can be adjusted by adjusting the second switching valve 42 in conjunction with the first switching valve 41.

Taking the first pressure reducer 341 and the second pressure reducer 342 as examples, since the capillary tube is a pressure reducing structure, the internal diameter and the flow rate of the arrangement of the capillary tube are far smaller than those of the switching valve and the refrigerant pipeline. Thus, if the parallel circuit with the capillary structure is in a conductive state, most or all of the refrigerant flows through the parallel circuit of the capillary structure.

As shown in fig. 6 and 7, the first switching valve 41 may be a two-position two-way electrically controlled valve, for example, one end of the first switching valve 41 is connected to one end of the first pressure reducer 341, and the other end of the first switching valve 41 is connected to the other end of the first pressure reducer 341, so that the first switching valve 41 and the first pressure reducer 341 are disposed in parallel (i.e., the first switching valve 41 is a parallel circuit of the first pressure reducer 341). The second switching valve 42 may be a two-position three-way electric control valve, and along the flow direction of the refrigerant, the condenser 33 may be disposed in series with the dew removing tube 36 through the first end and the second end of the second switching valve 42, and the third end of the second switching valve 42 may be disposed in connection with the first end or the second end of the second switching valve 42 through the second pressure reducer 342, that is, the first end and the second end of the second switching valve 42 are parallel circuits of the second pressure reducer 342.

In this way, the four-way valve 32, the first switching valve 41 and the second switching valve 42 are adjusted to enable the refrigerator 100 to be in the refrigerating condition shown in fig. 6, where the first switching valve 41 closes the parallel circuit of the first pressure reducer 341 (for example, the first switching valve 41 is closed), and the second switching valve 42 opens the parallel circuit of the second pressure reducer 342 (for example, the first end and the second end of the second switching valve 42 are in a conducting state), that is, the first switching valve 41 and the second switching valve 42 are in a first state. Under the refrigeration condition, the refrigerant sequentially flows through the condenser 33, the parallel circuit of the second pressure reducer 342, the second switching valve 42, the dew removing pipe 36, the first pressure reducer 341 and the evaporator 35, and because the dew removing pipe 36 is located at the upstream of the first pressure reducer 341, part of the refrigerant flowing through the dew removing pipe 36 can liquefy and release heat, and is used for heating the door frame and/or door body near the dew removing pipe 36 to avoid low-temperature condensation.

In addition, the four-way valve 32, the first switching valve 41 and the second switching valve 42 are adjusted to enable the refrigerator 100 to enter the defrosting operation shown in fig. 7, wherein the first switching valve 41 opens the parallel circuit of the first pressure reducer 341 (for example, the first switching valve 41 is opened), and the second switching valve 42 closes the parallel circuit of the second pressure reducer 342 (for example, the first end and the second end of the second switching valve 42 are closed), that is, the first switching valve 41 and the second switching valve 42 are in the second state. Under defrosting operation, the refrigerant flows through the evaporator 35, the first switching valve 41, the dew removing pipe 36, the first and second switching valves 42, the second pressure reducer 342 and the condenser 33 in sequence, and since the dew removing pipe 36 is located at the upstream of the second pressure reducer 342, part of the refrigerant flowing through the dew removing pipe 36 can liquefy and release heat for heating the door frame and/or door body near the dew removing pipe 36 to avoid low-temperature condensation.

In other embodiments, if the ambient temperature is high and the ambient humidity is low, the dew removing tube 36 may be configured to cool the door frame and/or door body nearby during the defrosting operation so that the opening of the storage cavity 11 (as shown in fig. 1) has a low temperature, thereby avoiding the case 1 and the door 2 from rapidly absorbing the cold energy in the storage cavity 11 due to the high temperature. In this defrosting mode, as shown in fig. 8, the first switching valve 41 and the second switching valve 42 need to be adjusted to the first state so that the refrigerant flows through the evaporator 35, the first pressure reducer 341, the dew removing pipe 36, the second switching valve 42, the parallel circuit of the second pressure reducer 342, and the condenser 33 in order, and the ambient humidity needs to be less than the preset humidity to avoid the dew condensation phenomenon caused by the low dew point temperature.

It should be noted that the second switching valve 42 may be a two-position two-way electric control valve, in which case one end of the condenser 33 is connected to one end of the dew removing tube 36 through the second pressure reducer 342, and the second switching valve 42 is disposed in parallel with the second pressure reducer 342, and the second switching valve 42 at this time may be regarded as a parallel circuit of the second pressure reducer 342.

Alternatively, the first switching valve 41 may be a two-position three-way electrically controlled valve, and along the flow direction of the refrigerant, the end of the dew removing tube 36 away from the condenser 33 may be connected to one end of the evaporator 35 through the first end and the second end of the first switching valve 41, and the third end of the first switching valve 41 may be connected to the first end or the second end of the first switching valve 41 through the first pressure reducer 341. I.e. the first and second ends of the first switching valve 41 may now be taken as parallel circuits of the first pressure reducer 341.

It should be noted that, in the embodiment of the present application, the first switching valve 41 may be a two-position two-way electric control valve or a two-position three-way electric control valve, and the second switching valve 42 may be a two-position three-way electric control valve or a two-position two-way electric control valve. The connecting line is not limited to this, and may be adjusted according to the actual structure of the first switching valve 41.

In some embodiments, first pressure reducer 341 and second pressure reducer 342 can be any structure in a capillary tube or an electronic expansion valve. If at least one of the first pressure reducer 341 and the second pressure reducer 342 is an electronic expansion valve, if a corresponding parallel circuit needs to be conducted, the electronic expansion valve corresponding to the parallel circuit may be correspondingly closed, so as to improve the switching and adjusting effects of the parallel circuit.

In some embodiments, to facilitate control of the first and second switching valves 41 and 42, as shown in fig. 9, the refrigerator 100 includes a first relay 51 and a second relay 52, the first relay 51 being electrically connected to the four-way valve 32 for controlling the four-way valve 32 to switch between a cooling condition and a defrosting condition, the first and second switching valves 41 and 42 being electrically connected to the second relay 52, and the first relay 51 being disposed in parallel with the second relay 52.

Based on this, in connection with fig. 6, the first relay 51 and the second relay 52 may receive the first signal and be configured to: the first relay 51 controls the four-way valve 32 to be in a cooling condition, and the second relay 52 controls the first switching valve 41 and the second switching valve to be in a first state. So that the dew removing tube 36 in the cooling mode can heat the adjacent door frame and body to avoid condensation due to the temperature of the door frame and body being below the dew point temperature.

As shown in fig. 7, the first relay 51 and the second relay 52 may also receive a second signal and be configured to: the first relay 51 controls the four-way valve 32 to switch to the defrosting operation, and the second relay 52 controls the first switching valve 41 and the second switching valve 42 to switch to the second state. So that the defrost duct 36 can also heat the adjacent door frame and body to avoid condensation from the door frame and body being below the dew point temperature.

It should be noted that, since the time of keeping the refrigeration condition of the refrigerator 100 is far longer than the time of keeping the refrigerator 100 in the defrosting condition, the default state of the four-way valve 32 may be set to be the refrigeration state (i.e. the refrigeration condition), that is, the first port a is conducted with the fourth port D, and the second port B is conducted with the third port C. When the first relay 51 receives the second signal and controls the four-way valve 32 to switch on, the four-way valve 32 is switched to the defrosting state (i.e. defrosting mode), i.e. the first port a is conducted with the third port C, and the second port B is conducted with the fourth port D.

Correspondingly, the default states of the first switching valve 41 and the second switching valve 42 may be configured to be the first state, and the second relay 52 receives the second signal to control the first switching valve 41 and the second switching valve 42 to be powered on and switched to the second state.

Because the defrosting operation of the refrigerator 100 is short, the power-on time of the four-way valve 32 can be reduced by setting the four-way valve 32 to be in a cooling state when power-off and switching power-on to a defrosting state. Correspondingly, the first switching valve 41 and the second switching valve 42 are configured to be powered off in a first state and to be powered on to be switched to a second state, so that the power-on time of the first switching valve 41 and the second switching valve 42 can be reduced, energy is saved, and consumption is reduced.

In other embodiments, as shown in fig. 10, the refrigerator 100 further includes a temperature and humidity control module 61, a temperature sensor 62, a humidity sensor 63, and a third relay 53, wherein the temperature sensor 62 is used for detecting an ambient temperature and is electrically connected to the temperature and humidity control module 61, and the humidity sensor 63 is used for detecting an ambient humidity and is electrically connected to the temperature and humidity control module 61. The second relay 52 is electrically connected to the first switching valve 41 and the second switching valve 42 through the temperature and humidity control module 61 and the third relay 53 in sequence.

In the cooling condition, the second relay 52 may close the temperature and humidity control module 61 (e.g. cut off the power supply to the temperature and humidity control module 61), and the third relay 53 is in a normally closed structure, so that the first switching valve 41 and the second switching valve 42 are powered off to be in the first state.

When the first relay 51 and the second relay 52 receive the second signal, the first relay 51 controls the four-way valve 32 to switch to the defrosting operation shown in fig. 7 and 8, and the second relay 52 controls to turn on the temperature and humidity control module 61 (e.g. make the temperature and humidity control module 61 turn on), so that the temperature and humidity control module 61 is configured to:

When the ambient temperature is greater than the preset temperature and the ambient humidity is less than the preset humidity, the temperature and humidity control module 61 controls the first switching valve 41 and the second switching valve 42 to be in the first state shown in fig. 8 through the third relay 53, so that the dew removing pipe 36 in the defrosting condition is cooled. The lower ambient humidity can avoid condensation phenomena near the door frame and the door body while avoiding the higher temperature near the door frame and the door body to quickly absorb the cold energy of the storage cavity 11 (shown in figure 1).

Otherwise, the temperature and humidity control module 61 may control the first switching valve 41 and the second switching valve 42 to be in the second state shown in fig. 7 through the third relay 53, so that the dew removing pipe 36 under the frame for defrosting heats, so as to avoid the condensation phenomenon near the door body and the door frame. If the ambient temperature is less than or equal to the preset temperature and the ambient humidity is greater than the preset humidity, the ambient temperature is less than or equal to the preset temperature and the ambient humidity is less than or equal to the preset humidity, and the ambient humidity is greater than or equal to the preset humidity and the ambient temperature is greater than the preset temperature, the temperature and humidity control module 61 may control the first switching valve 41 and the second switching valve 42 to be in the second state shown in fig. 7 through the third relay 53.

The preset temperature may be, for example, 36-38 ℃ or 38-40 ℃, i.e. the preset temperature satisfies: t is more than or equal to 36 ℃ and less than or equal to 38 ℃ or more than or equal to 38 ℃ and less than or equal to 40 ℃, and the preset temperature can be 36 ℃, 37 ℃, 38 ℃, 39 ℃ or 40 ℃. It is advantageous to improve the cooling efficiency and the power consumption ratio of the refrigerator 100.

If the preset temperature is greater than 40 ℃, the higher ambient temperature will cause the door frame and the door body of the refrigerator 100 to have higher temperature, thereby increasing the release speed of the cooling capacity in the storage cavity 11. If the preset temperature is less than 36 ℃, the dew point temperature is relatively high at the moment, so that condensation phenomenon is easy to occur near the door frame and the door body. The preset temperature may be 10 deg.c, for example.

Correspondingly, the preset humidity can be 70% -75% or 75% -80%, namely, the preset humidity is 70% -75% or 75% -80%, for example, the preset humidity can be 70%, 73%, 75%, 77% or 80%. It is advantageous to improve the cooling efficiency and the power consumption ratio of the refrigerator 100.

If the preset humidity is greater than 80%, the higher ambient humidity may cause condensation phenomenon to occur easily in the vicinity of the door frame and the door body of the refrigerator 100. If the preset humidity is less than 70%, the lower preset humidity will reduce the cooling time of the dew removing tube 36, so that the storage cavity 11 exchanges heat with the high-temperature door frame and door body for a long time, i.e. dissipates cold. For example, the preset temperature may be 75%.

As shown in fig. 9 and 10, the refrigerator 100 may further include a controller 7, the controller 7 being electrically connected to both the first relay 51 and the second relay 52, the controller 7 being configured to output a first signal and a second signal for adjusting a cooling condition and a defrosting condition of the refrigerator 100.

When the controller 7 outputs the first signal, the four-way valve 32 receives the first signal to maintain the refrigerating state (i.e., refrigerating condition), and when the controller 7 outputs the second signal, the four-way valve 32 receives the second signal to adjust to the defrosting state (i.e., defrosting condition). The first relay 51, the second relay 52, and the third relay 53 are one type of electronically controlled switch that controls a larger current by a smaller current (e.g., a signal current).

The temperature and humidity control module 61 and the third relay 53 may be corresponding relay structures (such as temperature control-humidity control relay), for example, relay structures that can control on or off of the switch by the combination of a lower temperature limit and an upper humidity limit. The trigger temperature (i.e., preset temperature) and trigger humidity (i.e., preset humidity) of the temperature control-humidity control relay can be flexibly adjusted according to the needs, and the trigger temperature and the trigger humidity are not limited.

In the above-described scheme, the temperature and humidity control module 61 and the third relay 53 may be normally closed-structured relays. In addition, the temperature and humidity control module 61 and the third relay 53 may be provided as relays having an open structure, and in this case, the arrangement state or the installation state of the first switching valve 41 and the second switching valve 42 may be adjusted accordingly.

The controller 7 may be an integrated circuit control structure, or the controller 7 may be a control device such as a remote controller, which is not limited thereto.

When the controller 7 is in an integrated circuit structure, the temperature and humidity control module 61 may also be configured as a part of functional modules of the controller 7, temperature control and humidity control of the above modules may be implemented through a preset functional program, and corresponding elements may be controlled through a relay structure using a smaller current signal or voltage signal. When the control module is a part of the controller 7, only one relay structure may be disposed between the controller 7 and the corresponding element (such as a switching valve), so that the controller 7 uses a smaller signal current or signal voltage to control the first state and the second state of the first switching valve and the second switching valve through the relay structure.

In the above-described embodiment, the second pressure reducer 342 is installed between the condenser 33 and the dew-removing tube 36 along the flow direction of the refrigerant.

In addition, taking the second switching valve 42 as an example, the two-position two-way electric control valve shown in fig. 11: along the flow direction of the refrigerant, one end of the condenser 33 is connected to one end of the dew removing tube 36 through the second switching valve 42 (i.e., the second switching valve 42 is located between the condenser 33 and the dew removing tube 36), and one end of the condenser 33 close to the dew removing tube 36 is also connected to one end of the dew removing tube 36 away from the condenser 33 through the second pressure reducer 342. That is, the second switching valve 42 is disposed in series with the dew-removing tube 36, and both in series are disposed in parallel with the second pressure reducer 342.

Thus, in the defrosting mode, the first switching valve 41 may be opened and the second switching valve 42 may be closed, so that the refrigerant flows from the evaporator 35 through the first switching valve 41, the dew removing pipe 36 and the condenser 33 in this order, and a part of the refrigerant may be liquefied at the dew removing pipe 36 and release heat.

Alternatively, the second switching valve 42 may be a two-position three-way valve, and the second switching valve 42 is located between the condenser 33 and the dew removing tube 36 along the flow direction of the refrigerant, for example, one end of the condenser 33 is connected to one end of the dew removing tube 36 through a first end and a second end of the second switching valve 42. And the third end of the second switching valve 42 may be connected to an end of the dew removing tube 36 remote from the condenser 33 through the second pressure reducer 342, which may achieve the above-mentioned effects.

In other embodiments, as shown in fig. 12 and 13, the refrigerator 100 may also include a condenser 33, a first pressure reducer 341, a second pressure reducer 342, an evaporator 35, a dew removing pipe 36, and a first switching valve 41, and the first switching valve 41 may be a two-position three-way valve. Along the flow direction of the refrigerant, one end of the condenser 33 is connected to one end of the evaporator 35 sequentially through the dew removing pipe 36, the first pressure reducer 341, the first end of the first switching valve 41 and the second end of the first switching valve 41, and the third end of the first switching valve 41 is connected to one end of the condenser 33 adjacent to the dew removing pipe 36 through the second pressure reducer 342.

Based on this, when the refrigerator 100 is in the cooling condition shown in fig. 12, the first and second ends of the first switching valve 41 are adjusted to be turned on so that the refrigerant sequentially flows through the condenser 33, the dew removing pipe 36, the first pressure reducer 341, the first switching valve 41 and the evaporator, and the dew removing pipe 36 heats. When the refrigerator 100 is in the defrosting mode shown in fig. 13, the second and third ends of the first switching valve 41 are adjusted to be turned on so that the refrigerant sequentially flows through the evaporator 35, the first switching valve 41, the second pressure reducer 342 and the condenser 33 to prevent the refrigerant from flowing through the dew removing pipe in the defrosting mode.

In the description of the present specification, a particular feature, structure, material, or characteristic may be combined in any suitable manner in one or more embodiments or examples.

The foregoing is merely illustrative embodiments of the present utility model, but the scope of the present utility model is not limited thereto, and any person skilled in the art can easily think about variations or substitutions within the technical scope of the present utility model, and the utility model should be covered. Therefore, the protection scope of the utility model is subject to the protection scope of the claims.

Claims (10)

1. A reverse flow defrost refrigerator, comprising:

a condenser configured to release heat during a cooling operation and absorb heat during a defrosting operation;

A dew removing pipe;

one end of the condenser is connected with one end of the first pressure reducer through the dew removing pipe;

A first switching valve at least partially disposed in parallel with the first pressure reducer;

A second pressure reducer;

And the second switching valve is arranged in series between the condenser and the dew removing pipe along the flowing direction of the refrigerant, and the second pressure reducer is positioned between the condenser and the dew removing pipe and is arranged in parallel with at least part of the second switching valve.

2. The reverse flow defrost refrigerator of claim 1, wherein the second switching valve is a two-position two-way electrically controlled valve, and the second pressure reducer is provided in parallel with the second switching valve; or alternatively

The second switching valve is a two-position three-way electric control valve, and is arranged in series with the dew removing pipe along the flowing direction of the refrigerant, the condenser is arranged in series with the dew removing pipe through the first end and the second end of the second switching valve, and the third end of the second switching valve is connected with the first end or the second end of the second switching valve through the second pressure reducer.

3. The reverse flow defrost refrigerator of claim 1, wherein the first switching valve is a two-position two-way electrically controlled valve, and the first switching valve is provided in parallel with the first pressure reducer; or alternatively

The first switching valve is a two-position three-way electric control valve and is positioned at one end of the dew removing pipe far away from the condenser along the flowing direction of the refrigerant; the first end of the first switching valve is connected with the dew removing pipe, the second end of the first switching valve is used for being connected with the evaporator, and the third end of the first switching valve is connected with the dew removing pipe or the evaporator through the first pressure reducer.

4. The reverse flow defrost refrigerator according to any one of claims 1 to 3, wherein the reverse flow defrost refrigerator comprises:

a four-way valve;

The first relay is electrically connected with the four-way valve and is used for controlling the four-way valve to switch and adjust the refrigerating working condition and the defrosting working condition;

The second relay is electrically connected with the first switching valve and the second switching valve, and the second relay is arranged in parallel with the first relay;

the first relay and the second relay are configured to:

The first relay controls the four-way valve to be in the refrigerating working condition, the second relay controls the first switching valve and the second switching valve to be in a first state, so that the first switching valve closes a loop connected with the first pressure reducers in parallel, and the second switching valve opens a loop connected with the second pressure reducers in parallel.

5. The reverse flow defrost refrigerator of claim 4, wherein the first relay and the second relay are further configured to:

The first relay controls the four-way valve to switch to the defrosting working condition, the second relay controls the first switching valve and the second switching valve to switch to a second state, so that the first switching valve opens a loop connected with the first pressure reducer in parallel, and the second switching valve closes the loop connected with the second pressure reducer in parallel.

6. The reverse flow defrost refrigerator of claim 4, further comprising:

a temperature and humidity control module;

The temperature sensor is used for detecting the ambient temperature and is electrically connected with the temperature and humidity control module;

the humidity sensor is used for detecting the ambient humidity and is electrically connected with the temperature and humidity control module;

The second relay is electrically connected with the first switching valve and the second switching valve sequentially through the temperature and humidity control module and the third relay;

In the refrigeration working condition, the first switching valve and the second switching valve are in a first state;

The four-way valve is controlled by the first relay to be switched to the defrosting working condition, the temperature and humidity control module is started by the second relay, and the temperature and humidity control module is configured to:

When the ambient temperature is higher than the preset temperature and the ambient humidity is lower than the preset humidity, the temperature and humidity control module controls the first switching valve and the second switching valve to be in the first state through the third relay;

Otherwise, the temperature and humidity control module controls the first switching valve and the second switching valve to be in a second state through the third relay.

7. The reverse flow defrost refrigerator according to any one of claims 1 to 3, wherein the first pressure reducer is a capillary tube or an electronic expansion valve; and/or the number of the groups of groups,

The second pressure reducer is a capillary tube or an electronic expansion valve.

8. The reverse flow defrost refrigerator according to any one of claims 1 to 3, further comprising:

a compressor having a return air end and an exhaust air end;

The four-way valve is provided with a first port, a second port, a third port and a fourth port, the first port is connected with the air return end, the second port is connected with the exhaust end, and the third port is connected with one end, far away from the dew removing pipe, of the condenser along the flowing direction of the refrigerant;

The evaporator is connected with the fourth port along the flowing direction of the refrigerant, and the first switching valve and the first pressure reducer are arranged between the other end of the evaporator and the dew removing pipe;

The first port is communicated with the fourth port, and the second port is communicated with the third port, so that the countercurrent defrosting refrigerator enters the refrigeration working condition;

The first port is communicated with the third port, and the second port is communicated with the fourth port, so that the countercurrent defrosting refrigerator enters the defrosting working condition.

9. A reverse flow defrost refrigerator, comprising:

A condenser configured to release heat during a cooling condition and absorb heat during a defrost condition;

A dew removing pipe;

one end of the condenser is connected with one end of the first pressure reducer through the dew removing pipe;

a first switching valve disposed at least partially in parallel with the first pressure reducer;

The second pressure reducer is arranged in parallel between the condenser and the first pressure reducer along the flowing direction of the refrigerant;

The reverse flow defrost refrigerator is configured to:

Under the refrigeration working condition, the refrigerant sequentially flows through the condenser, the dew removing pipe and the first pressure reducer;

And under the defrosting working condition, the refrigerant flows to the condenser from the first switching valve at least through the second pressure reducer.

10. The reverse flow defrost refrigerator of claim 9, further comprising a second switching valve, the second switching valve being located between the condenser and the dew-removing pipe in a flow direction of a refrigerant;

The second switching valve is connected with the dew removing pipe in series, and the second switching valve and the second pressure reducer are connected in parallel.